Tire inflation system

TECHNICAL FIELD [0001] The present invention relates generally to the field of pumping, and more particularly to a new and useful passive pumping system used in the pumping field. BACKGROUND OF THE INVENTION [0002] Tires that are not properly inflated increase fuel consumption. The effects are particularly felt in the field of lorry transport, where long distances and large loads result in increased effects of insufficient tire inflation. However, continuous stopping, checking and pumping the vehicle's tires to the optimal pressure is often uncomfortable and inefficient for truck drivers, which leads to longer periods of fuel consumption than optimal. This problem has led to the development of several automatic tire inflation systems. Conventional automatic tire inflation systems are either centralized or decentralized, but in each case there is a certain set of defects. Central pumping systems are complicated and expensive and require considerable work if they are installed after the vehicle has been manufactured (drilling via axles, connecting to existing air ducts and the like). Decentralized systems are mounted on each wheel and can be cheaper, but the possibility of reducing costs is usually associated with the constant replacement of the device (which crashes due to an unfavorable environment in the wheels). Central pumping systems are complicated and expensive and require considerable work if they are installed after the vehicle has been manufactured (drilling via axles, connecting to existing air ducts and the like). Decentralized systems are mounted on each wheel and can be cheaper, but the possibility of reducing costs is usually associated with the constant replacement of the device (which crashes due to an unfavorable environment in the wheels). Central pumping systems are complicated and expensive and require considerable work if they are installed after the vehicle has been manufactured (drilling via axles, connecting to existing air ducts and the like). Decentralized systems are mounted on each wheel and can be cheaper, but the possibility of reducing costs is usually associated with the constant replacement of the device (which crashes due to an unfavorable environment in the wheels).

Pumping systems for tires are known from GB350005, JP2005 / 231573, GB2089297 and DE4042446.

[0003] In addition, passive pumping systems may be desirable in tire pumping applications because it is then possible to eliminate electrical and software storage mechanisms from the system. In conventional passive pumping systems, however, there are several problems. First, conventional passive pump systems using piston pumps are often subject to wear due to high pressure and a large number of required pumping cycles. Secondly, in passive pumping systems there may be too high pressure in the tank if the pumping system continues to pump the fluid into the tank even after reaching the desired pressure in the tank. In conventional systems this problem is usually solved using a relief valve, wherein the relief valve discharges the contents of the tank into the external environment if the pressure in the tank exceeds the desired pressure. This results in losses of the fluid whose pressure has already been increased and additional pumping cycles to increase the fluid pressure, which is equal to the ambient pressure, to the desired pressure, which leads to a reduction in the life of the pump. Third, in conventional pumping systems driven by eccentric mass, such as pendulum systems, instabilities occur when the rotating surface with which the eccentric mass is connected rotates at a speed approaching that of the given eccentric mass. In particular, the eccentric mass rotates with the system at said excitation frequency, resulting in radial vibrations,

[0004] In the field of pumping there is therefore a need to develop a new and useful pump.

BRIEF DESCRIPTION OF THE FIGURES [0005]

Figure 1 shows a schematic representation of a pumping system connected to a rotating surface.

Figures 2A and 2B show schematic representations of a variation of the pumping system, respectively in the position of expansion and compression.

Figures 3A and 3B show partial sections of a variant of the main pump, respectively in the position of compression and expansion.

Figures 4A and 4B show a cross-section of a variation of the pumping system, respectively with the mass connection and with the mass connection removed.

Figures 5A, 5B and 5C show partial perspective sections of a variation of the pumping system, respectively in the expansion stroke, at the beginning of the compression stroke and at the end of the compression stroke.

Figure 6 is a perspective view of a variation of the pumping system.

Figures 7A and 7B show a schematic representation of a variation of the pumping system, wherein the pressure in the first tank is equal or below the pressure and the pressure in the first tank is higher than the ambient pressure.

Figures 8A and 8B show schematic representations of a variation of the torque stabilizing mechanism in the pumping and non-pumping modes, respectively.

Figures 9A and 9B show schematic representations of a second variation of the torque stabilizing mechanism in the pumping and non-pumping modes, respectively.

Figures 10A and 10B show schematic representations of a variation of the stabilizing mechanism in the pumping and non-pumping modes, respectively.

Figures 11A and 11B show schematic representations of a second variation of the stabilizing mechanism in the pumping and non-pumping modes, respectively. Figures 12A and 12B show sectional views of a variation of the pressure control mechanism in the pumping and non-pumping modes, respectively.

Figures 13A and 13B show cross-sectional views of the second variant of the pressure control mechanism in the pumping and non-pumping modes, respectively. Figures 14A and 14B show cross-sectional views of a third variation of the pressure control mechanism in the pumping and non-pumping modes, respectively. Figures 15A and 15B are schematic flow diagrams of a variation of the pressure control mechanism in the pumping and non-pumping modes, respectively. Figure 16 shows a partial section of a valve in a pressure control mechanism.

DESCRIPTION OF THE PREFERRED EMBODIMENTS [0006] The following description of preferred embodiments of the invention is not intended to limit the invention to these preferred embodiments, but to allow the person skilled in the art to make and use the invention.

1. The pumping system [0007] As shown in figure 1, the pumping system 10 comprises a drive mechanism 100 comprising a cam 120 connected to an eccentric mass 140, a main pump 200 comprising a piston element 220 and a pump body 240 and a force transfer element 300 cam 120 with a piston element 220. The pumping system 10 is used to convert the rotary motion into rectilinear motion. More preferably, the pumping system 10 provides for the movement of the main pump 200 and the cam 120 relative to each other in pumping force, wherein the eccentric mass 140 holds the cam position relative to the gravity vector when the main pump 200 rotates relative to the cam 120 (e.g. using a rotating surface 20). ). The pumping system 10 advantageously provides an additional increase in the pressure of the fluid being pumped.

Even more preferably, the force transfer element 300 moves the piston element 220 during the compression stroke. The force transfer element 300 can further facilitate the expansion stroke (return stroke). However, the pumping system 10 can alternatively convert relative rectilinear motion into rectilinear force, electric energy (e.g. using piezoelectric elements, motion in an induced electric field and the like) or any other suitable form of energy or motion. The pumping system 10 is preferably passively controlled, but can alternatively be actively controlled, whereby the system then comprises an energy source, a plurality of sensors and a controller controlling the operation of the valve based on measurements carried out by the sensors.

[0008] The pumping system 10 can advantageously be connected to a surface rotating with respect to the gravitational force vector (pivot surface 20). The pivot surface 20 is preferably in the form of a vehicle wheel, more preferably a truck, but may alternatively be any suitable pivoting system such as a fan, water wheel or any other suitable pivot surface 20.

[0009] Fluid originating from the first reservoir 400 is preferably introduced into the pumping system 10 and pumps fluid into the second reservoir 500. The fluid from the first reservoir 400 preferably has a first pressure and the fluid pumped into the second reservoir 500 preferably has a second pressure which is higher than the first pressure, but may alternatively have a pressure substantially similar to the first pressure. The fluid is preferably a gas, more preferably ambient air, but may alternatively be any other suitable gas, liquid or any other suitable fluid. The first reservoir 400 is preferably a surrounding environment, but may alternatively be a source of fluid (e.g. a fluid reservoir), an intermediate reservoir or any other suitable reservoir. If the first reservoir 400 is an intermediate reservoir, liquid from the fluid source such as the surrounding environment or the reservoir of liquid is preferably introduced into the first reservoir 400. The second reservoir 500 is preferably the interior of the tire, but may alternatively be any other suitable reservoir. The pumping system 10 can additionally process the pumped liquid, preferably before it is introduced into the main pump, but alternatively after it leaves the main pump. The fluid is preferably treated (e.g., filtered) to remove impurities, water or any other suitable undesirable component of the fluid. The fluid is preferably treated in an intermediate tank, if it is used. Alternatively, the fluid may be treated during insertion into the main pump (e.g.

[0010] The driving mechanism 100 of the pumping system 10 serves to generate a pumping force and control the size of the pumping force. The pumping force (occlusive force) is preferably a variable force exerted in the radial direction from the axis of rotation of the driving mechanism 100, but alternatively it can be a solid force, a force exerted at any suitable angle relative to the axis of rotation or any other suitable force. The driving mechanism 100 preferably comprises a cam 120 and an eccentric mass 140. The driving mechanism 100 comprises a pivot axis around which the driving mechanism 100 relative to the main pump 200 (and opposite about which the main pump 200 rotates relative to the driving mechanism 100) rotates. The axis of rotation of the driving mechanism 100 is preferably the axis of rotation of the cam 120, but may alternatively be the axis of rotation of the eccentric mass 140, around which the main pump 200 rotates, or any other suitable axis of rotation. The pumping system 10 is preferably configured such that the axis of rotation of the driving mechanism 100 substantially extends in tandem with the pivot axis of the pivot surface 20 when the pumping system 10 is connected to the pivot surface 20, but alternatively the pumping system 10 can be configured such that the axis The drive mechanism 100 is offset from the rotational axis of the rotary surface 20. The drive mechanism 100 further comprises a center of mass depending on the mass and positions of the cam 120 and the eccentric mass 140. The eccentric mass 140 is preferably connected to the cam 120 so that the center of mass of the driving mechanism 100 is displaced from the axis of rotation of the driving mechanism 100. or any other suitable axis of rotation. The pumping system 10 is preferably configured such that the axis of rotation of the driving mechanism 100 substantially extends in tandem with the pivot axis of the pivot surface 20 when the pumping system 10 is connected to the pivot surface 20, but alternatively the pumping system 10 can be configured such that the axis The drive mechanism 100 is offset from the rotational axis of the rotary surface 20. The drive mechanism 100 further comprises a center of mass depending on the mass and positions of the cam 120 and the eccentric mass 140. The eccentric mass 140 is preferably connected to the cam 120 so that the center of mass of the driving mechanism 100 is displaced from the axis of rotation of the driving mechanism 100. or any other suitable axis of rotation. The pumping system 10 is preferably configured such that the axis of rotation of the driving mechanism 100 substantially extends in tandem with the pivot axis of the pivot surface 20 when the pumping system 10 is connected to the pivot surface 20, but alternatively the pumping system 10 can be configured such that the axis The drive mechanism 100 is offset from the rotational axis of the rotary surface 20. The drive mechanism 100 further comprises a center of mass depending on the mass and positions of the cam 120 and the eccentric mass 140. The eccentric mass 140 is preferably connected to the cam 120 so that the center of mass of the driving mechanism 100 is displaced from the axis of rotation of the driving mechanism 100.

