JP6235332B2 - Radial piston hydraulic machine and wind power generator - Google Patents

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.

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

  When the cylinder is integrally provided in the cylinder block, the cylinder block is provided with a sliding portion with a piston or a valve. If wear progresses even at one of these sliding portions, the entire cylinder block must be replaced.

  An object of at least one embodiment of the present invention is to provide a radial piston hydraulic machine and a wind turbine generator that are easy to maintain.

A radial piston hydraulic machine according to at least one embodiment of the present invention,
A radial piston type hydraulic machine,
A plurality of pistons arranged along a radial direction of the hydraulic machine so as to be located along a circumferential direction of the hydraulic machine;
A plurality of cylinders for respectively guiding the plurality of pistons so as to reciprocate along a radial direction of the hydraulic machine;
A low-pressure line capable of communicating with a plurality of hydraulic chambers respectively formed by the plurality of pistons and the plurality of cylinders;
A high-pressure line capable of communicating with the plurality of hydraulic chambers;
A plurality of low-pressure valves provided between the plurality of hydraulic chambers and the low-pressure line, respectively, for switching a communication state between the plurality of hydraulic chambers and the low-pressure line;
A plurality of high pressure valves provided between the plurality of hydraulic chambers and the high pressure line, respectively, and a plurality of high pressure valves for switching communication states between the plurality of hydraulic chambers and the high pressure line;
Each of the low pressure valves and a cylinder block including a cylinder block body in which a plurality of cartridge holes into which cartridges including the high pressure valves are inserted are formed,
Each of the cartridges is configured to be insertable / removable along the radial direction with respect to each of the cartridge holes of the cylinder block body,
In the cylinder block main body, at least one low pressure oil passage for communicating the plurality of hydraulic chambers with the low pressure line, and at least one for communicating the plurality of hydraulic chambers with the high pressure line are provided. A high-pressure oil passage is formed,
Each of the plurality of cartridges includes a low-pressure communication passage for communicating the plurality of hydraulic chambers with the at least one low-pressure oil passage via the plurality of low-pressure valves, and the plurality of cartridges via the plurality of high-pressure valves. A high-pressure communication passage for communicating the hydraulic chamber of the at least one high-pressure oil passage,
At least one of the low-pressure communication path or the high-pressure communication path extends along the radial direction from each of the hydraulic chambers toward a part of the valve body of each of the low-pressure valve or the high-pressure valve. Including a radial flow path having a significantly smaller cross-section, the portion being the portion closest to the hydraulic chamber.
The “radial flow path having a significantly small cross section” means that the diameter of the radial flow path is smaller than ½ of the diameter of the hydraulic chamber.

In the radial piston hydraulic machine, the cartridge forms a sliding portion with the low pressure valve and the high pressure valve. Therefore, when the wear of the sliding portion between the cartridge and the low pressure valve and the high pressure valve progresses, it is sufficient to replace the cartridge and / or the low pressure valve and the high pressure valve, and the cylinder block main body is basically unnecessary.
Further, when replacing the cartridge, it is only necessary to insert and remove the cartridge in the radial direction with respect to the cartridge hole of the cylinder block body, so that the cartridge replacement operation is easy. In addition, since the cartridge can be inserted into and removed from the cartridge hole together with the low pressure valve and the high pressure valve, the low pressure valve and the high pressure valve can be extracted from the cartridge hole together with the cartridge during maintenance of the low pressure valve and the high pressure valve. For this reason, maintenance work such as replacement of the low pressure valve and the high pressure valve is also easy.
Therefore, this radial piston hydraulic machine is easy to maintain.

In one embodiment, each of the plurality of cartridges includes a plurality of cylinder sleeves forming the cylinder, each of the plurality of cylinder sleeves for restricting the piston from slipping out of the plurality of cylinder sleeves. Each of the plurality of pistons may be engaged with the plurality of cylinder sleeves by the end stop, and each of the plurality of cartridges may include each of the plurality of pistons and each of the cylinder block bodies. The cartridge hole is configured to be detachable along the radial direction.
In this case, the cylinder sleeve which is a part of the cartridge forms a sliding portion with the piston. Therefore, even when the wear of the sliding portion between the cylinder sleeve and the piston proceeds, it is not necessary to replace the cylinder block body, and it is sufficient to replace the cylinder sleeve and / or the piston according to the procedure described above.
Further, when replacing the cartridge, it is only necessary to insert and remove the cartridge in the radial direction with respect to the cartridge hole of the cylinder block body, and the replacement operation of the cartridge is easy. In addition, since the cartridge can be inserted into and removed from the cartridge hole together with the piston, the piston can be easily replaced.
Further, since the piston can be engaged with the cylinder sleeve by the end stop, the piston is prevented from coming out of the cylinder sleeve. For this reason, when the cylinder sleeve or the piston is exchanged, the piston is not dropped from the cylinder sleeve, so that the operation is easy.

In some embodiments, the radial piston hydraulic machine includes a plurality of rollers rotatably provided on each of the plurality of pistons, and a plurality of lobes arranged along a circumferential direction of the hydraulic machine. And a ring cam configured to abut the lobe against the plurality of rollers, the cartridge together with at least each of the pistons and each of the rollers from each cartridge hole of the cylinder block body. It is configured to be removable to the opposite side of the ring cam along the radial direction and to be inserted into the cartridge hole of each of the cylinder block main bodies along the radial direction from the opposite side of the ring cam.
In this configuration, the cartridge can be inserted into and removed from the cartridge hole together with the piston and the roller using the space on the opposite side of the ring cam with the cylinder block interposed therebetween without removing the ring cam from the hydraulic machine. Therefore, it is possible to efficiently replace the piston and the roller, and the maintenance of the hydraulic machine is facilitated.

In some embodiments, each of the plurality of rollers can be engaged with the plurality of pistons such that the plurality of rollers are prevented from coming out of the plurality of pistons in the axial direction of the piston.
In this configuration, when the roller is exchanged or the like, the roller is not dropped from the piston, and the operation is easy.

In some embodiments, each of the plurality of cartridge holes has a larger size than the plurality of rollers.
In this configuration, when replacing the roller, the roller can be smoothly extracted from the cylinder block body through the cartridge hole. For example, when a cartridge is inserted into and removed from a cartridge hole together with a piston and a roller, interference between the roller and the cartridge hole can be prevented, and the cartridge hole of the assembly of the piston, roller and cartridge can be smoothly inserted and removed. Can do.

