Self-driven centrifuge having vane module

Description: TECHNICAL FIELD [Detailed description of the invention]

【0001】

[Technical field to which the invention belongs]

The present invention is broadly related to the continuous separation of granules from a fluid performed using a centrifugal force field. More specifically, the present invention relates to the use of a spiral plate or vane in a centrifuge vessel with a suitable propulsion device for self-driven rotation of the spiral vane. In one embodiment of the invention, a jet nozzle is used as the propulsion device. In another embodiment of the invention, the specific shape and form of the spiral vane is modified to have a flat (planar) plate.

【0002】

[Previous technology]

The use of a spiral vane in a preferred embodiment of the present invention is a design change from the prior art using a conical separator stack as the basis for the separation of granules from the fluid, and thus the conical separator product. Examining the prior art with heavy objects is useful for recognizing the differences between the present invention and the prior art and the benefits gained by the present invention.

【0003】

U.S. Pat. No. 5,575,912, issued to Herman et al. On November 19, 1996, discloses a centrifuge for bypass circuits for separating particulate matter from circulating liquids. The centrifuge configuration includes a hollow, substantially cylindrical centrifuge container. The centrifuge container is combined with the base plate to form a chamber through which the liquid flows. A hollow central tube is provided through the base plate in the axial direction and extends into the hollow container of the centrifuge container. The centrifuge for this bypass circuit is designed to be incorporated into the cover assembly, with a pair of tangentially oriented jet nozzles located opposite the base plate rotating the centrifuge inside the cover. This separates the particles from the liquid. A plurality of conical separation plates are housed inside the centrifuge container. These conical separation plates form a single row of stacked bodies and are arranged close to each other to improve separation efficiency. A stack of rows of the conical separators is sandwiched between a top plate located adjacent to the top of the centrifuge container and a bottom plate located near the base plate. The inflowing liquid flows out of the central canal through the two oil inlets and from there through the top plate. The top plate, along with the ribs on the inner surface of the centrifuge vessel, accelerates this flow and directs it to the upper portion of the stack in a row of conical separators. Particles are separated as this flow flows inward in the radial direction through a flow path formed between adjacent conical separation plates. Upon reaching the inner diameter of the conical separator, the liquid continues to flow downward toward the tangentially oriented jet nozzle.

【0004】

US Pat. No. 5,637,217 issued to Harman et al. On June 10, 1997 is a partial continuation application from US Pat. No. 5,575,912. U.S. Pat. No. 5,637,217 discloses a centrifuge for bypass circuits for separating particulate matter from circulating liquids. The centrifuge configuration includes a hollow, substantially cylindrical centrifuge container. The centrifuge container is combined with the base plate to form a chamber through which the liquid flows. A hollow central tube is provided through the base plate in the axial direction and extends into the hollow container of the centrifuge container. The centrifuge for this bypass circuit is designed to be incorporated into the cover assembly, with a pair of tangentially oriented jet nozzles located opposite the base plate rotating the centrifuge inside the cover. This separates the particles from the liquid. A plurality of conical separation plates are housed inside the centrifuge container. The inflowing liquid flows out of the central canal through the two oil inlets and from there through the top plate. In one embodiment, a top plate and ribs on the inner surface of the centrifuge vessel accelerate this flow and direct it to the upper portion of a row of conical separators. In other embodiments, the row of stacks is part of a disposable assembly. In each embodiment, particles are separated as the flow passes through a flow path formed between adjacent conical separators, after which the liquid flows downward towards the tangential jet nozzle. Continue to flow to.

【0005】

U.S. Pat. No. 6,017,300, issued to Hermann et al. On January 25, 2000, discloses a centrifuge using a stack of conical separators to separate particulate matter from circulating liquids. ing. The centrifuge configuration includes an assembly that includes a stack of conical separators. The assembly, including the stack of conical separators, forms a hollow rotor hub that rotates about an axis. The assembly containing the stack of conical separators is attached to a shaft-type central canal. This shaft-type central tube is fixed to a hollow base hub of the base assembly. The base assembly further comprises a liquid inlet, a first flow path, and a second flow path communicating with the first flow path. The liquid inlet communicates with the base hub via a first flow path. A bearing device is placed between the rotor hub and the shaft-type central canal for the rotational movement of the assembly, including the conical separator stack. The rotor hub is fitted with an impulse turbine turntable. The fluid jet nozzle is arranged so as to face the turntable of this turbine. The fluid jet nozzle communicates with a second fluid passage to direct a liquid fluid jet to the turntable of the turbine in order to give rotational motion to the assembly containing the conical separator stack. The liquid to the fluid jet nozzle flows into the centrifuge using the stack of conical separators through the liquid inlet. The fluid that flows through the stack of conical separators also flows into this liquid inlet.

