JPWO2007129403A1 - Rotary fluid machine - Google Patents

Abstract

In the rotary fluid machine, the annular working chamber (5) faces the annular wall (3a) on one side of the rotor (3) in the axial direction of the rotating shaft (4) and the annular wall (3a). An annular groove (20b) formed in the housing (2), and a reciprocating partition member (6) is mounted on the housing so as to be movable in a direction parallel to the axis of the rotary shaft, thereby partitioning the annular working chamber. The reciprocating partition member is movable toward the advanced position by the urging mechanism (7), and can be moved between the advanced position and the retracted position retracted from the annular working chamber. An arcuate partition member (8) is formed on the rotor.

Description

  The present invention forms an annular working chamber by an annular wall portion on at least one side of a rotor in the axial direction of a rotating shaft and an annular groove formed in the housing, and a reciprocating partition member mounted on the housing. And a rotary fluid machine in which the reciprocating partition member is moved forward and backward in a direction parallel to the axis of the rotation shaft.

  Conventionally, volumetric fluid machines (fluid pressure pumps, fluid pressure motors) having various complicated structures have been put into practical use. Among them, the rotary fluid machine using the volume change caused by the rotation of the rotor has a relatively simple structure. However, the rotor is equipped with a plurality of vanes, or the rotor is equipped with a plurality of partition members that appear in the radial direction. In the fluid machine, the structure of the rotor and its attached mechanism is complicated.

  Therefore, in the rotary fluid machine proposed by the inventor of the present application (see Patent Document 1), the rotor is rotatably accommodated in a rotor accommodating chamber having a circular cross section in the housing, and the rotating shaft passes through the central portion of the housing and the rotor. The rotor rotates integrally with the rotor, and an annular working chamber is formed outside the outer periphery of the rotor in the rotor accommodating chamber. A first partition member is mounted on the outer side of the annular working chamber of the housing so as to be movable in a direction orthogonal to the axis of the rotating shaft (radial direction), and a spring member that biases the first partition member toward the rotor is mounted. The first partition member is in contact with the inner peripheral surface (the outer peripheral surface of the rotor) of the annular working chamber to partition the annular working chamber.

  A mountain-shaped second partition member (pressure receiving projection or pressure projection) is integrally formed on the outer periphery of the rotor, and the second partition member is in contact with the outer peripheral surface of the rotor accommodating chamber (inner peripheral surface of the housing). The annular working chamber is partitioned. The second partition member that rotates together with the rotor contacts the first partition member, moves the first partition member radially outward, and moves away from the annular working chamber. In the housing, a fluid introduction port is formed in the vicinity of the leading side of the rotor rotation direction with respect to the first partition member, and a fluid outlet port is formed in the vicinity of the trailing side of the rotor rotation direction with respect to the first partition member. .

JP-A-6-108981

  Conventional various rotary fluid machines of a positive displacement type generally have a complicated structure and a high manufacturing cost. In the rotary fluid machine of Patent Document 1, an annular working chamber is formed outside the outer periphery of the rotor by utilizing the space on the outer peripheral side from the rotor. For this reason, the annular working chamber cannot be formed by effectively utilizing the space in the axial direction with respect to the rotor, and the first partition member and the spring member are mounted on the outer peripheral portion of the housing from the annular working chamber. Therefore, the diameter (full height and full width) of the fluid machine becomes large and the size is increased, and the manufacturing cost is also expensive.

  When the radial width of the annular working chamber is increased, the amount of forward / backward movement of the first partition member is increased, so that it is difficult to ensure the responsiveness of the reciprocating operation of the first partition member, and the apparatus is also enlarged. Therefore, if the amount of forward and backward movement of the first partition member is kept within an appropriate range and the width in the axial direction of the annular working chamber is increased, a large-volume annular working chamber can be formed. The dead space increases.

  The first partition member is configured to contact the inner peripheral surface of the annular working chamber (the outer peripheral surface of the rotor). However, since the curvature of the outer peripheral surface of the rotor is not constant, the tip of the first partition member is placed on the outer peripheral surface of the rotor. Since it is difficult to make a surface contact and it is likely to be a line contact, it is difficult to secure a sealing performance for fluid tight partitioning, the durability is lowered, and it cannot be applied to a high pressure fluid. In addition, if the front-end | tip part of a 1st partition member is made into the structure which can be rotated, it can be made to substantially surface contact, but a structure becomes complicated. In addition, since only one set of annular working chambers can be configured in one fluid machine, the degree of freedom of design is poor, and it is difficult to reduce the size or increase the capacity, and the manufacturing cost is high.

  An object of the present invention is to provide a rotary fluid machine whose structure can be simplified, reduced in size or increased in capacity, and to form an annular working chamber by effectively utilizing the space on at least one side of the rotor in the axial direction. Providing a rotary fluid machine capable of fluid sealing, and providing a rotary fluid machine capable of fluid-tight sealing of a sliding portion by surface contact. One rotor can be used as a plurality of sets of fluid pressurizing mechanisms or fluid pressure receiving mechanisms. To provide a rotary fluid machine that can be utilized, to provide a rotary fluid machine that has a remarkably high degree of design freedom, and the like.

  The present invention includes a housing, a rotor housed in the housing so as to be relatively rotatable, and a rotary shaft that penetrates the central portion of the housing and the rotor and rotates integrally with the rotor, and pressurizes fluid. In a rotary fluid machine operable as a pump or a fluid pressure motor that rotationally drives the rotor with fluid pressure, the annular wall portion on at least one side of the rotor in the axial direction of the rotating shaft, and the annular wall portion facing the annular wall portion An annular working chamber formed by an annular groove formed in the housing, an advance position for partitioning the annular working chamber, mounted in the housing so as to be movable in a direction parallel to the axis of the rotation shaft, and retracted from the annular working chamber. At least one reciprocating partition member movable to the retracted position, urging means for urging the reciprocating partition member toward the advanced position, and an annular work formed on the rotor. At least one arcuate partition member for transversely partitioning the chamber, at least a first inclined surface formed on the leading side portion in the rotor rotational direction and capable of driving the reciprocating partition member to the retracted position, and the rotor rotational direction At least one arc-shaped partition member formed on the trailing side portion and having a second inclined surface allowing the return of the reciprocating partition member from the retracted position to the advanced position, and the reciprocating partition member of the housing Formed in the vicinity of the rotor rotating direction leading side, and a fluid introduction port for introducing fluid into the annular working chamber, and formed in the rotor rotating direction trailing side vicinity of the reciprocating partition member of the housing And a fluid outlet port for leading out the fluid from the annular working chamber.

Next, the operation and effect of the rotary fluid machine will be described.
When the rotary fluid machine is a fluid pressure motor, pressurized fluid is introduced from the fluid introduction port, the rotor and the rotation shaft are driven to rotate, and the fluid that has reached zero pressure or low pressure is discharged from the fluid outlet port. The When this rotary fluid machine is a fluid pressure pump, a fluid in a non-pressurized state (or a pressurized state) is introduced from the fluid introduction port and pressurized in the annular working chamber, and the pressurized fluid is derived from the fluid. Derived from the port.

