JP2014129782A - Radial piston type hydraulic machine and wind power generation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a radial piston type hydraulic machine having high productivity, and a wind power generation device.SOLUTION: A radial piston type hydraulic machine comprises: a plurality of pistons 22 arranged along radial directions of the hydraulic machine; a cylinder block 26 provided with a plurality of cylinders 24 for guiding the plurality of pistons respectively so as to allow reciprocation along the radial directions; and a ring cam 29A including a plurality of lobes 31 arranged along the circumferential direction of the hydraulic machine, opposed to the plurality of pistons, and configured rotatably so that the lobes move in the circumferential direction relatively with respect to the plurality of pistons. The plurality of cylinders include cylinder groups formed by a plurality of cylinders located at different positions in the axial direction of the hydraulic machine, and the plurality of lobes extend linearly in the axial direction over cylinder distribution ranges in the axial direction in the cylinder groups respectively.

Description

  The present disclosure relates to a radial piston hydraulic machine and a wind power generator including the same.

Conventionally, a radial piston type hydraulic machine in which a plurality of pistons are arranged radially is known.
For example, Patent Document 1 discloses a radial piston type hydraulic pump used in a power transmission device. This hydraulic pump includes an outer race having a cam surface on the inner peripheral surface and an inner race having a plurality of cylinders arranged radially facing the outer race. Each of the plurality of cylinders of the inner race is configured to guide a plurality of pistons. Each piston is provided with a ball that comes into contact with the cam surface.

  Patent Document 2 discloses a radial piston hydraulic machine that functions as a drive train for a wind turbine generator. The radial piston hydraulic machine described in Patent Document 2 includes a piston that reciprocates in a cylinder, a roller attached to the piston, and a cam having a cam surface that contacts the roller.

  For example, in the hydraulic pump described in Patent Document 3, a plurality of cams are arranged along the axial direction of the main shaft. From the viewpoint of reducing the vibration of the hydraulic pump, the phases of the plurality of cams are shifted from each other.

JP 2010-19192 A US Patent Publication No. 2010/0040470 International Publication No. 2012/073277

  As disclosed in Patent Document 3, when the phases of a plurality of cams are shifted from each other, it takes time to attach the cam to the main shaft in order to adjust the phase of each cam.

  An object of at least one embodiment of the present invention is to provide a radial piston hydraulic machine and a wind power generator having high productivity.

A radial piston hydraulic machine according to at least one embodiment of the present invention,
A plurality of pistons arranged along a radial direction of the hydraulic machine;
A cylinder block provided with a plurality of cylinders for respectively guiding the plurality of pistons so as to be capable of reciprocating along the radial direction;
The lobe has a plurality of lobes arranged along the circumferential direction of the hydraulic machine, is provided to face the plurality of pistons, and rotates so that the lobes move in the circumferential direction relative to the plurality of pistons. A ring cam configured to be possible,
The plurality of cylinders includes a cylinder group formed by a plurality of cylinders having different positions in the axial direction of the hydraulic machine,
Each of the plurality of lobes extends linearly in the axial direction over the axial distribution range of the cylinders in the cylinder group.

  In the radial piston hydraulic machine, the plurality of lobes extend linearly in the axial direction, so that the ring cam can be easily attached. For this reason, the radial piston hydraulic machine has high productivity.

  In some embodiments, for a plurality of cylinders of the cylinder group arranged along the circumferential direction in one section in the axial direction, along the circumferential direction in another section in the axial direction. At least one cylinder among the plurality of cylinders of the arranged cylinder group is displaced in the circumferential direction.

  In this configuration, two cylinders having different axial positions are arranged with the circumferential positions shifted, so that the phase of the reciprocating motion of the pistons in the two cylinders is shifted even if the lobe extends in the axial direction. be able to. Thereby, generation | occurrence | production of the pulsation and vibration in a radial piston type hydraulic machine can be prevented, and the noise reduction of a radial piston type hydraulic machine can be achieved.

In some embodiments, further comprising a plurality of rollers provided for each of the plurality of pistons between the plurality of pistons and the ring cam,
The ring cam is configured to be movable in the axial direction relative to the plurality of rollers so that the contact positions with the plurality of rollers are shifted.

  In this configuration, the life of the ring cam can be extended by moving the ring cam relatively in the axial direction and shifting the position of contact with the plurality of rollers, thereby extending the life of the radial piston hydraulic machine. it can.

  In some embodiments, a radial piston hydraulic machine includes at least one thrust-free bearing provided between a rotor part of the hydraulic machine including the ring cam and a stator part of the hydraulic machine including the cylinder block. A displacement restricting portion for restricting relative displacement of the rotor portion in the axial direction with respect to the stator portion, wherein the displacement restricting portion is in a state where the relative displacement is restricted, and the restriction of the relative displacement is released. It is configured to be able to switch between the two states.

According to this configuration, even if the ring cam can move in the axial direction relative to the roller, the displacement can be restricted by the displacement restricting portion. As a result, the ring cam rotates stably, and the operation of the radial piston hydraulic machine is stabilized.
On the other hand, according to this configuration, the ring cam can be easily moved in the axial direction relative to the roller by releasing the restriction of the relative displacement by the displacement restricting portion.

  In some embodiments, the ring cam is formed by an integrated body that is continuous in the circumferential direction and the axial direction.

When the ring cam is composed of a plurality of members, a step or a protrusion is generated on the cam surface due to the presence of a joint portion or a fastening member between the members. In this case, the surface pressure between the ring cam and the member in contact with the ring cam may suddenly increase due to the presence of steps or protrusions.
On the other hand, by integrally forming the ring cam, the step in the lobe can be substantially eliminated, and a sudden increase in surface pressure can be prevented. As a result, the life of the ring cam and the member in contact with the ring cam is extended, and the life of the radial piston hydraulic machine is also extended.
Further, by preventing a sudden increase in the surface pressure, it is possible to suppress pulsation and vibration, and to reduce the noise of the radial piston hydraulic machine.

A wind turbine generator according to at least one embodiment of the present invention,
At least one blade,
A hub to which the at least one blade is mounted;
A hydraulic pump configured to be driven by rotation of the hub;
A hydraulic motor configured to be driven by pressure oil generated by the hydraulic pump;
A wind turbine generator comprising a generator driven by the hydraulic motor,
At least one of the hydraulic pump and the hydraulic motor is a radial piston hydraulic machine,
The hydraulic machine includes a plurality of pistons arranged along a radial direction of the hydraulic machine, and a cylinder provided with a plurality of cylinders for respectively guiding the plurality of pistons so as to be capable of reciprocating along the radial direction. The lobe has a block and a plurality of lobes arranged along the circumferential direction of the hydraulic machine, and is provided to face the plurality of pistons, and the lobes move in the circumferential direction relative to the plurality of pistons. And a ring cam configured to be rotatable,
The plurality of cylinders includes a cylinder group formed by a plurality of cylinders having different positions in the axial direction of the hydraulic machine,
Each of the plurality of lobes extends linearly in the axial direction over the axial distribution range of the cylinders in the cylinder group.

  In the radial piston hydraulic machine of the wind power generator described above, the plurality of lobes extend linearly in the axial direction, so that the ring cam can be easily attached. For this reason, the radial piston hydraulic machine has high productivity, and the wind power generator has high productivity.

  According to at least one embodiment of the present invention, it is possible to provide a radial piston hydraulic machine and a wind power generator having high productivity.

It is a figure which shows the wind power generator which concerns on some embodiment. It is a schematic longitudinal cross-sectional view of the radial piston type hydraulic machine applicable to the hydraulic motor or hydraulic pump in FIG. FIG. 3 is a schematic partial longitudinal sectional view showing a part of FIG. 2 in an enlarged manner. FIG. 3 is a schematic partial cross-sectional view of the hydraulic machine of FIG. 2. FIG. 3 is a perspective view schematically showing a cylinder block in FIG. 2 together with a cylinder cartridge, a piston and a roller extracted from one sleeve hole. FIG. 3 is a perspective view schematically showing a ring cam in FIG. 2. FIG. 7 is a plan view schematically showing the ring cam of FIG. 6. It is a figure for demonstrating the state which the roller is contacting with respect to the ring cam in one axial direction position. It is a figure for demonstrating the state which the roller is contacting with respect to the ring cam in another axial direction position. FIG. 3 is a schematic longitudinal sectional view showing a state after the position of the ring cam is shifted in the axial direction in the hydraulic machine of FIG. 2. FIG. 3 is a schematic cross-sectional view for explaining a step of shifting the position of the ring cam in the axial direction in the hydraulic machine of FIG. 2. It is a schematic perspective view for demonstrating the manufacturing process of the ring cam of FIG. It is a perspective view which shows schematically the ring cam which concerns on other embodiment. FIG. 14 is a plan view schematically showing the ring cam of FIG. 13. FIG. 3 is a schematic cross-sectional view of a cylinder assembly disposed in the sleeve hole of FIG. 2. It is a schematic sectional drawing of the cylinder assembly concerning other embodiments. FIG. 17 is a perspective view schematically showing an engagement plate in FIG. 16. It is a schematic sectional drawing of the cylinder assembly concerning other embodiments. FIG. 16 is a perspective view schematically showing the cylinder assembly in FIG. 15 together with a sleeve hole in a state where a piston and a roller are removed from the cylinder sleeve. FIG. 20 is a plan view schematically showing a sleeve hole in FIG. 19 together with a roller. It is a perspective view which shows roughly a part of cylinder sleeve which concerns on other embodiment with a sleeve hole in the state which removed the piston and the roller. FIG. 22 is a plan view schematically showing a second portion of the sleeve hole in FIG. 21 together with a roller. FIG. 16 is a schematic cross-sectional view along the line XXIII-XXIII in FIG. 15. FIG. 16 is a schematic cross-sectional view along the line XXIV-XXIV in FIG. 15. FIG. 3 is a plan view schematically showing a cylinder block in FIG. 2. It is a top view which shows roughly the cylinder block which concerns on other embodiment. It is a top view which shows roughly the cylinder block which concerns on other embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, and relative arrangements of the components described in this embodiment are not intended to limit the scope of the present invention unless otherwise specified, and are merely illustrative examples. Only.