【0006】

US Pat. No. 6,019,717 issued to Herman on February 1, 2000 is a partial continuation of US Pat. No. 6,017,300. This U.S. Pat. No. 6,019,717 includes a structure similar to that of the parent patent, plus a honeycomb-like insertion member incorporated into the fluid jet nozzle to reduce turbulence at the inlet and improve turbine efficiency. It is disclosed.

【0007】

[Problems to be Solved by the Invention]

The improved separation efficiency gained by these inventions of U.S. Pat. Nos. 5,575,912, U.S. Pat. No. 5,637,217, U.S. Pat. No. 6,017,300, and U.S. Pat. Due to the reduction in heavy distance. According to the idea of the present invention, a similar effect is to replace the assembly containing the stack of conical separators with a spiral vane or a radial set of plates having a uniform axial cross-sectional shape. It is theoretically concluded that this is achieved by. The spiral vanes of the present invention are integrally joined to the central hub and the top plate, as will be described in detail later in the embodiments of the present invention. In a preferred embodiment, the combination of these components is a combination that is integrally molded to form a single member. The top plate acts with the accelerating vanes on the inner surface of the liner shell to direct the flow flowing out of the central portion of the centrifuge towards the outer edge of the top plate with an opening hole for the flow. And send. The divider adjacent to the outer circumference of the top plate prevents the flow from diverting from the inlet hole, that is, bypassing it, and flowing into the module of the spiral vanes through the gaps between the vanes on the outer circumference. If such a flow is allowed, turbulence may occur and the particles may be re-mixed by being injected into this region. In the form of each spiral vane in some embodiments, the outer peripheral edge of the top plate is a turbulence prevention portion. This turbulence protector extends over the axial length of each spiral vane and is between the outer stationary sludge collection area and the gap between the spiral vanes where particles are separated from the flow of liquid. It is a means to further reduce the interaction of fluids. The theoretical idea of this embodiment resulted in an actual reduction in implementation. The first test was done to confirm the benefits and improvements gained by this first embodiment.

【0008】

In a commercial embodiment of the invention disclosed in US Pat. No. 5,575,912, US Pat. No. 5,637,217, US Pat. No. 6,017,300, and US Pat. No. 6,019,717, a product of 20 to 50 conical separators. An assembly containing a heavy body is used. The individual conical separators are separately molded and stacked prior to assembly with the liner shell and base plate, or in the case of disposable rotor designs, with the hub or spool portion. Need to be aligned. This specific form is due to the increased equipment costs due to the large, multi-cavity mold and the assembly costs due to the time required to stack and align the individual conical separators separately. Causes a rise in. The idea of the present invention of "spiral molded into one member" makes it possible to replace all of the individual conical separators in the prior art with one molded component. The spiral vanes that make up the module, which is a member, can be injection molded at the same time together with the hub portion of the module and the top plate described above. As an alternative to this, these individual spiral vanes may be extruded with the hub portion and then combined with a separately molded top plate. Even in the alternative method according to the manufacturing method of the present invention, the total number of parts is reduced from 20 to 50 separate parts to 2 parts.

【0009】

The present invention provides an alternative design to the techniques using the conical separator stacks described above. Novelty and Performance Benefits of Design with Self-Driven Conical Separation Plate Stacks Disclosed in US Pat. Nos. 5,575,912, US Pat. No. 5,637,217, US Pat. No. 6,017,300, US Pat. No. 6,019,717. Has been proven in practical use. Some of the "secrets" to the success of these prior art inventions, namely the self-driving idea and the reduction in stacking spacing between conical separators, are maintained in the present invention, but the underlying design has changed. Has been done. Replacing the vertical stack of individually molded conical separators with a module of spiral vanes, a member, is an important structural change and a new and non-trivial advancement in the art. Probably showing.

【0010】

[Means for solving problems]

In one embodiment of the invention, the centrifuge that separates granular material from the liquid passing through the centrifuge is a base and a shell of the centrifuge that is assembled to the base to form a hollow internal space with the base. A hollow rotor hub that has a central axis of rotation, is assembled to the base, and extends through the hollow internal space, and is arranged in the hollow internal space to form an opening that serves as an outflow port between the hollow rotor hub. It comprises a support plate and a module of a centrifuge vane arranged in a hollow internal space and configured and arranged so as to be supported by the support plate and extend around a hollow rotor hub.

【0011】

One object of the present invention is to improve a self-driving centrifuge equipped with a module of vanes for separation processing.