The annular working chamber is composed of an annular wall portion on at least one side of the rotor in the axial direction of the rotation shaft, and an annular groove formed in the housing so as to face the annular wall portion. It is partitioned by at least one reciprocating partition member mounted, and is partitioned by at least one arc-shaped partition member formed on the rotor. The reciprocating partition member and the arc-shaped partition member desirably partition the annular working chamber in a fluid-tight manner, but may have a structure in which fluid leakage occurs.

When the arcuate partition member that rotates together with the rotor reaches the reciprocating partition member with the reciprocating partition member in the advanced position, the reciprocating partition member is placed on the first and second inclined surfaces of the arcuate partition member. Touching in sequence, the position moves from the advanced position to the retracted position, and after passing through the arc-shaped partition member, returns from the retracted position to the advanced position.

  According to this rotary type fluid machine, the structure of the annular machine chamber arranged on at least one side of the rotor in the axial direction is divided by the reciprocating partition member and the arc-shaped partition member, so the structure of the fluid machine is simplified. can do.

  Since it is not necessary to project the reciprocating partition member and the urging means to the outer peripheral side from the annular working chamber, the diameter (full height or full width) of the rotary fluid machine can be reduced and made compact. Since the capacity of the fluid machine can be secured by increasing the radial width of the annular working chamber without increasing the axial width of the annular working chamber so much, It can be configured compactly and manufacturing costs can be reduced.

  By forming the width of the annular working chamber in the axial direction to an appropriate size, the reciprocating partition member can be moved back and forth with high responsiveness while the reciprocating partition member is kept in an appropriate amount. be able to. Since the sliding portion where the reciprocating partition member contacts the rotor, the sliding portion where the arc-shaped partition member contacts the housing, and the sliding portion where the arc-shaped partition member contacts the housing can be structured to be in surface contact, The reliability and durability of the structure in which the moving part is sealed fluid-tight or almost fluid-tight can be ensured.

  Two sets of fluid machines are constructed by arranging annular working chambers on both sides of the rotor, or a plurality of sets of fluid machines are constructed by arranging a plurality of concentric annular working chambers on one or both sides of the rotor. Therefore, it is possible to realize a fluid machine having a very high degree of design freedom.

The following configuration can be adopted as the configuration of the dependent claims of the present invention.
(1) The annular working chambers are provided on both sides of the rotor in the axial direction of the rotating shaft, a reciprocating partition member corresponding to each annular working chamber, an urging means, an arc-shaped partition member, a fluid introduction port, And a fluid outlet port.
(2) The biasing means includes a gas spring.
(3) Most of the compressed gas storage chamber of the gas spring is formed in the wall of the housing.

(4) An engagement guide mechanism is provided for restricting the reciprocating partition member from moving in the circumferential direction while allowing the reciprocating partition member to move forward and backward.
(5) A tip sliding surface capable of fluid-tight contact with a portion of the annular wall surface of the rotor perpendicular to the axis of the rotating shaft, and a circular arc partition member Formed on the first and second inclined surfaces are first and second inclined sliding surfaces capable of fluid-tight contact with each other.

(6) The reciprocating partition member has an inner circumferential arc surface and an outer circumferential arc surface that can make fluid contact with a part of the inner circumferential surface and a part of the outer circumferential surface of the annular working chamber, respectively.
(7) The arc-shaped partition member has an inner peripheral sliding surface and an outer peripheral sliding surface that can be brought into fluid-tight contact with the inner peripheral surface and the outer peripheral surface of the annular working chamber, respectively.
(8) The tip of the arcuate partition member between the first and second inclined surfaces, the tip of the housing-side tip where the most of the back end of the annular groove of the housing can be brought into fluid-tight surface contact with the annular annular wall surface Form a sliding surface.

(9) At least one side of the rotor is formed with a plurality of the annular working chambers concentric with the axis of the rotation shaft by a rotor and a housing, and one or a plurality of return partitions corresponding to the respective annular working chambers. A member, one or a plurality of arc-shaped partition members, and a fluid introduction port and a fluid discharge port corresponding to each return partition member are provided.

(10) One or more return partition members each having a plurality of annular working chambers concentrically with the axis of the rotating shaft formed on both sides of the rotor by a rotor and a housing, each corresponding to each annular working chamber. And one or a plurality of arc-shaped partition members, and fluid introduction ports and fluid outlet ports corresponding to the respective return partition members.

(11) It is configured as a rotary fluid pressure motor, and controls a plurality of direction switching valve means for switching a plurality of fluid passages for supplying pressurized fluid to a plurality of fluid introduction ports, respectively, and the direction switching valve means. Provided with control means, and configured to selectively switch at least one of the rotational speed of the rotary shaft and the torque output from the rotary shaft by selectively switching the plurality of direction switching valve means via the control means. To do.

1 is a perspective view of a rotary fluid machine according to an embodiment of the present invention. It is a longitudinal cross-sectional view (II-II sectional view taken on the line of FIG. 3) of a rotary fluid machine. It is the III-III sectional view taken on the line of FIG. It is a perspective view of the principal part of a housing. It is a front view of a rotor. It is a perspective view of the principal part of a rotor. It is the VII-VII sectional view taken on the line of FIG. 2 (a reciprocating partition member is advancing position). FIG. 8 is a view corresponding to FIG. 7 when the reciprocating partition member is in the retracted position. It is the IX-IX sectional view taken on the line of FIG. It is operation | movement explanatory drawing which shows the state which the 1st inclined surface of the arc-shaped partition member and the 1st inclined sliding surface of the reciprocating partition member contacted. It is operation | movement explanatory drawing which shows the state which the tip sliding surface of the circular arc-shaped partition member and the tip sliding surface of the reciprocating partition member contacted. It is operation | movement explanatory drawing which shows the state which the 2nd inclined surface of the circular arc-shaped partition member and the 2nd inclined sliding surface of the reciprocating partition member contacted. FIG. 3 is a view corresponding to FIG. 2 of a rotary fluid machine of a first modification. FIG. 6 is a view corresponding to FIG. 3 of a rotary fluid machine of a second modification. FIG. 8 is a view corresponding to FIG. 7 showing a rotary fluid machine of a third modification. FIG. 10 is a view corresponding to FIG. FIG. 10 is a view corresponding to FIG. It is sectional drawing of the reciprocating partition member of the example 6 of a change. It is a perspective view of the circular-arc-shaped partition member of the example 7 of a change. FIG. 9 is a view corresponding to FIG. FIG. 6 is a view corresponding to FIG. 5 of a rotary fluid machine of a modification example 8. FIG. 22 is a cross-sectional view of the rotary fluid machine shown in FIG. 21 (corresponding to a cross section taken along line XXII-XXII in FIG. 20). It is a block diagram of the hydraulic multi-stage transmission of the modification 9.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,1A-1H Rotary type fluid machine 2,2B-2H Housing 3,3B, 3G, 3F, 3H Rotor 3a Annular wall part 4,4M Rotating shaft 5,5H1,5H2 Annular working chamber 6,6C, 6D, 6E, 6F, 6H1, 6H2 Reciprocating partition member 6a Inner circular arc surface 6b Outer circular arc surface 6d End sliding surface 6e First inclined sliding surface 6f Second inclined sliding surface 7, 7C Energizing mechanism 8, 8G, 8H1, 8H2 Arc-shaped partition member 8a Inner peripheral sliding surface 8b Outer peripheral sliding surface 8d End sliding surface 8f First inclined surface 8e Second inclined surfaces 9, 9a, 9b Fluid introduction ports 10, 10a, 10b Fluid outlet port 20b Annular groove 40, 40D engagement guide mechanism 60 gas spring 61 compressed gas storage chamber 101, 102 fluid passage 103 electromagnetic direction switching valve 107 control unit

  The rotary fluid machine of the present invention is a positive displacement fluid machine. In this rotary fluid machine, an annular working chamber is provided on the annular wall portion on at least one side of the rotor in the axial direction of the rotation shaft, and the annular wall portion. And an advancing position for partitioning the annular working chamber, wherein at least one reciprocating partition member is movably mounted in the housing in a direction parallel to the axis of the rotation shaft. At least one arc-shaped partition which is movable to a retracted position retracted from the annular working chamber, and the reciprocating partition member is biased toward the advanced position by the biasing means, and partitions the annular working chamber transversely. A member is formed on the rotor.