[0011] The cam 120 of the driving mechanism 100 serves to control the size of the pumping force. The cam 120 preferably acts to provide a substantially constant torque acting on the piston element 220 during the compression stroke, but alternatively it can provide variable torque acting on the piston element 220 during the compression or expansion stroke. The cam 120 preferably comprises a bearing surface 122, wherein the profile of the bearing surface 122 preferably provides control of the pumping force during the compression stroke. The support surface 122 is preferably continuous, but may alternatively be discontinuous. The support surface 122 is preferably formed on the outside of the cam 120 (outside of the bearing surface or outer supporting surface), but alternatively, it may be formed in the interior of the cam 120 (the interior of the bearing surface or the inner supporting surface) as illustrated in FIG. 6, where the bearing surface 122 forms a clearance in the cam 120. The bearing surface 122 is preferably arcuate, and its curvature is preferably not constant (e.g. has an oblong profile or a kidney profile, as shown in figures 2 and 5, respectively). Alternatively, the bearing surface 122 may have a constant curvature (e.g. a circular profile), a bent profile, or any other suitable profile. The bearing surface 122 preferably comprises a compression part and an expansion part which correspond respectively to the compression stroke and the expansion stroke of the main pump 200. The compression part preferably is continuous with the expansion part, but alternatively they may be discontinuous. The bearing surface 122 preferably comprises a first section 124 having a high curvature (preferably has a positive or negative curvature but alternatively has a negative or concave curvature) that is adjacent to the second section 126 having a small curvature (e.g., substantially flat or negative curvature) compared to the first section 124). The bearing surface 122 preferably further comprises a third section 128 joining together the first and second sections, wherein the third section 128 preferably provides a substantially smooth transition between the first and second section because it has a small curve adjacent the first section 124 and a high curvature adjacent to the second section 126 The compression part preferably starts at the end of the second section 126 remote from the first section 124, it extends along the third section 128 and terminates at the top of the first section 124, as shown in FIG. 5B. The prestressing portion is preferably convex (e.g. if the support surface 122 is an outer support surface), but alternatively it may be concave. The top of the first section 124 preferably corresponds to the upper point of the compression stroke (compression position 222), as illustrated in FIG. 5C. The expansion part preferably starts at the top of the first section 124, extends along the second section 126 and terminates at the end of the second section 126 remote from the first section 124, as shown in Figure 5A. The expansion portion is preferably substantially flat or concave (e.g., if the bearing surface 122 is the outer support surface 122), but alternatively it can be convex. The end of the second section 126 preferably corresponds to the lower point of the expansion stroke (releasing position 224). The inclination of the prestressing portion is preferably less than 30 degrees, but may alternatively be any suitable angle. If a roll is used as the force transfer element 300, the curvature of the support surface 122 is preferably at least three times greater than the curvature of the roll or the diameter of the roll, but may alternatively be larger or smaller. The bearing surface 122 may, however, have any suitable shape. The cam 120 is preferably substantially planar and comprises a bearing surface 122 formed along the side of the cam 120 in a plane normal to the axis of rotation of the cam. The inclination of the prestressing portion is preferably less than 30 degrees, but may alternatively be any suitable angle. If a roll is used as the force transfer element 300, the curvature of the support surface 122 is preferably at least three times greater than the curvature of the roll or the diameter of the roll, but may alternatively be larger or smaller. The bearing surface 122 may, however, have any suitable shape. The cam 120 is preferably substantially planar and comprises a bearing surface 122 formed along the side of the cam 120 in a plane normal to the axis of rotation of the cam. The inclination of the prestressing portion is preferably less than 30 degrees, but may alternatively be any suitable angle. If a roll is used as the force transfer element 300, the curvature of the support surface 122 is preferably at least three times greater than the curvature of the roll or the diameter of the roll, but may alternatively be larger or smaller. The bearing surface 122 may, however, have any suitable shape. The cam 120 is preferably substantially planar and comprises a bearing surface 122 formed along the side of the cam 120 in a plane normal to the axis of rotation of the cam. the curvature of the bearing surface 122 is preferably at least three times greater than the curvature of the roll or the diameter of the roll, but alternatively may be larger or smaller. The bearing surface 122 may, however, have any suitable shape. The cam 120 is preferably substantially planar and comprises a bearing surface 122 formed along the side of the cam 120 in a plane normal to the axis of rotation of the cam. the curvature of the bearing surface 122 is preferably at least three times greater than the curvature of the roll or the diameter of the roll, but alternatively may be larger or smaller. The bearing surface 122 may, however, have any suitable shape. The cam 120 is preferably substantially planar and comprises a bearing surface 122 formed along the side of the cam 120 in a plane normal to the axis of rotation of the cam.

120 (e.g. normal to the wide surface of the cam 120). The bearing surface 122 is preferably formed along the entire side of the cam, but can alternatively be formed along the side portion of the cam. The produced pumping force is preferably directed radially outward from the axis of rotation, and even more preferably along a plane normal to the axis of rotation. Alternatively, the cam 120 may comprise a rounded or otherwise shaped edge segment (transition between the wide cam surface and the side of the cam), and the support surface 122 may include a profiled edge. Alternatively, the arcuate surface is formed by a cam surface parallel to the axis of rotation of the cam 120, and the produced pumping force can be directed at any suitable angle relative to the axis of rotation, varying from parallel to the axis of rotation to normal to the axis of rotation. The prestressing portion preferably comprises a majority of the cam profile, but may alternatively comprise half of the cam profile or a small portion of the cam profile. In one variant, the compression part comprises 315 degrees of the cam profile, while the relieving portion comprises 45 degrees of the cam profile. The compression and expansion part may, however, comprise any other suitable proportions of the cam profile.

[0012] Eccentric mass 140 (mass-transmitting) of the driving mechanism 100 serves to move the center of mass of the driving mechanism 100 from the axis of rotation of the driving mechanism 100. This offset can serve to substantially maintain the angular position of the driving mechanism 100 relative to the gravitational force vector, which provides the motion of the propulsion mechanism. 100 relative to the components of the pumping system connected statically to the pivot surface 20 (which rotates relative to the gravity force vector). The eccentric mass 140 is preferably a substantially homogeneous element, but may alternatively be non-uniform. The eccentric mass 140 is preferably a substantially single element, but alternatively it may be made of a plurality of elements or segments. In the latter variant, many elements preferably have substantially similar shapes, angular and radial positions and mass, but alternatively may have substantially different shapes, masses, angular positions or radial positions. The eccentric mass 140 is preferably a substantially dispersed mass (e.g. extends along a substantial portion of the arc with a center located on the axis of rotation, as shown in Figure 4B), but may alternatively be a point mass. In some applications, especially in high speed applications, the scattered mass may be advantageous because the use of scattering mass results in low vibration frequencies, which ensures a reduction in the likelihood that the eccentric mass is excited in the system due to the presence of linear vibrations in the system (e.g. caused by impacts, system pulsations and the like). The eccentric mass 140 is preferably curved, but alternatively it may be substantially flat, oblique or of other suitable shape. The eccentric mass curvature radius is preferably maximized so that the eccentric mass follows along the arcuate periphery of the pumping system. The eccentric mass 140 may, however, have any other suitable curvature. The eccentric mass 140 preferably extends at least at an angle of 90 degrees about the axis of rotation of the driving mechanism 100, and more preferably at an angle of 180 degrees about the axis of rotation, but may extend over an angle of less than or greater than 180 degrees around the axis of rotation. The eccentric mass 140 preferably has a much larger mass than the cam 120, but may alternatively have a substantially similar mass or lower mass. The eccentric mass 140 preferably exerts a torque of 2 pounds per inch (0.225 Nm) on the cam 120, but may alternatively have greater or lesser torque.

[0013] The eccentric mass 140 preferably is a separate element from the cam 120 and is preferably connected to the cam 120 using a mass connection 142. Alternatively, the eccentric mass 140 may be incorporated into the cam 120, wherein the eccentric mass 140 is then built-in along the perimeter of the cam 120 inserted into the half of the cam 120 or built-in along any other relevant portion of the cam 120. The eccentric mass 140 may be statically connected to the cam 120 or rotatably connected to a cam 120. In a variation in which the eccentric mass 140 is statically connected to the cam 120, the eccentric mass 140 may be coupled to the cam 120 at the axis of rotation of the cam 120 at the axis of rotation of the driving mechanism 100 offset from the axis of rotation of the cam 120 or in any other suitable portion of the cam 120. The eccentric mass 140 may be permanently connected to the cam 120. Alternatively, the eccentric mass 140 may be transiently (detachably) connected to the cam 120, wherein the eccentric mass 140 may then be in the pumping mode, in which the eccentric mass 140 is connected. with the cam 120, and in non-pumping mode, in which the eccentric mass 140 is disconnected from the cam 120. The mass connection 142 preferably has a large moment of inertia, but alternatively may have a small moment of inertia. The mass connection 142 is preferably in the form of a disc (as shown in figure 4A), but alternatively it may be a lever arm, a plate or any other suitable connection. The mass connection 142 is preferably connected to the wide surface of the cam 120, but can alternatively be connected to the edge of the cam 120, along the outer bearing surface of the cam 120, with the inner bearing surface of the cam 120, with a semi-axle extending from the cam 120 (wherein the cam 120 can then be fixed permanently to the axle or mounted to it rotatably) or with any other suitable portion of the cam 120. 142 may be connected to the cam 120 by means of an intermediate connection mechanism (e.g. corresponding electrical or permanent magnets placed on the cam 120 and mass connection 142, piston, pin and groove mechanism and the like), using bearings or using any other suitable connection means. If the mass connection 142 is connected to the cam 120 using an intermediate connection mechanism, the mass connection 142 may advantageously operate in a combined mode, in which the mass connection 142 connects the eccentric mass 140 to the cam 120, and in the disconnected mode, where the mass connection 142 provides the disengagement of the eccentric mass 140 from the cam 120. The mass connection 142 may additionally serve as a tripping mechanism in this case, the mass connection 142 is switched from connected to disconnected mode in response to the detection of a shutdown event (e.g., a reservoir pressure of the pressure). In one variant, the mass connection 142 is in the form of a disc arranged in a lumen formed by the inner bearing surface of the cam 120, wherein in the disconnected mode the pulley can rotate relative to the inner supporting surface, and in the combined mode, the disc is connected to the inner bearing surface using a friction element. In another variation, the mass connection 142 is mounted by means of bearings rotatably on the axle extending from the cam 120, the mass connection 142 being then connected statically to the cam 120 using one or more sets of magnets or pistons extending from adjacent surfaces cams 120 and ground connections 142.

