Rotary union.

(54) Title: ROTATING BOARD.

(54) Title: ROTARY UNION.

(57) Summary

A rotary joint comprising: a rotary joint element (14) that can be rotated about an axis (24) and can be engageably engaged with a rotary device; the rotating device can be rotated around the axis and has a fluid channel arranged therein; a non-rotating joint element (12) arranged coaxially around the rotary joint element (14) and coupled to a support structure; the non-rotating seal element (12) comprises a support bearing, the support bearing is arranged between the non-rotating seal element and the rotary seal element; the support bearing supports the rotary device; and, a fluid passageway (28) disposed within the rotating union; the fluid passage comprises: a fluid material inlet arranged on a surface of the non-rotating seal element; a first portion in continuous communication with said fluid material inlet arranged within the non-rotating joint element; and, a second portion disposed within the rotating joint element and having a fluid material outlet arranged on a surface of the rotating joint element.

(57) Abstract

A rotary union comprising: a rotating union part (14) rotatable about an axis (24) and matingly engageable with a rotating device, said rotating device being rotatable about said axis and having a fluid channel disposed therein; a non-rotating union part (12) disposed coaxially about said rotating union part (14) and coupled to a support structure, said non-rotating union part (12) comprising a support bearing, said support bearing being disposed between said non- rotating union part and said rotating union part, said support bearing supporting said rotating device; and, a fluid passage (28) disposed within said rotary union, said fluid passage comprising: a fluid material inlet disposed upon a surface of said non-rotating union part; a first portion in fluid communication with said fluid material inlet disposed within said non-rotating union part; and, a second portion disposed within said rotating union part and having a fluid material outlet disposed upon a surface of said rotating union part.

ROTATIVE MEETING

FIELD OF THE INVENTION

The present invention relates to rotary joints. More particularly, the present invention relates to rotary joints used to provide and / or remove pressurized fluid to / from a high speed rotary device. The rotary joint is supplied with a non-rotating joint element and a rotating joint element that can be attached to a rotating device. The rotating union can be positioned between a bearing supporting the rotating device and the rotating device. Alternatively, the rotating union may incorporate a bearing that supports the rotating device.

BACKGROUND OF THE INVENTION

A rotary union is generally recognized as a mechanism used to transfer fluid (under pressure or vacuum) from a stationary inlet to a rotary outlet. The rotary joint is generally capable of preserving and isolating a fluid connection arranged between the stationary inlet and the rotary outlet. Rotary unions are used in a variety of applications - from compact rotary unions for the semiconductor industry to large heavy duty fluid pivots for industrial applications. Additionally, a variety of materials, sealing technology, and bearing types can be incorporated.

Rotary joints generally comprise a non-rotating joint element connected to an external fluid supply, and a rotating joint element that is or may be attached to a rotating device and rotates together with the rotating device. The seals are generally arranged between the non-rotating seal element and the rotary seal element. A rotary union can be called rotary union, rotary union, rotary valve, rotary coupling, rotary union, rotary union, hydraulic coupling, pneumatic rotary union, through hole rotary union, air rotary union, electric rotary union, vacuum and the like. The axis of rotation of the rotary joint is generally collinear with the axis of rotation of the rotary device.

Rotary unions can be designed to withstand a wide range of temperatures and pressures. Additionally, rotary unions can integrate multiple independent flow connections (passages) and handle different types of media simultaneously. A rotary union can generally be attached to an inlet valve at the same time that it rotates to reach an outlet. At that time, the fluid medium can flow into the rotary joint from a source external to the rotary joint and can be held within the device during its movement. This fluid medium exits the rotary joint where the valve openings meet during rotation, allowing more fluid medium to flow into the joint again for the next rotation. Because it frequently operates at high pressure and is in constant motion, a rotary union is designed to rotate about an axis.

Rotary unions can be used and can work cooperatively with contact printing systems and / or coating systems. Said contact systems (also known to those skilled in the art as impression cylinders) are generally formed from components that move a fluid on a weft or article substrate from a channel placed internally to said cylinder printer for, for example, printing an image or coating a pattern on the substrate. An illustrative impression cylinder can be provided as a rotogravure cylinder. Said printing cylinder can be used to contain a desired pattern and quantity of ink and transfer a portion of the ink from an internally positioned channel to a screen material that has been brought into contact with the printing cylinder.

In either case, the illustrative internally powered gravure cylinder can be used to apply a wide variety and range of fluids to a weft substrate at a desired speed and in a desired pattern. A suitable contact printing system incorporating a gravure cylinder can apply more than a single fluid (eg. For example, you can apply a plurality of individual inks (each with a different color) to a screen substrate compared to a conventional externally powered gravure printing system that can only apply a single ink. Mathematically represented, the intended contact printing system can use a rotogravure cylinder (center roll) and can print X colors on a weft substrate using Y print components, where X and Y are positive integers and 0 <Y <X.

In one example of a rotogravure system, predetermined networks of ink channels provided to each cell can typically be connected to individual colored ink receptacles arranged at the desired print location on the surface of the rotogravure cylinder. Providing a distribution system in this way can ensure that any part of a print design arranged on the surface of the rotogravure cylinder and arranged at any position on the surface of the roll can be fed by a connected ink channel to apply a color of ink designed at a specified flow rate.