Embodiments of the present invention will be described below with reference to the drawings.
In the following description, “axial center”, “axial direction”, “radial direction”, and “circumferential direction” are the axial center C and axial direction of the rotating shaft 4 (or the housing 2, the rotor 3, or the annular working chamber 5). , Radial direction and circumferential direction (see FIGS. 1 and 2).

  As shown in FIGS. 1 to 12, the rotary fluid machine 1 includes a housing 2, a rotor 3, a rotating shaft 4, an annular working chamber 5, a pair of reciprocating partition members 6, and a pair of biasing mechanisms 7, 1. A pair of arcuate partition members 8, a pair of fluid inlet ports 9, and a pair of fluid outlet ports 10 are provided. The fluid machine 1 can be operated as a fluid pressure pump (hydraulic pressure pump, gas pressure pump) for pressurizing fluid or a fluid pressure motor (hydraulic motor, air motor) for rotating the rotor 3 with fluid pressure.

  As shown in FIGS. 1 to 4 and 7 to 9, the housing 2 includes first and second housing members 20 and 21 that face each other in the axial direction. A reciprocating partition member 6 and a pair of urging mechanisms 7 are mounted, and a pair of fluid introduction ports 9 and a pair of fluid outlet ports 10 are formed. Shaft holes 20a and 21a are formed at the center of the first and second housing members 20 and 21, and bearings 22 and 23 are fitted into the shaft holes 20a and 21a in an internally fitted manner.

  In the first housing member 20, an annular groove 20b that opens toward the second housing member 21 is formed concentrically with the shaft hole 20a. The annular groove 20b is formed in a rectangular shape in a half section on a plane passing through the axis C. In the second housing member 21, a circular recess 21b that opens toward the first housing member 20 is formed concentrically with the shaft hole 21a and slightly larger in diameter than the annular groove 20b. The outer peripheral wall portion 20 c of the first housing member 20 and the outer peripheral wall portion 21 c of the second housing member 21 are coupled via a seal member 24. The first and second housing members 20 and 21 are fixed by, for example, a plurality of tie bolts (not shown) penetrating the outer peripheral wall portions 20c and 21c.

  Most of the back end of the annular groove 20b of the first housing member 20 is a ring-shaped annular wall surface 20d, and the circular wall surface 21d of the back end of the circular recess 21b of the second housing member 21 is formed in a plane orthogonal to the axis C. Has been. For example, the first and second housing members 20 and 21 have substantially the same axial width, the annular groove 20b and the circular recess 21b have substantially the same axial width, and the first housing member 20 has an axial center. For example, the annular groove 20b is formed in a radial portion having a radius of about 5/10 to 8/10 from the center of the first housing member 20.

  As shown in FIGS. 2, 3, and 5 to 9, the rotor 3 is accommodated in the housing 2 so as to be relatively rotatable. The rotor 3 has a disc portion 25, and a pair of arc-shaped partition members 8 are formed so as to protrude from the disc portion 25 toward the first housing member 20. The disc portion 25 is accommodated in the circular recess 21b of the second housing member 21 so as to be slidable and slidably abuts against the second housing member side end surface other than the annular groove 20b of the first housing member 20. Yes. A shaft hole 25 a and a key groove 25 b are formed at the center of the disc portion 25. Arrows A and B indicate the rotation direction (forward rotation direction) of the rotor 3.

  As shown in FIGS. 1 to 3, 7, and 8, the rotation shaft 4 passes through the central portion of the housing 2 and the rotor 3 and rotates integrally with the rotor 3. The rotary shaft 4 is fitted into the shaft holes 20a and 21a of the first and second housing members 20 and 21 via bearings 22 and 23 so as to be rotatably supported, and the shaft hole 25a of the disk portion 25 of the rotor 3 is supported. The key member 30 is engaged with the key groove 4 a formed in the portion of the rotary shaft 4 that is fitted in the shaft hole 25 a and the key groove 25 b of the disc portion 25. The rotating shaft 4 is prevented from being detached from the housing 2 and the rotor 3 by a pair of ring members 31 that are externally engaged with both ends of the rotating shaft 4 in the axial direction of the housing 2.

  As shown in FIGS. 2, 3, and 7 to 9, the annular working chamber 5 has an annular wall portion 3 a (arc-shaped partition member 8) on one side (first housing member 20 side) of the rotor 3 in the axial direction. The first and second inclined surfaces 8e and 8f) and an annular groove 20b formed in the housing 2 so as to face the annular wall portion 3a. The space between the first housing member 20 and the rotor 3 is sealed by an annular seal member 35 on the inner peripheral side of the annular working chamber 5, and the space between the first housing member 20 and the rotor 3 is disposed on the outer peripheral side of the annular working chamber 5. Sealed with a substantially annular sealing member 36.

  As shown in FIGS. 2, 4, and 7 to 12, the pair of reciprocating partition members 6 are rotationally symmetric about the axis C and are movable in the housing 2 in a direction parallel to the axis C. It is attached to. Each reciprocating partition member 6 is movable between an advance position (see FIGS. 7 and 9) that partitions the annular working chamber 5 and a retracted position (see FIG. 8) that retreats from the annular working chamber 5.

  Each reciprocating partition member 6 includes an inner peripheral circular arc surface 6a in fluid-tight surface contact with a part of the inner peripheral surface of the annular working chamber 5 (the inner peripheral wall surface of the annular groove 20b), and the outer peripheral surface of the annular working chamber 5 ( An outer peripheral circular arc surface 6b in fluid contact with a part of the outer peripheral wall surface of the annular groove 20b, a pair of side surfaces 6c provided approximately 15 degrees apart in the circumferential direction and orthogonal to the circumferential direction, and a tip sliding surface 6d Have The pair of side surfaces 6c are located on a plane passing through the axis C.

  The length of the reciprocating partition member 6 in the axial center direction is, for example, substantially the same as the width of the first housing member 20 in the axial center direction, and the reciprocating partition member 6 is reduced in weight to improve the responsiveness of the reciprocating movement. For this purpose, the reciprocating partition member 6 is formed as a cup-shaped cross-section member having a recess that opens to the opposite side of the rotor 3.

  The reciprocating partition member 6 is fluid-tightly connected to the front end portion on the rotor side of the annular wall surface 3a of the rotor 3 and the surface portion 3a1 orthogonal to the axis C and the front sliding surface 8d of the arcuate partition member 8. A front sliding surface 6d capable of surface contact and first and second inclined sliding surfaces 6e, 6f capable of fluid-tight surface contact with the first and second inclined surfaces 8e, 8f of the arcuate partition member 8, respectively. Is formed.