In some embodiments, each of the plurality of cartridge holes has a circular cross-section provided in a first region corresponding to each of a plurality of hydraulic chambers formed by the plurality of pistons and the plurality of cylinders, respectively. The first portion is provided in a second region closer to the roller than the first region, and corresponds to both end portions of each roller with respect to a cross-sectional circle having a diameter smaller than the diagonal length of each roller. And a second portion having a cross-sectional shape to which at least a notch is added.
In this configuration, the cross-sectional area of the second portion of the cartridge hole is smaller than the cross-sectional area of the first portion, and the thickness of the portion of the cylinder block body surrounding the second portion can be increased. Thereby, the intensity | strength of a cylinder block main body can be made high.

Each of the plurality of cartridges includes a plurality of cylinder sleeves forming the cylinder;
In some embodiments, the plurality of cylinder sleeves include a first sleeve portion corresponding to the first portion of the plurality of cartridge holes and a second sleeve portion corresponding to the second portion of the plurality of cartridge holes. And a step is provided between the first sleeve portion and the second sleeve portion.
In this configuration, the cylinder sleeve can be positioned in the cartridge hole using the step of the cylinder sleeve. Further, the thickness of the first sleeve portion can be made thicker than that of the second sleeve portion corresponding to the step, and the cylinder sleeve can be given high strength.

In some embodiments, the cartridge includes a valve block that holds each of the low pressure valves and each of the high pressure valves.
In this case, a valve block including a low pressure valve and a high pressure valve is incorporated in the cartridge. For this reason, there is no low-pressure valve or high-pressure valve between adjacent cartridges, and there is no need to provide a space for installing the low-pressure valve or high-pressure valve in the cylinder block body. Therefore, the installation density of cartridges in the cylinder block can be improved.
Accordingly, the diameter of the cylinder block main body can be reduced to reduce the size of the radial piston hydraulic machine. Alternatively, it is possible to increase the number of cartridges installed in the circumferential direction while maintaining the size of the cylinder block main body, suppress pulsation and vibration, and reduce the noise of the radial piston hydraulic machine.

In some embodiments, in the valve block, the low-pressure valves and the high-pressure valves are arranged along the axial direction of the cartridge.
In this case, since the low-pressure valve and the high-pressure valve are arranged in the axial direction of the cartridge, the valve installation space in the plane orthogonal to the radial direction of the hydraulic machine can be reduced. For this reason, the size of the valve block (cartridge) in the plane orthogonal to the radial direction of the hydraulic machine can be reduced, and the cylinder block main body is secured while maintaining the space between adjacent cartridges in the circumferential direction for the purpose of maintaining the rigidity of the cylinder block body. The block body can be reduced in diameter.

In some embodiments, in the valve block, the low-pressure valves and the high-pressure valves are arranged in a plane including a circumferential direction of the hydraulic machine and an axial direction of the hydraulic machine. The “surface including the circumferential direction and the axial direction of the hydraulic machine” refers to a cylindrical curved surface having the same axis as the hydraulic machine.
In this case, since the low pressure valve and the high pressure valve are arranged in a plane including the circumferential direction and the axial direction of the hydraulic machine, the valve installation space in the radial direction of the hydraulic machine can be reduced. For this reason, the size of the valve block (cartridge) in the radial direction of the hydraulic machine can be reduced, and the thickness of the cylinder block body in the radial direction of the hydraulic machine can be reduced.

In some embodiments, the cylinder block is attached to the cylinder block body, and each of the cartridge blocks inserted into the cartridge holes is restricted from coming out of the cylinder block body along the radial direction. A plurality of lid members.
In this configuration, by using the lid member, it is possible to effectively regulate removal of the cartridge from the cylinder block body.

  In some embodiments, inside the cylinder block body, the at least one low-pressure oil passage and the at least one high-pressure oil passage extend along an axial direction of the hydraulic machine, and the at least one The radial position of one low pressure oil passage is different from the radial position of the at least one high pressure oil passage.

According to this configuration, since both the low-pressure oil passage and the high-pressure oil passage extend in the axial direction, the cylinder block can be prevented from increasing in diameter, and connected to the low-pressure oil passage and the high-pressure oil passage. The piping structure to be made can also be simplified. Further, since both the low pressure oil passage and the high pressure oil passage extend in the axial direction, when there are a plurality of cylinders in the axial direction, the low pressure oil passage and the high pressure oil passage can be communicated with a plurality of hydraulic chambers. . For this reason, one low-pressure oil passage and a plurality of hydraulic chambers can communicate with each other, and one high-pressure oil passage and a plurality of hydraulic chambers can communicate with each other, so that the efficiency of piping can be improved. it can.
Further, the low-pressure oil passage and the high-pressure oil passage 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 low pressure oil passage and the high pressure oil passage may be small, and there is no need to increase the distance between the cylinders. Also from this point, an increase in the size of the cylinder block can be prevented. Or since the space required for the low pressure oil passage and the high pressure oil passage may be small, the number of cylinders arranged in the circumferential direction can be increased. When the number of cylinders is increased, pulsation and vibration can be suppressed.

In some embodiments, the plurality of low-pressure valves are provided at positions farther from the plurality of hydraulic chambers than the plurality of high-pressure valves, and the low-pressure communication path extends from each of the hydraulic chambers to each of the low-pressure valves. Including at least one radial flow path extending along the radial direction toward a valve body of the valve, wherein the high pressure communication path extends from the valve body of each of the high pressure valves toward each of the high pressure oil paths. Including at least one orthogonal flow path extending along a direction orthogonal to the at least one radial flow path so as to avoid the at least one radial flow path.
According to this configuration, the high pressure communication path is provided so as to avoid the low pressure communication path extending along the radial direction, so that the hydraulic chamber and the low pressure oil path communicate with each other through the low pressure valve in a limited space in the cartridge. Thus, the hydraulic chamber and the high-pressure oil passage can be communicated with each other via the high-pressure valve.

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;
At least one hydraulic motor configured to be driven by pressure oil generated by the hydraulic pump;
A wind turbine generator comprising a generator driven by the at least one hydraulic motor,
At least one of the hydraulic pump and the at least one hydraulic motor is a radial piston type hydraulic machine,
The radial piston type hydraulic machine reciprocates along a radial direction of the hydraulic machine with a plurality of pistons arranged along a radial direction of the hydraulic machine so as to be positioned along a circumferential direction of the hydraulic machine. A plurality of cylinders for guiding each of the plurality of pistons so as to be movable, a low pressure line communicating with a plurality of hydraulic chambers formed by the plurality of pistons and the plurality of cylinders, and the plurality of hydraulic chambers. A plurality of low-pressure valves provided between the plurality of hydraulic chambers and the low-pressure line, respectively, for switching a communication state between the plurality of hydraulic chambers and the low-pressure line; Are provided between the hydraulic chamber and the high-pressure line, respectively, for switching the communication state between the plurality of hydraulic chambers and the high-pressure line, respectively. A high pressure valve, a cylinder block including a cylinder block body cartridge hole is formed with a plurality of the cartridge is inserted that contains each of the each of the low-pressure valve the high pressure valve,
Each of the cartridges is configured to be insertable / removable along the radial direction with respect to each of the cartridge holes of the cylinder block body,
In the cylinder block main body, at least one low pressure oil passage for communicating the plurality of hydraulic chambers with the low pressure line, and at least one for communicating the plurality of hydraulic chambers with the high pressure line are provided. A high-pressure oil passage is formed,
Each of the plurality of cartridges includes a low-pressure communication passage for communicating the plurality of hydraulic chambers with the at least one low-pressure oil passage via the plurality of low-pressure valves, and the plurality of cartridges via the plurality of high-pressure valves. A high-pressure communication passage for communicating the hydraulic chamber of the at least one high-pressure oil passage,
At least one of the low-pressure communication path or the high-pressure communication path extends along the radial direction from each of the hydraulic chambers toward a part of the valve body of each of the low-pressure valve or the high-pressure valve. Including a radial flow path having a significantly smaller cross-section, the portion being the portion closest to the hydraulic chamber.
The “radial flow path having a significantly small cross section” means that the diameter of the radial flow path is smaller than ½ of the diameter of the hydraulic chamber.