Conventionally, the rotating unions are generally arranged external to the bearing that supports the axis of the rotating device (that is, on the side of the bearing opposite to the rotating device thus supported). This is because a person skilled in the art will feed fluids into the rotating device in a position close to the axis of rotation. This provides the ability to incorporate such fluid feeders on the shaft that supports the rotating device. This is the current industry standard for roller design.

Furthermore, it is understood that high rotational speeds (line) are considered highly desirable for increasing production rates. However, it has been discovered that when currently available rotary joints, whether or not they are connected to a rotary device such as the example of an internally powered gravure printing system described above, provide a fluid near the axis of rotation and are spun at a high circumferential speed, the centrifugal force was determined to create a low pressure region (i.e. a vacuum is made) in the fluid passages, or the portions of fluid passages, arranged within the region of the rotary joint that is close to the axis of rotation of the rotary joint element. This low pressure region is thought to cause three undesirable phenomena in operations where high rotational speeds are required:

one. When the rotary joint element reaches a certain speed of rotation, the local pressure in any channel, or portion (s) thereof, arranged within the rotary joint element that is close to the axis of rotation is reduced below the pressure of Fluid evaporation at local temperature. The fluid is caused to evaporate and gas bubbles form. This phenomenon can be considered as analogous to the cavitation observed in a hydraulic pump that operates at high rpm.

2. If the fluid is not purged properly, the size of any air bubbles trapped in the fluid will increase as the pressure decreases.

3. According to Henry's law, the amount of air dissolved in a fluid is proportional to the local pressure. When a fluid is transported from a position outside the rotary union to the center of the rotary union, the pressure exerted on the fluid changes from atmospheric to near-vacuum. Some of this dissolved air can then be released as bubbles in the fluid.

In accordance with the ideal gas law, the volume of air or gas bubbles is inversely proportional to the local pressure. Therefore, the size of the bubbles within the fluid will increase as the rotational speed increases. This is because the pressure in the fluid passages of the rotary joint located in the region near the axis of rotation decreases as the speed of rotation increases. These air or gas bubbles cause difficulties in high rotational speed operations such as printing and coating. Such difficulties may include undesirable flow rates, partial blockages within the roller's internal pipe, noise, vibration, and damage to the pipe network. The latter can be considered analogous to damage due to cavitation caused by an impeller.

Therefore, a person skilled in the art will recognize that such undesirable phenomena caused by these centrifugal forces such as those described above must be controlled to improve the speed and performance of the equipment used in the materials processing technologies. In the manufacturing industry, a design is needed that controls and increases the performance of high-speed rotary unions. Clearly, a design is needed that can correlate equipment design, fluid dynamics, and high-speed manufacturing.

The rotary union of the present invention overcomes these problems associated with the prior art by providing a rotary union for use in a fluid supply system that can transport single or multiple fluids, reduce sealing problems, and control pressure drop due to the high speed rotation of the rollers fed internally into the fluid inlets, prevents the creation of a low pressure region (s) in an economical manner and mitigates these effects by allowing an internally powered rotary device to be provided with a fluid in a position other than near the axis of rotation or through the axis it supports the rotary device. The described rotary union can be modified to accommodate different numbers of flow channels, is designed to ensure efficient rotation between inbound and outbound duct configurations, and provides better location options between the rotary device and the bearings that support the shaft of the rotary device.

BRIEF DESCRIPTION OF THE INVENTION

The present invention provides a rotary joint comprising a rotary joint element that can rotate about an axis and that can be engageably engaged with a rotary device, a non-rotary joint element arranged coaxially around the rotary joint element, and a fluid passage arranged within the rotating union. The rotating device can be rotated about the axis and has at least one fluid channel arranged therein. The rotary device is arranged around, and is supported by, a shaft supported by a support bearing. The fluid passageway comprises a fluid material inlet disposed on a surface of the non-rotating gasket element, a first portion in continuous communication with the fluid material inlet disposed within the non-rotary gasket element, and a second portion disposed within the element of rotary joint and having a fluid material outlet arranged on a surface of the rotary joint element. The surface of the rotating joint element can be engageably engaged with the surface of the rotating machine element to provide continuous communication of the fluid material from the fluid passage to the fluid channel. A fluid can communicate through the fluid passage from the fluid material inlet, through the first portion, to the second portion, to the fluid material outlet, and to the at least one fluid channel. The rotating joint element and the non-rotating joint element are arranged between the rotating device and the support bearing.

The present invention further provides a rotary joint comprising a rotary joint element which can rotate about an axis and can be engageably engaged with a rotary device, a non-rotating joint element arranged coaxially around the joint element rotatable and coupled to a support structure comprising support bearings, and fluid passage arranged within the rotary joint. The rotating device can be rotated about the axis and has at least one fluid channel arranged therein. The rotary device is arranged around, and is supported by, a shaft supported by a support bearing. The support bearings are arranged between the non-rotating sealing element and the rotating sealing element. The fluid passageway comprises a fluid material inlet disposed on a surface of the non-rotating gasket element, a first portion in continuous communication with the fluid material inlet disposed within the non-rotary gasket element, and a second portion disposed within the element of rotary joint and having a fluid material outlet arranged on a surface of the rotary joint element. The surface of the rotating joint element can be engageably engaged with the surface of the rotating machine element to provide continuous communication of the fluid material from the fluid passage to the fluid channel. A fluid can communicate through the fluid passage from the fluid material inlet, through the first portion, to the second portion, to the fluid material outlet, and to the at least one fluid channel.