  In order to mount the pair of reciprocating partition members 6 on the housing 2, the first housing member 20 has a pair of mounting holes 20 e in which the reciprocating partition members 6 are mounted in a substantially fluid-tight manner in an annular shape. It is formed so as to communicate with the groove 20b. A reciprocating partition member 6 is fitted into each mounting hole 20e so as to be slidable in a direction parallel to the axis C, and an annular seal member 45 provides fluid tightness between the reciprocating partition member 6 and the first housing member 20. It is sealed.

  Here, the reciprocating partition member 6 is always mounted in the mounting hole 20e, and when the reciprocating partition member 6 is in the retracted position, about half of the reciprocating partition member 6 protrudes from the mounting hole 20e to the opposite side of the rotor 3. Thus, when the reciprocating partition member 6 is in the advanced position, approximately half of the reciprocating partition member 6 protrudes toward the rotor 3, and the mounting hole 20e advances and retracts between the advanced position and the retracted position of the reciprocating partition member 6. An engagement guide mechanism 40 that restricts movement in the circumferential direction while allowing the movement is configured.

  As shown in FIGS. 2 and 7 to 9, the pair of urging mechanisms 7 urge the pair of reciprocating partition members 6 toward the advanced positions. Each urging mechanism 7 includes a pair of compression coil springs 50. A spring receiving member 51 that receives the compression coil springs 50 is provided in the first housing member 20, and an annular flange portion 51a of the spring receiving member 51 is the first. It is fixed to the housing member 20. The pair of compression coil springs 50 are disposed at different positions in the radial direction, and are mounted in a compressed state between the reciprocating partition member 6 and the spring receiving member 51. The pair of compression coil springs 50 is configured to generate an elastic force larger than the axial fluid force acting on the reciprocating partition member 6 even when the reciprocating partition member 6 is in the advanced position.

  As shown in FIGS. 2, 3, 5, 6, 8, and 10 to 12, the pair of arcuate partition members 8 are located at rotationally symmetric positions about the axis C in the rotor 3. Each arcuate partition member 8 is formed in a fluid-tight manner across the annular working chamber 5. Each arc partition member 8 is formed, for example, so as to protrude from the disk portion 25 of the rotor 3 toward the first housing member 20 over about 85 degrees in the circumferential direction, and is slidably rotatable in the annular groove 20b. Is engaged.

  Each arc-shaped partition member 8 has an inner peripheral sliding surface 8a and an outer peripheral sliding surface 8b that can make fluid contact with the inner peripheral surface and the outer peripheral surface of the annular working chamber 5, respectively, and a rotor rotating direction leading side portion. The first inclined surface 8e formed and capable of driving the reciprocating partition member 6 to the retracted position and the return of the reciprocating partition member 6 formed on the trailing side portion of the rotor rotational direction from the retracted position to the advanced position are allowed. A second inclined surface 8f and a tip sliding surface 8d between the first and second inclined surfaces 8e and 8f are provided. The tip sliding surface 8d is formed at the housing-side tip portion of the arc-shaped partition member 8 so as to be in fluid-tight surface contact with the annular wall surface 20d at the back end of the annular groove 20b of the first housing member 20.

  The tip sliding surface 8d is formed, for example, in an area portion of about 5 degrees in the circumferential direction and parallel to a plane orthogonal to the axis C, and radial line segments 8d1 and 8d2 hypothesized at both ends of the tip sliding surface 8d are It lies on a plane passing through the axis C. The first inclined surface 8e is formed, for example, in a region portion of about 45 degrees in the circumferential direction. The first inclined surface 8e is inclined in the circumferential direction with respect to a plane orthogonal to the axis C (the annular wall surface toward the trailing side). It is formed in an inclined shape so as to approach 20d. A radial line segment 8e1 assumed at the leading end of the first inclined surface 8e is on a plane passing through the axis C. Therefore, the circumferential inclination angle of the first inclined surface 8e increases linearly from the outer peripheral side toward the inner peripheral side. The average inclination angle in the circumferential direction of the first inclined surface 8e is, for example, about 20 degrees.

  The first inclined sliding surface 6e of the reciprocating partition member 6 is formed as an inclined sliding surface that is slightly twisted so as to come into surface contact with the first inclined surface 8e. Note that the region of about 45 degrees is merely an example, and is not limited to about 45 degrees. The inclination angle (about 20 degrees) is merely an example, and is not limited to about 20 degrees.

  The second inclined surface 8f is formed, for example, in an area portion of about 35 degrees in the circumferential direction. The second inclined surface 8f is inclined in the circumferential direction with respect to a plane orthogonal to the axis C (the annular wall surface toward the trailing side). It is formed so as to be separated from 20d. A radial line segment 8f1 imaginary at the trailing end of the second inclined surface 8f is on a plane passing through the axis C. Therefore, the circumferential inclination angle of the second inclined surface 8f increases linearly from the outer peripheral side toward the inner peripheral side. The average inclination angle in the circumferential direction of the second inclined surface 8f is, for example, about 25 degrees. The second inclined sliding surface 6f of the reciprocating partition member 6 is formed as an inclined sliding surface that is slightly twisted so as to come into surface contact with the second inclined surface 8f. The region of about 35 degrees is merely an example, and the present invention is not limited to this. The inclination angle (about 25 degrees) is merely an example, and is not limited to about 20 degrees.

  Radial line segments formed by intersecting an arbitrary plane in which the first and second inclined surfaces 8e and 8f are orthogonal to the circumferential direction (passing through the axis C) are all on the plane orthogonal to the axis C. It should be noted that the portions of the radial line segments 8d1 and 8d2 are preferably formed in a curved shape rather than a folded surface, and the portions of the radial direction line segments 8e1 and 8f1 are preferably formed in a curved shape instead of a folded surface.

  As shown in FIGS. 1, 2, and 4, the pair of fluid introduction ports 9 is formed in the vicinity of the leading side in the rotor rotation direction with respect to the pair of reciprocating partition members 6 in the housing 2. The pair of fluid outlet ports 10 are formed in the vicinity of the reciprocating partition member of the housing 2 in the vicinity of the rotor rotation direction trailing side. The fluid introduction port 9 and the fluid outlet port 10 are formed in communication with the annular working chamber 5 on the outer peripheral wall portion 20c of the first housing member 20, and a fluid introduction pipe (not shown) is connected to each fluid introduction port 9. A fluid outlet pipe (not shown) is connected to each fluid outlet port 10.

  The housing 2, the rotor 3, the rotating shaft 4, and the pair of reciprocating partition members 6 are made of various steel materials, spheroidal graphite cast iron, cast iron, stainless steel, aluminum, aluminum alloy, synthetic resin, FRP (fiber reinforced synthetic resin). ) Or a high-strength ceramic material, but is not limited to these materials.

The operation and effect of the rotary fluid machine 1 described above will be described.
The annular working chamber 5 includes an annular wall portion 3a on one side of the rotor 3 in the axial direction of the rotating shaft 4, and an annular groove 20b formed in the housing 2 so as to face the annular wall portion 3a. The annular working chamber 5 is partitioned by a pair of reciprocating partition members 6 and partitioned by a pair of arc-shaped partition members 8.