【0012】

BEST MODE FOR CARRYING OUT THE INVENTION

In order to facilitate understanding of the principles of the present invention, the embodiments shown in the drawings will be described below, and specific terms will be used for this description. However, this is not intended to limit the scope of the invention. Modifications and further modifications of the described apparatus and further applications of the described principles of the invention can usually be conceived by those skilled in the art.

【0013】

1 and 2 show an automatically driven centrifuge 20 having a spiral vane module 21 as a member. Module 21 of this spiral vane is a stack of conical separators in a conventional design as disclosed in US Pat. No. 5,575,912, US Pat. No. 5,637,217, US Pat. No. 6,017,300, and US Pat. No. 6,019,717. It replaces the including assembly.

【0014】

Most of the overall container and structure of the centrifuge 20 is identical to that disclosed in the two US patents cited above. A notable difference is that the assembly containing the stack of conical separators of the prior art has been replaced by the module 21 of the spiral vane of the present invention. Other minor structural changes have also been made to fit module 21 of the spiral vane, as shown in the side-by-side comparison in FIG.

【0015】

It operates in a manner very similar to that described in No. 217, accepting an influx of liquid, typically oil, through an inlet opening provided for each support base (not shown). The connection passages provided in this support base allow liquid to flow into the hollow interior of the rotor hub. In this specification, the rotor hub is also referred to as a bearing pipe 22. The liquid then flows upward until it reaches the opening 23 at the top of the tube. On the outer peripheral surface above the tube 22, typically four equally spaced openings 23 are provided. The liquid flows out through these openings 23 and flows outward in the radial direction when it reaches the vicinity of the module 21 of the spiral vane. The upper portion of the liner 24 is formed integrally with the acceleration vane 25. The acceleration vanes 25, together with the upper portion of the liner 24, form a flow path (passage formed between adjacent acceleration vanes). These accelerating vanes 25 are typically four, six or eight evenly spaced to allow oil (or other liquid) to flow radially outward and this liquid flow. Is sent to the entrance hole 26 point formed in the top plate 27 of the module 21 of the spiral vane. The liner 24 is wrapped by a shell 28 assembled to the base 29. The liquid enters the inlet hole 26, flows through the module 21 of the spiral vane, and finally flows out from the lower edge 31 of the module 21. In this case, the flow flows through the annular gap 32 between the support base plate 33 and the bearing tube 22, i.e. the outer surface of the rotor hub. This outflow continues to flow to the two jet orifices 34 (only one is shown in cross section). These two jet orifices correspond to the inner openings as two tangentially oriented jet nozzles. High-speed jets flowing out of each of the orifices, which are nozzles, generate torque, which is a reaction. This torque centrifuges at a high speed of 3000-6000 rpm, which is sufficient for particles to be separated within the spiral vane module as the liquid flows through the spiral vane module 21. Drive (rotate) the machine 20. The flow of liquid through the centrifuge 20 including the specific flow path and the use of effluent for self-driving of the centrifuge 20 are the actions that occur within module 21 of the spiral vane and US Pat. No. 5,575,912. U.S. Pat. No. 5,575,912, U.S. Pat. No. 5,637,217, except for the important difference in the structure of Module 21, which is significantly different from the structure of the assembly including the conical separator stack described in U.S. Pat. It is essentially the same as that disclosed in US Pat. No. 6,017,300 and US Pat. No. 6,019,717.

【0016】

As can be seen further with reference to FIGS. 1 and 2, the spiral vane module 21 is essentially identical to the position within the liner 24 occupied by the assembly containing the stack of prior art conical separators. It is placed at the position of. The module 21 has a top plate 27 and a series of spiral vanes 38 that are identically shaped and evenly spaced (see gap 37). The concept of "equally spaced" simply means a uniform pattern between the spiral vanes, meaning that the space or gap formed by the adjacent vanes is uniform over the radial direction. It's not a thing. The space or gap 37 between the adjacent vanes 38 gradually increases (that is, becomes wider in the circumferential direction) from the inner hub portion 39 point toward the outermost peripheral edge 40 in the radial direction.

【0017】

The entire spiral vane module 21 is molded from plastic as an integral single member. The individual vanes 38 are connected to the central canal or hub portion 39 along the medial edge. This hub portion has a shape that is slidably fitted onto the support pipe of the centrifuge, that is, the rotor hub 22. By making the inner diameter 41 of the hub portion 39 an appropriate dimension with respect to the outer diameter of the rotor hub, coaxial fitting can be achieved with a small tolerance. This contributes to obtaining the overall weight balance required for the rotational speed of the centrifuge.