The present invention further provides a rotary joint comprising a non-rotary joint element disposed about an axis, a rotary joint element disposed coaxially around the non-rotary joint element, and a fluid passage disposed within the rotative meeting. The rotating joint element can be engageably engaged with a rotating device that can be rotated about the axis. The rotary device has a surface that contacts the weft and has at least one fluid channel disposed therein. The fluid passageway comprises a fluid material inlet disposed on a surface of the non-rotating gasket element, a first portion in continuous communication with the fluid material inlet disposed within the non-rotary gasket element, and a second portion disposed within the element of rotary joint, and a fluid material outlet arranged on a surface of the rotary joint element. A fluid can communicate through the fluid passage from the fluid material inlet, through the first portion disposed within the non-rotating seal element, to the second portion disposed within the rotary seal element, towards the fluid material outlet and into the fluid channel disposed within the rotating machine element. The non-rotating joint element and the rotating joint element are arranged coaxially about an axis. The shaft is supported by a support bearing, and the non-rotating seal element and the rotary seal element are arranged in a position between the support bearing and the rotary device.

BRIEF DESCRIPTION OF THE FIGURES

Figure 1 is an example of a rotary device that contains an example of pipeline inside, which is used to demonstrate the forces in a pipeline containing a fluid and which is used to derive equation 15 below, Figure 1A is a example of pipe that is used to demonstrate the forces present in a pipe that contains a fluid and is arranged within the example of rotary device of Figure 1 and that is used to derive equation 15 below, Figure 2 is an example of a rotary object pipe design showing an example inside and Rfueraí Figure 3 are alternative examples of a rotary rotary object pipe design showing another example of R ^ o and Rfueraí Figure 4 is an elevation view of an exemplary embodiment of a rotary joint in accordance with the present disclosure;

Figure 5 is a cross-sectional view of the rotary joint of Figure 4 taken along line 4-4;

Figure 6 is a cross-sectional view of the rotary joint of Figure 4 taken along line 4-4 where the rotary joint is geared with contact and fluid with an example of a process impression roller;

Figure 7 is a cross-sectional view of the region labeled 7 in Figure 6;

Figure 8 is an elevation view of an alternative embodiment of a rotary joint in accordance with the present disclosure;

Figure 9 is a cross sectional view of the rotary joint of Figure 8 taken along line 8-8;

Figure 10 is a cross-sectional view of another alternative embodiment of a rotary joint geared in contact and fluid with a rotary device and disposed outside of the bearing supporting a rotary device;

Figure 11 is a cross-sectional view of yet another alternative embodiment of a rotary joint geared in contact and fluid with a rotary device and disposed between the bearing supporting a rotary device and the rotary device, and the rotary joint is arranged around the non-rotating joint element; and, Figure 12 is a cross-sectional view of yet another alternative embodiment of a rotary joint geared in contact and fluid with a rotating device where the non-rotating member of the rotating joint comprises the bearing support for the rotating device.

DETAILED DESCRIPTION OF THE INVENTION

In accordance with the present disclosure, it is believed that control of evaporation (eg, the formation of air or gas bubbles) in liquids arranged in elongated, pivotable pipes can be achieved by advancing the mathematical basis of the pressures in these systems. In order to understand and evaluate the fluid evaporation process and use the results to describe the exceptional rotary joint described in this description, a review of the forces involved in the movement of the fluid media through a pipe is necessary (or fluid passage) that rotates about an axis of rotation. Using these results to design a rotary joint suitable for use in high rotational speed applications can result in the prevention or reduction of evaporation of fluid within the fluid passage by carefully selecting the position in which fluid exits a rotary joint in relation to fluid channels arranged within a rotary device (such as an internally powered gravure roller) attached and in continuous communication with this. This involves the intentional design of the fluid passages within the rotary union.

Figure 1 depicts an example of a rotary device 16 having a fluid channel (or pipe) 38 capable of containing a fluid located therein. Fluid channel 38 has an inlet arranged at a distance, R_dentr₀, from the axis of rotation 24 and an outlet arranged at a distance, R_outside, from the axis of rotation 24. Figure 1A shows a system force balance analysis in a region of the fluid channel 38 generally arranged perpendicular to an axis of rotation 24. The fluid channel 38 filled with fluid rotates , generally, about the axis of rotation 24. In other words, the fluid channel 38 rotates around the axis of rotation 24. The force balances in the selected region of the fluid channel 38 can be expressed as:

Equation 1 F_t + F_c = F₂ + F_F where:

Fi and F₂ = Forces on sides of the region due to static pressure,

F_c = centrifugal force, and

F_F = resistance force due to friction.

Centrifugal force can be re-expressed as follows:

Equation 2 F_c = m * a where:

m = mass of the fluid in the specific region, ya = acceleration due to rotation.

The acceleration due to rotation, a, can be calculated from

Equation 3 a = cú²R where:

ω = angular velocity, and

R = distance from the axis of rotation to the center of the infinitesimal fluid region.

Therefore, Equation 1 can be re-expressed as:

Equation 4 Pinr² + p nr²Ark²R) - P2nr² + Ff where:

Pi and P₂ = static pressure on sides of the region, p = fluid density, and r = radius of the pipe.

For simplicity's sake, we can assume a cylindrical pipe to derive Equation 4. However, a person skilled in the art will recognize that the following equations and results are independent of the cross-sectional shape of the pipe. Therefore, by dividing both sides of the equation by the cross-sectional area nr², Equation 4 can be re-expressed as:

Equation 5 p AR (oü²R) - P₂ - P_t + AP_F where:

AP_F = pressure drop in the infinitesimal region due to friction.