The main pump 200 of the pumping system 10 serves to increase the pressure of the fluid using a pumping force generated between the cam 120 and the piston element 220. The main pump 200 is preferably a positive displacement pump comprising a working element and a pump chamber, and more preferably a piston pump, wherein the main pump 200 then comprises a piston element 220 and a pump body 240. The main pump 200 preferably comprises a clearance formed between the piston element 220 and the pump body 240, this clearance essentially not permeating the fluid. The main pump 200 is preferably rotatably connected to the axis of rotation of the driving mechanism 100. The main pump 200 is preferably located at a certain radial distance from the axis of rotation of the driving mechanism 100, wherein the radial position of the main pump 200 is preferably constant, but it can alternatively be regulated. Even more preferably, the main pump 200 is preferably statically mounted to the housing (wherein the housing is then statically connected to the rotatable surface 20), but can alternatively be mounted to the housing temporarily (in a regulating manner). During operation, the main pump 200 preferably rotates around the axis of rotation. During rotation, the variable profile of the bearing surface preferably exerts a variable force on the piston element 220 as a result of varying the distance between the support surface 122 and the bottom of the pump body. The main pump 200 preferably comprises a working axis, and the piston element 220 preferably moves during the compression stroke along the working axis. The piston element 220 can also move along the working axis during the return stroke. The main pump 200 is preferably oriented so that the working axis is substantially normal to the axis of rotation, but alternatively it can be arranged such that the working axis extends at any suitable angle relative to the axis of rotation. The main pump 200 and the cam 120 preferably share a common plane, and the pumping force is preferably transmitted along a common plane, but alternatively can be substantially offset. The system preferably comprises one main pump 200, and even more preferably comprises two pump chambers. However, the pumping system 10 may comprise any suitable number of pump chambers. If the pumping system 10 comprises a plurality of pumping chambers, the pumping chambers are preferably substantially evenly distributed around the axis of rotation (e.g., between similar angular positions, substantially similar distances occur), but alternatively they may be unevenly distributed. The pump chambers preferably occupy substantially similar radial positions with respect to the axis of rotation, but alternatively may occupy different radial positions. The pump chambers may be substantially different (e.g. may have different headroom volumes, different work areas, etc.) or may be substantially similar.

[0015] The piston element 220 of the main pump 200 serves to receive the pumping force from the cam 120 and translate in a lumen, moving relative to the pump body 240. This movement preferably results in the production of variable pressure in the lumen. The piston element 220 can preferably be moved between the compression position 222 and the deployment position 224, as shown in figures 3A and 3B, respectively. In the compression position 222, a portion of the piston element 220 (e.g., center) is preferably located near the bottom of the pump body. In the expansion position 224, a portion of the piston element 220 is preferably spaced from the bottom of the pump body and is preferably located near the opening of the pump body.

[0016] The piston element 220 preferably travels during the compression stroke in the main pump 200 along the working axis and can also move along the working axis during the expansion stroke. The piston element 220 preferably includes a working area for providing a pressure-boosting force. The working area is preferably in the form of a wide area of ​​the piston element 220, more preferably a wide area near the lumen, but can alternatively be any other wide surface. Alternatively, the working area may be a surface area of ​​a portion of the piston element 220 traveling between the position of the compression 222 and the release position 224 (e.g. central part).

[0017] The piston element 220 preferably forms a fluid-tight seal with the pump body 240, and even more preferably with walls forming the pump body aperture, whereby the piston element 220 substantially seals the pump body aperture. The piston element 220 can be sealed to the pump housing 240 by means of a holding mechanism. The retaining mechanism is preferably in the form of a detent that exerts a compressive force on the edge of the piston element and the wall of the pump body, but may alternatively be screws or bolts extending through the edge of the piston element, the glue between the piston element 220 and the wall of the pump body or on the piston element 220 and the wall of the pump body or any other suitable retaining mechanism.

[0018] The piston element 220 preferably has the form of a flexible membrane, but can alternatively be a substantially stiff piston, a piston connected to a diaphragm or any other suitable element that is actuated by a pumping force. The diaphragm is preferably a disc diaphragm (e.g. having a rolled rim, the membrane preferably connected to the pump body 240 using additional material away from the lumen), but it can also be a flat membrane, a dome membrane (preferably connected to the pump body 240 using a tip away from the lumen, but alternatively connected to the pump body 240 using a tip closer to the lumen) or any other suitable membrane.

The body 240 of the main pump 200 serves to compress the fluid by interacting with the piston element 220. The pump body 240 is preferably substantially rigid, but can alternatively be flexible. The pump body 240 is preferably in the form of an open pump body with a closed end, wherein the pump body 240 preferably comprises a closed end (bottom), walls extending from the closed end and an opening opposite the closed end. Alternatively, the pump body 240 may include two open ends or any other suitable configuration. The closed end is preferably substantially flat, but may alternatively be curved or have any other suitable shape. The walls are preferably substantially flat, but alternatively they can be curved or have any other suitable shape. The walls are preferably connected to the closed end at an angle, more preferably at right angles, but the transition between the walls and the closed end may alternatively be substantially fluid (e.g. have a bell-shaped or paraboloidal longitudinal section). The closed end is preferably substantially parallel to the opening formed by the walls, but may alternatively be oriented at an angle relative to the opening. The pump body 240 may be in the form of a groove formed in an arcuate or angular element (e.g. in longitudinal or transverse direction), cylinder, prism or any other suitable shape. The pump body 240 preferably has a substantially symmetrical cross section (e.g. circular, ovoid, or rectangular cross-section and the like), but alternatively it may have an asymmetrical cross-section. The pump body 240 is preferably oriented in the pumping system 10 so that the closed end is substantially normal to a radial vector extending from the axis of rotation of the driving mechanism 100 (e.g. a normal vector extending from the closed end is substantially parallel to the radial vector), but alternatively can be oriented so that the closed end extends at an angle relative to the radial vector. The pump body 240 is preferably oriented so that the opening is closer and the closed end is further away from the axis of rotation, especially when the main pump 200 rotates around the outer surface of the cam, but can alternatively be oriented so that the opening is located continue,

The main pump 200 may further include a return element 260 for returning the piston element 220 to an expansion position 224. The return element 260 preferably provides a restoring force that is less than the compression force provided by the third section 128 of the cam 120, but greater than the force exerted by the piston. a cam 120 in the second section 126. The restoring force is preferably exerted in a direction substantially parallel to the radial vector extending from the axis of rotation of the driving mechanism 100, but alternatively can be exerted in any suitable direction. The return element 260 is preferably arranged on the piston element 220 from the side of the pump body 240 (further from the cam 120, taking into account the piston element 220), The return element 260 is preferably connected to the piston element 220 outside the pump body 240, but can alternatively be connected to the piston element 220 within the pump body 240. The return element 260 is preferably in the form of a spring, but it can also use the natural properties of the working element (e.g. resilience of the membrane) or it can be any other suitable returning element 260.

The main pump 200 preferably further comprises one or more inlets facilitating the introduction of fluid into the lumen from the first reservoir 400 and one or more outlets facilitating the release of fluid from the lumen into the second reservoir 500. Alternatively, the main pump 200 may comprise one branched conduit a fluid which functions as both inlet and outlet, wherein said manifold fluid conduit is fluidly connected to the first and second reservoirs, allowing selective flow of the fluid therefrom. The inlet and outlet are preferably formed in the walls of the pump body 240, but alternatively may be formed in the piston element 220, in the connection between the pump body 240 and the piston element 220 or may be formed in any other suitable part of the main pump 200.

[0022] The inlet and outlet of the pump 200 preferably include inlet and outlet valves that control the flow of fluid through the corresponding fluid channels. The valves are preferably passive valves, but may alternatively be active valves controlled by the controller based on system state measurements carried out with the use of sensors. The valves are preferably one-way valves, but may alternatively be two-way valves or any other suitable valves. Each of the valves may advantageously be operated in open and closed mode and preferably has a lower pressure limit at which the valves are switched from closed to open mode. The inlet valve located in the inlet is preferably configured as to control the introduction of fluid into the main pump 200 and prevent fluid from escaping from the main pump 200. The inlet valve preferably operates in open mode to allow fluid introduction when the pressure in the lumen is lower or the same as the pressure in the first reservoir 400. Alternatively, the valve the inlet may operate in open mode when there is negative pressure in the clearance. The intake valve preferably operates in closed mode when the pressure in the lumen is greater or the same as the pressure in the first reservoir 400. The outlet valve is preferably configured to control fluid exiting the main pump 200 and prevents fluid from entering the primary pump. 200. The outlet valve preferably operates in open mode to allow liquid to escape, when the pressure in the lumen is greater than the pressure in the second tank 500 and the limit pressure of the outlet valve. The exhaust valve preferably operates in closed mode when the pressure in the gauge is lower or the same as the pressure in the second reservoir 500.