In the radial piston hydraulic machine, the cartridge forms a sliding portion with the low pressure valve and the high pressure valve. Therefore, when the wear of the sliding portion between the cartridge and the low pressure valve and the high pressure valve progresses, it is sufficient to replace the cartridge and / or the low pressure valve and the high pressure valve, and the cylinder block main body is basically unnecessary.
Further, when replacing the cartridge, it is only necessary to insert and remove the cartridge in the radial direction with respect to the cartridge hole of the cylinder block body, and the replacement operation of the cartridge is easy. In addition, since the cartridge can be inserted into and removed from the cartridge hole together with the low pressure valve and the high pressure valve, the low pressure valve and the high pressure valve can be extracted from the cartridge hole together with the cartridge during maintenance of the low pressure valve and the high pressure valve. For this reason, maintenance work such as replacement of the low pressure valve and the high pressure valve is also easy. Therefore, this radial piston hydraulic machine is easy to maintain, and the wind turbine generator is also easily maintained.

  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 that are easy to maintain.

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 which concerns on one Embodiment 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 the cylinder block in FIG. 2 together with a cartridge, a piston, and a roller extracted from one cartridge hole. FIG. 3 is a schematic cross-sectional view of a cylinder assembly disposed in the cartridge hole of FIG. 2. It is a schematic sectional drawing of the cylinder assembly concerning other embodiments. FIG. 8 is a perspective view schematically showing an engagement plate in FIG. 7. It is a schematic sectional drawing of the cylinder assembly concerning other embodiments. FIG. 7 is a perspective view schematically showing the cylinder assembly in FIG. 6 together with a cartridge hole in a state where a piston and a roller are removed from a cylinder sleeve. It is a top view which shows schematically the cartridge hole in FIG. 10 with a roller. It is a perspective view which shows roughly a part of cylinder sleeve concerning other embodiments with a cartridge hole in the state which removed the piston and the roller. FIG. 13 is a plan view schematically showing a second portion of the cartridge hole in FIG. 12 together with a roller. It is a schematic sectional drawing which follows the XIV-XIV line | wire in FIG. FIG. 7 is a schematic cross-sectional view taken along line XV-XV in FIG. 6. It is a schematic sectional drawing of the cylinder assembly concerning other embodiments. It is schematic sectional drawing in alignment with the XVII-XVII line | wire in FIG. It is a schematic sectional drawing of the cylinder assembly concerning other embodiments. It is a schematic sectional drawing which follows the XIX-XIX line | wire in FIG. 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. 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. It is a top view which shows roughly the cylinder block which concerns on other embodiment. It is a schematic sectional drawing of the cylinder assembly concerning other embodiments. FIG. 27 is a schematic cross-sectional view of the cylinder assembly of FIG. 26 as viewed from 90 degrees. FIG. 27 is a schematic cross-sectional view along the line XXVIII-XXVIII in FIG. 26. FIG. 27 is a schematic cross-sectional view along the line XXIX-XXIX in FIG. 26. FIG. 27 is a perspective view schematically showing the cylinder assembly of FIG. 26 together with a cartridge hole in a state where a piston and a roller are removed from a cylinder sleeve. It is a schematic longitudinal cross-sectional view of the radial piston type hydraulic machine which concerns on other embodiment applicable to the hydraulic motor or hydraulic pump in FIG.

  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 through a high pressure line 12 and a low pressure line 14. Specifically, the outlet of the hydraulic pump 8 is connected to the inlet of the hydraulic motor 10 via the high pressure line 12, and the inlet of the hydraulic pump 8 is connected to the outlet of the hydraulic motor 10 via the low pressure 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 line 12, and the hydraulic motor 10 is driven by this pressure oil. The low-pressure hydraulic oil that has worked in the hydraulic motor 10 is returned to the hydraulic pump 8 again via a low-pressure 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 and 31 are schematic longitudinal sectional views along the axial direction of a radial piston hydraulic machine according to some embodiments, and FIG. 3 is a schematic enlarged view of a part of FIG. FIG. 4 is a schematic partial cross-sectional view showing an enlarged cross section orthogonal to the axial direction of the hydraulic machine in FIG. 2.
In the embodiment shown in FIGS. 2 to 4 and 31, the hydraulic machine 20 includes a plurality of pistons 22 arranged along the circumferential direction of the hydraulic machine 20 and a plurality of pistons 22 for slidably holding the pistons 22. And a cylinder block 26 provided with a plurality of cylinders 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 mechanical element 29 is configured to rotate with the rotating shaft 28 as shown in FIGS. 2 and 31 and has a cam surface that abuts an abutment 23 provided on the piston 22. The cam 29A. In this case, in order to create a relative rotational movement of the cam (mechanical element 29) with respect to the abutting portion 23, at least one between the cam (mechanical element 29) or the rotating shaft 28 rotating with the cam and the cylinder block 26 is provided. Two bearings 27 may be provided. In the exemplary embodiment shown in FIG. 2, two bearings 27 are provided between a rotating shaft 28 and a cylinder block 26 that rotate with a cam (mechanical element 29). In the exemplary embodiment shown in FIG. 31, the cam 29 </ b> A (mechanical element 29) rotates with the housing 21 provided so as to surround the outer periphery of the cylinder block 26 and to rotate integrally with the rotary shaft 28. To do. Two bearings 27 are provided between the housing 21 and the cylinder block 26.
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 other embodiments, the mechanical element 29 is a crankshaft having at least one crankpin configured to rotate with the rotating shaft 28 and coupled to the piston 22 via a connecting rod.
In another embodiment, the cylinder block is provided so as to be rotatable 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, the contact portion is provided on the radially outer side with respect to the piston 22. That is, the ring cam may be outward or inward.