【0018】

The spiral vane module 21 has an annular shape and includes individual spiral vanes 38 (34 in total) arranged in a substantially cylindrical shape. The hub portion 39 is formed into a cylindrical shape. The top plate 27, which is substantially conical, has a substantially flat annular ring portion 27a that surrounds the hollow interior 42. As the shape of the top plate 27, it is conceivable to have a hemispherical upper surface. Further, as a part of the module 21, a dividing plate 44 is provided adjacent to the outer peripheral edge 43 of the top plate 27. The dividing plate 44 has a ring shape and extends horizontally outward in the radial direction. Further, a plurality of inlet holes 26 are formed in the top plate 27. These inlet holes 26 are arranged adjacent to the outer peripheral edge 43 of the top plate and adjacent to the position where the split plate 44 starts. In the cross-sectional view of FIG. 2, the inlet hole 26 and the dividing plate 44 are shown by broken lines because they are actually above the cut surface 2-2. This dashed line illustrates the position of these parts with respect to vane 38.

【0019】

The flow of liquid flowing out of the opening 23 of the tube and flowing in the direction of the inlet hole 26 is actually "dropped" by the accelerating vane 25 located (radially) corresponding to the inlet hole 26. .. The flow flows from these inlet holes through the top plate 27. In this case, one inlet hole corresponds to each of the separation processing gaps 37 between each pair of adjacent spiral vanes 38. As the flow flows through the inlet holes into each gap 37, the flow is directed inward in the radial direction and downward in the axial direction because the outlet of the flow is between the outer surface of the rotor hub and the inner edge of the base plate. And pass through the gap. The dynamics of this flow is such that the flow flowing out of the opening 23 of the tube is evenly distributed across the surface of the top plate, thereby evenly distributing it to the 34 inlet holes 26. As mentioned above, each gap corresponds to one inlet hole and each vane 38 corresponds to one gap. As the liquid flow through the gap 37 from the wide outer point to the narrow inner point adjacent to the rotor hub, the centrifugal force due to the high speed rotation of the centrifuge acts on the heavy particulate matter. As a result, the heavy particulate matter gradually moves outward in the radial direction and continues to slide outward while being collected on the concave surface of the spiral vane, and finally flows out of the module to the outer peripheral edge of the module 21 and the liner. It can accumulate in the sludge collection area between the inner surface of the shell 24. One possible path of particle 45 is schematically illustrated in FIG.

【0020】

The dividing plate 44 extends outward in the radial direction from the vicinity of the inlet hole 26 to the vicinity of the inner surface 48 that does not contact the inner surface 48 of the liner 24. The split plate 44 prevents the flow from circumventing around the inlet hole 26 and disturbing the stationary region 50 where sludge (ie, separated particulate matter and oil) is collected. The design of the present invention can significantly suppress the re-mixing of particulate matter already separated from the fluid by preventing the flow from disturbing the rest region 50. The concept of remixing is to release or pick up some of the particulate matter that has already separated from the flow of the liquid, allowing these particulate matter to return into the liquid, thereby overriding the treatment already performed. Including to put away. The distance between the dividing plate 44 and the inner surface 48 of the liner 24 is set to be large enough to allow large particulate matter separated in the region of the accelerating vane 25 to be discharged into the stationary region 50.

【0021】

When the liquid flow passes through the inlet hole 26 and flows into the gap 37 where the separation process is performed, it spreads in this gap, travels inward in the radial direction and downward in the axial direction, and reaches the lower edge 31 from here. It flows out through the gap 32. This flow is prevented by the use of the base plate 33 from diverting from the planned flow through the gap 37. This base plate blocks any other exit path except the opening in the gap 32. Here, the gap is formed between the inner circular end edge 51 of the base plate 33 and the outer surface 52 of the bearing tube 22, that is, the rotor hub (see FIG. 1A).

【0022】

In one alternative embodiment of the invention (see FIG. 1B), the base plate 33a extends to contact with the bearing tube 22 and the gap 32 is closed. A plurality of gap holes 33b are formed in the base plate 33a so as to be a flow path so as to be substantially at the same position as the gap portion 32. For simplicity, the individual vanes 38 are omitted from the cross-sections of FIGS. 1A and 1B. Virtually any type of opening can be used instead of the circular hole 33b. Radial and / or circumferential slots may be used as such openings.

【0023】

With reference to FIGS. 3, 4 and 5, the detailed structure of the spiral vane module 21 is illustrated. 3 and 4 are perspective views of a shape formed into one member of the module 21. FIG. 5 is a top view schematically showing a pair of spiral vanes 38 and a gap 37 formed between the spiral vanes 38. As described in part in relation to the flow path, the spiral vane module 21 comprises 34 spiral vanes 38. Each of these vanes has substantially the same structure and is integrally connected so as to be a module formed into one member. Each of these 34 spiral vanes 38 is integrally connected to the underside or underside of the apex plate 27 at the apex edge as part of a structure that is a member. Each of the spiral vanes 38 extends axially from the top plate towards the corresponding lower edge 31. The inner edges of each vane together form the inner hub portion 39. Each spiral vane 38 has a convex outer surface 55 and a concave inner surface 56. These faces form a spiral vane of substantially uniform thickness of about 1.0 mm (0.04 inch). The convex surface 55 of one vane and the concave surface 56 of the adjacent vanes each form a gap 37 between the two vanes. The width of the gap between the vanes, that is, the thickness in the circumferential direction, increases as it goes to the outside of the vanes.