FIG. 1 is a diagram illustrating a wind turbine generator according to some embodiments.
As shown in FIG. 1, the wind power generator 1 includes a rotor 3 including at least one blade 2 and a hub 4. The hub 4 may be covered with a hub cover 5.
In some embodiments, a hydraulic pump 8 is coupled to the rotor 3 via a rotating shaft 6. A hydraulic motor 10 is connected to the hydraulic pump 8 via a high pressure oil line 12 and a low pressure oil line 14. Specifically, the outlet of the hydraulic pump 8 is connected to the inlet of the hydraulic motor 10 via the high-pressure oil line 12, and the inlet of the hydraulic pump 8 is connected to the outlet of the hydraulic motor 10 via the low-pressure oil line 14.

  The hydraulic pump 8 is driven by the rotary shaft 6 to increase the pressure of the hydraulic oil and generate high-pressure hydraulic oil (pressure oil). The pressure oil generated by the hydraulic pump 8 is supplied to the hydraulic motor 10 via the high-pressure oil line 12, and the hydraulic motor 10 is driven by this pressure oil. The low-pressure hydraulic oil after the work is performed by the hydraulic motor 10 is returned again to the hydraulic pump 8 via the low-pressure oil line 14 provided between the outlet of the hydraulic motor 10 and the inlet of the hydraulic pump 8.

A generator 16 is connected to the hydraulic motor 10. In some embodiments, the generator 16 is a synchronous generator linked to the power system and driven by the hydraulic motor 10.
At least a part of the rotating shaft 6 is covered with a nacelle 18 installed on the tower 19. In some embodiments, the hydraulic pump 8, the hydraulic motor 10, and the generator 16 are installed inside the nacelle 18.

  In some embodiments, at least one of the hydraulic pump 8 or the hydraulic motor 10 is a radial piston hydraulic machine described below.

2 is a schematic longitudinal sectional view along the axial direction of a radial piston type hydraulic machine according to some embodiments, and FIG. 3 is a schematic partial longitudinal sectional view showing a part of FIG. 2 in an enlarged manner. FIG. 4 is a schematic partial cross-sectional view showing an enlarged cross section orthogonal to the axial direction of the hydraulic machine of FIG.
In the embodiment shown in FIGS. 2 to 4, the hydraulic machine 20 includes a plurality of pistons 22 arranged along the radial direction of the hydraulic machine 20 and a plurality of cylinders for slidably holding the plurality of pistons 22. And a cylinder block 26 provided with 24. Each piston 22 is guided by a cylinder 24 so as to reciprocate along the radial direction of the hydraulic machine 20. When each piston 22 reciprocates in the cylinder 24, the volume of the hydraulic chamber 25 formed by the piston 22 and the cylinder 24 changes periodically. The reciprocating motion of the piston 22 accompanied with the periodic volume change of the hydraulic chamber 25 is converted into a motion mode with the rotational motion of the mechanical element 29.

For example, when the hydraulic machine 20 is a hydraulic pump, the rotational movement of the mechanical element 29 that rotates together with the rotary shaft 28 of the hydraulic machine 20 is converted into the reciprocating movement of the piston 22, and a periodic volume change of the hydraulic chamber 25 occurs. High pressure hydraulic oil (pressure oil) is generated in the hydraulic chamber 25. On the other hand, when the hydraulic machine 20 is a hydraulic motor, the reciprocating motion of the piston 22 occurs due to the introduction of the pressure oil into the hydraulic chamber 25, and the reciprocating motion is converted into the rotational motion of the mechanical element 29. The rotating shaft 28 of the hydraulic machine 20 rotates together with 29.
Thus, the mechanical element 29 converts the energy between the rotational energy (mechanical energy) of the rotary shaft 28 of the hydraulic machine 20 and the fluid energy of the hydraulic oil, so that the hydraulic machine 20 functions as a hydraulic pump or a hydraulic motor. It has come to fulfill its intended role.

In some embodiments, the machine element 29 is a cam 29A configured to rotate with the rotating shaft 28 and having a cam surface that abuts an abutment 23 provided on the piston 22, as shown in FIG. is there. In this case, at least one bearing 27 may be provided between the cam (mechanical element 29) and the cylinder block 26 in order to create a relative rotational movement of the cam (mechanical element 29) with respect to the contact portion 23.
In the embodiment shown in FIGS. 3 and 4, the contact portion 23 is a roller 23 </ b> A that is rotatably attached to the piston 22. The cam 29A is a ring cam having a plurality of lobes (cam crests) 31 arranged along the circumferential direction of the hydraulic machine 20 and configured to come into contact with the plurality of rollers 23A.

In some embodiments, the cylinder block 26 is formed with at least one internal oil passage 30 (30A, 30B) communicating with the plurality of hydraulic chambers 25.
In some embodiments, a plurality of internal oil passages 30 (30A, 30B) are provided along the axial direction of the hydraulic machine 20, and annular assemblies that communicate with the plurality of internal oil passages 30 (30A, 30B), respectively. A path 35 (35A, 35B) is formed inside the annular end plate 34. The end plate 34 is an annular plate member attached to the end of the cylinder block 26.

  In some embodiments, the bearing 27 is provided between the end plate 34 and the rotating shaft 28, and the end plate 34 and the cylinder block 26 are affected by the rotational movement of the mechanical element 29 by support means (not shown). Without being stationary. The annular collecting path 35 (35A, 35B) inside the end plate 34 is connected to the external pipe 36 (36A, 36B), respectively. Thus, each hydraulic chamber 25 communicates with the external pipe 36 (36A, 36B) via the internal oil passage 30 (30A, 30B) and the annular collecting passage 35 (35A, 35B).

In some embodiments, the cylinder block 26 includes a plurality of cylinder sleeves 40 each having a plurality of cylinders 24 and a cylinder block body 50 having a plurality of sleeve holes 52 into which the plurality of cylinder sleeves 40 are respectively inserted. .
The roles required for the cylinder block 26 include the formation of a cylinder 24 as a sliding portion for slidably guiding the piston 22 and the formation of a structure for holding the cylinder 24. As described above, if the cylinder sleeve 40 and the cylinder block main body 50 are provided separately, the roles required for the cylinder block 26 (formation of the cylinder 24 and formation of the structure) are assigned to the cylinder sleeve 40 and the cylinder block main body 50, respectively. Can be shared. Therefore, a suitable design according to the roles of the cylinder sleeve 40 and the cylinder block body 50 is possible, and the weight of the cylinder block 26 as a whole can be reduced.

  FIG. 5 is a perspective view schematically showing the cylinder block body 50 according to some embodiments together with the cylinder cartridge 38, the piston 22 and the roller 23A extracted from one sleeve hole 52. FIG. The cylinder cartridge 38 is a replaceable container that forms the cylinder 24, and includes at least a cylinder sleeve 40 and parts to be combined with the cylinder sleeve 40. In addition, the cylinder sleeve 40 should just contain the cylindrical part (sleeve main-body part) which forms the cylinder 24 at least.

  The cylinder block body 50 includes at least a forged part 51 formed by forging. The forged component 51 is provided with at least one internal oil passage 30 (30A, 30B). Since the forged product portion 51 is excellent in liquid tightness, the hydraulic oil can flow through the internal oil passage 30 provided in the forged product portion 51 of the cylinder block 26 while suppressing leakage of the hydraulic oil.

In the embodiment shown in FIGS. 2 to 5, the forged product portion 51 is an annular body having both at least one internal oil passage 30 (30 </ b> A, 30 </ b> B) and a plurality of sleeve holes 52.
In this case, since the forged product portion 51 has a relatively high rigidity, it can withstand an external force acting on the forged product portion 51 via the piston 22 and the cylinder sleeve 40. An example of an external force that acts on the forged product portion 51 is a pressing force from a mechanical element (for example, a cam) 29 that causes the piston 22 to reciprocate.

  Moreover, since the forged product part 51 is an annular body, the freedom degree of arrangement | positioning of the internal oil path 30 (30A, 30B) in the circumferential direction of the forged product part 51 improves, and the internal oil path 30 (30A in the forged product part 51 is improved. , 30B) can be increased. Therefore, the cross-sectional area of each internal oil passage 30 can be reduced, and the thickness of the forged part 51 can be reduced. Therefore, the manufacturing cost of the relatively expensive forged product portion 51 can be reduced.

  By the way, in the case of a cylinder block divided into a plurality of segments in the circumferential direction of the hydraulic machine 20, there is a merit that each segment can be replaced. On the other hand, if the machining accuracy and assembly accuracy of each segment are insufficient, The positional accuracy of each cylinder 24 with respect to the rotation center of the machine 20 is lowered. Of course, it is possible to improve the positional accuracy of each cylinder 24 with respect to the rotation center of the hydraulic machine 20 to some extent by inserting shims between the segments, but in this case, a great deal of labor is spent on the assembly work of the cylinder block. It will be.

In addition, for example, in the case of a hydraulic machine for a drive train of a wind turbine generator, when a part of the segment is replaced in the field, there is a considerable wind load acting on the cylinder block. It is difficult to assemble a new segment because the positions of the other segments are slightly shifted.
In this regard, if the cylinder block main body 50 (forged product portion 51) that is continuous over the entire circumference in the circumferential direction of the hydraulic machine 20 is employed as in the embodiment shown in FIGS.