In the cylinder block 26, at least one internal oil passage 30 (30A, 30B) communicating with the plurality of hydraulic chambers 25 is formed.
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). One of the external pipes 36 </ b> A and 36 </ b> B is the high-pressure line 12, and the other is the low-pressure line 14. When the external pipe 36A is the high pressure line 12 and the external pipe 36B is the low pressure line 14, the internal oil path 30A is a high pressure oil path and the internal oil path 30B is a low pressure oil path. On the other hand, when the external pipe 36A is the low pressure line 14 and the external pipe 36B is the high pressure line 12, the internal oil path 30A is a low pressure oil path and the internal oil path 30B is a high pressure oil path.

In some embodiments, the cylinder block 26 includes a plurality of cartridges 38 each having a plurality of cylinders 24 and a cylinder block body 50 having a plurality of cartridge holes 52 into which the plurality of cartridges 38 are respectively inserted. The cartridge 38 is included in the cylinder assembly 43.
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 cartridge 38 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 shared by the cartridge 38 and the cylinder block main body 50, respectively. be able to. Therefore, a suitable design according to the roles of the cartridge 38 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 cartridge 38 extracted from one cartridge hole 52, the piston 22 and the roller 23A. The cartridge 38 is a replaceable container that forms the cylinder 24. In some embodiments, the cartridge 38 includes a cylinder sleeve 80 and also includes components that are combined with the cylinder sleeve 80. The cylinder sleeve 80 only needs to include at least a cylindrical portion (sleeve body portion) that forms the cylinder 24.

  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 cartridge 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 80. 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 internal oil passage 30 extends along the axial direction of the hydraulic machine 20 inside the cylinder block body 50. In this configuration, since the internal oil passage 30 extends along the axial direction, the cylinder block main body 50 can be compared with the case where the internal oil passage 30 extends along the radial direction of the hydraulic machine 20. Miniaturization can be achieved.

In some embodiments, as shown in FIG. 5, the cartridge 38 is configured to be detachable along the radial direction with respect to each cartridge hole 52 of the cylinder block body 50 together with each piston 22. .
Here, “inserting / removing along the radial direction” includes both the case of inserting / removing along the direction away from the axis of the hydraulic machine and the case of inserting / removing along the direction toward the axis of the hydraulic machine. For example, in the case of the exemplary embodiment shown in FIG. 2, the cylinder block 26 and the cartridge 38 (cylinder assembly 43) are arranged on the outer peripheral side of the rotating shaft 28 and the cam 29A. 43) is configured to be detachable along the direction away from the axis of the hydraulic machine 20. On the other hand, in the exemplary embodiment shown in FIG. 31, the cylinder block 26 and the cartridge 38 (cylinder assembly 43) are arranged on the inner peripheral side of the housing 21 and the cam 29A that rotate together with the rotary shaft 28, and the cartridge 38 (cylinder assembly 43) is configured to be detachable along a direction toward the axis of the hydraulic machine 20.

  Further, in some embodiments, as shown in FIG. 5, the cartridge 38 including each cylinder sleeve 80 includes a low pressure valve and a high pressure valve, which will be described later, and the cartridge 38 together with each piston 22 is a cylinder block. The cartridge hole 52 of the main body 50 is configured to be detachable along the radial direction.

  FIG. 6 is a cross-sectional view schematically showing the cylinder assembly 43 disposed in the cartridge hole 52.

  In the configuration according to some embodiments, the cylinder sleeve 80 forms a sliding portion with the piston 22, and when the wear of the sliding portion between the cylinder sleeve 80 and the piston 22 progresses, the cylinder sleeve 80 and / or Alternatively, it is sufficient to replace the piston 22, and the replacement of the cylinder block body 50 is basically unnecessary. Then, when replacing the cylinder sleeve 80 and / or the piston 22, the cartridge 38 to be replaced is pulled out from the cartridge hole 52 of the cylinder block body 50 along the radial direction of the hydraulic machine 20, and a new or repaired cylinder sleeve 80 and It is only necessary to insert the cartridge 38 including the piston 22 into the cartridge hole 52, and the replacement 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 80 having the cylinder 24 are provided separately, the machining on the cylinder block body 50 can be reduced and the number of machining 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 includes an end stop (engagement means) for restricting the withdrawal from the plurality of cylinder sleeves 80, and each of the plurality of pistons 22 includes an end stop (engagement means). ) Can be engaged with a plurality of cylinder sleeves 80. In this configuration, the piston 22 is prevented from coming out of the cylinder sleeve 80, so that the piston 22 does not fall out of the cylinder sleeve 80 when the cylinder sleeve 80 is replaced.

In some embodiments, as shown in FIG. 6, an engagement screw 54 and an engagement groove 55 are provided as an end stop (engagement means) for engaging the cylinder sleeve 80 and the piston 22. Yes. 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 80, 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 80 while allowing the piston 22 to reciprocate in the axial direction of the cylinder 24. In this embodiment, the engaging groove 55 forms an engaging portion with the cylinder sleeve 80 of the piston 22.
In order to prevent damage to the piston 22 and the cylinder sleeve 80, the engagement screw 54 and the engagement groove 55 do not collide with each other in the stroke of the reciprocating motion of the piston 22 and the piston 22 (the wall surface of the engagement groove 55). Configured as follows. In other words, the range of the engagement groove 55 along the piston axial direction is such that the engagement screw 54 does not collide with the wall surface of the engagement groove 55 on the contact portion 23 (roller 23A) side at the top dead center of the piston 22. In addition, at the bottom dead center of the piston 22, it is set according to the stroke of the piston 22 so that the engagement screw 54 does not collide with the wall surface of the engagement groove 55 on the hydraulic chamber 25 side.

In another embodiment, as shown in FIGS. 7 and 8, an engagement plate 56 is provided as an end stop (engagement means) for engaging the cylinder sleeve 80 and the piston 22. The engagement plate 56 has a band plate shape, is fixed to the pressure receiving surface (piston head top 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 80 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 80. In this embodiment, the engagement plate 56 forms an engagement portion with the cylinder sleeve 80 of the piston 22. In order to prevent damage to the piston 22, the engagement plate 56, and the cylinder sleeve 80, the engagement plate 56 is configured so that the engagement plate 56 and the cylinder sleeve 80 do not collide during the reciprocal movement of the piston 22. In other words, the thickness of the engagement plate 56 and the position of the diameter-reduced portion of the cylinder sleeve 80 are such that, at the top dead center of the piston 22, the wall surface on the opposite side of the contact portion 23 (roller 23A) of the hydraulic chamber 25 and the engagement plate. The piston is arranged such that there is a gap between the upper surface of the piston 56 and a gap between the upper surface of the reduced diameter portion of the cylinder sleeve 80 and the lower surface of the engagement plate 56 at the bottom dead center of the piston 22. It is set according to 22 strokes.
The engaging plate 56 can be inserted into the cylinder sleeve 80 before the piston 22 and screwed through a hole provided in the cylinder sleeve 80 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 80, and a screw-in type closing member 57 that can close the hole may be used.