[0023] The portion 300 for transferring the force of the pumping system 10 serves to move the piston element 220 during the compression stroke when the main pump 200 rotates about the pivot axis may also additionally serve for the rectilinear displacement of the piston element 220 during the expansion stroke. The force transfer element 300 preferably comprises an axis having an arcuate position which is invariant with respect to the arcuate position of the main pump 200 (the angular position of the axis of the force transfer member 300 about the axis of rotation preferably remains unchanged relative to the angular position of the main pump 200). Even more advantageously, the force transfer element 300 or a part thereof has an angular position which is unchanged relative to the angular position of the main pump 200 about the axis of rotation and substantially similar to it,

wherein the axis of rotation of the roller is preferably an axis that is unchanged relative to the angular position of the main pump. The force transfer member 300 preferably contacts the sliding bearing surface 122 non-skidably, but alternatively can slide along an arcuate bearing surface 122. The force transfer member 300 is preferably rotatably connected to the piston element 220, but can alternatively be connected to the piston element 220 in a different manner . If the piston element 220 is in the form of a piston, the piston element 220 is preferably pivotally connected to the roll at the axis of rotation of the roll, but may be connected to the roll by using a semicircular bell surrounding the roll or using any other suitable connecting mechanism. If the piston element 220 is in the form of a diaphragm, the piston element 220 may be in direct contact with the diaphragm,

[0025] In another variation of the force transfer element 300, the force transmission member 300 is rotatably connected to the cam 120 at a fixed location on the cam 120 and rotatably connected to the fixed position of the piston element 220. The force transmission member 300 is preferably rotatably connected to the piston element 220 (for example at the piston) but alternatively may be connected to the piston element 220 in a slidable manner or connected to the piston element 220 in a different manner. In this variant, the force transfer element 300 preferably converts the variable distance between the respective fixed ends into a variable occlusive power. The force transfer member 300 preferably has the form of a connecting mechanism with two or more fasteners, but may alternatively be any suitable force transfer element 300.

[0026] The force transfer element 300 may alternatively be in the form of any suitable mechanism for converting the cam rotation relative to the main pump 200 into a variable occlusive force exerted on the piston element 220.

[0027] The pumping system 10 preferably further comprises a housing used to connect the components of the pumping system to the rotatable surface 20. The housing is preferably configured to be releasably connected statically to the rotatable surface 20, but it can also be connected to the pivoting surface 20 in another way. way. Even more preferably, the housing is configured to be mounted (e.g. using a screw, screw and the like) to the wheel hub, but can alternatively be mounted to the rim, axle or any other suitable wheel component. The housing is preferably rotatably connected to the driving mechanism 100 and is preferably connected statically to the body 240 of the main pump 200, whereby the main pump 200 rotates together with the housing. The housing can additionally be used to mechanically secure the components of the pumping system, the housing basically containing the components of the pumping system. The housing is preferably substantially rigid, but alternatively it can be substantially flexible. The housing is preferably substantially fluid-permeable, but can alternatively pass the fluid. In the case of one variation of the pumping system 10, the casing is used as the first reservoir 400, whereby the inlet of the main pump 200 is then fluidly connected to the interior of the housing and sucked in fluid therefrom. In the case of this variant, the casing may comprise a branched inlet conduit that fluidically connects the inside of the housing to the surrounding environment. As illustrated in Figures 7A and 7B, the branched inlet conduit preferably includes a waterproof membrane, which preferably allows gas to flow through it (e.g., the gas flow rate through the waterproof membrane is greater than the water flow rate through the waterproof membrane). The waterproof membrane is preferably a GORE ™ membrane, but may alternatively be any other suitable membrane. The inlet manifold may alternatively comprise an inlet valve that controls the passage of fluid into the interior of the housing, but alternatively it does not include any valves. The inlet valve is preferably a passive one-way valve that can operate in open mode if the pressure inside the housing decreases to a value less or equal to the ambient pressure, and in a closed mode if the pressure inside the housing is greater than the ambient pressure . However,

2. relief valve [0028] The pumping system 10 may further comprise a relief valve 700 used to vent air from the interior of the second tank 500 (e.g. tire interior) to the pumping system 10, in particular to the pumping system housing 10 (e.g., the first tank 400). but, alternatively, it can provide air extraction from the second tank 500 to the surrounding environment. Draining air through the relief valve 700 can provide several benefits. First, the air discharge through the relief valve 700 can prevent too high a pressure in the second reservoir 500. Second, the air discharge through the relief valve 700 can allow direct measurement by the pumping system 10 of the internal pressure in the second reservoir 500. Third, drainage of air through the relief valve 700 into the housing (first tank 400) can ensure effective re-use of the previously pumped air, which involves reducing the required processing (e.g. drying) of the air. The relief valve 700 is preferably connected to the interior of the second tank via the Schraeder valve of the second tank 500, but it can also be connected to the second tank 500 in a different manner. The relief valve 700 is preferably switched between the open mode in which the air flow through the relief valve 700 is possible and the closed mode in which the air flow through the relief valve is prevented. The relief valve preferably has a limit value for the opening pressure and is preferably an emergency relief shut-off valve. The closure limit value is preferably set to provide pressure reduction in the second vessel at a speed substantially close to the flow rate provided by the pump (e.g. 10 cubic inches per minute), but alternatively can provide a flow rate at substantially the same as the normal outflow velocity from the second one. the tank (e.g. 1 - 3 pounds per square inch per month), and may alternatively provide a pressure reduction in the second tank at a higher or lower velocity. The relief valve 700 is preferably a normally closed relief valve, but alternatively it may be a normally open relief valve that is maintained in a closed state or any other suitable valve. The relief valve 700 is preferably passive, but may alternatively be active. The relief valve 700 is preferably a one-way relief valve, but may alternatively be any other suitable relief valve 700. Examples of possible relief valves include a duckbill valve, impulse relief valve, ball relief valve, mushroom relief valve and diaphragm valve redundant. Alternatively, it is possible to use any other suitable relief valve. [0029] The measuring element serves to monitor the operating parameter and present a measurement indicative of the internal pressure in the second reservoir. The measuring element is preferably arranged in the interior of the body of the pumping system 10, but it may be located partly or completely outside the pumping system 10.

[0030] The measuring element preferably comprises a sensor and an indicator. The sensor preferably measures the operating parameter and may be in the form of a pressure sensor, a flow sensor, a temperature sensor or other suitable sensor. The sensor can be mechanical or digital (for example, generating voltage / current, powered or using voltage / current for measurements). The indicator is preferably passive and can be in the form of a dial indicator, a bar graph or any other suitable indicator element. However, the indicator may be active (e.g. powered, such as a digital display), whereby the displayed value may then be calculated by the controller.

[0031] In the first variant, the measuring element comprises a measuring container and a pressure gauge. The tank is fluidly connected to the relief valve 700, so that after opening the valve, the air escapes from the interior of the second tank to the measuring tank. The measuring reservoir is preferably substantially small, whereby the pressure in the measuring reservoir equalises with the pressure in the second reservoir even at the low air flow rate enabled by the relief valve.

However, the measuring container may alternatively have any suitable dimensions. The measuring container is preferably in the form of a compressed air chamber, but may alternatively be in the form of a pipe, channel or any other suitable container. The pressure gauge is preferably connected to the reservoir and measures the pressure inside the reservoir. The measured pressure is preferably a manometric pressure, but may alternatively be in the form of a pressure difference (e.g. between the interior of the tank and the outside / the environment of the filling system of the second tank) or absolute pressure. The indicating part of the pressure gauge is preferably arranged on the outer surface of the pumping system 10, and more preferably is parallel to the surface of the wheel to which the pumping system 10 is mounted.

[0032] In a second variant, the measurement element comprises a mass air flow meter connected to the indicator. The flow rate meter preferably measures the pumping side of the relief valve (e.g. after the relief valve) and is fluidly connected thereto, but alternatively can measure the flow rate to the relief valve (e.g. flow rate on the other tank 500 side) or flow through the body a relief valve, wherein a part of the flow meter is then placed inside the relief valve. In this variation on the downstream side of the relief valve it is preferable to maintain an approximately known pressure which is higher than the ambient pressure, but slightly lower than the expected pressure in the second reservoir. For example, the relief valve may be connected to a reservoir located at the lower pressure side having a relief valve having an opening pressure limit slightly lower than the expected pressure in the second reservoir, so that the pressure at the lower pressure side will always be approximately equal to the opening pressure limit. In another exemplary embodiment, the relief valve may be connected to a filling tank of a second tank in which air to be pumped to the second tank 500 is stored. The flow rate meter preferably generates a voltage or current indicating the air flow rate, wherein the voltage / current is supplied to the second tank 500. controller, transformed by the controller into a pressure measurement result and presented in the form of a pressure reading. Alternatively, the flow rate meter may be passive and measure the flow rate mechanically, wherein the position of the scale or indicator is then converted into a pressure reading. The flow rate meter may be a paddle gauge, a hot wire sensor, a cold wire sensor, a sensor using a Karmana swirl path, a diaphragm sensor, a laminar flow sensor, a turbine flow meter, a rotating piston, or any other flow meter. The indicator is preferably in the form of a digital display, but may alternatively be an analog indicator. The flow rate meter may be a paddle gauge, a hot wire sensor, a cold wire sensor, a sensor using a Karmana swirl path, a diaphragm sensor, a laminar flow sensor, a turbine flow meter, a rotating piston, or any other flow meter. The indicator is preferably in the form of a digital display, but may alternatively be an analog indicator. The flow rate meter may be a paddle gauge, a hot wire sensor, a cold wire sensor, a sensor using a Karmana swirl path, a diaphragm sensor, a laminar flow sensor, a turbine flow meter, a rotating piston, or any other flow meter. The indicator is preferably in the form of a digital display, but may alternatively be an analog indicator.

[0033] However, to facilitate the regulation of the pressure in the second reservoir, any other suitable relief valve may be used in the pumping system 10.

3. Torque Stabilizing Mechanism [0034] The pumping system 10 may further include a torque stabilizing mechanism 600 that compensates for the retraction force exerted by the main pump 200 on the cam 120 at the start of the expansion stroke. Compensating the retraction force may be desirable because the retraction force may cause radial force to be exerted on the cam 120, which in turn may be transmitted to the eccentric mass 140, thereby causing the system to interrupt. The torque stabilizing mechanism 600 is preferably located on the cam 120, but alternatively it can be placed on the force transfer element 300 (e.g. having an adjustable size that varies in response to force), on the main pump 200 or on any other suitable portion. component of the pumping system.

[0035] In one variation of the pumping system 10, the cam profile acts as a torque stabilizing mechanism 600, wherein the compensation of the reversing force then ensures a low curvature of the second segment.