【0024】

Each spiral vane 38 curves radially outward from the inner hub portion 39 (curved portion 57) and surrounds a portion of the corresponding inlet hole 26. The portion 57 extends along the tangent to the side away from the inlet hole to form the turbulence prevention portion 58. The turbulence prevention portion 58 of one spiral vane 38 extends in the counterclockwise direction when viewed from the top view and in the circumferential direction toward the adjacent vane. A separation gap 59 is formed between the free end or edge of the turbulence prevention portion 58 of one vane and the curved portion 57 of the adjacent spiral vane. This separation gap is substantially an axial, i.e., full-length slit, with a circumferential width of approximately 1.8 mm (0.07 inches). The small curvatures of each turbulence prevention section 58 form a substantially cylindrical shape with alternating separation gaps 59. This cylindrical shape forms the outermost side of the spiral vane module 21 located below the top plate 27.

【0025】

The curved shape from the inner edge of each spiral vane to the outer curved portion 57 has a characteristic geometric morphology. The line 60 drawn from the centrifuge axial rotation centerline 60a to the intersection 61 above any one of the 34 spiral vanes 38 is 45 ° with respect to the tangent 62 to the curvature of the spiral vanes at this intersection. Has an internal angle of 60b (Fig. 2). This characteristic geometry applies to the convex and concave portions of the main portion of each spiral vane, but not to either the curved portion 57 or the turbulence prevention portion 58. An internal angle of 45 ° in a preferred embodiment can be referred to as the angle of the spiral vane with respect to the module of the spiral vane and the corresponding centrifuge. The preferred range of this internal angle is considered to be 30 ° to 60 °. U.S. Pat. No. 5,575,912 and U.S. Pat. No. 5,637,217 cited above defined the angle of the cone, typically 45 °, based on the slope or slope of the cone wall of each cone. In the present invention, the angle of the spiral vane is defined.

【0026】

In the process of the flow passing through the gap 37, the particulate matter to be separated passes through the gap along a substantially radial flow path outward due to the action of the radial centrifugal force component, and between adjacent vanes. Go through the gap. This particulate matter is, in fact, U.S. Pat. No. 5,575,912 and U.S. Pat. No. 5,637, As in the case of the shape of the assembly including the stack of conical separators of No. 217, the flow flows in the retroactive direction. Once the particles that make up the particulate matter to be separated from the liquid flow arrive at the concave inner spiral surface of the corresponding vane (see Figure 5), these are due to the absence of flow velocities at the fluid boundary layer. Particles move outward in the radial direction. This radial outer path is towards the sludge collection area, the stationary region 50. The particles then "fall off" from the spiral vane module through axially continuous slits formed between the circumferentially discontinuous turbulence protectors (ie, the separation gap 59) of the spiral vane. ". As mentioned above, the function of the turbulence prevention section is to reduce the fluid interaction between the flow occurring within the gap 37 and the sludge collection region (stationary region 50). The sludge collection area is referred to as a "stationary area", but this term merely represents a preferable state. Ideally, this sludge collection area 50 is completely stationary so that there is virtually no turbulence and there is no risk of any particulate matter re-mixing into the liquid stream. It is good to do. In the present embodiment, the turbulence prevention unit 58 is configured to form a circular contour when viewed from the top surface side. However, in the present invention, each of these turbulence prevention sections 58 is slightly tilted outward so that the particulate matter that would be collected on the inner surface of each turbulence prevention section is also "in the collection area." You may be able to "slide out". Since corners are formed at the positions of the curved portions of each spiral vane, some particulate matter tends to accumulate in the corners. By tilting the turbulence prevention portion, this corner can be widened and the collected particulate matter can easily slide into the sludge collection region (stationary region 50). The shape of this alternative turbulence prevention section is shown by the dashed line in FIG.

【0027】

The flow leaves the gap between adjacent spiral vanes, exits the gap adjacent to the rotor hub, then reaches the jet nozzle and is expelled at high speed from this jet nozzle. As a result, the reaction force causes the rotor to rotate at a high speed. As an alternative to this form, the rotor may be driven by an impulse turbine to which the rotor is mounted. In addition, the molded spiral vane module is "wrapped" inside the sludge-holding liner shell and base plate assembly, similar to that disclosed in US Pat. No. 5,637,217. This unique form makes it possible to quickly and easily maintain the rotor of the centrifuge. This is because the sludge is completely retained in the inner capsule, eliminating the need for disassembly or cleaning. Alternatively, the spiral vane module of the present invention can be replaced with an assembly that includes a stack of conical separators that are part of a completely disposable centrifuge rotor.