In still another embodiment, as shown in FIG. 9, a snap ring 58 is provided on the outer periphery of the piston 22 as an end stop (engaging means) for engaging the cylinder sleeve 80 and the piston 22. Yes. The snap ring 58 is fitted to the outer periphery of the piston 22 and abuts against the reduced diameter portion of the cylinder sleeve 80, thereby restricting the piston 22 from coming out of the cylinder sleeve 80. In this embodiment, the snap ring 58 forms an engaging portion with the cylinder sleeve 80 of the piston 22.
In order to prevent damage to the piston 22, the snap ring 58, and the cylinder sleeve 80, the snap ring 58 is configured so that the snap ring 58 and the cylinder sleeve 80 do not collide during the stroke of the piston 22. That is, there is a gap between the snap ring 58 mounting position and the reduced diameter portion of the cylinder sleeve 80 at the bottom dead center of the piston 22 between the snap ring 58 and the upper surface of the reduced diameter portion of the cylinder sleeve 80. Thus, it is set according to the stroke of the piston 22.
In order to fit the snap ring 58, the cylinder sleeve 80 may be separable.

In some embodiments, the cartridge 38, along with the piston 22 and the roller 23A, is removable from the plurality of cartridge holes 52 of the cylinder block body 50 to the opposite side of the ring cam that abuts the roller 23A along the radial direction, and It is configured to be insertable into each cartridge hole 52 of the cylinder block body 50 along the radial direction from the opposite side of the ring cam.
In this configuration, without removing the ring cam from the hydraulic machine 20, the cartridge 38 is inserted into and removed from the cartridge hole 52 together with the piston 22 and the roller 23A using the space opposite to the ring cam with the cylinder block 26 interposed therebetween. be able to. Therefore, it is possible to efficiently replace the piston 22 and the roller 23A, and maintenance of the hydraulic machine 20 is facilitated.

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. 6, 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 obstruct the contact between the roller 23A and the cam 29A, and the two arm portions 59 support the roller 23A in a rotatable manner, while maintaining the roller 23A in the axial direction. The escape of the roller 23A from the piston 22 is restricted.
In order to prevent wear and damage to the piston 22 and the arm portion 59, the arm portion 59 is configured so that the arm portion 59 and the cylinder sleeve 80 do not collide during the reciprocating stroke of the piston 22. That is, the length of the arm portion 59 is set according to the stroke of the piston 22 so that a gap exists between the upper surface of the arm portion 59 and the cylinder sleeve 80 at the top dead center of the piston 22.

  In some embodiments, each of the plurality of cartridge holes 52 has a larger size than the plurality of rollers 23A. In this configuration, when replacing the roller 23A, the roller 23A can be extracted from the cylinder block body 50 through the cartridge hole 52 regardless of the size of the roller 23A. When replacing the roller 23A, the roller 23A can be smoothly extracted from the cylinder block body 50 through the cartridge hole 52. For example, when the cartridge 38 is inserted into and removed from the cartridge hole 52 together with the piston 22 and the roller 23A, interference between the roller 23A and the cartridge hole 52 can be prevented. For this reason, the assembly of the piston 22 and the roller 23A and the cartridge 38 can be smoothly inserted into and removed from the cartridge hole 52.

FIG. 10 is a perspective view schematically showing the cylinder assembly 43 and the cartridge hole 52. However, the piston 22 and the roller 23 </ b> A are extracted from the cylinder sleeve 80. FIG. 11 is a plan view schematically showing the roller 23 </ b> A and the cartridge hole 52.
As shown in FIGS. 10 and 11, in some embodiments, each of the plurality of cartridge holes 52 is circular in cross section and has 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 cartridge hole 52.
A notch 63 is formed at one end of the cylinder sleeve 80 located on the roller 23A side so as to correspond 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. 12 is a perspective view schematically showing a cylinder assembly 43 and a cartridge hole 52 according to another embodiment. However, only a part of the cylinder sleeve 80 is shown, and the piston 22 and the roller 23 </ b> A are extracted from the cylinder sleeve 80. FIG. 13 is a plan view schematically showing the roller 23 </ b> A and the cartridge hole 52.

In some embodiments, as shown in FIGS. 12 and 13, the plurality of cartridge 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 cartridge hole 52. On the other hand, according to this configuration, the cross-sectional area of the second portion 52B of the cartridge 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 strength of the cylinder block body 50 can be increased within a range that does not prevent the roller 23A from passing through the cartridge hole 52.
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. 13, 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. 12, the plurality of cylinder sleeves 80 includes a first sleeve portion 80 </ b> A corresponding to the first portion 52 </ b> A of the plurality of cartridge holes 52, and the first of the plurality of cartridge holes 52. And a second sleeve portion 80B corresponding to the two portions 52B. A step 65 is provided between the first sleeve portion 80A and the second sleeve portion 80B.
In the case of this configuration, the cylinder sleeve 80 can be positioned in the cartridge hole 52 using the step 65 of the cylinder sleeve 80. That is, the cylinder sleeve 80 can be positioned in the cartridge hole 52 by bringing the step of the cylinder sleeve 80 into contact with the step 67 of the cartridge hole 52. Further, the thickness of the first sleeve portion 80A can be made thicker than the second sleeve portion 80B corresponding to the step 65, and the cylinder sleeve 80 can be given high strength.

  In some embodiments, as shown in FIGS. 2-4 and 31, the cylinder block 26 is attached to the cylinder block body 50 and the cylinder block bodies of the plurality of cartridges 38 inserted into the plurality of cartridge holes 52. A plurality of lid members 70 are further included for restricting the radial displacement from 50. 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 can effectively restrict the cartridge 38 from coming out of the cylinder block body 50. For this reason, even if the hydraulic oil pressure acts on the cylinder sleeve 80, the cylinder sleeve 80 can be prevented from coming out.