  In some embodiments, at least one oil passage 30 extends along the axial direction of the hydraulic machine 20 inside the cylinder block body 50. In this configuration, since the oil passage 30 extends along the axial direction, the size of the cylinder block main body 50 can be reduced as compared with the case where the oil passage 30 extends along the radial direction of the hydraulic machine 20. Can be achieved.

6 is a perspective view schematically showing the ring cam 29A in FIG. 2, and FIG. 7 is a plan view schematically showing the ring cam 29A.
In some embodiments, as shown in FIG. 5, the plurality of cylinders 24 includes a group of cylinders formed by a plurality of cylinders 24 having different positions in the axial direction of the hydraulic machine 20. As shown in FIGS. 6 and 7, the plurality of lobes 31 of the ring cam 29 </ b> A extend linearly in the axial direction over the distribution range of the axial cylinders 24 in the cylinder group. .
In this configuration, since the plurality of lobes 31 extend linearly in the axial direction, it is easy to attach the ring cam 29A to the rotary shaft 28. For this reason, the radial piston hydraulic machine 20 has high productivity.

  In some embodiments, as shown in FIG. 5, the shaft of the hydraulic machine 20 is not connected to a plurality of cylinders 24 arranged in the circumferential direction in one section in the axial direction of the hydraulic machine 20. At least one cylinder 24 out of the plurality of cylinders 24 of the cylinder group arranged along the circumferential direction in other sections in the direction is arranged shifted in the circumferential direction.

  In this configuration, the two cylinders 24 having different axial positions are arranged with the circumferential positions being shifted, so that the reciprocating motion of the piston 22 in the two cylinders 24 even if the lobe 31 extends in the axial direction. Can be shifted in phase. Thereby, generation | occurrence | production of the pulsation and vibration in the hydraulic machine 20 can be prevented, and the noise reduction of the hydraulic machine 20 can be achieved.

In some embodiments, as shown in FIG. 5, a plurality of cylinders 24 periodically arranged in the circumferential direction at one axial position of the hydraulic machine 20 are rotated at other axial positions. A plurality of cylinders 24 periodically arranged in the direction are arranged with their circumferential positions shifted so as to have a constant phase difference. In other words, when the plurality of cylinders 24 form the cylinder row 53 along the axial direction, the plurality of cylinders 24 belonging to one cylinder row 53 are displaced in the circumferential position as the axial position is separated. Are arranged as follows.
With this configuration, it is possible to give a phase difference of equal intervals to the reciprocating motion of the piston 22 in the cylinders 24 having different axial positions, and to effectively prevent the occurrence of pulsation and vibration in the hydraulic machine 20.

  In some embodiments, the ring cam 29A is configured to be movable in the axial direction relative to the plurality of rollers 23A so that the contact positions with the plurality of rollers 23A are shifted. FIG. 8 schematically shows a state before the relative position between the ring cam 29A and the roller 23A is shifted, and FIG. 9 schematically shows a state after the relative position between the ring cam 29A and the roller 23A is shifted. . 8 and 9, the ring cam 29A is hatched in a striped manner in order to explain the change in the relative position.

In this configuration, the life of the ring cam 29A can be extended by moving the ring cam 29A relative to the roller 23A in the axial direction and shifting the contact position with the plurality of rollers 23A. The life of the hydraulic machine 20 can be extended.
In some embodiments, the ring cam 29A can be displaced with respect to the roller 23A by a distance longer than the length of the roller 23A in the axial direction of the hydraulic machine 20.

In some embodiments, as shown in FIG. 2, the hydraulic machine 20 includes a rotor portion 20A including a ring cam 29A, a stator portion 20B including a cylinder block 26, and between the rotor portion 20A and the stator portion 20B. And at least one bearing 27 provided. The bearing 27 includes a thrust-free bearing 27A. The thrust free bearing 27A is configured not only to allow relative rotation of the rotor portion 20A with respect to the stator portion 20B in the axial direction of the hydraulic machine 20, but also to allow relative displacement of the rotor portion 20A with respect to the stator portion 20B. Has been. And the hydraulic machine 20 has the displacement control part 32 for controlling the relative displacement in the axial direction of the rotor part 20A with respect to the stator part 20B.
The displacement restricting unit 32 is configured to be able to switch between a state where the relative displacement is restricted and a state where the restriction of the relative displacement is released.

According to this configuration, even if the ring cam 29A is movable in the axial direction relative to the roller 23A, the displacement regulating portion 32 can regulate the relative displacement of the ring cam 29A with respect to the roller 23A. As a result, the ring cam 29A rotates stably, and the operation of the radial piston hydraulic machine 20 is stabilized.
On the other hand, according to this configuration, the ring cam 29A can be easily moved in the axial direction relative to the roller 23A by releasing the restriction of the relative displacement by the displacement restricting portion 32.

In some embodiments, the thrust-free bearing 27A includes a race 33A fitted to the rotary shaft 28, a bearing box 33B fixed to the end plate 34, and rotatably accommodated in the bearing box 33B. It consists of a plurality of rolling elements 33C that are in sliding contact. The race 33A has a length corresponding to the relative displacement in the axial direction so that the ring cam 29A can be slidably contacted with the rolling element 33C before and after the relative displacement when the ring cam 29A is relatively displaced with respect to the roller 23A.
The bearing box 33 </ b> B may be a race fixed to the end plate 34.
In another embodiment, a sliding bearing can be used as the thrust-free bearing 27A.

  In some embodiments, the displacement restricting portion 32 is adjacent to the cup 32A, a cup 32A that is penetrated by the rotary shaft 28 so as to be relatively rotatable, a thrust bearing 32B that is disposed between the cup 32A and the end plate 34, and the cup 32A. The semi-cylindrical member 32C with a pair of flanges and the bolt 32D and the nut 32E for fastening the flanges of the semi-cylindrical member 32C to each other.

In this configuration, the pair of semi-cylindrical members 32C can be fixed to the rotary shaft 28 by fastening the flanges with the bolts 32D and the nuts 32E. The two pairs of semi-cylindrical members 32C fixed to the rotary shaft 28 can sandwich the two end plates 34 and the cylinder block 26 in the axial direction via the two cups 32A and the thrust bearing 32B. As a result, the relative displacement of the ring cam 29 with respect to the roller 23A is restricted. On the other hand, the restriction | limiting of a relative displacement is cancelled | released by cancel | releasing fastening of the flanges by the volt | bolt 32D and the nut 32E.
According to this configuration, the relative displacement can be reliably regulated with a simple configuration.

FIG. 10 shows a schematic cross section of the hydraulic machine 20 in a state where the ring cam 29A is shifted in the axial direction of the hydraulic machine 20 with respect to the roller 23A from the state of FIG. FIG. 11 is a view for explaining a process of relatively displacing the ring cam 29A from the state of FIG. 2 to the state of FIG.
In some embodiments, as shown in FIG. 11, the ring cam 29 </ b> A can be relatively displaced with respect to the roller 23 </ b> A using a relative displacement device 37. The relative displacement device 37 includes a fixing member 37A that is fixed to the end plate 34, and a screw member 37B that is brought into contact with the end surface of the rotating shaft 28 and screwed into the fixing member 37A along the axial direction of the rotating shaft 28. Become.
According to the relative displacement device 37, the screw cam 37B is screwed into the fixing member 37A in a state where the restriction by the displacement restricting portion 32 is released, so that the ring cam 29A can be relatively displaced relative to the roller 23A. it can. Then, the relative displacement may be regulated by the displacement regulating unit 32 after the relative displacement.

  In some embodiments, as shown in FIGS. 6 and 7, the ring cam 29 </ b> A is formed by a single piece that is continuous in the circumferential direction and the axial direction.

When the ring cam is composed of a plurality of members, a step or a protrusion is generated on the cam surface due to the presence of a joint portion or a fastening member between the members. In this case, the surface pressure between the ring cam and the member in contact with the ring cam may suddenly increase due to the presence of steps or protrusions.
On the other hand, by forming the ring cam 29A integrally, steps in the lobe 31 can be substantially eliminated, and a sudden increase in surface pressure can be prevented. As a result, the life of the ring cam 29A and the member in contact with the ring cam 29A is extended, and the life of the radial piston hydraulic machine 20 is also extended.
Further, by preventing a sudden increase in surface pressure, pulsation and vibration can be suppressed, and noise reduction of the radial piston hydraulic machine 20 can be achieved.

FIG. 12 is a schematic perspective view showing a manufacturing process of the ring cam 29 </ b> A constituted by a single body. The ring cam 29 </ b> A constituted by a single body can be manufactured by a hobbing machine having a hob 39 as shown in FIG. 12. At this time, since the lobe 31 extends linearly in the axial direction of the ring cam 29A, the lobe 31 can be formed all at once by moving the hob 39 along the axial direction of the ring cam 29A to be processed. For this reason, the ring cam 29 comprised by the integrated object can be manufactured easily.
Note that the ring cam 29 </ b> A configured as a single unit can be manufactured by a surface grinding machine.

  In some embodiments, the ring cam 29 </ b> A formed by a single body is fitted to the rotary shaft 28 by shrink fitting.

13 is a perspective view schematically showing a ring cam 29B having a lobe 31 on the inner peripheral surface, and FIG. 14 is a plan view schematically showing the ring cam 29B in FIG.
In some embodiments, the cylinder block is rotatably provided integrally with the rotary shaft 28, and mechanical elements provided so as to surround the cylinder block are arranged in a stationary state. In this case, an abutting portion is provided on the radially outer side with respect to the piston 22, and an inward ring cam 29B as shown in FIGS. 13 and 14 is used as a mechanical element.