[0036] In another variation of the pumping system 10, a mass connection is used as the torque stabilizing mechanism 600, during which during the compression stroke (through the third section 128, up to the top of the second section 126) the mass connection 142 can operate in combined mode and the during the expansion stroke, it can operate in disconnected mode. In one example, as shown in Figures 8A and 8B, the torque stabilizing mechanism 600 includes a profiled channel 610 formed between the inner bearing surface of the cam and the mass connection 142 (e.g. in the case where the mass connection 142 is in the form of a disc) through the inner surface. carrier. The profiled channel 610 preferably comprises a section 612 with a small clearance extending to the high clearance section 614, the clearance being the distance between the surface of the mass connection and the inner bearing surface. The top of the large gauge section is preferably substantially radially aligned with the first section 124, and more preferably with the top of the first section 124, but alternatively may be aligned with the beginning of the second section 126 just before the top of the first section 124 or aligned with any other suitable cam portion. 120. The beginning of the low clearance section is preferably aligned radially with the arc defined by the third section 128, but may alternatively be aligned with each respective portion of the cam 120. The torque stabilizing mechanism 600 preferably further comprises a movable element 620 positioned in the profiled channel 610 which connects and disconnects the mass connection 142 from the inner supporting surface. The movable element preferably combines the mass connection 142 with the inner friction bearing surface, but alternatively it can be a ratchet mechanism or any other suitable mechanism. The movable element preferably has a dimension substantially the same as the distance between the surface of the mass connection and the inner support surface in the low lumen section. The movable member is preferably wedged in the low lumen section when the eccentric mass 140 is in combined mode, the movable element holding the position of the mass junction 142 relative to the inner supporting surface. The movable element is preferably arranged in a high clearance section when the eccentric mass 140 is in the disconnected mode, the movable element then being substantially detached from the surface of the mass and / or the inner supporting surface, and allowing the mass joint 142 to move relative to the inner support surface. The movable element is preferably in the form of a roll, but alternatively it may be a cylinder or any other suitable movable element. During operation, when the main pump 200 reaches the top of the first section 124 (compression position 222), the piston element 220 exerts a radial retraction force on the force transfer element 300, which causes the cam 120 to pivot radially from the main pump 200. When this position is reached, it decreases in addition, the angular velocity of the cam 120 relative to the main pump 200. Such a radial movement, in combination with a lower angular velocity, removes the movable element from the low clearance section (the movable element is still traveling at a higher angular speed), which causes the movable member to move to the high clearance section when the main pump is moved. 200 through the second section 126 of the arcuate surface, as shown in Figure 8B. As the main pump 200 moves through the second section 126, the angular velocity of the cam is preferably increased, but alternatively it can remain substantially constant or be reduced. At the end of the second section 126 the angular velocity of the cam is preferably reduced due to the increase in contact force between the cam 120, the force transfer element 300 and the main pump 200.

[0037] In another variation, the torque stabilizing mechanism 600 comprises a groove 630 formed in the cam 120 and a pin 640 extending into the groove from the mass connection 142. The groove is preferably used to compensate for the radial retraction force by converting the rectilinear retraction force into a rapid rotation of the cam 120 (relative to the main pump 200) through the first section 124. The pin may preferably be moved in the groove between the connected position (shown in Figure 9A) and the detached position ( shown in Figure 9B). The groove is preferably formed in the cam body in a direction normal to the wide cam surface, but can alternatively be formed in any suitable portion of the cam body. The groove is preferably aligned with the second section 126 of the arcuate bearing surface 122, but it can also be fixed in any other suitable portion of the cam 120. The groove preferably extends along the arc, but can alternatively be substantially rectilinear, sinuate, or any other suitable shape. During operation, the retraction force exerted by the main pump 200 on the cam 120 causes the pin to move from a connected to a disconnected position resulting in the cam 120 rotating relative to the eccentric mass 140. When the main pump 200 reaches the end of the second section 126, the force exerted by the cam 120 on the main pump 200 preferably causes the pin to be re-positioned in a connected position. serpentine or may have any other suitable shape. During operation, the retraction force exerted by the main pump 200 on the cam 120 causes the pin to move from a connected to a disconnected position resulting in the cam 120 rotating relative to the eccentric mass 140. When the main pump 200 reaches the end of the second section 126, the force exerted by the cam 120 on the main pump 200 preferably causes the pin to be re-positioned in a connected position. serpentine or may have any other suitable shape. During operation, the retraction force exerted by the main pump 200 on the cam 120 causes the pin to move from a connected to a disconnected position resulting in the cam 120 rotating relative to the eccentric mass 140. When the main pump 200 reaches the end of the second section 126, the force exerted by the cam 120 on the main pump 200 preferably causes the pin to be re-positioned in a connected position.

[0038] However, it is possible to use any other suitable torque stabilizing mechanism 600 that provides for compensating for the radial force exerted on the cam 120 by the main pump 200 in which the pressure is increased.

4. Passive pressure control mechanism [0039] The pumping system 10 may additionally comprise a passive pressure control mechanism 800, which is preferably used to passively pressurize the reservoir after reaching the pressure limit in the reservoir. This is preferably achieved by passively interrupting pumping by the main pump. The passive pressure regulating mechanism 800 preferably interrupts the pumping by interrupting the application of force to the piston element 220, wherein force exertion may be interrupted by disengaging the force transfer element 300 from the cam 120, disengaging the main pump 200 from the cam 120, disengaging the force transfer member 300 from the main pump. 200 or eliminating the movement of the main pump 200 relative to the cam 120, as exemplified in Figures 15A and 15B. The passive mechanism 800 for regulating the pressure of the pumping system 10 preferably comprises an auxiliary pump 820 comprising a pump body 240 and a working mechanism 840, additionally comprising a regulating valve 860 having a limit value for opening and closing pressure. Alternatively, the passive pressure control mechanism 800 may include a control valve 860 and a main pump 200. The passive pressure regulating mechanism 800 is fluidly connected to the second tank 500, and the control valve 860 selectively controls the fluid flow to the auxiliary pump 820 based on the pressure in the second tank 500 . wherein it further comprises a regulating valve 860 having a limit value for opening and closing pressure. Alternatively, the passive pressure control mechanism 800 may include a control valve 860 and a main pump 200. The passive pressure regulating mechanism 800 is fluidly connected to the second tank 500, and the control valve 860 selectively controls the fluid flow to the auxiliary pump 820 based on the pressure in the second tank 500 . wherein it further comprises a regulating valve 860 having a limit value for opening and closing pressure. Alternatively, the passive pressure control mechanism 800 may include a control valve 860 and a main pump 200. The passive pressure regulating mechanism 800 is fluidly connected to the second tank 500, and the control valve 860 selectively controls the fluid flow to the auxiliary pump 820 based on the pressure in the second tank 500 .

[0040] The auxiliary pump 820 is preferably a piston pump substantially similar to that described above, in which the operating mechanism 840 is a piston element. Even more preferably, the auxiliary pump 820 is a reciprocating pump, but may alternatively be a diaphragm pump. The auxiliary pump 820 may alternatively be any other suitable displacement pump. The passive pressure control mechanism 800 may advantageously be operated in an increased pressure and a reduced pressure mode. The increased pressure mode is preferably achieved when the pressure in the reservoir exceeds the pressure limit. Even more advantageously, the increased pressure mode is achieved when the pressure in the reservoir exceeds the limit value of the valve opening pressure 860. In the increased pressure mode, the valve 860 is preferably in the open position and allows liquid to flow from the reservoir to the pump body 240, the pressure of the fluid being introduced causing the operating mechanism 840 to be placed in the elevated pressure position. In the elevated pressure position, the operating mechanism 840 preferably activates the drive mechanism 100, the force transfer element 300 or the main pump 200 to interrupt the application of force to the main pump 200. In the reduced pressure mode the valve 860 is preferably in the position closed and prevents fluid from flowing from the reservoir to the pump body 240, and the return mechanism causes the operating mechanism 840 to be positioned at a reduced pressure, wherein the position of the reduced pressure is preferably the position of the expansion 224, but alternatively may be the position of the compression 222 or any other suitable position therebetween. The pumping system preferably comprises at least one pressure regulating mechanism 800, but may alternatively comprise any suitable number of pressure regulating mechanisms.

The position of the pressure control mechanism 800, and more preferably the position of the pump body 240, is preferably statically associated with the main pump position, but alternatively may be movably associated with the position of the main pump 200. Angular position of the pressure control mechanism 800 relative to the main pump position preferably it is maintained, but alternatively it is possible to maintain a radial or linear distance. The working axis of the pressure control mechanism 800 preferably extends in the same plane as the working axis of the main pump 200, but alternatively may extend in other planes, perpendicular to the working axis of the main pump 200 or may extend in any other suitable manner. The pressure control mechanism 800 is preferably arranged relative to the main pump 200,

[0042] In one variation of the pressure control mechanism 800, the operating mechanism 840 disconnects the main pump 200 or the main pump component from the driving mechanism 100 when in the increased pressure position, and allows the main pump 200 to connect to the driving mechanism 100 when in the reduced pressure position (as shown in Figures 12A and 12B). The operating mechanism 840 preferably disengages the force transfer element 300 from the driving mechanism 100, but alternatively disconnects the piston element 220 or the entire main pump 200 from the driving mechanism 100. During the transition from the reduced pressure position to the increased pressure position, the operating mechanism 840 preferably moves the main pump component along the working axis of the main pump 200 in the direction away from the cam 120. The operating mechanism 840 can, however, move the main pump component in a direction away from the cam 120 at an angle to the working axis of the main pump 200 (e.g. in a perpendicular direction). The operating mechanism 840 preferably moves the main pump component in a plane containing the pump axle 240 of the pump, but alternatively moves the main pump component out of the plane. The force exerted on the operating mechanism 840 by the return element 260 of the auxiliary pump 820 advantageously provides a connection of the main pump component with the driving mechanism 100 when the working mechanism 840 returns to the reduced pressure position, but the pumping system 10 may alternatively comprise a second return element 260, which connects the main pump component with the driving mechanism 100 (e.g. a spring biased in such a way that the spring acts in the opposite direction to the direction in which the operating mechanism 840 moves the main pump component and the like). The second return element 260 preferably restores the contact of the main pump component with the driving mechanism 100 when the disconnecting force of the operating mechanism becomes less than the return force provided by the second return element.