In some embodiments, as shown in FIGS. 3 and 4, the hydraulic machine 20 includes a plurality of hydraulic chambers 25, a low pressure line (not shown) and a high pressure line (not shown) that can communicate with the plurality of hydraulic chambers 25. And a plurality of valves 60 (60A, 60B) provided between them. The plurality of hydraulic chambers 25 are formed by a plurality of pistons 22 and a plurality of cylinders 24, respectively. One of the plurality of valves 60A and 60B is a low-pressure valve that is provided between the plurality of hydraulic chambers 25 and the low-pressure line and switches the communication state between the plurality of hydraulic chambers 25 and the low-pressure line. The other of the plurality of valves 60A and 60B is a high-pressure valve that is provided between the plurality of hydraulic chambers 25 and the high-pressure line and switches the communication state between the plurality of hydraulic chambers 25 and the high-pressure line. That is, when the external piping 36A shown in FIG. 2 is a low pressure line, the internal oil passage 30A shown in FIGS. 3 and 4 is a low pressure oil passage communicating with the low pressure line, and the valve 30A is a low pressure valve. At this time, the external pipe 36B shown in FIG. 2 is a high-pressure line, the internal oil passage 30B shown in FIGS. 3 and 4 is a high-pressure oil passage communicating with the high-pressure line, and the valve 30B is a high-pressure valve. On the other hand, when the external pipe 36A shown in FIG. 2 is a high pressure line, the internal oil passage 30A shown in FIGS. 3 and 4 is a high pressure oil passage communicating with the high pressure line, and the valve 30A is a high pressure valve. At this time, the external pipe 36B shown in FIG. 2 is a low-pressure line, the internal oil passage 30B shown in FIGS. 3 and 4 is a low-pressure oil passage communicating with the low-pressure line, and the valve 30B is a low-pressure valve.
The cartridge 38 including the valve 60 (60A, 60B) is configured to be detachable along the radial direction with respect to the plurality of cartridge holes 52 of the cylinder block body 50.

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

In some embodiments, as shown in FIG. 6, the plurality of cylinders 24 have a central axis (cylinder axis) that coincides with the central axis of the plurality of cylinder sleeves 80.
In this configuration, the inner peripheral surface and the outer peripheral surface of the cylinder sleeve 80 can be formed by lathe processing with a common center hole, and the cylinder sleeve 80 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 cartridge 38 is provided on the outer peripheral surface of the cartridge 38 and opens to at least one internal oil passage 30 (30 </ b> A, 30 </ b> B). A groove 41 is provided.
In this configuration, by providing the oil groove 41 that opens to the internal oil passage 30 on the outer peripheral surface of the cartridge 38, the internal oil passage 30 and the hydraulic chamber 25 can be reliably communicated with each other with a simple configuration. . Accordingly, since high machining accuracy is not required for connection between the hydraulic chamber 25 and the internal 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 80.

In some embodiments, as shown in FIGS. 3 and 4, at least one oil passage 30 includes a plurality of internal oil passages 30 extending along the axial direction of the hydraulic machine 20, and at least one oil passage 30 is provided. Each of the two oil grooves 41 is open to two or more internal oil passages 30 among the plurality of internal oil passages 30.
In this configuration, since the oil groove 41 is provided on the outer peripheral surface of the cartridge 38, the degree of freedom in the configuration of the hydraulic oil flow path is high, and two or more internal oil paths 30 are provided via one oil groove 41. Can be communicated with the hydraulic chamber 25. Therefore, the diameter of each internal 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. 10, the at least one oil groove 41 includes an annular groove 42 (42 </ b> A, 42 </ b> B) that is continuous over the entire circumference of the outer peripheral surface of the cartridge 38. In this configuration, the oil groove 41 on the outer peripheral surface of the cylinder sleeve 80 that opens to the internal oil passage 30 inside the cylinder block body 50 is the annular groove 42, so that the degree of freedom of arrangement of the internal oil passage 30 with respect to the 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 80.

In some embodiments, as shown in FIG. 6, the hydraulic machine 20 includes a plurality of sealing members 44 provided on the outer peripheral surface of the cartridge 38 on both sides of the annular groove 42 to seal each annular groove 42. 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 cartridge 38 and the cartridge hole 52. The seal member 44 is an O-ring made of an elastic material, for example.

  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 for discharging the hydraulic oil from the hydraulic chamber 25. In this case, one of the internal oil passages 30A and 30B is an oil supply passage and the other is an oil discharge passage.

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 internal oil passage 30A and the internal oil passage 30B extend in the axial direction, it is possible to prevent the cylinder block 26 from increasing in diameter, and the internal oil passage 30A and the internal oil passage 30B The piping structure connected to the oil passage 30B can also be simplified.

In some embodiments, the internal oil passage 30 </ b> A and the internal oil 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 internal oil passage 30A and the internal oil 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 internal oil passage 30A and the internal oil 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 internal oil passage 30A and the internal oil 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, a communication path 46 (46 A, 46 B) for communicating the internal oil passage 30 (30 A, 30 B) and the hydraulic chamber 25 is provided inside the cartridge 38. ) 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. One of the communication passages 46A and 46B is a low-pressure communication passage for communicating the hydraulic chamber 25 with the low-pressure oil passage via a low-pressure valve, and the other of the communication passages 46A and 46B is hydraulic via a high-pressure valve. This is a high-pressure communication passage for communicating the chamber 25 with the low-pressure oil passage.
In the exemplary embodiment shown in FIG. 6, the internal oil passage 30 (30A, 30B) and the communication passage 46 (46A, 46B) are connected via an annular groove 42 (42A, 42B).

In some embodiments, as shown in FIGS. 3 and 4, the plurality of valves 60 includes a plurality of oil supply valves 60 </ b> A for switching the supply state of hydraulic oil to the plurality of hydraulic chambers 25, and a plurality of hydraulic pressures, respectively. And a plurality of oil discharge valves 60B for switching the discharge state of the hydraulic oil from the chamber 25, respectively. The plurality of oil supply valves 60A and the plurality of oil discharge valves 60B are included in the plurality of cartridges 38, respectively. A plurality of cartridges 38 each including a plurality of oil supply valves 60A and a plurality of oil discharge valves 60B are disposed in the plurality of cartridge holes 52, respectively.
One of the oil supply valve 60A and the oil discharge valve 60B is provided between the hydraulic chamber 25 and the low pressure line (external piping 36), and the communication state between the hydraulic chamber 25 and the low pressure line (external piping 36) is established. The other of the oil supply valve 60A and the oil discharge valve 60B is provided between the hydraulic chamber 25 and the high pressure line (external piping 36), and the hydraulic chamber 25 and the high pressure line (external piping 36). ) Is a high pressure valve for switching the communication state.

In this configuration, the cartridge 38 including the oil supply valve 60 </ b> A and the oil discharge valve 60 </ b> B is disposed in the cartridge hole 52. The space for installing the oil supply valve 60A and 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 cartridge 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.

More specifically, the oil supply valve 60A and the oil discharge valve 60B are held in a later-described valve block 81 in the cartridge 38.
In this case, a valve block 81 including an oil supply valve 60A and an oil discharge valve 60B is incorporated in the cartridge 38. Therefore, the oil supply valve 60A and the oil discharge valve 60B are not arranged between the adjacent cartridges 38, and it is 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. Absent. Therefore, the installation density of the cartridges 38 in the cylinder block 26 can be improved.
Therefore, it is possible to reduce the diameter of the hydraulic machine 20 by reducing the diameter of the cylinder block body 50. Alternatively, it is possible to increase the number of installed cartridges 38 in the circumferential direction while maintaining the size of the cylinder block main body 50, suppress pulsation and vibration, and reduce the noise of the hydraulic machine 20.