  The inner peripheral circular arc surface 6a and the outer peripheral circular arc surface 6b of the pair of reciprocating partition members 6 are in fluid-tight surface contact with a part of the inner peripheral surface and a part of the outer peripheral surface of the annular working chamber 5, respectively. The pair of reciprocating partition members 6 is movable in the direction parallel to the axis C along the advance position and the retract position, and the inner peripheral sliding surface 8a and the outer peripheral slide of the pair of arcuate partition members 8 The pair of arc-shaped partition members 8 together with the rotor 3 and the rotating shaft 4 are rotated around the axis C while the moving surfaces 8b are in fluid-tight contact with the inner and outer peripheral surfaces of the annular working chamber 5, respectively. It is free to rotate.

  When the pair of arcuate partition members 8 rotate together with the rotor 3, the tip sliding surfaces 6 d of the pair of reciprocating partition members 6 at the advanced position are basically the annular wall portions 3 a of the rotor 3. The surface sliding portion 8d of the pair of arcuate partition members 8 is in fluid contact with the surface portion 3a1 orthogonal to the axis C of the rotary shaft 4 and the annular wall surface 20d of the annular groove 20b of the housing 2 is in contact with the surface portion 3a1. Maintain fluid-tight surface contact. However, when the pair of reciprocating partition members 6 and the pair of arcuate partition members 8 overlap in the circumferential direction, a slightly different state is obtained.

  When the pair of arcuate partition members 8 that rotate together with the rotor 3 reach the pair of reciprocating partition members 6, the reciprocating partition members 6 are connected to the first inclined surface 8 e of the arcuate partition member 8, the tip slide. The moving surface 8d and the second inclined surface 8f are sequentially contacted, moved from the advanced position to the retracted position, and returned to the advanced position again after passing through the arcuate partition member 8.

Next, the above will be described in detail with reference to FIGS.
As indicated by a chain line in FIG. 10, the tip sliding surface 6 d of the reciprocating partition member 6 at the advanced position is in surface contact with the surface portion 3 a 1 of the annular wall portion 3 a of the rotor 3. After the leading end of the first inclined surface 8e in the rotor rotational direction comes into surface contact with the first inclined sliding surface 6e of the reciprocating partition member 6, as shown by the solid line in FIG. The reciprocating partition member 6 is driven toward the retracted position. At this time, the volume of the space between the reciprocating partition member 6 and the arc-shaped partition member 8 is reduced to zero.

  Next, as shown in FIG. 11, when the reciprocating partition member 6 is driven to the retracted position by the first inclined surface 8 e, the tip sliding surface 8 d of the arc-shaped partition member 8 is moved to the reciprocating partition member 6. After the surface contact with the tip sliding surface 6d, the second inclined surface 8f of the arcuate partition member 8 permits the reciprocating partition member 6 to return to the advanced position.

  In this case, as shown by a solid line in FIG. 12, the second inclined sliding surface 6 f of the reciprocating partition member 6 urged toward the advanced position by the urging mechanism 7 is the second inclined sliding surface 6 f of the arc-shaped partition member 8. The reciprocating partition member 6 moves back toward the advanced position while being in surface contact with the inclined surface 8f, and then, as shown by a chain line in FIG. 12, the tip sliding surface 6d of the reciprocating partition member 6 at the advanced position. However, the surface contact with the surface portion 3a1 of the annular wall 3a of the rotor 3 is completed, and the passage of the arc-shaped partition member 8 is completed. At this time, the volume of the space between the reciprocating partition member 6 and the arcuate partition member 8 increases from zero.

  As shown in FIG. 2, in this rotary fluid machine 1, the annular working chamber 5 is partitioned into a pair of working compartments 5a by a pair of reciprocating partition members 6, and the rotor rotating direction trailing side of each working compartment 5a. The fluid introduction port 9 communicates with the end portion, and the fluid outlet port 10 communicates with the leading end portion in the rotor rotation direction of each working partition chamber 5a. When the rotor 3 rotates, fluid is introduced from the fluid introduction port 9 into the volume expansion space 5 a 1 on the trailing side of the rotor rotation direction from the arc-shaped partition member 8 in each working compartment 5 a, and from the arc-shaped partition member 8. Also, the fluid is discharged to the fluid outlet port 10 from the volume contraction space 5a2 on the leading side in the rotor rotation direction.

  When this rotary fluid machine 1 is used as a fluid pressure pump (liquid pressurization pump or gas pressurization pump), the rotary shaft 4 is rotationally driven by a rotational drive means (not shown) such as an electric motor, and the rotor 3 and a pair of arc-shaped partition members 8 rotate, and the fluid (liquid or gas) introduced into the pair of volume expansion spaces 5a1 from the fluid introduction port 9 by these arc-shaped partition members 8 is a pair of Pressurized in the volumetric contraction space 5 a 2 and discharged from the pair of fluid outlet ports 10.

On the other hand, when the rotary fluid machine 1 is used as a fluid pressure motor (hydraulic motor or air motor), a pressurized fluid (acceleration) is applied from a pair of fluid introduction ports 10 to a pair of volume expansion spaces 5a1 of the annular working chamber 5. Pressure oil, pressurized air) is introduced, and the fluid pressure of these pressurized fluids acts on the pair of arcuate partition members 8 to generate rotational torque, and together with the pair of arcuate partition members 8, the rotor 3. Is driven to rotate. In this fluid pressure motor, since the two arc-shaped partition members 8 receive the fluid pressure, the generated torque T is T = 2 × Sa × P × R.
However, Sa is the rectangular sectional area of the annular working chamber 5 (one-side sectional area in the plane passing through the axis C), P is the fluid pressure, and R is the radius from the axis to the annular working chamber 5. It is.

  When used as a fluid pressure motor, the first and second inclined surfaces 8e and 8f of the arcuate partition member 8 are preferably formed at equal inclination angles (first and second inclined surfaces 8e and 8f). From the forward operation mode in which the fluid pressure is supplied to the fluid inlet port 9 and the fluid is discharged from the fluid outlet port 10. The rotation direction of the fluid pressure motor can be reversed by switching to the reverse operation mode in which the fluid pressure is supplied to the fluid and the fluid is discharged from the fluid introduction port 9.

  The first and second inclined sliding surfaces 6e and 6f formed at the front end of the reciprocating partition member 6 are not essential, and in the case of a fluid machine having a low fluid pressure, the first and second inclined sliding surfaces. The moving surfaces 6e and 6f may be omitted, and the tip sliding surface 6d may be formed in a partial cylindrical surface shape.

  In the fluid machine 1 described above, one annular working chamber 5 is formed on one side of the rotor 3, but a plurality of annular working chambers are formed concentrically, and a reciprocating partition member 6 corresponding to each annular working chamber is attached. Rotating fluid provided with a plurality of sets of fluid machines having a plurality of sets of fluid pressurizing mechanisms or fluid pressure receiving mechanisms by providing a biasing mechanism 7, an arc-shaped partition member 8, a fluid introduction port 9, a fluid outlet port 10, and the like It is also possible to implement a machine.