【0028】

FIG. 6 shows the assembly 64 containing a stack of typical prior art conical separators on the left half of the centrifuge 63 and the spiral vane module 21 according to the invention on the right half side by side. It is a schematic diagram. FIG. 6 shows that the spiral vane module 21 of the present invention is a conical separator of the prior art described in US Pat. No. 5,575,912, US Pat. No. 5,637,217, US Pat. No. 6,017,300, US Pat. It is an object of the present invention to further clarify the above description showing that it can be replaced with an assembly containing a stack. The shapes of the corresponding base plates 65, 33 differ slightly between the two molds, but the rest of the centrifuge structure is substantially identical between these molds.

【0029】

7A, 7B and 7C show three alternative forms of the spiral vane form used as part of the spiral vane module. Each of these alternative forms is in the same theory and action as in the present invention, while maintaining the idea of replacing the assembly containing the stack of conical separators of the prior art with a module of spiral vanes. Can be used.

【0030】

In FIG. 7A, the curved spiral vane 38 of module 21 has been replaced with a vane 68 having a substantially flat planar surface. The vanes 68 are staggered so that they extend outward, though not exactly in the radial direction. The top view of FIG. 7A shows a total of 24 vanes or flat plates 68, but the actual numbers are based on the overall dimensions of the centrifuge, the viscosity of the liquid, and the size of the particles to be separated. It can be increased or decreased based on variables such as the required efficiency. The tilt angle (α) or slope of each plate is another variable. Each plate 68 is set at the same angle (α) with respect to the radial direction, but the choice of this angle can be changed. The choice of angle depends, in part, on the speed of rotation of the centrifuge.

【0031】

In FIG. 7B, the individual vanes 69 are curved like vanes 38, but have a larger curved shape or concave shape. Further, each vane 69 gradually increases in curvature toward a point away from the bearing pipe 22. Such a vane shape is called a "super-spiral", and this "super-spiral" is geometrically defined as follows. First, a radial line 72 is drawn from the axial center line of the bearing pipe 22, which is also the axial center line of the module 21. This line intersects the convex plane of one vane at point 73. The tangent line 74 at this intersection 73 has an internal angle 75 with the radial line 72. The size of the internal angle 75 increases as the intersection 73 moves away from the bearing pipe 22. The theory in this embodiment of the spiral vanes is to shape each vane so that the slip velocity of the particles becomes constant as the inertial force increases in proportion to the distance from the axis of rotation. Except for the curved shape of each vane 69, the spiral vane module shown in the schematic of FIG. 7B is identical to the spiral vane module 21.

【0032】

In FIG. 7C, the shape of the spiral vane in the module is based on the shape of vane 69 in FIG. 7B with the addition of a partially shortened vane 70. A shortened vane 70 is placed between each pair of full-length vanes 69. The dimensions, shape and placement of each shortened vane are the same throughout the module. These shortened vanes 70 are placed in a turbocharger compressor so that the total surface area of the vanes can be increased if the number of vanes and the spacing between the vanes are limited by being densely arranged within the inner diameter of the hub. Similar to the one used.

【0033】

Other design changes in the present invention include changes in manufacturing and molding methods. For example, a substantially cylindrical shape of a vane (or plate) was extruded as a connecting member, then cut to the desired axial length or height and manufactured separately (typically molded). It can also be attached to the top plate. The top plate is molded to have the desired inlet hole and split plate as previously described as a component of the module 21.

【0034】

Another possible design modification in the present invention is to divide the spiral vane module into two parts, one on the top side and one on the bottom side. This manufacturing technique can be used to avoid molding difficulties due to the tight spacing between vanes. After manufacturing the two parts, connect them into a single module. In this case, it is conceivable to mold the top plate together with the top side portion of the vane assembly and the base plate together with the bottom side portion of the vane assembly.

【0035】

The three alternative (spiral) vane types of the spiral vane module 21 and / or FIGS. 7A, 7B and 7C are impulse turbine driven centrifuges, as illustrated in FIGS. 8 and 8A. Can be used in combination with 80. In the following description, the case where the spiral vane module 21 is combined will be described. FIG. 8A schematically shows the impulse turbine device 81.