In some embodiments, as shown in FIG. 5, a cylinder cartridge 38 including each cylinder sleeve 40, along with each piston 22, along the radial direction with respect to each sleeve hole 52 of the cylinder block body 50. It is configured to be detachable.
In this configuration, the cylinder sleeve 40 forms a sliding portion with the piston 22, and when the wear of the cylinder sleeve 40 progresses, only the cylinder sleeve 40 needs to be replaced. When replacing the cylinder sleeve 40, the cylinder cartridge 38 to be replaced is pulled out from the sleeve hole 52 of the cylinder block body 50 along the radial direction of the hydraulic machine 20, and the cylinder cartridge 38 including the new cylinder sleeve 40 is removed from the sleeve hole 52. What is necessary is just to insert in 52, and replacement | exchange operation | work is easy. For this reason, the radial piston type hydraulic machine 20 is easy to maintain.

By the way, the shape of the cylinder block of the radial piston type hydraulic machine is usually a combination of a trapezoid, a circular arc, an inclined surface, and the like, and the machining difficulty is high. In particular, a cylinder block applied to a radial piston type hydraulic machine for a drive train of a wind turbine generator is large in size and is difficult to process.
In addition, when the cylinder is integrally provided in the cylinder block, a large number of cylinder blocks are required, and the processing difficulty level is further increased. Moreover, high reliability is required for the material for processing.

  On the other hand, in the hydraulic machine 20, since the cylinder block body 50 and the cylinder sleeve 40 having the cylinder 24 are provided separately, the processing on the cylinder block body 50 can be reduced and the number of processing steps can be reduced. In addition, the strength of the cylinder block main body 50 can be prevented from being reduced due to processing.

  In some embodiments, each of the plurality of pistons 22 is engageable with the plurality of cylinder sleeves 40 such that the escape from the plurality of cylinder sleeves 40 is restricted. In this configuration, since the piston 22 is prevented from coming out of the cylinder sleeve 40, the piston 22 is not dropped from the cylinder sleeve 40 when the cylinder sleeve 40 is replaced.

FIG. 15 is a cross-sectional view schematically showing the cylinder assembly 43 disposed in the sleeve hole 52. The cylinder assembly 43 includes a cylinder cartridge 38.
In some embodiments, as shown in FIG. 15, an engagement screw 54 and an engagement groove 55 are provided as engagement means for engaging the cylinder sleeve 40 and the piston 22. The engagement groove 55 is provided on the side portion of the piston 22, extends in the axial direction of the cylinder 24, and opens on the side surface of the piston 22. The engagement screw 54 is screwed into a screw hole provided through the cylinder sleeve 40, and the distal end portion of the engagement screw 54 is disposed in the engagement groove 55. The engaging screw 54 restricts the piston 22 from coming out of the cylinder sleeve 40 while allowing the piston 22 to reciprocate in the axial direction of the cylinder 24.

  In another embodiment, as shown in FIGS. 16 and 17, an engagement plate 56 is provided as an engagement means for engaging the cylinder sleeve 40 and the piston 22. The engagement plate 56 has a band plate shape and is fixed to the upper surface of the piston 22 with screws, and both end portions of the engagement plate 56 slightly protrude from the outer edge of the piston 22. The cylinder sleeve 40 is provided with a reduced diameter portion, and the engagement plate 56 abuts the reduced diameter portion, thereby restricting the piston 22 from coming out of the cylinder sleeve 40.

The engaging plate 56 can be inserted into the cylinder sleeve 40 before the piston 22 and screwed through a hole provided in the cylinder sleeve 40 after the piston 22 is inserted.
Alternatively, a hole into which the engagement plate 56 can be inserted may be formed in the cylinder sleeve 40, and a screw-in type closing member 57 that can close the hole may be used.

In still another embodiment, as shown in FIG. 18, a snap ring 58 is provided as an engaging means for engaging the cylinder sleeve 40 and the piston 22. The snap ring 58 is fitted on the outer periphery of the piston 22 and abuts on the reduced diameter portion of the cylinder sleeve 40, thereby restricting the piston 22 from coming out of the cylinder sleeve 40.
In order to fit the snap ring 58, the cylinder sleeve 40 may be separable.

In some embodiments, the cylinder cartridge 38 is configured to be detachable along the radial direction with respect to the plurality of sleeve holes 52 of the cylinder block body 50 together with the piston 22 and the roller 23A.
In this configuration, when exchanging the piston 22 and the roller 23A, etc., the piston 22 and the roller 23A can be extracted from the cylinder block body 50 together with the cylinder sleeve 40, and the operation is easy.

In some embodiments, the plurality of rollers 23 </ b> A can be engaged with the plurality of pistons 22 so that the pistons 22 are prevented from coming out of the plurality of pistons 22 in the axial direction. In this configuration, when the roller 23A is exchanged, the roller 23A is not dropped from the piston 22, and the operation is easy.
In some embodiments, as shown in FIG. 15, two arm portions 59 are provided on the piston 22 as engaging means for engaging the piston 22 and the roller 23 </ b> A. The two arm portions 59 have an arc surface. The circular arc surface defines a substantially cylindrical space orthogonal to the axial direction of the piston 22, and the roller 23A is inserted coaxially into the space. The tips of the two arm portions 59 are separated from each other so as not to impede the contact between the roller 23A and the ring cam 29A, and the two arm portions 59 support the roller 23A in a rotatable manner in the axial direction of the piston 22. The escape of the roller 23A from the piston 22 is restricted.

  In some embodiments, each of the plurality of sleeve holes 52 has a size through which the plurality of rollers 23A can pass. In this configuration, when replacing the roller 23A, the roller 23A can be extracted from the cylinder block body 50 through the sleeve hole 52 regardless of the size of the roller 23A.

FIG. 19 is a perspective view schematically showing the cylinder assembly 43 and the sleeve hole 52. However, the piston 22 and the roller 23 </ b> A are extracted from the cylinder sleeve 40. FIG. 20 is a plan view schematically showing the roller 23 </ b> A and the sleeve hole 52.
As shown in FIGS. 19 and 20, in some embodiments, the plurality of sleeve holes 52 are each circular in cross section and have a diameter D1 that is greater than the diagonal length L of the plurality of rollers 23A. According to this configuration, the roller 23 </ b> A can be extracted from the cylinder block body 50 through the sleeve hole 52.
A notch 63 is formed at one end of the cylinder sleeve 40 located on the roller 23A side corresponding to both ends of the roller 23A. The notch 63 can receive both ends of the roller 23 </ b> A and allows the piston 22 to reciprocate.

FIG. 21 is a perspective view schematically showing a cylinder assembly 43 and a sleeve hole 52 according to another embodiment. However, only a part of the cylinder sleeve 40 is shown, and the piston 22 and the roller 23 </ b> A are extracted from the cylinder sleeve 40. FIG. 22 is a plan view schematically showing the roller 23 </ b> A and the sleeve hole 52.
In some embodiments, as shown in FIGS. 21 and 22, the plurality of sleeve holes 52 includes a first portion 52A and a second portion 52B. The first portion A is provided in the first region of the cylinder block body 50 corresponding to the plurality of hydraulic chambers 25 formed by the plurality of pistons 22 and the plurality of cylinders 24, and has a circular cross section.

  The second portion 52B is provided in the second region of the cylinder block body 50 closer to the roller 23A than the first region. The second portion 52B has a cross-sectional shape in which at least notches 61 corresponding to both ends of each roller 23A are added to a circular cross-section having a diameter D2 smaller than the diagonal length L of each roller 23A. Have

According to this configuration, the roller 23 </ b> A can be extracted from the cylinder block body 50 through the second portion 52 </ b> B and the first portion 52 </ b> A of the sleeve hole 52. On the other hand, according to this configuration, the cross-sectional area of the second portion 52B of the sleeve hole 52 is smaller than the cross-sectional area of the first portion 52A, and the thickness of the portion of the cylinder block body 50 surrounding the second portion 52B is increased. be able to. Thereby, the intensity | strength of the cylinder block main body 50 can be made high.
In some embodiments, two side plates 69 that restrict the movement of the roller 23 </ b> A in the axial direction are attached to the piston 22. The two side plates 69 sandwich the roller 23A so as to be relatively rotatable from both axial sides. As shown in FIG. 22, the notch 61 also corresponds to the side plate 69 and is formed by a plurality of arcuate surfaces.

In some embodiments, as shown in FIG. 21, the plurality of cylinder sleeves 40 includes a first sleeve portion 40 </ b> A corresponding to the first portion 52 </ b> A of the plurality of sleeve holes 52, and the first sleeve portions 52 </ b> A. And a second sleeve portion B corresponding to the two portions 52B. A step 65 is provided between the first sleeve portion 40A and the second sleeve portion 40B.
In the case of this configuration, the cylinder sleeve 40 can be positioned in the sleeve hole 52 using the step 65 of the cylinder sleeve 40. That is, the cylinder sleeve 40 can be positioned in the sleeve hole 52 by bringing the step of the cylinder sleeve 40 into contact with the step 67 of the sleeve hole 52. Further, the thickness of the first sleeve portion 40A can be made thicker than the second sleeve portion 40B corresponding to the step 65, and the cylinder sleeve 40 can be given high strength.

  In some embodiments, as shown in FIGS. 2-4, the cylinder block 26 is attached to the cylinder block body 50 and from the cylinder block bodies 50 of the plurality of cylinder cartridges 38 inserted into the plurality of sleeve holes 52. A plurality of lid members 70 are further included for restricting slipping out along the radial direction. The lid member 70 is fixed to the cylinder block body 50 using, for example, bolts.

  In this configuration, the use of the lid member 70 makes it possible to easily regulate the withdrawal of the cylinder cartridge 38 from the cylinder block body 50. For this reason, even if the hydraulic oil pressure acts on the cylinder sleeve 40, the cylinder sleeve 40 can be prevented from coming out.