According to the rotary fluid machine 1 described above, the following effects can be obtained.
(1) The rotary fluid machine 1 includes a housing 2, a rotor 3, a rotary shaft 4, an annular working chamber 5, a pair of reciprocating partition members 6, a pair of biasing mechanisms 7, and a pair of arc-shaped partition members. 8, a simple structure including a pair of fluid introduction ports 9 and a pair of fluid outlet ports 10, and the structure of the rotary fluid machine 1 can be significantly simplified as compared with a conventional rotary fluid machine. it can.
In particular, the rotary fluid machine 1 employs a structure in which the annular working chamber 5 disposed on at least one side of the rotor 3 in the axial direction is partitioned by the reciprocating partition member 6 and the arc-shaped partition member 8. The structure of the machine 1 can be simplified.

(2) Since it is not necessary to project the reciprocating partition member 6 and the urging mechanism 7 to the outer peripheral side from the annular working chamber 5, the diameter (full height or full width) of the fluid machine 1 is reduced to reduce the size or increase the capacity. be able to. Since the capacity of the fluid machine 1 can be increased by increasing the radial width of the annular working chamber 5 without increasing the width of the annular working chamber 5 in the axial direction, the fluid machine 1 can be increased as a whole. It can be configured compactly and the manufacturing cost can be reduced.

(3) By forming the width of the annular working chamber 5 in the axial direction in an appropriate size, the reciprocating partition member 6 is suppressed in an appropriate size and the reciprocating partition member 6 has a high response. You can move forward and backward with sex. The sliding part in which the reciprocating partition member 6 contacts the rotor 3 and the sliding part in contact with the first housing 20 and the sliding part in which the arcuate partition member 8 contacts the first housing 20 have a surface contact structure. Therefore, it is possible to ensure the reliability and durability of the structure in which the sliding portion is sealed in a fluid-tight or almost fluid-tight manner.

(4) Two sets of fluid machines are configured by disposing the annular working chambers 5 on both sides of the rotor 3, or a plurality of concentric annular working chambers 5 are disposed on one or both sides of the rotor 3. Therefore, a fluid machine having a very high degree of design freedom can be realized.
(5) The rotary fluid machine 1 can be applied as a fluid pressure pump having various uses, capacities and discharge pressures, and as a fluid pressure motor having various uses, capacities and fluid pressures.

Next, a modified example in which the rotary fluid machine 1 is partially changed will be described.
However, the same or similar members as those of the rotary fluid machine 1 are denoted by the same or similar reference numerals, and description thereof is omitted.

  1) In the rotary fluid machine 1A shown in FIG. 13, a reciprocating partition member 6, an urging mechanism 7, an arc-shaped partition member 8, a fluid introduction port 9, and a fluid outlet port 10 are provided. In a large rotary fluid machine, three or more sets of the reciprocating partition member 6, the biasing mechanism 7, the arc-shaped partition member 8, the fluid introduction port 9, and the fluid outlet port 10 can be provided.

  2) In the rotary fluid machine 1B shown in FIG. 14, the annular working chambers 5 are provided on both sides of the rotor 3B in the axial direction of the rotating shaft 4, and the reciprocating partition members 6 corresponding to the respective annular working chambers 5; An urging mechanism 7, an arc-shaped partition member 8, a fluid introduction port 9, and a fluid outlet port 10 are provided. This rotary fluid machine 1B is suitable for a large fluid machine. However, it can also be applied to small fluid machines.

  The housing 2B has a pair of housing members 20B facing each other in the axial direction, and these outer peripheral wall portions are fixed by a plurality of tie bolts with a seal member 24B interposed therebetween. The rotating shaft 4 is connected to the rotor 3B so as not to rotate relative to the rotor 3B. The rotating shaft 4 is rotatably supported at the center of a pair of housing members 20B via a bearing 22B. A space between the housing member 20B and the rotor 3 is sealed by an annular seal member 35B on the inner peripheral side from each annular working chamber 5, and a portion between the housing member 20B and the rotor 3 is substantially annular on the outer peripheral side from each annular working chamber 5. The sealing member 36B is sealed.

  Here, the reciprocating partition member 6, the urging mechanism 7, the arc-shaped partition member 8, the fluid introduction port 9, and the fluid outlet port 10 corresponding to each annular working chamber 5 may each be provided, or a plurality of sets may be provided. May be. However, when multiple sets of them are provided, the fluctuation range of the rotational torque load is minimized in the fluid pressure pump, and the fluctuation width of the output rotational torque is minimized in the fluid pressure motor. It is desirable to select an arrangement position in the circumferential direction.

  3) In the rotary fluid machine 1 </ b> C shown in FIG. 15, the urging mechanism 7 </ b> C is configured by a gas spring 60 that operates with a compressed gas G (for example, compressed nitrogen gas). Most of the compressed gas storage chamber 61 of the gas spring 60 is formed in the wall portion of the housing 2C. The reciprocating partition member 6 </ b> C has a cup-shaped cross section, is mounted in a mounting hole 20 e formed in the first housing member 20 </ b> C so as to be slidable in a direction parallel to the axis, and is fluidized by a plurality of annular seal members 62. It is tightly sealed.

  An annular groove 20f concentric with the annular working chamber 5 is formed from the outer surface on the opposite side to the rotor 3 on the inner peripheral side portion of the first housing member 20C from the annular working chamber 5, and the annular groove 20f is formed as an annular lid member. An annular housing chamber 64 that is hermetically closed by welding 63 and forms the majority of the compressed gas housing chamber 61 is formed. A cover member 65 is disposed on the opposite side of the mounting hole 20e from the rotor 3 so as to allow the reciprocating partition member 6 to move forward and backward, and an annular flange portion 65a of the cover member 65 is a first housing member. The mounting hole 20e and the annular lid member 63 are partially airtightly fixed in 20C.

  A communication hole 63 a is formed in a part of the annular lid member 63, and the communication chamber 63 communicates with the inner space of the cover member 65 through the communication hole 63 a, and the reciprocating partition member 6 C is compressed in the compressed gas storage chamber 61. It is comprised so that the gas pressure of gas may be received. That is, the compressed gas storage chamber 61 is composed of the annular storage chamber 64, the cover member 65, and the reciprocating partition member 6. The reciprocating partition member 6C is moved toward the advanced position by the gas pressure in the compressed gas storage chamber 61. Be energized.

  Since the volume of the compressed gas storage chamber 61 can be increased, the fluctuation of the gas pressure due to the forward / backward movement of the reciprocating partition member 6C becomes very small, and the reciprocating partition member 6C is biased with a substantially constant biasing force. can do. Since most of the annular housing chamber 64 of the gas spring 60 can be formed in the wall portion of the housing 2, the rotary fluid machine 1 </ b> C does not increase in size because the gas spring 60 is provided.

  When the temperature of the fluid machine 1C increases, the gas pressure of the gas spring 60 increases, so the compressed gas storage chamber 61 may be connected to a small accumulator. The compressed gas storage chamber 61 of the gas spring 60 may be formed outside the wall portion of the housing 2C, and the reciprocating partition member 6 may be urged by the output rod of the gas spring. As other biasing means for biasing the reciprocating partition member 6C toward the advanced position, various elastic members such as a leaf spring, a disc spring, and a synthetic resin foam, an air cylinder, a hydraulic cylinder connected to an accumulator, and the like Various fluid pressure biasing means can be applied.