After integrating the left and right sides from the inlet position of the pipe to the outlet position of the pipe, we have:

Equation 6 ρω²/? 0 ?? = P_{It was}r_to - Pdentro + Pf κ inside where:

In and Out = the radius relative to the axis of rotation at the pipe inlet and the pipe outlet, respectively,

Inside and Outside = I^to static pressure at the pipe inlet and at the pipe outlet, respectively, and

P_F - the pressure drop along the pipeline due to friction.

A person with experience in the field can find P_F in appropriate engineering manuals. Alternatively, a person with experience in the field can calculate P_Ffrom the Hagen-Poiseuille equation if the flow through a long cylindrical pipe in constant cross section is laminar. For reference, the Hagen-Poiseuille Equation is:

Equation 7

<img file="MX2016003545A_D0001.tif" />

where:

μ = fluid viscosity, / = pipe length, r = pipe internal radius, and Q = volumetric flow rate.

Starting from Equation 6, you now have:

Equation 8

<img file="MX2016003545A_D0002.tif" />

The roll surface speed, v, can be calculated from

Equation 9 v = coR_torch

By substituting the surface velocity, v, (Equation 9) for Equation 8, we obtain:

Equation 10

After the change, you have:

Equation 11

<img file="MX2016003545A_D0003.tif" />

¿(Pfuera - Pden ^ Pf) pv²

To use a pipe to supply a fluid, P_givetro must be greater than the vapor pressure of the fluid, P_v, at the applied temperature. Otherwise, the liquid in the inlet will evaporate. Therefore, it is reasonable to assume that P_givetro&gt; ^pv Therefore, Equation 11 can be re-expressed as:

(Rta-y _{&gt; 1} _ 2 (Ptoa-Pv + Pf) Equation 12 ^{Rf, m pl? 2}

A person with experience in the field will appreciate that there are two options regarding Equation 12; namely:

₁ _ 2 (Pfuera-Py + Pf) &lt;θ ₁ _ 2 (Ρ ^ - Py + Pf) _&gt; θ pV² 7 pV²

In the case of the last relationship (eg. ₁ 2 (Pfüera - Py + Pf) .. θ pv² (that is, it is a positive number, greater than the zero value)) evaporation of the fluid is possible. The net effect is that inside it must be a non-zero value (that is, inside it moves radially counter to the axis of rotation). In other words:

₁ 2 (Pwa - Py + Pf) θ

Equation 13 ^pv2

By way of example, when using an example of a fluid suitable for use with the present invention (eg, H₂O @ 25 ° C), it can be assumed that the friction losses through the Pf pipe are negligibly small (i.e. close to zero). By using H₂Or @ 25 ° C, a theoretical critical rotational speed can be defined for an example rotary system, where the fluid example is provided in a channel located inside a rotary device (eg, the rotogravure system rotary device described above), and the rotary device deposits water on a substrate that is in contact with the rotary device from the internal channel at atmospheric pressure, v_c:

V _ | 2 (Pfuera Py + Pf)

Equation 14 ^c NP = 14 m / s = 2756 ft / min where the known tabulated values ​​are:

Outside = 101325 Pa (atmospheric pressure @ STP),

P_v = 3200 Pa (eg, vapor pressure of H₂O at 25 ° C), and p = 1000 kg / m³ (for H₂O @ 25 ° C).

Therefore, in order to avoid the harmful effects described above, v &lt;14 m / s (and &lt;2755 ft / min) for H₂O @ 25 ° C. This rotation speed limitation may prevent the use of rotation speeds greater than 14 m / s (2755 ft / min) for H₂O @ 25 ° C for a manufacturing operation due to vaporization of the fluid within the pipe.

When the surface velocity has the relation v&gt; v_c, it can be seen that a pipe design inside a rotating object must meet the following equation:

^ inside&gt; L 2 (P_F (Py + Pf)

Equation 15 N ^py2 so that H₂O @ 25 ° C prevents liquid from evaporating at the inlet of the pipe.

Additionally, it is preferred that:

Equation 16 for H₂O @ 25 ° C.

In addition, it is useful to consider the following additional relationships: Henry's Law states that gas dissolved in liquid is proportional to the partial pressure of the gas:

Equation 17 P ⁼ ^ h^c where:

<img file="MX2016003545A_D0004.tif" />

p is the partial pressure of the gas in equilibrium with the liquid;

k_H is Henry's constant;

ce the concentration of the dissolved gas (eg, oxygen and nitrogen).

The equation to obtain the ideal equation of state:

Equation 18 PV = nRF where:

Fes the gas pressure;

l / is the volume of the gas;

n is the quantity of substance quantity of gas substance (also called the number of moles);

Tes the gas temperature; and,

Res is the ideal or universal constant gas.

A representative drawing showing the relationships between In / Out and the axis of rotation 24 in a single fluid channel system that is generally parallel to and rotates about an axis of rotation 24 is shown in Figure 2. A representative drawing showing the aforementioned relationships between Rdentra and Rtuera in an example of a multiple fluid channel system having two fluid channels 38a, 38b rotating about an axis of rotation 24a is shown in Figure 3. As shown shown in Figure 3, it is not necessary that all, or even any defined portion, of the fluid channel example 38b be continuously parallel (ie, collinear) to the axis of rotation 24a.