  In some embodiments, as shown in FIGS. 3 and 4, the hydraulic machine 20 is configured to supply or discharge hydraulic fluid with respect to a plurality of hydraulic chambers 25 respectively formed by a plurality of pistons 22 and a plurality of cylinders 24. And a plurality of valves 60 (60A, 60B) for switching between the two. The cylinder cartridge 38 is configured to be detachable along the radial direction with respect to the plurality of sleeve holes 52 of the cylinder block body 50 together with the piston 22 and the valve 60 (60A, 60B).

  In this configuration, the cylinder cartridge 38 can be inserted into and removed from the sleeve hole 52 together with the valve 60 (60A, 60B), and therefore the valve 60 (60A) together with the cylinder cartridge 38 during maintenance of the valve 60 (60A, 60B). 60B) can be extracted from the sleeve hole 52. Therefore, the maintenance work of the valve 60 (60A, 60B) can be easily performed.

In some embodiments, as shown in FIG. 15, the plurality of cylinders 24 have a central axis (cylinder axis) that coincides with the central axis of the plurality of cylinder sleeves 40.
In this configuration, the inner peripheral surface and the outer peripheral surface of the cylinder sleeve 40 can be formed by lathe processing with a common center hole, and the cylinder sleeve 40 can be easily manufactured. For this reason, the productivity of the hydraulic machine 20 can be further increased.

In some embodiments, as shown in FIGS. 3 and 4, the cylinder cartridge 38 is provided on the outer peripheral surface of the cylinder cartridge 38 and has at least one opening to at least one internal oil passage 30 (30A, 30B). Two oil grooves 41 are provided.
In this configuration, by providing the oil groove 41 that opens to the oil passage 30 on the outer peripheral surface of the cylinder cartridge 38, the oil passage 30 and the hydraulic chamber 25 can be reliably communicated with each other with a simple configuration. Therefore, since high processing accuracy is not required for connection between the hydraulic chamber 25 and the oil passage 30, the hydraulic machine 20 has high productivity.
In some embodiments, the oil groove 41 is formed on the outer peripheral surface of the cylinder sleeve 40.

In some embodiments, as shown in FIGS. 3 and 4, at least one oil passage 30 includes a plurality of oil passages 30 extending along the axial direction of the hydraulic machine 20, and includes at least one oil passage 30. Each of the oil grooves 41 opens into two or more oil passages 30 among the plurality of oil passages 30.
In this configuration, since the oil groove 41 is provided on the outer peripheral surface of the cylinder cartridge 38, the degree of freedom in the configuration of the hydraulic oil flow path is high, and two or more oil paths 30 are provided via one oil groove 41. Can be communicated with the hydraulic chamber 25. Therefore, the diameter of each oil passage 30 can be reduced, and the strength of the cylinder block 26 can be improved while suppressing the flow resistance of the hydraulic oil.

In some embodiments, as shown in FIG. 19, the at least one oil groove 41 includes an annular groove 42 (42 </ b> A, 42 </ b> B) that is continuous over the entire outer circumference of the cylinder cartridge 38. In this configuration, since the oil groove 41 on the outer peripheral surface of the cylinder sleeve 40 that opens to the oil passage 30 inside the cylinder block body 50 is the annular groove 42, the degree of freedom of the arrangement of the oil passage 30 with respect to the cylinder cartridge 38 is improved.
In some embodiments, the annular groove 42 (42 </ b> A, 42 </ b> B) is formed over the entire circumference of the outer peripheral surface of the cylinder sleeve 40.

In some embodiments, as shown in FIG. 15, the hydraulic machine 20 includes a plurality of sealing members that are provided on the outer peripheral surface of the cylinder cartridge 38 on both sides of the annular groove 42 to seal each annular groove 42. 44 is further provided. In this configuration, since both sides of the annular groove 42 are sealed by the seal member 44, good liquid tightness is ensured.
In some embodiments, the seal member 44 seals the gap between the annular cylinder cartridge 38 and the sleeve hole 52. The seal member 44 is an O-ring made of an elastic material, for example.

  In some embodiments, as shown in FIG. 15, inside the cylinder cartridge 38, communication passages 46 (46 </ b> A, 46 </ b> B) for communicating the respective annular grooves 42 (42 </ b> A, 42 </ b> B) and the hydraulic chamber 25. ) Is provided. In each communication passage 46 (46A, 46B), a valve 60 (60A, 60B) for switching the communication state between each internal oil passage 30 (30A, 30B) of the cylinder block 26 and the hydraulic chamber 25 is provided. Is provided.

  In some embodiments, as shown in FIGS. 2 to 4, at least one internal oil passage 30 provided in the forged product portion 51 (cylinder block body 50) supplies hydraulic oil to the hydraulic chamber 25. An oil supply passage 30A for discharging the hydraulic oil from the hydraulic chamber 25 and an oil discharge passage 30B for discharging the hydraulic oil from the hydraulic chamber 25 are included.

In some embodiments, the oil supply passage 30 </ b> A and the oil discharge passage 30 </ b> B provided inside the cylinder block 26 extend along the axial direction of the hydraulic machine 20.
According to this configuration, since both the oil supply passage 30A and the oil discharge passage 30B extend in the axial direction, the cylinder block 26 can be prevented from increasing in diameter, and the oil supply passage 30A and the oil discharge passage can be prevented. The piping structure connected to 30B can also be simplified.

In some embodiments, the oil supply passage 30 </ b> A and the oil discharge passage 30 </ b> B provided in the cylinder block 26 are at different positions in the radial direction of the hydraulic machine 20.
According to this configuration, the oil supply passage 30A and the oil discharge passage 30B are at different positions in the radial direction, and are not arranged in parallel at the same radial position. For this reason, the space required for the oil supply passage 30A and the oil discharge passage 30B may be small, and there is no need to increase the distance between the cylinders 24. As a result, an increase in the size of the cylinder block 26 can be prevented. Alternatively, since the space required for the oil supply passage 30A and the oil discharge passage 30B may be small, the number of cylinders 24 arranged in the circumferential direction can be increased. When the number of cylinders 24 is increased, pulsation and vibration can be suppressed.

  In some embodiments, as shown in FIGS. 3 and 4, the plurality of valves 60 are respectively disposed in the plurality of sleeve holes 52 to switch the supply state of the hydraulic oil to the plurality of hydraulic chambers 25, respectively. A plurality of oil supply valves 60 </ b> A and a plurality of oil discharge valves 60 </ b> B that are respectively disposed in the plurality of sleeve holes 52 and switch the discharge state of the hydraulic oil from the plurality of hydraulic chambers 25.

In this configuration, the oil supply valve 60 </ b> A and the oil discharge valve 60 </ b> B are disposed in the sleeve hole 52, and the oil supply valve 60 </ b> A is compared with the case where the oil supply valve 60 </ b> A and the oil discharge valve 60 </ b> B are installed at different locations from the sleeve hole 52. And the space for installing the oil discharge valve 60B is reduced. As a result, the cylinder block body 50 can be reduced in size, and the radial piston type hydraulic machine 20 can be reduced in size.
Further, since the oil supply valve 60A and the oil discharge valve 60B are disposed in the sleeve hole 52, the distance between the oil supply valve 60A and the oil discharge valve 60B and the hydraulic chamber 25 can be shortened. Dead space can be reduced. As a result, the efficiency of the radial piston type hydraulic machine 20 can be increased.

In some embodiments, as shown in FIGS. 3 and 4, at least one annular groove 42 provided in the cylinder cartridge 38 includes an oil supply groove 42 </ b> A that opens to the oil supply passage 30 </ b> A in the forged product portion 51. , And an oil drain groove 42B that opens to the oil drain path 30B in the forged product portion 51. Further, the communication passage 46 communicates the oil chamber 25A with the oil supply groove 42A through the oil supply valve 60A and the oil supply chamber 46A with the oil supply groove 42B through the oil discharge valve 60B. And an oil discharge passage 46B.
In this configuration, the oil supply passage 46A and the oil discharge passage 46B are provided in the cylinder cartridge 38, so that the oil supply passage 30A, the oil discharge passage 30B, the oil supply valve 60A, and the oil discharge valve 60B are respectively configured with a simple structure. Communication can be ensured.

  In other words, each cylinder cartridge 38 is provided with a first communication passage for communicating the hydraulic chamber 25 with the oil supply passage 30A and a second communication passage for communicating the hydraulic chamber 25 with the oil discharge passage 30B. The first communication path includes an oil supply groove (first annular groove) 42A provided on the outer peripheral surface of the cylinder cartridge 38 and opening to the oil supply path 30A, and the second communication path extends in the radial direction from the oil supply groove 42A. And a drain oil groove (second annular groove) 42B provided on the outer peripheral surface of the cylinder cartridge 38 and opened to the oil drain passage 30B.

  In this configuration, by providing the oil supply groove 42A that opens to the oil supply passage 30A on the outer peripheral surface of the cylinder cartridge 38, the oil supply passage 30A and the hydraulic chamber 25 can be reliably communicated with each other with a simple structure. Further, in this configuration, the oil drainage passage 42B that opens to the oil drainage passage 30B is provided at a radial position different from the oil supply groove 42A on the outer peripheral surface of the cylinder cartridge 38. 30B and the hydraulic chamber 25 can be reliably communicated with each other.

  In some embodiments, the first communication path connects the hydraulic chamber 25 to at least one oil supply path 30A via the oil supply valve 60A, and the second communication path is hydraulic via the oil discharge valve 60B. The chamber 25 is communicated with at least one oil drain passage 30B.