  4) In the rotary fluid machine 1D shown in FIG. 16, the engagement guide mechanism 40D has an engagement extending in a direction parallel to the axial centers formed on the inner peripheral wall portion and the outer peripheral wall portion of the annular groove 20b of the first housing member 20D. Grooves 70 and 71 are provided, and the engagement grooves 70 and 71 are slidably engaged with the radially inner end and the radially outer end of the reciprocating partition member 6D so that the reciprocating partition member 6D advances. It is configured not to move in the circumferential direction even when fluid pressure is applied while allowing forward and backward movement over the position and the retracted position.

  5) In the rotary fluid machine 1E shown in FIG. 17, in the rotary fluid machine 1D shown in FIG. 16, the inner peripheral wall portion of the annular groove 20b of the first housing member 20E and the radially inner end portion of the reciprocating partition member 6E. A seal member 72 that seals the gap is mounted, and a seal member 73 that seals between the outer peripheral wall of the annular groove 20b of the first housing member 20E and the radially outer end of the reciprocating partition member 6E is mounted. . It is to be noted that the engagement guide mechanism 40D shown in FIG. 17 can also be adopted in the rotary fluid machine 1 of the main embodiment.

  6) As shown in FIG. 18, the tip sliding surface 6d, the first inclined sliding surface 6e, and the second inclined sliding surface 6f of the reciprocating partition member 6F are excellent in solid lubricity made of metal or nonmetal. The seal members 80 to 82 may be mounted respectively.

  7) As shown in FIG. 19, a seal member that is excellent in solid lubricity made of metal or non-metal on the inner peripheral sliding surface 8a, the outer peripheral sliding surface 8b, and the tip sliding surface 8d of the arc-shaped partition member 8. 85 to 87 may be mounted respectively.

  8) In the rotary fluid machine 1H shown in FIGS. 20 to 23, two annular working chambers 5H1 and 5H2 that are concentric with the axis of the rotary shaft 4 are respectively provided on both sides of the rotor 3H in the axial direction. The annular working chambers 5H1 on both the left and right sides in FIG. 22 are formed symmetrically with respect to the rotor 3H, but may be formed asymmetrically. Although the annular working chambers 5H2 on the left and right sides are formed symmetrically with respect to the rotor 3H, they may be formed asymmetrically. In the example shown in FIG. 22, the shape of the cross section on one side in the plane including the axis of the rotating shaft 4 of the annular working chambers 5H1 and 5H2 is the same, but the cross sectional shape and the cross sectional area may be different. .

  One reciprocating partition member 6H1, 6H2, one urging mechanism 7H1, 7H2, one arcuate partition member 8H1, 8H2, and each of the four annular working chambers 5H1, 5H2, Fluid introduction ports 9a and 9b and fluid outlet ports 10a and 10b corresponding to the reciprocating partition members 6H1 and 6H2 are provided.

The housing 2H has a pair of housing members 20H opposed in the axial direction, and these outer peripheral wall portions are fixed by a plurality of tie bolts with a seal member 24 interposed therebetween. The rotating shaft 4 is connected to the rotor 3H so as not to rotate relative to the rotor 3H, and the rotating shaft 4 is rotatably supported via a bearing 22 at the center of a pair of housing members 20H.
Each housing member 20H and the rotor 3H are sealed by an annular seal member 90 on the inner peripheral side from the annular working chamber 5H1, and are annular on the outer peripheral side from the annular working chamber 5H1 and on the inner peripheral side from each annular working chamber 5H2. Sealed by a seal member 91 and sealed by a substantially annular seal member 92 on the outer peripheral side from the annular working chamber 5H2.

  The two reciprocating partition members 6H1, the two arc-shaped partition members 8H1, the two reciprocating partition members 6H2, and the two arc-shaped partition members 8H2 are provided at positions that differ by 180 degrees in the rotational direction. On one side of the rotor 3H, the reciprocating partition member 6H1 is at a position shifted 90 degrees toward the trailing side with respect to the reciprocating partition member 6H2, and the arc-shaped partition member 8H1 is located with respect to the arc-shaped partition member 8H2. It is at a position shifted 90 degrees to the trailing side. Thereby, the fluctuation range of the rotational torque load when used as a fluid pressure pump can be reduced, and the fluctuation range of the output torque output when used as a fluid pressure motor can be reduced.

  A fluid introduction port 9a and a fluid outlet port 10a corresponding to the annular working chamber 5H1 are formed in the side wall portion of each housing member 20H facing the annular working chamber 5H1, and the annular working chamber 5H2 is formed on the outer peripheral wall portion of each housing member 20H. Corresponding fluid introduction ports 9b and fluid outlet ports 10b are formed. The reciprocating partition members 6H1 and 6H2, the biasing mechanisms 7H1 and 7H2, the arc-shaped partition members 8H1 and 8H2, the fluid introduction ports 9a and 9b, and the fluid outlet ports 10a and 10b corresponding to the annular working chambers 5H1 and 5H2, respectively. Each of them may have a plurality of sets.

  According to the fluid machine 1H, since the fluid pressurizing mechanism or the fluid pressure receiving mechanism can be configured by effectively utilizing the space on both sides of the axis of the rotor 3H, the capacity of the fluid machine can be increased and the size can be reduced. When used as a fluid pressure pump, a plurality of discharge pressures can be generated from a plurality of annular working chambers, and when used as a fluid pressure motor, the fluid pressure to the plurality of annular working chambers can be generated. By switching the supply, a plurality of rotation speeds and / or output torques can be generated.

  In the above example, two concentric annular working chambers are formed on both sides in the axial direction of the rotor 3H. However, three or more sets of fluid pressurizing mechanisms including three or more annular working chambers or A fluid pressure receiving mechanism may be formed. Alternatively, a fluid pressurizing mechanism or a fluid pressure receiving mechanism including a plurality of concentric annular working chambers may be provided only on one side of the rotor 3H in the axial direction.

  9) The hydraulic multi-stage transmission 100 shown in FIG. 23 has the same structure as the rotary hydraulic motor 1M having the same structure as the rotary fluid machine 1H shown in FIGS. 20 to 22 and the rotary fluid machine 1B shown in FIG. The hydraulic pump 1P, fluid passages 101 and 102, four electromagnetic direction switching valves 103, and the like are included.

  The rotary shaft 4P of the hydraulic pump 1P is connected to the output shaft 104a of the internal combustion engine 104, the hydraulic pump 1P is driven by the internal combustion engine 104, the pressurized oil is discharged from the hydraulic pump 1P, and the total amount of the pressurized oil is The fluid is supplied to the hydraulic motor 1M through the fluid passages 101 and 102. The fluid outlet port of the hydraulic pump 1P is connected to the fluid passage 101, and four fluid passages 102 branched from the fluid passage 101 are connected to the four fluid introduction ports 9a and 9b of the hydraulic motor 1M, respectively. Each fluid passage 102 is provided with a three-port electromagnetic direction switching valve 103.

  An oil tank 105 is provided that supplies hydraulic oil to the hydraulic pump 1P and is supplied with hydraulic oil having a drain pressure from the hydraulic motor 1M. Each electromagnetic direction switching valve 103 supplies the pressurized oil in the fluid passage 102 to the hydraulic motor 1M. It is configured to selectively switch between a pressurized oil supply position to be supplied and a hydraulic oil supply position to supply the hydraulic oil in the oil tank 105 to the hydraulic motor 1M, and the four electromagnetic direction switching valves 103 are provided from the operation unit 106. Is electrically connected to a control unit 107 that controls the four electromagnetic directional control valves 103 based on the command.