In some embodiments, as shown in FIGS. 3 and 4, at least one annular groove 42 provided in the 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 And an oil drain groove 42B opened to the oil drain passage 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. One of the oil supply communication passage 46A and the drain oil communication passage 46B is a low pressure communication passage for communicating the low pressure oil passage (internal oil passage 30) and the hydraulic chamber 25, and the other is a high pressure oil passage (internal oil passage). 30) and a high-pressure communication passage for communicating the hydraulic chamber 25 with each other.
In this configuration, the oil supply communication passage 46A and the oil discharge communication passage 46B are provided in the 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 can be reliably configured with a simple structure. Can be communicated to.

In other words, each 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 cartridge 38 and opening to the oil supply path 30A, and the second communication path is separated from the oil supply groove 42A in the radial direction. An oil drain groove (second annular groove) 42B provided on the outer peripheral surface of the cartridge 38 at the opened position and opening to the oil drain passage 30B is included.
Of the first communication path and the second communication path, one is a low pressure communication path for communicating the low pressure oil path (internal oil path 30) and the hydraulic chamber 25, and the other is a high pressure oil path (internal oil path 30). ) And the hydraulic chamber 25 to communicate with each other.

  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 cartridge 38, the oil supply passage 30A and the hydraulic chamber 25 can be reliably communicated with each other with a simple configuration. Further, in this configuration, the oil drain groove 30B that opens to the oil drain path 30B is provided at a radial position different from the oil groove 42A on the outer peripheral surface of the cartridge 38, so that the oil drain path 30B can be configured with a simple configuration. 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 cartridge 38 including the cylinder sleeve 80 has the oil supply valve 60 </ b> A and the oil discharge valve 60 </ b> B arranged in the radial direction of the hydraulic machine 20. Has been.

  In this configuration, the oil supply valve 60 </ b> A and the oil discharge valve 60 </ b> B are arranged in the cartridge 38 in a state where they are aligned in the axial direction of the cartridge 38. For this reason, since the oil supply valve 60A and the oil discharge valve 60B are arranged in the radial direction of the hydraulic machine 20, the valve installation space in the plane orthogonal to the radial direction of the hydraulic machine 20 can be reduced. For this reason, the size of the valve block 26 (cartridge 38) in the plane orthogonal to the radial direction of the hydraulic machine 20 can be reduced, and the interval between the adjacent cartridges 38 in the circumferential direction can be reduced for the purpose of maintaining the rigidity of the cylinder block body 50. The diameter of the cylinder block body 50 can be reduced while ensuring.

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 60A and the oil discharge valve 60B are incorporated in the 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 cartridge 38, the cover member 70 can be used to prevent the cartridge hole 52 from being pulled out.
Further, if the oil supply valve 60A and the oil discharge valve 60B are incorporated in the cartridge 38, the processing for the cylinder block body 50 can be reduced, the number of processing steps can be reduced, and the strength of the cylinder block body 50 by the processing can be reduced. A decrease can also be prevented.

3 and 4, in each cartridge hole 52, the valve body 62A of the oil supply valve 60A and the valve body 62B of the oil discharge valve 60B are disposed in the radial direction of the hydraulic machine 20, as shown in FIGS. Are overlapping.
In this configuration, since the valve body 62A of the oil supply valve 60A and the valve body 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 cartridge hole 52 can be reduced. can do.
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 in this way on the outer peripheral surface of each cartridge 38. Are provided at different positions in the radial direction.

In some embodiments, as shown in FIG. 6, 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. In this case, the oil supply radial flow path (first flow path) 48 is a radial flow path, and the oil discharge orthogonal flow path (second flow path) 72 is an orthogonal flow path.
According to this configuration, since the second flow path 72 is provided so as to avoid the first flow path 48 extending along the radial direction, the hydraulic chamber 25 is provided via the oil supply valve 60A in a limited space in the cartridge. The hydraulic chamber 25 and the oil discharge passage 30B can be communicated with each other via the oil discharge valve 60B.

  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.

  The first flow path 48 (a part of the first communication path) extending along the radial direction of the hydraulic machine 20 may be formed by cutting with a drill, or may be formed by cutting or grinding with another machine tool. Good. Further, the first flow path 48 extending along the radial direction of the hydraulic machine 20 has a substantially single diameter, and the diameter of the first flow path 48 in the length direction of the first flow path 48 is substantially equal. Is unchanged. A plurality of straight lines in the length direction of the first flow path 48 included in the curved surface constituting the inner wall of the first flow path 48 are substantially parallel to each other. In addition, the first flow path 48 extending along the radial direction of the hydraulic machine 20 may intersect the draining orthogonal flow path (second flow path) 72, which is a region of different pressures, at a twisted position. Do not cross each other.

14 is a schematic cross-sectional view taken along line XIV-XIV in FIG. 6, and FIG. 15 is a schematic cross-sectional view taken along line XV-XV in FIG.
In some embodiments, as shown in FIG. 14, a plurality of first channels 48 and third channels 47 are arranged around the central axis of the cylinder sleeve 80. As shown in FIG. 15, 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. As shown in FIG. 6, 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, 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, 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.

  FIG. 16 is a schematic cross-sectional view of a cylinder assembly 43 according to another embodiment, and FIG. 17 is a schematic cross-sectional view taken along line XVII-XVII in FIG. In some embodiments, as shown in FIGS. 16 and 17, the plurality of spherical valve bodies 62 </ b> B and the plurality of valve holes 74 are arranged rotationally symmetrically with respect to the central axis of each cylinder 24.

  In this configuration, by providing a plurality of spherical valve bodies 62B and valve holes 74, each valve body 62B and each valve chamber 75 can be made smaller. For this reason, the dead space in the oil discharge valve 60B can be reduced, and the responsiveness of the oil discharge valve 60B can be increased.

FIG. 18 is a schematic cross-sectional view of a cylinder assembly 43 according to another embodiment, and FIG. 19 is a schematic cross-sectional view taken along line XIX-XIX in FIG. In some embodiments, 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. As shown in FIG. 18, the first communication passage that communicates the oil supply passage 30 </ b> A and the hydraulic chamber 25 and the second communication passage that communicates the oil discharge passage 30 </ b> B and the hydraulic chamber 25 are provided from each hydraulic chamber 25. The common flow path 78 extending along the radial direction of the hydraulic machine 20 is shared. Furthermore, the first communication path extends along a direction orthogonal to the common flow path 78, and at least one oil supply orthogonal flow path that communicates the common flow path with the oil supply groove 42A via each oil supply valve 60A. (Fourth flow path) 47 is included.
On the other hand, the second communication passage extends along a direction orthogonal to the common flow path 78, and at least one oil drain that communicates the common flow path 78 with the oil drain groove 42B via each oil drain valve 60B. And an orthogonal flow path (fifth flow path) 72 for use.