The part of the working mechanism 840 is preferably statically connected to a part of the main pump 200, and actuation of the operating mechanism results in a change of the position of the main pump 200 or the main pump component. Even more advantageously, actuation of the operating mechanism selectively couples and disconnects the main pump 200 from the driving mechanism 100 when the operating mechanism 840 is in the reduced and increased pressure position, respectively. The operating mechanism 840 is statically connected to the power transfer element 300, but alternatively can be statically connected to the piston element 220, statically connected to the entire main pump 200 or statically connected to any other suitable central pump component. The operating mechanism 840 is preferably statically connected to the main pump component by means of the frame 880, but can alternatively be connected using a housing housing the pumping system 10 or using any other suitable connecting mechanism. The frame 880 can be aligned with the plane containing the main pump's working axis 200 relative to the plane containing the working axis of the pressure control mechanism 800, extend beyond any of the two planes, or be otherwise oriented relative to the pumping system 10. In a particular example, the force transfer element 300 it has the form of a roll, the operating mechanism 840 is connected to the axis of rotation of the roller by means of a frame 880 aligned with the plane containing both the working axis of the pressure control mechanism 800 and the working axis of the main pump 200, wherein the pressure control mechanism 800 and the main pump 200 preferably share a common plane. Alternatively, the operating mechanism 840 is temporarily connected to the main pump component when in the elevated pressure position, and is moved away from the main pump component when in the reduced pressure position.

[0044] In another variation of the pressure control mechanism 800, the operating mechanism 840 disengages the force transfer element 300 from the main pump 200 when in the increased pressure position and allows the power transfer element 300 to communicate with the main pump 200 when in the reduced pressure position. . The operating mechanism 840 is preferably connected to the force transmission element and changes its linear position relative to the driving mechanism 100 when in the increased pressure position, but alternatively can be combined with the main pump and change its linear position with respect to the force transmission element 300 and the driving mechanism 100 The operating mechanism 840 preferably moves the force transfer element 300 out of the common plane shared by the main pump 200 and the driving mechanism 100, but alternatively, it can move the force transfer element 300 so that it is not aligned with the working axis (e.g. perpendicular, in a common plane). The operating mechanism 840 can be connected statically to the force transmission element 300 or the main pump 200 using the frame 880, a weld, an adhesive or any other suitable connecting mechanism. Alternatively, the working mechanism 840 may be temporarily connected to the force transfer element 300 or main pump 200, wherein the operating mechanism 840 may then be in the form of a piston or rod temporarily connected to the force transfer element 300 or the main pump 200 using a connection solution (e.g. groove) or thorns. [0045] In another variation of the pressure control mechanism 800, the operating mechanism 840 interrupts force generation. For one alternative, the pressure control mechanism 800 statically associates the angular position of the driving mechanism 100 with the main pump 200, interrupting force generation by eliminating the movement of the driving mechanism 100 relative to the main pump 200 (as shown in Figures 13A and 13B). For example, the operating mechanism 840 may statically fix the angular position of the cam 120 to the angular position of the main pump 200 when in the increased pressure position, and make the cam position of the cam 120 independent of the angular position of the main pump 200 when in the reduced pressure position. In a particular example, the working mechanism 840 is in the form of a rod which is frictionally connected to the wide surface of the cam. In another particular example, the operating mechanism 840 is in the form of a rod extending to a groove in a wide cam surface (e.g. a wide surface closer to the housing or away from the housing) when in elevated pressure position and retracted from the groove when in the position of the reduced pressure. In another particular example, the operating mechanism 840 is statically connected to the arcuate bearing surface 122 of the cam 120. However, other mechanisms may be used to temporarily maintain the angular position of the cam. In another example, the work mechanism 840 can statically bind the angular position of the eccentric mass 140 to the angular position of the main pump 200. In a particular example, the operating mechanism 840 may comprise a frictionally connected rod with a wide surface of eccentric mass 140 or a mass connection 142. In another particular example, the working mechanism 840 has the form of a rod extending to the groove in a wide eccentric mass surface when in the increased pressure position and retracted from the groove when in the reduced pressure position. It is, however, possible to consider other mechanisms for temporarily maintaining the angular eccentric mass position. In another example, the body 240 of the main pump 200 may be statically connected to the driving mechanism 100, thereby eliminating the movement of the piston element 220 relative to the pump body 240 (e.g. when using a linear or rotary actuator). and the work mechanism 840 extends through the hole in the cam 120 (or eccentric mass 140) and pushes the wide surface of the eccentric mass 140 (or cam 120) to disengage the eccentric mass 140 from the cam 120. The operating mechanism 840 can be statically connected to the transfer member 300 force or main pump 200 using frame 880 or other connecting mechanism. Alternatively, the operating mechanism 840 may be temporarily connected to the force transfer element 300 or the main pump 200, wherein the operating mechanism 840 may then be in the form of a piston or rod connected to a force transfer element 300 or a main pump 200. The operating mechanism 840 can be connected statically to the force transfer element 300 or the main pump 200 using a frame 880 or other connecting mechanism. Alternatively, the operating mechanism 840 may be temporarily connected to the force transfer element 300 or the main pump 200, wherein the operating mechanism 840 may then be in the form of a piston or rod connected to a force transfer element 300 or a main pump 200. The operating mechanism 840 can be connected statically to the force transfer element 300 or the main pump 200 using a frame 880 or other connecting mechanism. Alternatively, the operating mechanism 840 may be temporarily connected to the force transfer element 300 or the main pump 200, wherein the operating mechanism 840 may then be in the form of a piston or rod connected to a force transfer element 300 or a main pump 200.

[0046] In another variation of the pressure control mechanism, the pressure control mechanism 800 switches the main pump 200 between pumping and blocking modes.

The main pump 200 preferably pumps fluid in pumping mode and does not pump fluid in blocking mode. Even more preferably, the components of the pumping system 10 are kept in the locking position in a static position relative to each other, whereby the piston element 220 is kept substantially stationary. The blocking mode of the main pump 200 is preferably activated when the pressure in the second reservoir 500 exceeds the valve opening pressure limit of 860, and the pumping mode is preferably activated when the pressure in the second reservoir 500 becomes lower than the limit valve closing pressure 860. Specifically, when the pressure in the second reservoir 500 exceeds the opening pressure limit, the valve 860 is opened, which allows the increased pressure air from the second reservoir 500 to flow into the compression space of the main pump 200, thus providing substantially keeping the piston element 220 in the initial position of the compression stroke (e.g., in the expanded position). In this way, the increased force exerted by the pressurized air on the piston element 220 substantially prevents the cam from moving when the piston element 220 is at the second cam profile section 126, but alternatively or additionally can prevent the cam from moving when the piston element 220 is in position. at the first section 124 or the third section 128 of the cam profile. Because the cam 120 is preferably configured to exert only a small amount of force on the piston element 220 located at the second section 126, the cam 120 can not overcome the high retraction force exerted by the retraction of the piston element 220. These pumping system features effectively stop pumping by the main pump 200. The force caused by the back prevents the cam from moving relative to the main pump 200 causing the cam pumping system to rotate. 120, as well as eccentric mass 140. If the pumping system 10 comprises a plurality of pumps, all of the pumps are preferably filled with air at increased pressure. Alternatively, in order to interrupt pumping it is possible to fill a single pump with increased pressure air, alternate filling of the pumps with air at increased pressure or filling any other subset of pumps. These characteristics of the pumping system 10 effectively interrupt pumping by the main pump 200. The reversal force prevents the cam from moving relative to the main pump 200 causing rotation in the pumping system 10 of the cam 120 as well as the eccentric mass 140. If the pumping system 10 comprises a plurality of pumps, all the pumps are preferably filled with air at increased pressure. Alternatively, in order to interrupt pumping it is possible to fill a single pump with increased pressure air, alternate filling of the pumps with air at increased pressure or filling any other subset of pumps. These characteristics of the pumping system 10 effectively interrupt pumping by the main pump 200. The reversal force prevents the cam from moving relative to the main pump 200 causing rotation in the pumping system 10 of the cam 120 as well as the eccentric mass 140. If the pumping system 10 comprises a plurality of pumps, all the pumps are preferably filled with air at increased pressure. Alternatively, in order to interrupt pumping it is possible to fill a single pump with increased pressure air, alternate filling of the pumps with air at increased pressure or filling any other subset of pumps. The retraction force prevents the cam from moving relative to the main pump 200 causing rotation of the pump system 10 of the cam 120 as well as the eccentric mass 140. If the pumping system 10 comprises a plurality of pumps, all pumps are preferably filled with increased pressure air. Alternatively, in order to interrupt pumping it is possible to fill a single pump with increased pressure air, alternate filling of the pumps with air at increased pressure or filling any other subset of pumps. The retraction force prevents the cam from moving relative to the main pump 200 causing rotation of the pump system 10 of the cam 120 as well as the eccentric mass 140. If the pumping system 10 comprises a plurality of pumps, all pumps are preferably filled with increased pressure air. Alternatively, in order to interrupt pumping it is possible to fill a single pump with increased pressure air, alternate filling of the pumps with air at increased pressure or filling any other subset of pumps.

[0047] However, it is possible to use any other suitable means to interrupt the application of force to the piston element 220.