【0036】

Module 21 of the spiral vane and / or one of the three alternative (spiral) vane types of FIGS. 7A, 7B and 7C is part of the disposable rotor 82 used in the centrifuge. obtain. FIG. 9 contains a spiral vane module 21. It is believed that the disposable rotor 82 of FIG. 9 can also be used in combination with an impulse turbine driven centrifuge such as the centrifuge 80.

【0037】

The impulse turbine driven centrifuge 80 equipped with the impulse turbine device 81 is schematically shown in FIG. The centrifuge 80a incorporates a spiral vane module 91, as in other embodiments of the present invention. The spiral vane module 91 can also be used for other types of centrifuges. Similar to the centrifuge of the above embodiment, the centrifuge 80a includes a bearing pipe 22a having a large number of top-side openings 23a. During operation, the working fluid is supplied to the module 91 of the spiral vane through the opening 23a on the top side of the pipe.

【0038】

As shown in FIGS. 11-14, the spiral vane module 91 comprises a central tube or hub portion 92, a number of vanes 94, and a top plate 95. As shown in FIG. 11, the central tube 92 extends along the rotation center axis L of the centrifuge 80a. The vane 94 extends radially outward from the central canal 92 and also extends along the central axis of rotation L. As shown in FIG. 14, the radial inner edge 98 of each vane 94 is attached to the central canal 92, and the radial outer edge 99 extends away from the central canal 92. The inner edge 98 of the plurality of vanes 94 forms the vane inner diameter VID. Also, the outer edges 99 of the plurality of vanes 94 form the vane outer diameter VOD. In one embodiment, the central tube 92, the vane 94, and the top plate 95 are integrally molded, and the spiral vane module 91 is a member. Although the vane 94 has a spiral shape in the illustrated embodiment, it may have another shape as shown in FIGS. 7A to 7C described above.

【0039】

As shown in FIG. 11, the top plate 95 is attached to the first (inlet side) end 100 of the central canal 92. The end opposite to the first end 100 of the central canal 92 is the second (exit side) end 101. In the present embodiment, the small portion 102 of the central tube 92 extends above the top plate 95, but the top plate 95 may be coplanar with the upper end 103 of the central tube 92. As shown in FIG. 10, the central canal 92 does not extend over the entire length of the vane 94. In the first end portion 100 of the central pipe 92, a plurality of fluid inlet passages 106 are formed by the upper end portion 103 of the central pipe 92 and the inner edge 98 of the vane 94. Similarly, at the second end portion 101, a plurality of fluid outlet passages 107 are formed by the lower end portion 102 of the central canal and the inner edge 98 of the vane 94. In the fluid inlet passage 106, the upper portion 108 of the vane 94 extends upward through the top plate 95. During operation of the centrifuge 80a, the upper portion 108 of the vane 94 prevents fluid from slipping along the top plate 95.

【0040】

As shown in FIG. 11, the top plate 95 includes an inner flat portion 110, an outer inclined portion 111, an outer peripheral edge 112, and an inner peripheral edge 113 attached to the central canal 92. Retention of collection of (submicron) ultrafine particles is achieved when the fluid velocity relative to the rotation of the rotor is minimized. The minimum average relative velocity of the centrifuge 80a in the sludge collection area 50a (see Figure 10) is that the outer edge 112 of the top plate 95 is the distance between the vane inner diameter VID and the vane outer diameter VOD (see Figure 14). Obtained when placed between about 1/4 and 3/4. In particular, the average relative velocity of the sludge collection area 50a is minimized when the outer diameter POD of the top plate 95 is halfway between the vane inner diameter VID and the vane outer diameter VOD. In other words, the optimum diameter of the top plate 95 is approximately the mean of the vane inner diameter VID and the vane outer diameter VOD, in which case the outer edge 112 of the top plate 95 is along the radial direction from the central axis of rotation L. It is at half the length of the measured vane 94. For example, if the inner diameter VID of the spiral vane is about 5 cm (2 inches) and the outer diameter VOD of the spiral vane is about 12.5 cm (5 inches), the optimum diameter of the top plate 95 is about 8.75. It becomes cm (3.5 inches) ((12.5-5) / 2 = 8.75). FIG. 11 illustrates this relationship from another perspective. Here, the width PW of the top plate 95 is half the width VW of the vane 94.

【0041】

Graph 114 of Computational fluid dynamics (CFD) in FIG. 15 shows the effect of placing the outer diameter of the top plate 95 between the inner and outer diameter VIDs of the vane 94. This graph 114 shows the fluid velocity gradient 115 in the fluid passage between adjacent vanes 94 for each of three different conditions. These fluid velocity gradients 115 are in a cross section perpendicular to the central axis of rotation L at the axial midpoint of the rotor (ie, the midpoint between the top plate 95 and the bottom outlet). In graph 114, graph portion 120 shows the distribution of the velocity gradient 115 without the top plate 95 in the centrifuge 80a. Further, the graph portion 121, the speed photographies when the outer diameter POD top plate 95 is substantially half of the vane inner diameter VID and the vane outer diameter VOD showing the distribution of distribution 115. Further, the graph portion 122 shows the distribution of the velocity gradient 115 when the outer diameter POD of the top plate 95 is equal to the vane outer diameter VOD.