With reference to Figures 2 and 3, by using the mathematical derivation described above, for the purposes of the present description, the value of R_ofnter can be determined as the distance between the axis of rotation 24, 24a and the point at which any portion of a particular fluid channel 38, 38a, 38b, and following, arranged within the rotary device 16 or fluid passage 28 arranged within of the rotating joint element 14 of the rotating joint 10 provided in continuous communication with a respective fluid channel 38, 38a, 38b, and the following, arranged within the rotating device 16 is closer to the axis of rotation 24, 24a. Each fluid channel 38, 38a, 38b, and following, which may be present within a given rotary device 16 or fluid passageway 28 disposed within the rotary joint 10 in continuous communication therewith may have its own associated R inside.

As shown in Figure 3, it should be recognized that there may be deviations in the distance that the exemplary fluid channel portions 38b or fluid passage 28 (defined microscopically) are disposed from the axis of rotation 24a, despite that the general direction of flow of the fluid material macroscopically through the rotary device 16 or rotary joint 10 can be considered to be generally parallel to the axis of rotation 24a. In other words, the fluid channel 38 and / or the fluid passage 28 is not required to be parallel to the axis of rotation 24a.

With reference to Figures 2 and 3, by using the mathematical derivation described above, for the purposes of the present description, the value of R_outside can be determined as the distance between the axis of rotation 24, 24a and the point at which a particular fluid channel 38, 38a, 38b, and following, arranged within the rotating device 16, terminates on the surface that is in contact with the frame 48 of the rotating device 16 relative to the axis of rotation 24, 24a. Each fluid channel 38, 38a, 38b, and following, which may be present within a given rotary device 16, may have at least a portion of a fluid channel 38, 38a, 38b, and following, which is in communication Continuous with the surface of the rotating device and arranged at a radial distance of Rf_EUra from the axis of rotation 24, 24a.

Figures 4 to 7 provide an example of a similar rotary joint 10 in scope with the present disclosure. Rotary joint 10 has a rotary joint element 14 that can be rotated about an axis of rotation 24 and has a fluid passage 28 disposed within rotary joint element 14. At least a portion of the fluid passage 28 is disposed at a distance R within θη relative to the axis of rotation 24 and can be adapted to be attached to an example rotary device 16 to provide continuous communication between the fluid passage 28 and a fluid channel 38 arranged within the rotating device 16 in a fluid material outlet 44. Fluid channel 38 of rotating device 16 is adapted to provide fluid communication with surface 48 of rotating device 16 at a distance Rf_Uera relative to the axis of rotation 24. The rotary joint 10 generally further comprises a rotating joint element 14 which is dynamically balanced with the non-rotating joint element 12 about the longitudinal axis 24. As would be understood by an experienced person in the matter, the rotating joint element 14 generally rotates together with the rotating device 16. As shown, the non-rotating seal element 12 and the rotating seal element 14 are generally positioned in a coaxial or annular relationship with the non-rotating seal element 12 generally arranged around the rotary seal element 14. The seals 18 can generally be arranged between the non-rotating seal element 12 and the rotary seal element 14 to facilitate continuous communication of a fluid between a first portion of the fluid passage 28 arranged within the non-rotatable seal element 12 and a second portion of the fluid passage 28 disposed within the rotating joint element 14. As a person skilled in the art would understand, a rotary joint 10 is used to supply channels 38 arranged within the rotary device 16 with a fluid material. The rotary device 16 is generally supported by the axis 20 in such a way as to facilitate cooperative rotation of the rotary device 16 and the rotary joint element 14 coupled and cooperatively connected therewith about the longitudinal axis 24. Generally, shaft 20 is supported by support bearings 22. As will be described below, support bearings 22, 22a, 22b, 22c, and thereafter may be placed between rotating union 10c and rotating device 16c (eg. ., Figure 10), outside the joint rotary joint 10b and the rotary device 16b (eg, Figure 11), or even incorporated in the rotary joint lOd (p. eg, Figure 12) being arranged between the rotating joint element 14d and the non-rotating joint element 12d that has been coupled to a support structure 42.

Rotary joint 10 may be produced in accordance with a variety of constructions as known to a person skilled in the art, or as generally shown in the accompanying figures. A first portion of the fluid passage 28 disposed within the non-rotating seal member 12 is provided in continuous communication with a source of pressurized fluid material through the fluid material inlet 40 and the fluid ring 26. A second portion of the fluid passage 28 is disposed within the rotating joint element 14 as described above and generally rotates about the axis of rotation 24. The seals 18 arranged between the non-rotating joint element 12 and the joint element Rotary 14 can provide exclusive continuous communication (eg. eg, sealed) of a fluid from the first portion of the fluid passage 28 disposed within the non-rotating seal member 12 to the second portion of the fluid passage 28 disposed within the rotary seal element 14 and further avoid the fluid outlet to regions that are not near the junction between the portion of the fluid passage 28 disposed within the non-rotating seal member 12 and the portion of the fluid passage 28 arranged within the rotary seal element 14.

The second fluid passage portion 28 disposed within the rotary joint member 14 provides an outlet for fluid material 44 that relates to the fluid channel 38 disposed within the rotary device 16 to preferably provide sealed fluid communication. The second portion of the fluid passage 28 is preferably arranged within the rotary joint element 14 at a distance from the axis of rotation 24 that provides a Reentro value relative to R_{It was}associated channel of fluid channel 38 on surface 48 of rotary device 16 in accordance with Equation 15 described above.