The valve 860 of the pressure regulating mechanism 800 is used to selectively allow liquid to flow to the body 240 of the auxiliary pump 820. The valve 860 preferably has a limit opening pressure value substantially the same as the desired pressure in the tank (e.g. upper limit of the desired pressure range in the tank) and may additionally have a lower closing pressure value which is smaller, greater or equal to the desired pressure in the tank (e.g. lower limit of the desired pressure range in the tank). The valve 860 can additionally be used as a timer and have a pumping pressure resume at which the pumping by the main pump is resumed. The pumping restart pressure is preferably determined by the ratio of the first and the second pressure region in the valve. Alternatively, the pressure control mechanism 800 may include a timer that is used to delay the resumption of pumping after reaching the limit value of the closing pressure. The valve 860 is preferably arranged in a branch fluid line that fluidically connects the second reservoir 500 to the pump body 240. The valve 860 can, however, be located in the second tank 500 or in the inlet of the pump body. The limit value of the opening pressure is preferably greater than the limit value of the closing pressure, whereby the limit values ​​of opening and closing pressure are preferably determined on the basis of the return force provided by the return element. The condition of the valve is preferably determined based on the pressure in the second reservoir 500. The pumping restart pressure is preferably less than the limit value of the closing pressure, but alternatively, it may be greater than the limit value of the closing pressure or it may be any suitable pressure. The valve 860 may preferably operate in an open mode when the pressure in the second reservoir 500 is greater than the limiting opening pressure value, the valve 860 then allowing fluid to flow from the second reservoir 500 to the pump body 240, and in the closed mode when the pressure in the second one. the reservoir 500 is smaller than the limiting value of the closing pressure, the valve 860 thus preventing fluid from flowing from the second reservoir 500 to the pump body 240. Pumping by the main pump 200 is preferably resumed when the pressure in the second pump 820 becomes less than the pumping rest pressure, but alternatively can be resumed, when the pressure in the tank becomes less than the limit closing value. The valve 860 is preferably a snap type valve, but may alternatively be any other suitable valve 860. The valve 860 is preferably passive, but alternatively may be active. The valve 860 preferably comprises a valve member 864 that is disposed in the valve body 862 and may further include a return mechanism (e.g., a spring) urging the valve member 864 toward the valve body 862. Valve member 864 and valve body 862 can be made of different materials (e.g. to compensate for material expansion due to temperature changes), they can be made of the same material, or they can be made of materials with similar thermal expansion coefficients. but alternatively, it can be any other suitable valve 860. The valve 860 is preferably passive, but alternatively it can be active. The valve 860 preferably comprises a valve member 864 that is disposed in the valve body 862 and may further include a return mechanism (e.g., a spring) urging the valve member 864 toward the valve body 862. Valve member 864 and valve body 862 can be made of different materials (e.g. to compensate for material expansion due to temperature changes), they can be made of the same material, or they can be made of materials with similar thermal expansion coefficients. but alternatively, it can be any other suitable valve 860. The valve 860 is preferably passive, but alternatively it can be active. The valve 860 preferably comprises a valve member 864 that is disposed in the valve body 862 and may further include a return mechanism (e.g., a spring) urging the valve member 864 toward the valve body 862. Valve member 864 and valve body 862 can be made of different materials (e.g. to compensate for material expansion due to temperature changes), they can be made of the same material, or they can be made of materials with similar thermal expansion coefficients. which is arranged in the valve body 862 and may further comprise a return mechanism (e.g. a spring) urging the valve member 864 towards the valve body 862. Valve member 864 and valve body 862 can be made of different materials (e.g. to compensate for material expansion due to temperature changes), they can be made of the same material, or they can be made of materials with similar thermal expansion coefficients. which is arranged in the valve body 862 and may further comprise a return mechanism (e.g. a spring) urging the valve member 864 towards the valve body 862. Valve member 864 and valve body 862 can be made of different materials (e.g. to compensate for material expansion due to temperature changes), they can be made of the same material, or they can be made of materials with similar thermal expansion coefficients.

[0049] In one variation of the adjusting mechanism 800, the valve pressure 860 is substantially similar to the valve described in US Patent Application No. 13 / 469,007 of May 10, 2012.

[0050] In another variation of the pressure control mechanism 800, which is shown in Figure 16, the sign valve 860 comprises a valve body 862, a valve member 864, a spring 865, a first space 866, a second space 867, a reservoir channel 868, and a branched conduit 869. Spring or the return element 865 moves the valve body 862 relative to the valve member 864. The spring constant is preferably selected based on the desired reservoir pressure (pressure limit or opening pressure) and the desired operating characteristics of the valve. The first space is preferably formed between the valve body 862 and the valve member 864, preferably comprising a first pressure region normal to the direction of force exerted by the spring. The second space is preferably also formed between the valve body 862 and the valve member 864, preferably comprising a second pressure region normal to the direction of force exerted by the spring. The channel of the second tank advantageously fluidly connects the first space to the second reservoir 500. The branched channel is preferably formed in the valve body 862, preferably being fluidly connected to the pressure regulating mechanism 800. The branched channel is preferably formed by the valve member 864 along the axis of exerting a return force, opposite to the return element 260, but alternatively it can be formed at any other suitable location. The valve 860 may further comprise a time regulating channel fluidly connecting the second space to the ambient environment, wherein the time regulating channel has a cross-section selected on the basis of the desired outflow speed. The ratio of the first pressure region to the second pressure region is preferably selected based on the desired time for the valve 860 to receive the closed position again, but may alternatively be any suitable ratio. The combined volumes of the first and second spaces are preferably substantially insignificant compared to the volume of the second tank. The valve 860 may advantageously be switched between an open position and a closed position. In the open position, the valve body 862 and valve member 864 together form a connection channel that fluidically connects the first space to the second space, and the valve member 864 is spaced from the valve body 862. The open position is preferably achieved, if the pressure force produced by the pressure in the first space is greater than the force exerted by the spring on the valve body 862. In the closed mode, the valve member 864 and the valve body 862 close the connection channel together, and the valve member 864 substantially seals the branch channel, the valve member 864 being seated in the valve body 862. The closed mode is preferably achieved if the pressure force is less than the force exerted by the spring. In one variant of the valve 860, the valve member 864 has a symmetrical cross-section and includes a stem configured to match the branch channel, a first protrusion protruding from the stem, and a second protrusion protruding from the first projection. The valve body 862 has a cross-section corresponding to the cross-section of the valve member and includes a first section forming a branched channel, a second section extending from the first section, and walls extending from the second section. The first space is preferably formed between the second section and the second projection, the second space is preferably formed between the first section and the first projection, and the connection channel is preferably formed between the transition between the first projection and the second projection and the transition between the first section and the second section. The valve 860 may further include limiting seals and together form the first and second spaces. In one variant of the 860 valve, valve 860 includes a first seal disposed in the connecting passage and forming in the closed mode a substantially fluid-tight seal with valve member 864 and a second fluid-impervious seal formed between the second projection and the walls. The valve 860 may further include a seal in a manifold channel that forms a fluid-tight seal with the stem when the valve 860 is in closed mode (e.g. to jointly create a second space), and allows fluid to flow through it when the valve 860 finds in open mode.

5. Stabilizing mechanism [0051] The pumping system 10 may further include a stabilizing mechanism 900 used to reduce the rotational surface imbalance in the excitation of the eccentric mass 140 (e.g., start rotating) when the pumping system 10 rotates at or near the equivalent The stabilizing mechanism 900 is preferably in the form of an eccentric mass 140, where the eccentric mass 140 is then formed from a plurality of sections. Alternatively, the stabilizing mechanism 900 may be in the form of any other suitable stabilizing mechanism 900. When the eccentric mass 140 begins to rotate, the sections forming the eccentric mass separate from each other. This is especially useful in the case of when the oscillations of the system cause the eccentric mass 140 (and the positioning mechanism) to rotate around the shaft; centrifugal forces cause the eccentric mass 140 to separate and evenly distribute it around the axis of rotation, as shown in figures 10A and 10B. This not only ensures dynamic balancing of the system and / or revolving surface 20, but the even distribution of the eccentric mass 140 in the system also stops the pumping by the system. The latter effect additionally makes it possible to use the eccentric mass 140 as a control mechanism, wherein the resonant frequency of the eccentric mass can then be selected so that the pumping is stopped when a predetermined rotational speed or vibration frequency is reached. Each of the plurality of sections is preferably placed at the same radial distance from the axis of rotation (the maso-center 140 is radially divided into a plurality of sections, wherein a plurality of sections occupy different angular connections), but alternatively they can be placed at different radial distances (e.g. when the plurality of sections occupy substantially similar angular connections and the like). The plurality of sections advantageously share a common plane, the common plane preferably being substantially parallel to the rotational surface. A plurality of sections can together form an arc with a center located on the axis of rotation that intersects a common plane (e.g., many sections are adjacent to one another on an arc), can form a block that intersects a common plane, or can form any other suitable structure. Alternatively, a plurality of sections may be stacked along the section thickness, wherein the section thicknesses are preferably parallel to the axis of rotation. Many sections preferably have substantially the same mass, but alternatively they may have different weights. The center of mass of each eccentric mass section is preferably moved away from the junction point of the mass junction, preferably being near the adjacent eccentric mass section. During operation, the eccentric mass sections separate from each other until the centers of mass of the eccentric mass section are opposite one another with respect to the axis of rotation. but alternatively they can have different masses. The center of mass of each eccentric mass section is preferably moved away from the junction point of the mass junction, preferably being near the adjacent eccentric mass section. During operation, the eccentric mass sections separate from each other until the centers of mass of the eccentric mass section are opposite one another with respect to the axis of rotation. but alternatively they can have different masses. The center of mass of each eccentric mass section is preferably moved away from the junction point of the mass junction, preferably being near the adjacent eccentric mass section. During operation, the eccentric mass sections separate from each other until the centers of mass of the eccentric mass section are opposite one another with respect to the axis of rotation.