【0042】

Comparing with the graph portion 121, it can be seen that a large number of velocity gradients 115 exist in both the case where the top plate 95 is absent and the case where the top plate 95 covers the entire vane 94. In the absence of the top plate 95 (graph portion 121), the volume average of relative velocities across the axial direction of the flow path is 0.023 m / sec. In the illustrated embodiment, the spiral vane module 91 rotates counterclockwise, resulting in a pressure surface 124 being formed on the surface of each vane 94 facing the direction of rotation. As shown in graph portion 120, in the absence of the top surface 95, there are numerous velocity gradients on the pressure surface 124. The spiral vane module 91 may be rotated in the clockwise direction. When the outer diameter POD of the top plate 95 is equal to the vane outer diameter VOD (graph part 122), the volume average of the relative velocities is 0.021 m / sec. As shown in graph portion 122, a number of velocity gradients 115 occur near the outer end 99 of vane 94, where the top plate 95 terminates. If the outer diameter POD of the top plate 95 is half the vane inner diameter VID and the vane outer diameter VOD (graph part 121), the number of velocity gradients 115 should be at either the pressure plane 124 of the vane 94 or near the outer end 99. Is also decreasing. According to this design, the average velocity of the fluid is minimized to 0.006 m / sec. This overall reduction in fluid velocity enhances the ability to collect ultrafine particles.

【0043】

Although the present invention has been described in detail in the above-described embodiment, this is an example and does not limit the scope of the present invention.

[Simple explanation of drawings]

[Figure 1]

It is a full sectional view of the self-driving centrifuge in the typical embodiment of this invention seen from the front.

[Fig. 1A]

It is a partial cross-sectional view of the centrifuge seen from line 1A-1A of FIG.

[Fig. 1B]

FIG. 5 is a partial cross-sectional view of the centrifuge according to another embodiment of the present invention as viewed from the line corresponding to line 1A-1A in FIG.

[Figure 2]

It is a full sectional view of the centrifuge seen from line 2-2 of FIG.

[Fig. 3]

It is a perspective view which shows the module of the spiral vane included in the centrifuge of FIG.

[Fig. 4]

It is a perspective view of the module of the spiral vane of FIG. 3 seen from the bottom side.

[Fig. 5]

It is a figure which shows the two spiral vanes and the flow path in the module of the spiral vanes of FIG.

[Fig. 6]

It is sectional drawing which compared the stacked body of the conical separation plate in the prior art, and the module of the spiral vane of FIG. 3 by this invention side by side side by side.

[Fig. 7A]

It is a top view which shows one alternative form of vane in this invention.

[Fig. 7B]

It is a top view which shows the other alternative form of vane in this invention.

[Fig. 7C]

FIG. 5 is a plan view showing still another alternative form of vanes in the present invention.

[Fig. 8]

It is a full sectional view of the impulse turbine drive type centrifuge in still another embodiment of this invention seen from the front.

[Fig. 8A]

It is a top view which shows the impulse turbine apparatus in the centrifuge of FIG.

[Fig. 9]

It is a full sectional view from the front view of the disposable rotor in still another embodiment of this invention.

[Fig. 10]

It is a full sectional view of the impulse turbine drive type centrifuge in still another embodiment of this invention seen from the front.

[Fig. 11]

It is the full cross-sectional view which looked at the module of the spiral vane used for the centrifuge of FIG. 10 from the front.

[Fig. 12]

It is a front view of the module of the spiral vane of FIG.

[Fig. 13]

It is a perspective view of the module of the spiral vane of FIG.

[Fig. 14]

It is a plan view of the module of the spiral vane of FIG.

[Fig. 15]

It is the figure which calculated the relative fluid velocity in three different designs by fluid analysis.

[Explanation of symbols]

20 Self-driving centrifuge 21 Spiral vane module 22 Bearing pipe (rotor hub) 23 opening 27 Top plate 28 shell 29 base 32 Circular gap 33 Support base plate 34 Jet orifice 37 gap 38 spiral vane 39 Hub part (central canal) 44 split plate 58 Turbulence prevention unit 59 gap 68 vane (flat plate) 69 Super spiral vane 70 shortened vanes 72 Radial line 73 intersection 74 Tangent 91 Spiral vane module 92 Hub part 94 vane 95 top plate