  In some embodiments, as shown in FIGS. 3 and 4, the cylinder cartridge 38 including the cylinder sleeve 40 includes an oil supply valve 60 </ b> A and an oil discharge valve 60 </ b> B aligned in the radial direction of the hydraulic machine 20. It has been incorporated.

In this configuration, the oil supply valve 60A and the oil discharge valve 60B are arranged in the cylinder cartridge 38 in a state where they are aligned in the radial direction. For this reason, the oil supply valve 60A and the oil discharge valve 60B are not arranged between the adjacent cylinders 24, and it is not necessary to provide a space for installing the oil supply valve 60A and the oil discharge valve 60B in the cylinder block body 50 independently. For this reason, the distance between the adjacent cylinders 24 can be shortened, and the size of the cylinder block body 50 can be reduced. As a result, the radial piston type hydraulic machine 20 can be downsized.
Alternatively, the number of cylinders 24 in the circumferential direction can be increased, pulsation and vibration can be suppressed, and noise reduction of the radial piston type hydraulic machine 20 can be achieved.

By the way, when the hydraulic machine 20 is used at a high pressure, the hydraulic oil becomes a high pressure, and the volume of the hydraulic oil is reduced even in an incompressible fluid. For this reason, if there is a dead space around the hydraulic chamber 25, the efficiency of the hydraulic machine 20 decreases. This problem is particularly noticeable in large machines such as wind power generators.
In the above configuration, since the oil supply valve and the oil discharge valve are incorporated in the cylinder cartridge 38, the dead space around the hydraulic chamber 25 can be reduced. As a result, the efficiency of the hydraulic machine 20 can be increased.

Further, if the oil supply valve 60A and the oil discharge valve 60B are incorporated in the cylinder cartridge 38 in a state where they are aligned in the radial direction of the hydraulic machine 20, the cover member 70 is used to collectively pull out from the sleeve hole 52. Can be prevented.
Furthermore, if the oil supply valve 60A and the oil discharge valve 60B are incorporated in the cylinder cartridge 38 in a state where they are aligned in the radial direction of the hydraulic machine 20, the processing for the cylinder block body 50 can be reduced, and the number of processing steps can be reduced. In addition, the strength of the cylinder block main body 50 can be prevented from being reduced due to processing.

In some embodiments, as shown in FIGS. 3 and 4, in each sleeve hole 52, the valve body 62A of the oil supply valve 60A and the valve body 62B of the oil discharge valve 60B are arranged in the radial direction of the hydraulic machine 20. Are overlapping.
In this configuration, since the valve element 62A of the oil supply valve 60A and the valve element 62B of the oil discharge valve 60B overlap in the radial direction, the installation space for the oil supply valve 60A and the oil discharge valve 60B in the sleeve hole 52 is ensured. Can be made smaller.
Thus, the oil supply groove 42A and the oil discharge groove 42B also correspond to the oil supply valve 60A and the oil discharge valve 60B provided at different positions in the radial direction of the hydraulic machine 20 on the outer peripheral surface of each cylinder cartridge 38. Twenty radial positions are provided.

In some embodiments, as shown in FIG. 15, the plurality of oil supply valves 60A are provided at positions farther from the plurality of hydraulic chambers 25 than the plurality of oil discharge valves 60B, respectively. The first communication passage that connects the oil supply passage 30A and the hydraulic chamber 25 is at least one for oil supply extending along the radial direction of the hydraulic machine 20 from each hydraulic chamber 25 toward the valve body 62A of each oil supply valve 60A. A radial flow path (first flow path) 48 is included. The second communication passage that communicates the oil discharge passage 30B and the hydraulic chamber 25 is for at least one oil discharge extending along a direction orthogonal to the first flow passage so as to avoid at least one first flow passage. An orthogonal flow path (second flow path) 72 is included.
According to this configuration, by providing the second flow path 72 so as to avoid the first flow path 48 extending along the radial direction, the hydraulic chamber 25 and the oil supply path can be connected via the oil supply valve 60A with a simple structure. The hydraulic chamber 25 and the oil discharge passage 30B can be communicated with each other via the oil discharge valve 60B while communicating 30A.

  In some embodiments, the first communication path includes at least one oil supply orthogonal flow path (first flow path) that connects at least one first flow path 48 to the oil supply groove 42A via each oil supply valve 60A. 3 flow paths) 47.

23 is a schematic cross-sectional view taken along line XXIII-XXIII in FIG. 15, and FIG. 24 is a schematic cross-sectional view taken along line XXIV-XXIV in FIG.
In some embodiments, as shown in FIG. 23, a plurality of first flow paths 48 and third flow paths 47 are arranged around the central axis of the cylinder sleeve 40. As shown in FIG. 24, the plurality of second flow paths 72 extend between the plurality of first flow paths 48.

  When the hydraulic machine 20 described above is a hydraulic pump, when the oil supply valve 60A is opened, the hydraulic oil from the oil supply passage 30A in the forged product portion 51 is introduced into the hydraulic chamber 25 via the oil supply groove 42A and the oil supply communication passage 46A. The The hydraulic oil introduced into the hydraulic chamber 25 is compressed and pressurized by the volume reduction of the hydraulic chamber 25 accompanying the movement of the piston 22 from the bottom dead center toward the top dead center. The high-pressure hydraulic oil (pressure oil) generated in this way is taken out to the oil discharge passage 30B in the forged product portion 51 via the oil discharge communication passage 46B and the oil discharge groove 42B when the oil discharge valve 60B is opened. .

  On the other hand, when the hydraulic machine 20 is a hydraulic motor, when the oil supply valve 60A is opened, high-pressure hydraulic oil (pressure oil) from the oil supply passage 30A in the forged part 51 passes through the oil supply groove 42A and the oil supply communication passage 46A. It is introduced into the hydraulic chamber 25. The piston 22 is moved from the top dead center toward the bottom dead center by the pressure oil introduced into the hydraulic chamber 25. Thereafter, the hydraulic oil in the hydraulic chamber 25 is taken out into the oil discharge passage 30B in the forged product portion 51 via the oil discharge communication passage 46B and the oil discharge groove 42B when the oil discharge valve 60B is opened.

  In some embodiments, the hydraulic machine 20 is a hydraulic pump that boosts hydraulic oil by reciprocating movement of a plurality of pistons 22. Further, as shown in FIG. 15, each of the plurality of oil discharge valves 60B includes at least one spherical valve disposed in a valve chamber 75 communicating with the plurality of hydraulic chambers 25 via at least one valve hole 74. Body 62B and at least one biasing member 76 for biasing at least one spherical valve body 62B toward at least one valve hole 74, wherein at least one first flow path 48 is at least It arrange | positions avoiding the valve chamber 75 which has arrange | positioned one spherical valve body 62B.

In this configuration, the oil drain valve 60B is a check valve having a spherical valve body 62B, and has a simpler configuration than the electromagnetic valve. For this reason, even if the oil discharge valve 60B is disposed closer to the hydraulic chamber 25 than the oil supply valve 60A, the oil supply valve 60A and the hydraulic chamber 25 can be easily connected across the oil discharge valve 60B.
Moreover, since the oil discharge valve 60B is not a solenoid valve, it does not require electrical connection. Therefore, even if the oil discharge valve 60B, which is a check valve, is arranged near the hydraulic chamber 25, wiring is not complicated.
As the urging member 76, a compression coil spring can be used.

  In some embodiments, the at least one spherical valve body 62B is a single spherical valve body 62B disposed on the central axis of each cylinder 24, and the at least one first flow path 48 includes: It arrange | positions around the valve chamber 75 which has arrange | positioned one spherical valve body 62B.

  In this configuration, the valve body 62B is a spherical valve body, and the valve chamber 75 can be made small. Therefore, a space for the first flow path 48 can be easily secured around the valve chamber 75.

  In some embodiments, as shown in FIGS. 3 and 4, a plurality of hydraulic chambers 25, a plurality of oil discharge valves 60 </ b> B, and a plurality of oil supply valves from the inner peripheral side to the outer peripheral side of the cylinder block 26. 60A is arranged in this order, and each of the plurality of oil supply valves 60A is a solenoid electromagnetic valve.

  In this configuration, the oil supply valve 60A made up of a solenoid solenoid valve is arranged on the outer peripheral side of the cylinder block 26, so that electrical wiring is easy.

In some embodiments, as shown in FIG. 15, the plurality of cylinder sleeves 40 each include a sleeve body 80 and a sleeve end 81 integral with one end of the sleeve body 80. The sleeve body 80 has a substantially cylindrical shape and forms a cylinder 24. The sleeve end portion 81 closes one end of the sleeve main body portion 80.
The sleeve end portion 81 incorporates a valve close to each hydraulic chamber 25 out of each oil supply valve 60A and each oil discharge valve 60B, and each of the oil supply valve 60A and each oil discharge valve 60B. A valve far from the hydraulic chamber 25 is provided separately from the cylinder sleeve 40.

In the cylinder assembly 43 of FIG. 15, the oil drain valve 60 </ b> B is incorporated in the sleeve end portion 81. More specifically, a bottomed hole extending in the axial direction of the cylinder sleeve 40 is formed on the inner end surface of the sleeve end portion 81 on the hydraulic chamber 25 side. The valve chamber 75 is formed by the bottomed hole. A sleeve 83 having a valve seat that forms a valve hole 74 is screwed into the bottomed hole, and the valve body 62B is prevented from coming out of the valve chamber 75 by the valve seat.
And the spring hole which forms a spring seat is provided in the bottom face of a bottomed hole, and the end of the compression coiled spring as the biasing member 76 is accommodated in the spring hole.

  On the other hand, the cylinder cartridge 38 includes a valve casing 85 attached to the cylinder sleeve 40. The valve casing 85 incorporates a valve close to the hydraulic chamber 25 among the oil supply valve 60A and the oil discharge valve 60B. In the cylinder assembly 43 of FIG. 15, the oil supply valve 60 </ b> A is incorporated in the valve casing 85.