As shown in Figures 5 to 9, the non-rotating seal element 12 is preferably arranged coaxially around the rotating seal element 14. In other words, the rotary seal element 14 can be received within a cavity formed within the non-rotating joint element 12 to provide a coaxial relationship between the rotating joint member 14 and the non-rotating joint member 12. Rotating joint member 14 can be attached to and attached to it by a retaining clip 36 and is preferably attached to rotating device 16 by means known to those of skill in the art to clamp together mechanical members including bolts that can extend towards the coupling end of the rotating device 16. Furthermore, suitable static sealing members 34, such as toner seals and the like, known to those skilled in the art, can be provided to seal the fluid channel 38 of the rotary device 16 to the fluid passage 28 of the rotary joint 10 to create exclusive continuous communication by and between the outlet 46 of the fluid channel 38 of the rotating device 16 and the outlet of the fluid material 44 of the fluid passage 28 of the rotating union 10. A person skilled in the art will understand that, conventionally, the longitudinal axis of rotary joint 10 is the same as the longitudinal axis of rotary device 16.

The fluid material inlet 40 and the fluid ring 26 can be formed in the non-rotating seal element 12 to provide continuous communication between the first portion of the fluid passage 28 arranged within the non-rotatable seal element 12 and the second portion of the passage of fluids 28 arranged within the rotating joint element 14. Alternatively, the fluid material inlet 40 and the fluid ring 26 can be formed in the rotating joint element 14 to provide continuous communication between the first portion of the fluid passage 28 disposed within the non-rotating joint element 12 and the second portion of the fluid passage 28 arranged within the rotating joint element 14.

Adequate provisions are also provided to provide continuous communication between fluid passage 28 and purge port 32. In a preferred embodiment, purge port 32 is provided in an orientation that disposes purge port 32 on top. of the non-rotating joint element 12 of the rotating joint 10. In either case, the bleed port 32 must be arranged in an orientation that facilitates the removal of any vapors disposed within the fluid passage 28 and / or fluid ring 26 of the rotating union 10 or fluid channel 38 of the rotating device 16 and to form a conduit extending between them. Suitable fluid line connections can be provided in continuous communication with fluid material inlet 40, fluid passage 28, fluid channel 38, and purge port 32. Purge port 32 is preferably provided as a purge valve that closes once any amount of trapped air / gas is purged from the system.

A person skilled in the art will recognize that a bleed valve works by releasing air or gas through a valve opening to reduce any accumulated pressure existing within a closed space to remove excess air or gas within that closed space. . A preferred bleed valve can be provided with a manually or automatically operated valve opening, which serves as an outlet point for air, gas, or other fluid. The main operating component is the valve itself, which can be provided as a simple opening. Other components, such as automatic controls, pressure sensing elements, springs and levers, may depend on the type of valve and system in which said components are used.

Rotary joint 10 may further include bearings 30 to allow for rotatable and removable mounting of rotary joint element 14 to a shaft or other internal element disposed within rotary device 16. Bearings 30 are held in place (i.e., are captive) with respect to the non-rotating sealing element 12 and the rotating sealing element 14 by the retaining clip 36.

Seals 18 and fluid ring 26 can be provided and placed between non-rotating seal element 12 and rotary seal element 14 to seal the first portion and the second portion of fluid passages 28 disposed within the non-seal element. rotary 12 and rotary joint element 14, respectively, to avoid cross-contamination of the fluid materials from a fluid passage 28a to an adjacent fluid passage 28b at a multi-fluid rotary joint (see Figure 9). A surface that provides a contact gear between the non-rotating sealing element 12 and / or the rotating sealing element 14 can be treated with a friction reducing substance or material (eg, tungsten chromium carbide) that can act as a supporting surface. When configured in this way, these coaxial / annular components can act as supports for each other. In the event that axis 20 changes shape due to pressure and / or temperature fluctuations in the transported fluids or axis 20 experiences any side-directed loading, such movements can be accommodated because seals 18 can float with the axis to find a 'better' position. As would be recognized by a person skilled in the art, seals 18 can be provided and, without limitation, include seal types such as surface seals, labyrinth seals, and the like, etc.

Furthermore, when it is indicated that the fluid pressure source and the non-rotating seal member 12 are fixed, this is, of course, only a frame of reference. Rotation of shaft 20, rotary joint member 14, and any associated rotation control apparatus portions, as described, are with respect to the rotational position of the fluid pressure source. Of course, if the fluid pressure source is rotatable, the other elements described would have ratios of rotation with respect to the rotational position of the fluid pressure source. Furthermore, it should be immediately obvious that any rotation control apparatus that requires portions or elements to be fluid activated and rotate at different speeds is intended to be encompassed herein.

An example of a multi-fluid rotary joint 10a attached to a rotating device 16 is shown in Figures 8 to 9. This embodiment of a rotating union in accordance with the present invention is interpreted similarly to the embodiment shown in the Figures. 4 to 7. The rotary joint 10a generally comprises a non-rotating joint element 12a and a rotating joint element 14a which are dynamically balanced about a longitudinal axis 24 and rotate together with the rotating machine element 16a. The non-rotating seal element 12a and the rotating seal element 14a are placed in an annular or coaxial relationship with the non-rotating seal element 12a generally arranged around the rotary seal element 14a. The seals 18a are generally arranged between the fluid material inlets and the fluid passages 28a, 28b formed between the non-rotating seal element 12a and the rotary seal element 14a. Said rotary joint 10a is used to supply a rotary device 16a such as rollers or cylinders having an axis 20 and cooperatively rotating around longitudinal axis 24 and whose ends can be supported by support bearings with a fluid material. The support bearings can be arranged inside or outside the space through which the fluid material flows.