For example, if the discharge amount of the pressurized oil from the hydraulic pump 1P is constant, the control unit 107 selectively switches the four electromagnetic direction switching valves 103 to the pressurized oil supply position, so that the hydraulic motor 1M The rotational speed and output torque of the rotating shaft 4M can be switched in a plurality of ways. For example, as shown in Table 1, by selectively switching the four electromagnetic direction switching valves 103 to the pressurized oil supply position, it is possible to perform switching in eight ways from the first gear to the eighth gear. In Table 1, “left side” and “right side” indicate “left side” and “right side” in the fluid machine 1H shown in FIG.

  For example, the rotational speed of the rotating shaft 4M gradually increases from the first gear to the eighth gear, and the output torque decreases. However, for example, the first to fourth speed stages are decelerated (the rotating shaft 4M is lower than the output shaft 104a), and the fifth to eighth speed stages are increased (the rotating shaft 4M is more than the output shaft 104a). It is also possible to set it to be (high speed). When the rotational speed of the internal combustion engine 104 increases, the discharge amount from the hydraulic pump 1P increases, and when the load of the hydraulic motor 1M increases, the hydraulic pressure of the pressurized oil increases.

The hydraulic pump 1P and the hydraulic motor 1M can be combined integrally and the electromagnetic direction switching valve 103 and the fluid passages 101 and 102 can be three-dimensionally incorporated therein.
As the hydraulic motor 1M, in addition to the rotary fluid machine 1H, one in which a plurality of annular working chambers are formed only on one side in the axial direction of the rotor 3F, or the rotary fluid machine 1B in FIG. 14 is also applicable. As the hydraulic pump 1P, the above-described various rotary fluid machines 1, 1A to 1F can be applied. However, various existing pumps can be employed as the hydraulic pump 1P.

  Various driving machines other than the internal combustion mechanism 104 can be adopted as the driving machine. By selectively switching the plurality of electromagnetic direction switching valves 103 via the control unit 107, it is possible to switch between one of the rotational speed of the rotating shaft 4 and the torque output from the rotating shaft 4. is there. The hydraulic multi-stage transmission 100 can be applied to multi-stage transmissions of various vehicles, and can be applied to multi-stage transmissions of various industrial machines other than vehicles.

  10) In addition, various modifications other than the above-described disclosure are added and the housing 2, the rotor 3, the annular working chamber 5, and the pair of reciprocating partition members 6 and 1 are added without departing from the spirit of the present invention. It can be implemented by appropriately changing the size and shape of the pair of arcuate partition members 8 and the like.

  The rotary fluid machine 1 of the present invention is a fluid machine having various uses, capacities, discharge pressures or fluid pressures, and quantifies liquid pressurization pumps, gas pressurization pumps, hydraulic motors, air motors, and fluids (particularly liquids). It can be applied to weighing devices that distribute each item.

Claims (12)

A fluid pressure pump or a fluid pressure comprising a housing, a rotor accommodated in the housing so as to be relatively rotatable, and a rotating shaft that passes through the housing and a central portion of the rotor and rotates integrally with the rotor, and pressurizes a fluid. In a rotary fluid machine operable as a fluid pressure motor that rotationally drives the rotor at
An annular working chamber composed of an annular wall portion on at least one side of the rotor in the axial direction of the rotating shaft and an annular groove formed in the housing so as to face the annular wall portion;
At least one reciprocating partition member which is mounted on the housing so as to be movable in a direction parallel to the axis of the rotary shaft and is movable between an advance position for partitioning the annular working chamber and a retracted position retracted from the annular working chamber; ,
Biasing means for biasing the reciprocating partition member toward the advanced position;
At least one arc-shaped partition member formed in the rotor and transversely partitioning the annular working chamber, and formed in at least a leading side portion in the rotor rotation direction and capable of driving the reciprocating partition member to the retracted position. At least one arcuate partition member having one inclined surface and a second inclined surface that is formed on the rotor rotation direction trailing side portion and allows the reciprocating partition member to return from the retracted position to the advanced position;
A fluid introduction port formed in the vicinity of the leading side of the rotor rotation direction with respect to the reciprocating partition member of the housing for introducing fluid into the annular working chamber, and a rotor for the reciprocating partition member of the housing A fluid outlet port formed in the vicinity of the rotational direction trailing side for extracting fluid from the annular working chamber;
A rotary fluid machine comprising: Providing the annular working chamber on both sides of the rotor in the axial direction of the rotating shaft;
2. The rotary fluid according to claim 1, further comprising a reciprocating partition member corresponding to each annular working chamber, a biasing means, an arc-shaped partition member, a fluid introduction port, and a fluid outlet port. machine.   The rotary fluid machine according to claim 1, wherein the biasing means is a gas spring.   4. The rotary fluid machine according to claim 3, wherein most of the compressed gas storage chamber of the gas spring is formed in a wall portion of the housing.   3. The engagement guide mechanism is provided for restricting the reciprocating partition member from moving in a circumferential direction while allowing advancing and retreating movement between an advancing position and a retracting position of the reciprocating partition member. Rotary fluid machine.   A tip-side sliding surface capable of fluid-tight contact with a surface portion orthogonal to the axis of the rotary shaft of the annular wall surface of the rotor on the rotor-side tip portion of the reciprocating partition member, and first and second arc-shaped partition members 6. The rotary fluid machine according to claim 5, wherein the first inclined surface and the second inclined sliding surface capable of fluid contact with each other are formed on the second inclined surface.   6. The reciprocating partition member has an inner circular arc surface and an outer circular arc surface that can make fluid contact with a part of the inner peripheral surface and a part of the outer peripheral surface of the annular working chamber, respectively. A rotary fluid machine according to 1.   6. The arcuate partition member has an inner peripheral sliding surface and an outer peripheral sliding surface that can make fluid-tight contact with the inner peripheral surface and the outer peripheral surface of the annular working chamber, respectively. Rotary fluid machine.   A tip sliding surface in which most of the innermost end of the annular groove of the housing is in fluid-tight surface contact with the annular annular wall surface between the first and second inclined surfaces of the arcuate partition member. The rotary fluid machine according to claim 8, wherein:   A plurality of the annular working chambers concentric with the axis of the rotation shaft are formed on at least one side of the rotor by a rotor and a housing, and one or a plurality of reciprocating partition members respectively corresponding to the respective annular working chambers; 2. The rotary fluid machine according to claim 1, wherein one or a plurality of arc-shaped partition members and a fluid introduction port and a fluid discharge port corresponding to each of the reciprocating partition members are provided.   A plurality of annular working chambers concentric with the axis of the rotating shaft are formed on both sides of the rotor by a rotor and a housing, and one or a plurality of reciprocating partition members respectively corresponding to the respective annular working chambers, 2. The rotary fluid machine according to claim 1, further comprising a plurality of arc-shaped partition members and a fluid introduction port and a fluid discharge port corresponding to each of the reciprocating partition members. Configured as a rotary fluid pressure motor,
A plurality of direction switching valve means for switching a plurality of fluid passages for supplying pressurized fluid to a plurality of fluid introduction ports, respectively, and a control means for controlling the direction switching valve means;
It is characterized in that at least one of the rotational speed of the rotating shaft and the torque output from the rotating shaft is switched in plural ways by selectively switching a plurality of direction switching valve means via the control means, The rotary fluid machine according to claim 11.