  More specifically, the valve casing 85 is disposed in the sleeve hole 52 and is disposed adjacent to the outer end surface of the sleeve end portion 81 of the cylinder sleeve 40. A cylindrical recess is formed coaxially on the outer end surface of the sleeve end portion 81. The valve casing 85 has a stepped cylindrical shape including a small diameter portion and a large diameter portion, and is disposed coaxially with the cylinder sleeve 40. A small diameter portion of the valve casing 85 is disposed on the cylinder sleeve 40 side and is fitted into the opening of the concave portion of the sleeve end portion 81. As a result, the opening of the concave portion of the sleeve end portion 81 is closed by the small diameter portion, and a valve chamber 87 for the valve body 62A is formed in the gap between the concave portion and the small diameter portion. The oil supply radial flow path 48 passes through the sleeve end portion 81 in the axial direction of the cylinder sleeve 40, and opens in a concave portion of the sleeve end portion 81.

  The oil supply orthogonal flow path 47 is provided radially in the small diameter portion of the valve casing 85. The small diameter portion of the valve casing 85 is provided with a plurality of valve holes 88 that communicate the inner ends of the plurality of oil supply orthogonal flow channels 47 and the outer end surfaces of the small diameter portions of the valve casing 85. The plurality of valve holes 88 extend in the axial direction of the small diameter portion.

  The oil supply valve 60A is a poppet valve, and an annular valve seat for the valve body 62A is provided on the outer end surface of the small diameter portion of the valve casing 85 in a region where the valve hole 88 is opened. The shaft portion of the valve body 62 </ b> A penetrates the small diameter portion of the valve casing 85 in the axial direction, and the tip of the shaft portion is disposed in the large diameter portion of the valve casing 85.

An armature 89 is provided integrally at the tip of the shaft portion of the valve body 62 </ b> A. A core 90 and a solenoid 92 are fixedly provided inside the large-diameter portion of the valve casing 85, and a compression coil spring is provided as a biasing member 94 between the core 90 and the armature 89. . The compression coil spring as the urging member 94 urges the valve body 62 </ b> A in a direction away from the valve seat in the axial direction of the cylinder sleeve 40.
The fuel supply valve 60A is configured such that by supplying power to the solenoid 92, the armature 89 is sucked toward the core 90 against the biasing force of the biasing member 94, and the fuel supply valve 60A is closed. Yes.

  In the cylinder assembly 43 shown in FIG. 15, the oil supply valve 30 </ b> A or the oil discharge valve 30 </ b> B is incorporated in a valve casing 85 separate from the cylinder sleeve 40, so that the oil supply valve 30 </ b> A and the oil discharge valve 30 </ b> B are provided to the cylinder cartridge 38. The processing for incorporating is facilitated. As a result, the productivity of the radial piston type hydraulic machine 20 can be increased.

  In some embodiments, as shown in FIG. 5, a plurality of axial hole rows 53 formed by a plurality of sleeve holes 52 arranged in the axial direction of the hydraulic machine 20 are arranged in the circumferential direction of the hydraulic machine 20. Provided. In the cylinder block 26 shown in FIG. 5, a plurality of sleeve holes 52 are provided in the circumferential direction of the hydraulic machine 20 in each of a plurality of sections in the axial direction of the hydraulic machine 20, and sleeve holes 52 belonging to different sections are provided. They are arranged with a predetermined phase difference in the circumferential direction of the hydraulic machine 20. For this reason, the arrangement direction of the axial hole row 53 is inclined with respect to the axial direction.

  On the other hand, in the forged part 51 (cylinder block body 50), as shown in FIGS. 2 to 4, a plurality of oil supply passages 30A and a plurality of oil discharge passages 30B extend along the axial direction of the hydraulic machine 20. ing. The oil supply passages 30A and the oil discharge passages 30B in the forged product part 51 are respectively connected to the oil supply grooves 42A of the plurality of cylinder cartridges 38 inserted into the plurality of sleeve holes 52 belonging to the respective axial hole rows 53 and the oil discharge. It opens to the groove 42 </ b> B and communicates with a plurality of hydraulic chambers 25 corresponding to the axial hole rows 53. At this time, as shown in FIGS. 3, 4, and 25, a plurality of oil supply passages 30 </ b> A and a plurality of oil discharge passages 30 </ b> B may be communicated with each hydraulic chamber 25. FIG. 25 is a plan view schematically showing the cylinder block 26.

  In this configuration, even if the arrangement direction of the axial hole rows 53 is inclined with respect to the axial direction, as shown in FIG. 25, each of the oil supply passages 30A and the oil discharge passages 30B is connected to different axial hole rows 53. By communicating with a plurality of hydraulic chambers 25 belonging to the above, each hydraulic chamber 25 can be easily communicated with the oil supply passage 30 and the oil discharge passage 30B.

In some embodiments, as shown in FIGS. 2 to 4, the positions of the plurality of oil supply paths 30 </ b> A in the radial direction of the hydraulic machine 20 are the same as the positions of the plurality of oil discharge paths 30 </ b> B in the radial direction of the hydraulic machine 20. Is different.
Accordingly, the oil supply groove 42A and the oil discharge groove 42B provided at different positions in the radial direction of the hydraulic machine 20 on the outer peripheral surface of each cylinder cartridge 38, and the oil supply path 30A and the oil discharge path 30B in the cylinder block body 50 are provided. Connection with each other becomes easy. Further, by making the positions of the plurality of oil supply passages 30A and the plurality of oil discharge passages 30B in the radial direction of the hydraulic machine 20 different from each other, the same kind of internal oil passage 30 (the oil supply passage 30A or the oil discharge passage 30B) and each annular assembly are arranged. Connection to the paths 35A and 35B (see FIG. 2) is facilitated.

In some embodiments, as shown in FIG. 4, each oil supply passage 30 </ b> A and each oil discharge passage 30 </ b> B are also different from each other in the circumferential direction of the hydraulic machine 20.
In this configuration, the circumferential positions of the oil supply passage 30A and the oil discharge passage 30B are different from each other in the circumferential position where the oil supply passage 30A and the oil discharge passage 30B are provided compared to the case where the oil supply passage 30A and the oil discharge passage 30B are provided at the same circumferential position. The thickness of the cylinder block 26 in the radial direction can be increased. For this reason, the strength of the cylinder block 26 can be increased, and even when a side force acts on the cylinder block 26 from the piston 22 when the piston 22 reciprocates, the torsion of the cylinder block 26 is suppressed. As a result, the durability of the cylinder block 26 is improved and the life of the hydraulic machine 20 can be extended.

  Specifically, in some embodiments, the plurality of internal oil passages 30 (30A, 30B) are arranged in a zigzag shape (staggered shape) in the forged product portion 51 (cylinder block body 50). Thereby, the rigidity of the forged product portion 51 against the torsional moment caused by the force received by the piston 22 from the mechanical element 29 via the contact portion 23 can be ensured.

In some embodiments, the plurality of cylinders 24 includes at least one cylinder row in which m cylinders 24 corresponding to m hydraulic chambers 25 are arranged along the axial direction (where m is an integer of 2 or more). Including. That is, the plurality of sleeve holes 52 include at least one axial hole row 53.
Compared to the downstream group including at least one hydraulic chamber 25 located downstream in the oil supply flow direction in the cylinder block 26 among the m hydraulic chambers 25, the oil supply flow direction in the m hydraulic chambers 25. The upstream group including at least one hydraulic chamber 25 located on the upstream side communicates with more oil supply passages 30A.

  FIG. 26 shows an arrangement of the oil supply passages 30 </ b> A in the case where the axial hole row 53 is constituted by four sleeve holes 52. In this configuration, the hydraulic chamber 25 in the upstream group communicates with more oil passages 30A than the hydraulic chamber 25 in the downstream group. The flow path resistance can be reduced, and the hydraulic oil can be smoothly supplied to the hydraulic chambers 25 in the downstream group.

  In some embodiments, as shown in FIG. 26, the plurality of oil supply passages 30 </ b> A includes a through hole provided in the cylinder block 26 so as to communicate with all of the m hydraulic chambers 25, and an upstream side. And a non-through hole provided in the cylinder block 26 so as to communicate only with at least one hydraulic chamber 25 of the group.

  In this configuration, by providing a non-through hole that communicates with the upstream group hydraulic chamber 25 as the oil supply passage 30A, the flow resistance of the oil supply passage 30A upstream of the upstream group hydraulic chamber 25 with a simple configuration. Can be reduced.

  In some embodiments, the plurality of cylinders 24 includes at least one cylinder row in which m cylinders 24 corresponding to m hydraulic chambers 25 are arranged along the axial direction (where m is an integer of 2 or more). Compared to the downstream group including at least one hydraulic chamber 25 located downstream in the oil supply flow direction in the cylinder block 26 among the m hydraulic chambers 25, the oil supply flow direction in the m hydraulic chambers 25 The upstream group including at least one hydraulic chamber 25 located on the upstream side communicates with the oil supply passage 30A having a larger flow passage area.

  FIG. 27 shows a configuration of the oil supply passage 30 </ b> A in the case where the axial hole row 53 is configured by four sleeve holes 52. In this configuration, the hydraulic chamber 25 in the upstream group communicates with the oil supply passage 30 </ b> A having a larger channel cross-sectional area than the hydraulic chamber 25 in the downstream group, so that it is upstream of the hydraulic chamber 25 in the upstream group. The flow resistance of the oil supply passage 30A can be reduced, and the hydraulic oil can be smoothly supplied to the hydraulic chambers 25 in the downstream group.