Similar to the discussion related to rotary joint 10 described above, the first fluid passage 28a is provided in continuous communication with a source of pressurized fluid material through an associated fluid material inlet 40a and a fluid ring 26a. Additionally, a second fluid passage 28b can be provided in continuous communication with a second source of pressurized fluid material through an associated fluid material inlet 40b and a fluid ring. Both the first fluid passage 28a and the second fluid passage 28b are respectively located within the rotating joint element 14a in a manner that complies with Equation 15 described above.

Fluid passages 28a, 28b are located within rotating joint member 14a and generally rotate about axis of rotation 24. The rotating joint element 14a is received within a cavity within the non-rotating joint element 12a and fixed therein by a retaining clip 36, and is attached to the rotating device 16a by means known to those skilled in the art to clamp together the mechanical members including bolts extending towards the mating end of the rotating device 16a. The longitudinal axis 24 of the rotating joint 10a is located along the longitudinal axis of the rotating device 16a.

Suitable static sealing members 34a, 34b such as O-rings and the like, known to those skilled in the art, can be provided to seal the rotary device 16a and its associated fluid passages 28a, 28b of the rotary seal element 14a of the rotary joint 10a to create continuous communication by and between the respective outlets 46a, 46b of the fluid channels 38a, 38b of the rotating device 16a and the respective fluid material outlets 44a, 44b of the fluid passages 28a, 28b of the rotating joint 10a, respectively. Both fluid channels 38a, 38b of rotary device 16a are arranged within rotary device 16b in a manner that complies with Equation 16 described above.

Fluid material outlets and associated fluid rings 26a, 26b are formed in the non-rotating seal element 12a to provide continuous communication with the respective fluid passages 28a, 28b and the fluid chamber defined by and between the rotating seal element 14a and the cavity formed within the non-rotating seal element 12a to serve as the base for the rotating seal element 14a. Suitable provisions are further supplied to provide continuous communication between a respective fluid passage 28a, 28b and a respective purge port 32a, not shown. In a preferred embodiment, the bleed port 32a is provided in an orientation that disposes the bleed port 32a on top of the non-rotating seal member 12a of the rotating seal 10a. In any case, the purge port 32a must be arranged in an orientation that facilitates the elimination of any vapors arranged within the respective fluid passage 28a, 28b of the rotating union 10a or of respective fluid channels formed or integral with the rotating device. 16a and to form a duct that extends between them. Suitable fluid line connections can be provided in continuous communication with the respective fluid material inlet, fluid passages 28a, 28b, respective fluid channels arranged within rotary device 16a, and associated purge ports 32.

Rotary joint 10a further includes a suitable supply such as bearings 30a to allow rotatable and removable mounting of rotary joint element 14a to a shaft or other internal element disposed within rotary device 16a. Bearings 30a are held in position with respect to non-rotating seal element 12a and rotary seal element 14a by retaining clip 36.

The seals 18a and the fluid rings 26a, 26b can be placed between the non-rotating seal element 12a and the rotating seal element 14a and seal the fluid passages 28a, 28b to avoid cross-contamination of the flowing materials from a segment of fluid material to, for example, an adjacent fluid material segment on the multi-fluid rotary joint. As with the individual fluid medium embodiment described above, the surface that provides a contact gear between the non-rotating seal member 12a and / or the rotating seal member 14a can be treated with a friction reducing substance or material that can act as a supporting surface.

Again, when the fluid pressure source and the non-rotating seal member 12a are indicated to be stationary, this is, of course, only a frame of reference. The rotation of the shaft 20, the rotary joint member 14a, and any associated rotation control apparatus portions, as described, are with respect to the rotational position of the fluid pressure source. Of course, if the fluid pressure source is rotatable, the other elements described would have ratios of rotation with respect to the rotational position of the fluid pressure source. Furthermore, it should be immediately obvious that any rotation control apparatus that requires portions or elements to be fluid activated and rotate at different speeds is intended to be encompassed herein.

As mentioned above, the support bearings used to support rotary devices and rotary joints attached to them as described herein may be positioned to supply the rotary joint in a position outside of the support bearing 22b (eg. , Figure 10), between the support bearing 22a and the rotary device (p. eg, Figure 11), or even supplying the support bearings 22c incorporated in the rotating union 10 within the space through which the fluid or fluid material flows (eg, Figure 12).

As illustrated in Figure 10, the support bearing 22b used to support the rotary device 16c coupled with the rotary joint example 10c is coaxially positioned around the rotary device 16c. This allows the rotary joint 10c to be placed completely outside of the support bearing 22b and the rotary device 16c. In this embodiment, the non-rotating seal element 12c is arranged coaxially around the rotary seal element 14c which rotates about the axis of rotation 24b. A fluid can communicate continuously from fluid passage 28e to fluid channel 38e. Alternatively, as will be understood by a person skilled in the art, the rotary device 16c can be supported by a shaft which, in turn, can be supported by and in support gear with the support bearing 22b. In this case, the rotating union 10c would be located on the side of the bearing 22b that is opposite the side close to the rotating device 16c. The rotating union would supply a fluid from a respective fluid passage to a respective fluid channel through the shaft that supports the rotating device.