[0052] If the eccentric mass 140 is formed in the form of a plurality of sections, the mass connection 142 preferably also comprises a plurality of sections, each mass connection section being statically connected to the eccentric mass section. The mass connection sections are preferably pivotally connected to the cam 120, but alternatively they may be statically connected to the cam 120. Each mass connection section is preferably rotatably connected to the other mass connection sections, but alternatively may be statically connected to one or more other mass connection sections. . In one embodiment, which is shown in Figures 11A and 11B, the end of each mass connection section opposite the eccentric mass section is pivotally connected to the housing. The angular positions of the ends of the mass connection section are preferably static with respect to the housing, the ends of the mass connection section preferably being evenly distributed around the axis of rotation. In another variation, the end of each mass connection section opposite the eccentric mass section comprises a bearing, the bearing being slidably connected to a circumferential groove connected statically to the cam 120 and the surrounding axis of rotation. When the frequency of rotation of the rotating surface 20 is smaller or larger than the frequency invoking the eccentric mass 140 formed in the form of a set, the centrifugal force generated by rotation preferably holds the eccentric mass sections (and mass connection sections) in substantially adjacent positions. When the rotation frequency of the rotary surface 20 is the same as the excitation frequency, the centrifugal force preferably causes the bearings to move in the groove resulting in the arrangement of the plurality of eccentric mass sections substantially uniformly around the axis of rotation. Each / each of the bearings and / or eccentric mass sections can additionally contain magnets disposed in a manner that repels adjacent magnets, which facilitates the separation of the eccentric mass in response to the occurrence of system oscillations. In another variation, the mass connection sections are pivotally connected along a longitudinal axis extending from the cam 120 (e.g., the mass joining sections are arranged in a stack along the axis). In another variation, one mass connection section is statically connected to the cam 120,

[0053] If the mass connection 142 is connected to the cam 120 at the axis of rotation, the mass connection 142 may preferably operate in combined mode, where the mass connection 142 connects the eccentric mass 140 to the cam 120, and in the disconnected mode where the mass connection 142 provides detaching the eccentric mass 140 from the cam 120. In one variation, the mass connection 142 is in the form of a disc positioned in the lumen formed by the inner bearing surface of the cam 120, the disc can be rotated in the disconnected mode with respect to the inner bearing surface and in connected mode connected to the inner surface bearing surface using a friction element. The mass connection sections are preferably pivotably connected to the disc, but alternatively they may be disc sections (e.g. coaxial circles, arcuate elements and the like). The friction element may be a coating having a high friction coefficient extending along the inner supporting surface, a coating having a high coefficient of friction extending along the outer surface of the mass connection 142, roller or wedge or any other suitable means to ensure friction between the inner bearing surface and the mass connection 142 . The friction element is preferably selected such that the resulting centrifugal force generated by the eccentric mass 140 in the combined mode provides sufficient force to attach the mass 142 to the friction between the mass splice 142 and the inner support surface to maintain the mass junction position relative to the cam 120. The friction element preferably is chosen yes, that the resulting centrifugal force produced by the eccentric mass sections in split or disconnected mode does not provide sufficient force that the friction of contact maintains the position of the mass connection with respect to the cam 120, so that the mass connection can rotate freely. In another variation, the mass connection 142 is rotatably mounted on an axis extending from the cam 120, using the bearings 120, wherein the mass connection 142 can then be statically connected to the cam 120 using one or more sets of magnets or pistons extending from adjacent wide distances. surface of cam 120 and mass connection 142.

[0054] The eccentric mass 140 may further comprise a connection mechanism used to connect the plurality of sections to each other. The connecting mechanism is preferably arranged on the contact surfaces of neighboring sections, but alternatively may be placed in the body of the section, at the contact surfaces of adjacent mass connection sections or at any other suitable location. The connecting force provided by the connection mechanism is preferably chosen to be substantially the same or smaller than the angular separation force acting on individual sections of the eccentric mass when the system rotates at an excitation frequency. The connecting force may, however, have any other suitable value. The connecting mechanism may be in the form of a mechanical connection (e.g. using glue, fasteners,

In one embodiment, the eccentric mass 140 is formed in the form of an assembly of the first and second sections (e.g. the eccentric mass 140 is divided radially into two sections), the first section being a mirror image of the second section. In operation, the first and second sections preferably are diametrically opposed to each other and rotate about the axis of rotation of the positioning mechanism when the system vibrations reach the resonant frequency of the eccentric mass 140. In a second variant embodiment, the eccentric mass 140 is formed in the form of a first, a second and a third section having substantially the same mass, wherein the first, second and third sections are preferably substantially uniformly distributed around the axis of rotation, when the rotational speed of the system reaches the resonant frequency of the eccentric mass 140. The eccentric mass 140 can, however, be formed from any number of component sections in any suitable configuration. Alternatively, the stabilizing mechanism 900 may be in the form of any other suitable mechanism.

[0056] The pumping system 10 may further comprise a damping mechanism used to minimize the eccentric mass oscillations 140 in the system. Oscillations of eccentric mass 140 may cause excitation of the eccentric mass, during which the eccentric mass 140 rotates in the system instead of remaining substantially static relative to the vector of gravity. Oscillations may be caused by unevenness of the running surface (e.g. road), dynamic imbalance (e.g. caused by the mass distribution of the wheel), pumping pulse (e.g. when the pumping pulse occurs at a ground frequency) or may be caused by any suitable mechanism that can generate eccentric mass oscillations 140.

[0057] In a first variant, the damping mechanism comprises DynaBeads balls or other mechanisms for providing dynamic balancing placed in the inner channel surrounding the axis of rotation. In a second variant, the damping mechanism is a torsional mass-spring system, wherein the period of resonant vibrations of the mass-spring system is preferably adapted to the gravity-related resonant frequency of the eccentric mass 140. The torsional spring is preferably connected to the cam 120 so that the eccentric mass oscillates 140 cause an inertial displacement inducing a resonance of the torsional mass-spring system with a phase shift of 180 degrees relative to the phase of eccentric mass oscillation 140. The torsional spring is preferably mounted between the torsional mass and the cam 120,

wherein the first pump 200a pumps the fluid into the second tank 500 and increases the pressure therein. The first pump 200a preferably comprises an inlet fluidly connected to a source of fluid, the source of fluid being the surrounding environment, the housing (e.g., in the case where the housing contains dried air) or any other suitable source of fluid. The second pump 200b may further include an inlet (separate from the connected fluid manifold 202, but alternatively may be the same inlet) and outlet that are respectively fluidly connected to the fluid source and reservoir, wherein the second pump 200b may pump fluid to the second fluid. tank 500 and increase the pressure in it. Alternatively, the inlet and outlet of the second pump 200b may be connected respectively to the fluid source and the inlet of the first pump 200, thanks to which a two-stage pump is created. In this alternative solution, the fluid pressure is increased to the first pressure in the second pump 200b and increased to the second pressure in the first pump 200a. The first and second piston pumps preferably include first and second pump bodies (240a and 240b) respectively, and first and second piston elements (220a and 220b) respectively. The first and the second piston pump preferably share a common plane (e.g. the corresponding working axes share a common plane), but alternatively they can be placed in different planes. The first and second piston pumps are preferably evenly distributed radially around the driving mechanism 100, and more preferably evenly distributed around the axis of rotation of the driving mechanism 100. The pumps can, however, be arranged in a different way. The positions of the bodies of the first and second pumps are preferably fixed by means of a casing or other component, the casing providing a static connection of the pumping system 10 to the pivot surface 20, and further accommodating a pumping system 10. The first and the second piston pump are preferably opposite each other wherein the closed end of the body 240a of the first pump is spaced from the closed end of the body 240b of the second pump and the first piston element 220a is located near the second piston element 220b. The first piston element 220 a preferably comprises a first pressure region (an area on which the pressure-related force acts or which exerts it), and the second piston element 220b preferably comprises a second pressure region. The first pressure region is preferably smaller than the second pressure region, but alternatively may be larger or smaller. The driving mechanism 100 preferably comprises a rotation axis 102, a cam 120 that can rotate about a rotation axis, the cam 120 having a work surface 122 and an eccentric mass 140 connected to a cam 120 that moves the center of mass of the driving mechanism 100 away from the axis of rotation. The first force transfer member 300a may advantageously be non-skidably connected to the bearing surface 122 of the cam 120 and is preferably statically connected to the piston member 220 of the first pump along an axis (e.g., a rotational axis). The second power transfer element 300b preferably slides relative to the bearing surface 122 of the cam 120, but can alternatively be connected to the bearing surface 122 non-slip. The second power transfer element 300b is preferably statically connected to the piston element 220 of the second pump along an axis (e.g. a pivot axis). Each of the first and second force-transmitting elements may be in the form of a roller, a piston, a piston connected to the roller at an axis of rotation or any other suitable force-transmitting element. The positions of the first and second force transfer members are preferably maintained in a static state through the frame 880, but alternatively can be maintained using any other suitable mechanism. The frame 880 preferably houses a driving mechanism 100, whereby the driving mechanism 100 is located in the region surrounded by the frame 880. The frame 880 can, however, be arranged in a different manner with respect to the driving mechanism 100. The frame 880 is preferably arranged in a common plane shared by the first and second pumps, but alternatively it can be placed in a separate plane (e.g. extending in a normal direction to said plane and extending along a second plane that is parallel to the first). During operation, the radial or linear position of the frame 880 is preferably moved from the first position to the second position relative to the point provided on the driving mechanism 100 (e.g., the axis of rotation) when the second piston element 220 moves from the no-increased pressure position to the increased pressure position, respectively. . The distance between the first position and the second position is preferably substantially similar to the distance between the absence of increased pressure and the increased pressure position, but alternatively may be greater (e.g., if the frame 880 causes an increase in the position of the piston element) or smaller. The displacement of the frame 880 advantageously causes a similar displacement of the first and second force transferring members, the first first force transmission element 300a engaging the driving mechanism 100 in the first position and detaching the first power transmission element 300a from the driving mechanism 100 in the second frame position. Alternatively, the displacement of the frame can cause displacement of the first and second piston pumps relative to the driving mechanism 100, wherein the frame 880 provides a static relationship between the positions of the bodies of the first and second pumps. However, the force transfer means may be otherwise connected and disconnected from the driving mechanism 100. The frame 880 may further comprise solutions, e.g. arched grooves located in the surface of the frame 880 in the vicinity of the driving mechanism 100, which facilitate the advancing of the second force transfer element 300b relative to each other. of the bearing surface 122. The branched fluid conduit preferably fluidically connects the second reservoir 500 to the inlet of the second pump, but in addition can fluidly connect the second reservoir 500 to the inlet of the first pump. In the case of the latter variant solution, a valve is arranged between the three fluid connections or in the connection prior to connection. In the case of the latter alternative, the opening of the valve causes the simultaneous filling of both clearances of the first and second piston pump. Since the second piston pump preferably has a larger pressure area than the first piston pump, the second piston pump preferably applies to the frame 880 a straight (e.g. radial) disengagement force which is transformed by the frame 880 into retracting the position of the first power transfer element 300a from the driving mechanism 100, which ensures effective disconnection of the first power transfer element 300a from the driving mechanism 100.

[0059] Having become familiar with the above detailed description and the figures and claims, one skilled in the art will appreciate that modifications and variations may be made to the preferred embodiments of the invention that do not depart from the scope of the present invention as defined in the following claims.