  In some embodiments, as shown in FIG. 27, the plurality of oil supply passages 30A are directed from the upstream end of the cylinder block 26 in the oil supply flow direction to at least one hydraulic chamber 25 of the upstream group. A large-diameter hole that extends and communicates with at least one hydraulic chamber 25 of the upstream group, and is provided downstream of the large-diameter hole and concentrically with the large-diameter hole in the oil supply flow direction. And at least one axial oil supply passage having a small-diameter hole communicating with at least one hydraulic chamber 25 of the group.

  In this configuration, by providing a large-diameter hole portion communicating with the upstream group hydraulic chamber 25 as the oil supply passage 30A, the flow path of the oil supply passage 30A upstream of the upstream group hydraulic chamber 25 can be achieved with a simple configuration. The resistance can be reduced, and the hydraulic oil can be smoothly supplied to the hydraulic chambers 25 in the downstream group via the small diameter hole portion concentric with the large diameter hole portion.

  In some embodiments, the plurality of cylinders 24 includes at least one cylinder row in which m cylinders 24 corresponding to m hydraulic chambers 25 are arranged along the axial direction (where m is an integer of 2 or more). Compared to the upstream group including at least one hydraulic chamber 25 located on the upstream side in the oil discharge flow direction in the cylinder block 26 among the m hydraulic chambers 25, the drained oil in the m hydraulic chambers 25 The downstream group including at least one hydraulic chamber 25 located on the downstream side in the flow direction communicates with more drainage passages 30B.

  FIG. 26 also shows the arrangement of the oil drain passages 30 </ b> B in the case where the axial hole row 53 is constituted by four sleeve holes 52. In this configuration, since the hydraulic chamber 25 in the downstream group communicates with more drainage passages 30B than the hydraulic chambers 25 in the upstream group, the drainage passages downstream of the hydraulic chambers 25 in the downstream group. The flow path resistance of 30B can be reduced, and the hydraulic oil can be smoothly discharged from the hydraulic chamber 25 of the upstream group.

  As shown in FIG. 26, in some embodiments, the plurality of oil drain passages 30 </ b> B includes a through hole provided in the cylinder block 26 so as to communicate with all of the m hydraulic chambers 25, and a downstream side. And a non-through hole provided in the cylinder block 26 so as to communicate only with at least one hydraulic chamber 25 of the side group.

  In this configuration, a non-through hole that communicates with the hydraulic chamber 25 in the downstream group is provided as the oil exhaust passage 30 </ b> B. Resistance can be reduced.

  In some embodiments, the plurality of cylinders 24 includes an axial hole row 53 in which m cylinders 24 corresponding to m hydraulic chambers 25 are arranged along the axial direction (where m is an integer of 2 or more). Of m hydraulic chambers 25 as compared with an upstream group including at least one hydraulic chamber 25 located upstream in the direction of oil discharge in the cylinder block 26 among the m hydraulic chambers 25. Among them, the downstream group including at least one hydraulic chamber 25 located on the downstream side in the oil discharge flow direction communicates with the oil discharge passage 30B having a larger flow path area.

  FIG. 27 also shows the configuration of the oil drain passage 30 </ b> B in the case where the axial hole row 53 is configured by four sleeve holes 52. In this configuration, the hydraulic chamber 25 in the downstream group communicates with the oil discharge passage 30 </ b> B having a larger channel cross-sectional area than the hydraulic chamber 25 in the upstream group, so that it is downstream from the hydraulic chamber 25 in the downstream group. Thus, the flow resistance of the oil discharge passage 30B can be reduced, and the hydraulic oil can be smoothly discharged from the hydraulic chamber 25 of the upstream group.

  In some embodiments, as shown in FIG. 27, the plurality of oil discharge passages 30 </ b> B are arranged from the downstream end of the cylinder block 26 in the oil discharge flow direction to at least one hydraulic chamber 25 in the downstream group. A large-diameter hole that extends toward the downstream and communicates with at least one hydraulic chamber 25 of the downstream group, and is provided concentrically with the large-diameter hole on the upstream side in the oil discharge direction from the large-diameter hole. And at least one axial oil drain passage having a small-diameter hole communicating with at least one hydraulic chamber 25 of the upstream group.

  In this configuration, by providing a large-diameter hole portion communicating with the downstream group hydraulic chamber 25 as the oil drain passage 30B, the drain passage 30B downstream of the downstream group hydraulic chamber 25 can be configured with a simple configuration. The flow resistance can be reduced, and the hydraulic oil can be smoothly discharged from the hydraulic chamber 25 of the upstream group via the small diameter hole portion concentric with the large diameter hole portion.

In some embodiments, as shown in FIG. 3, an accumulator 96 that further communicates with the oil supply passage 30A or the oil discharge passage 30B and suppresses pulsation in the oil supply passage 30A or the oil discharge passage 30B is further provided.
In this configuration, since the pulsation is suppressed by the accumulator 96, the radial piston type hydraulic machine 20 can be operated stably.

  As mentioned above, although embodiment of this invention was described in detail, it cannot be overemphasized that this invention is not limited to this, In the range which does not deviate from the summary of this invention, various improvement and deformation | transformation may be performed. For example, a plurality of the above-described embodiments may be appropriately combined.

  For example, in the above-described embodiment, the hydraulic machine 20 used as at least one of the hydraulic pump 8 or the hydraulic motor 10 of the wind turbine generator 1 has been described, but the application of the hydraulic machine 20 is not limited to this.

  In addition, the term “along” used in the description of the above-described embodiment does not indicate only a state that is strictly parallel in a geometric sense to a reference direction or object, It also includes a state in which a certain angle (for example, an angle within 30 degrees) is formed with respect to a reference direction or object.

DESCRIPTION OF SYMBOLS 1 Wind power generator 2 Blade 3 Rotor 4 Hub 5 Hub cover 6 Rotating shaft 8 Hydraulic pump 10 Hydraulic motor 12 High pressure oil line 14 Low pressure oil line 16 Generator 18 Nacelle 19 Tower 20 Hydraulic machine 22 Piston 23 Contact part 23A Roller 24 Cylinder 25 Hydraulic chamber 26 Cylinder block 27 Bearing 27A Thrust-free bearing 28 Rotating shaft 29 Machine element 29A Ring cam 30 Internal oil passage 30A Oil supply passage 30B Oil discharge passage 31 Lobe 32 Displacement restricting portion 32A Cup 32B Thrust bearing 32C Semi-cylindrical member 33A Race 33B Bearing box 33C Rolling element 34 End plate 37 Relative displacement device 38 Cylinder cartridge 40 Cylinder sleeve 40A First sleeve portion 40B Second sleeve portion 41 Oil groove 42 Annular groove 43 Cylinder Assembly 42A oil groove 42B oil discharge groove 50 the cylinder block body 51 forgings 52 sleeve bore 53 axially bore column 60 valve 60A oil feed valve 60B oil discharge valve

Claims (6)

A radial piston type hydraulic machine,
A plurality of pistons arranged along a radial direction of the hydraulic machine;
A cylinder block provided with a plurality of cylinders for respectively guiding the plurality of pistons so as to be capable of reciprocating along the radial direction;
The lobe has a plurality of lobes arranged along the circumferential direction of the hydraulic machine, is provided to face the plurality of pistons, and rotates so that the lobes move in the circumferential direction relative to the plurality of pistons. A ring cam configured to be possible,
The plurality of cylinders includes a cylinder group formed by a plurality of cylinders having different positions in the axial direction of the hydraulic machine,
Each of the plurality of lobes extends linearly in the axial direction over the distribution range of the cylinders in the axial direction in the cylinder group.   For a plurality of cylinders of the cylinder group arranged along the circumferential direction in one section in the axial direction, the cylinder group arranged along the circumferential direction in another section in the axial direction. The radial piston hydraulic machine according to claim 1, wherein at least one cylinder among the plurality of cylinders is displaced in the circumferential direction. A plurality of rollers provided for each of the plurality of pistons between the plurality of pistons and the ring cam;
3. The radial according to claim 1, wherein the ring cam is configured to be movable in the axial direction relative to the plurality of rollers so that a position of contact with the plurality of rollers is shifted. 4. Piston hydraulic machine. At least one thrust-free bearing provided between a rotor portion of the hydraulic machine including the ring cam and a stator portion of the hydraulic machine including the cylinder block;
A displacement restricting portion for restricting relative displacement in the axial direction of the rotor portion with respect to the stator portion,
The radial piston hydraulic machine according to claim 3, wherein the displacement restricting portion is configured to be switchable between a state in which the relative displacement is restricted and a state in which the restriction of the relative displacement is released. .   The radial piston hydraulic machine according to any one of claims 1 to 4, wherein the ring cam is formed by an integrated body continuous in the circumferential direction and the axial direction. At least one blade,
A hub to which the at least one blade is mounted;
A hydraulic pump configured to be driven by rotation of the hub;
A hydraulic motor configured to be driven by pressure oil generated by the hydraulic pump;
A wind turbine generator comprising a generator driven by the hydraulic motor,
At least one of the hydraulic pump and the hydraulic motor is a radial piston hydraulic machine,
The hydraulic machine includes a plurality of pistons arranged along a radial direction of the hydraulic machine, and a cylinder provided with a plurality of cylinders for respectively guiding the plurality of pistons so as to be capable of reciprocating along the radial direction. The lobe has a block and a plurality of lobes arranged along the circumferential direction of the hydraulic machine, and is provided to face the plurality of pistons, and the lobes move in the circumferential direction relative to the plurality of pistons. And a ring cam configured to be rotatable,
The plurality of cylinders includes a cylinder group formed by a plurality of cylinders having different positions in the axial direction of the hydraulic machine,
Each of the plurality of lobes extends linearly in the axial direction over the axial distribution range of the cylinders in the cylinder group.

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