As illustrated in Figure 11, the support bearing 22a is placed on the shaft 20a that supports the rotating device 16b. Rotary joint 10b may be located entirely outside of bearing support 22a and rotary device 16b. As shown, the rotating joint member 14b is coaxially arranged around the non-rotating joint member 12b and rotates about the axis of rotation 24a. A fluid can communicate continuously from fluid passages 28c, 28d to fluid channels 38d, 38c, respectively. This configuration can provide a rotating union capable of arranging a fluid in any radial position disposed away from the axis of rotation 24a and can prevent centrifugal forces produced during rotation from creating a low pressure region (s) (i.e., a vacuum) within fluid channels 38c, 38d, or fluid channel portions 38c, 38d, which may be arranged in the region close to the axis of rotation 24a of the rotating joint element 14b when the rotating device 16b and the rotating joint element 12b are supplied with a high rotational speed (line). Here, there is no need to provide and / or confine any portion of the fluid passage 28c, 28d disposed within the rotary joint element 14b to the region near the axis 20a as is done with current available rotary joint and rotary joint designs. commercially. Instead, the portion of the fluid passage 28c, 28d disposed within the rotating joint member 14b and connected to a respective fluid channel 38c, 38d of the rotating device 16b may be disposed in any radial position with respect to the axis of rotation. 24a in accordance with Equation 15. This can provide continuous communication with a fluid channel 38d disposed within or even on the surface of the rotary device 16b anywhere in / on it.

As illustrated in Figure 12, the rotary joint lOd can be and / or can directly supply a support bearing (or bearings) 22c, 22d to support the rotary device 16d. In this illustrative embodiment, the support bearings 22c, 22d are coaxially positioned around the rotating joint member 14d. This embodiment may allow the non-rotating joint member 12d to be mechanically and / or otherwise structurally attached to a support structure 42 for direct support of the combination of the rotating joint member 14d of the rotary joint lOd and the rotary device 16d. In other words, the entire inertia of the rotating joint element 14d and the rotating device 16d is supported by the support bearing (or bearings) 22c, 22d, the non-rotating joint element 12d and the support structure 42. As will become clear For a person skilled in the art, the non-rotating seal element 12d is arranged coaxially around the rotary seal element 14d which rotates about the axis of rotation 24c. A fluid can communicate continuously from fluid passage 28f to fluid channel 38f of a rotary device 16d.

This configuration can further provide a rotating union capable of arranging a fluid at any location away from the axis of rotation 24a and can prevent centrifugal forces produced at high rotational speeds from creating a low pressure region (s) (i.e. , a vacuum is made) in any fluid channels, or portions of any fluid channels, arranged in the region proximate the axis of rotation 24a of the rotating joint member 14d. In other words, there is no need to confine the portion of the fluid passage 28f disposed within the rotary joint element 14d to the region near the axis of rotation 24a as is done with current commercially available rotary joint and rotary joint designs. Instead, the portion of the fluid passage 28f disposed within the rotary joint member 14d may be disposed at any location with respect to the axis of rotation 24a in accordance with Equation 15 in order to provide continuous communication with a fluid channel. 38f disposed within or even on rotary device 16d anywhere in / on it.

A person skilled in the art will recognize that the rotary joint 10 of the present invention or any of the component elements of the rotary joint 10 of the present invention can be heated and / or cooled. Furthermore, it should be recognized that the application of heating and / or cooling can help control the clearance / interference of the elements constituting the rotary joint 10. This can be especially helpful in maintaining the integrity of the fluid distribution. For example, heating or cooling, when properly applied, can help regulate the amount of compression in seals 18.

In addition, heating or cooling of the rotary joint 10 of the present invention or any of the component elements of the rotary joint 10 of the present invention can help control the viscosity of the fluid being used. A person skilled in the art will recognize that many fluids have a temperature dependent viscosity. Viscosity control can make it easier to apply the desired amount of a fluid, to flourish the fluid on a substrate, to the potential release characteristics of the fluid for application to a substrate, and to the propensity of a fluid to come out of a roller, for example. In other words, the rotary joint 10 could act as a heat exchanger to cool or heat a fluid, depending on what is desired for the process.

Furthermore, the temperature control of the rotary union 10 can additionally be used as an aid to degassing some fluids. A person skilled in the art will recognize that some fluids can often be degassed better and / or worse depending on their temperature.

The dimensions and values ​​described in the present description are not to be understood as strictly limited to the detailed exact numerical values. Instead, unless otherwise specified, each of these dimensions refers to the mentioned value and a functionally equivalent range close to that value. For example, a dimension described as 40mm is intended to mean approximately 40mm.

All documents cited in the Detailed Description of the Invention are incorporated, in their relevant part, as a reference in this description. The citation of any document should not be construed as an admission that it is a prior matter with respect to the present invention. To the extent that any meaning or definition of a term in this document contradicts any meaning or definition of the same term in a document incorporated by reference, the meaning or definition assigned to that term in this document shall govern.

Although specific embodiments of the present invention have been illustrated and described, it will be apparent to those skilled in the art that other changes and modifications can be made without departing from the spirit and scope of the invention. Therefore, the appended claims are intended to cover all such modifications and changes that are within the scope of this invention.