  In this configuration, the fourth flow path 47 and the fifth flow path 72 extending along the direction orthogonal to the common flow path 78 are provided, so that the common flow can be made via the oil supply valve 60A with a simple structure. The passage 78 can be communicated with the oil supply groove 42A, and the common flow path 78 can be communicated with the oil discharge groove 42B via the oil discharge valve 60B.

  In some embodiments, each of the plurality of drain valves 60B includes at least one spherical valve body 62B disposed in a valve chamber 75 that communicates with the common flow path 78 via at least one valve hole 74; And an urging member 76 for urging at least one spherical valve body 62 </ b> B toward at least one valve hole 74.

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.

In some embodiments, as shown in FIGS. 6 and 18, the plurality of cartridges 38 each include a cylinder sleeve 80 and a valve block 81. The cylinder sleeve 80 has a substantially cylindrical shape and forms the cylinder 24. The valve block 81 closes one end of the cylinder sleeve 80.
Further, the cartridge 38 is configured to be divided into a first segment 40 and a second segment 85.
In the exemplary embodiment shown in FIGS. 6 and 18, the first segment 40 mainly forms the cylinder sleeve 80, and a part of the first segment 40 and the second segment 85 form the valve block 81.
Each valve block 81 incorporates each oil supply valve 60A and each oil discharge valve 60B. In the exemplary embodiment shown in FIG. 6, the valve block 81 is provided across the first segment 40 and the second segment 85, and each of the oil supply valves 60 </ b> A and the oil discharge valves 60 </ b> B is provided. A valve close to the hydraulic chamber 25 is incorporated in the first segment 40, and a valve far from each hydraulic chamber 25 among each of the oil supply valves 60 </ b> A and each oil discharge valve 60 </ b> B is a second segment separate from the first segment 40. 85.

In the cylinder assembly 43 of FIG. 6, the oil drain valve 60 </ b> B is incorporated in the end portion 84 of the first segment 40. More specifically, a bottomed hole extends in the first segment 40 along the axial direction of the cylinder sleeve 80 so as to open to the hydraulic chamber 25 side, and the valve of the oil discharge valve 60B is provided by the bottomed hole. A chamber 75 is formed. 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 cartridge 38 includes a second segment 85 attached to the first segment 40. The second segment 85 incorporates a valve far from the hydraulic chamber 25 out of the oil supply valve 60A and the oil discharge valve 60B. In the cylinder assembly 43 of FIG. 6, the oil supply valve 60 </ b> A is incorporated in the second segment 85.

  More specifically, the second segment 85 is disposed in the cartridge hole 52 and is disposed adjacent to the end portion 84 of the first segment 40. A cylindrical recess is coaxially formed at the end 84 of the first segment 40. The second segment 85 has a stepped cylindrical shape composed of a small diameter portion and a large diameter portion, and is arranged coaxially with the first segment 40. The small-diameter portion of the second segment 85 is disposed on the first segment 40 side and is fitted into the opening of the concave portion of the end portion 84 of the first segment 40. Thereby, the opening of the recessed part of the end part 84 of the 1st segment 40 is obstruct | occluded by the small diameter part of the 2nd segment 85, and the valve chamber 87 for valve body 62A is formed in the clearance gap between a recessed part and a small diameter part. . The oil supply radial flow path 48 penetrates the end portion 84 of the first segment 40 in the axial direction of the cylinder sleeve 80 and opens in the recess of the end portion 84 of the first segment 40.

  The oil supply orthogonal flow path 47 is provided radially in the small diameter portion of the second segment 85. The small diameter portion of the second segment 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 second segment 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 second segment 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 second segment 85 in the axial direction, and the tip of the shaft portion is disposed at the large diameter portion of the second segment 85.

An armature 89 is provided integrally at the tip of the shaft portion of the valve body 62A. The armature 89 is provided in the large-diameter portion of the second segment 85 so as to freely reciprocate. A core 90 and a solenoid 92 are fixedly provided inside the large diameter portion of the second segment 85, and a compression coil spring is provided as a biasing member 94 between the core 90 and the armature 89. Yes. 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 80.
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.

  On the other hand, in the cylinder assembly 43 of FIG. The lateral hole extends in a direction orthogonal to the axis of the cylinder sleeve 80. A sleeve 83 and a closing member 95 are screwed into the lateral hole, and a valve chamber 75 for accommodating the valve body 62B is formed between the valve seat of the sleeve 83 and the closing member 95. A bottomed spring hole that forms a spring seat is formed on the inner end surface of the closing member 95, and one end of a compression coil spring as the biasing member 76 is accommodated in the spring hole. The compression coil spring as the urging member 76 urges the valve body 62 </ b> B toward the valve hole 74 in a direction orthogonal to the axis of the cylinder sleeve 80.

In the cylinder assembly 43 shown in FIGS. 6 and 18, the oil supply valve 30 </ b> A or the oil discharge valve 30 </ b> B valve is incorporated in the second segment 85 that is separate from the first segment 40 including the cylinder sleeve 80, thereby The processing for incorporating the oil supply valve 30A and the oil discharge valve 30B becomes easy. As a result, the productivity of the radial piston type hydraulic machine 20 can be increased.
Further, in the cylinder assembly 43 shown in FIG. 18, a spherical valve body 62B and a compression coil spring 76 as an urging member 76 are provided side by side in a direction orthogonal to the axial direction of the cylinder sleeve 80. The length of the oil drain valve 60B in the 80 axial direction can be shortened. Thereby, the dead space around the hydraulic chamber 25 can be reduced and the efficiency of the hydraulic machine 20 can be increased.

  Then, while providing a plurality of spherical valve bodies 62B as in the cylinder assembly 43 shown in FIG. 16, a plurality of spherical valve bodies 62B and biasing members 76 are provided as in the cylinder assembly 43 shown in FIG. If the plurality of compression coil springs 76 are provided side by side in the direction orthogonal to the axial direction of the cylinder sleeve 80, the length of the oil discharge valve 60B in the axial direction of the cylinder sleeve 80 can be further reduced. This further reduces the dead space around the hydraulic chamber 25 and increases the efficiency of the hydraulic machine 20.

In some embodiments, as shown in FIG. 5, a plurality of axial hole rows 53 formed by a plurality of cartridge holes 52 arranged in the axial direction of the hydraulic machine 20 are arranged in the circumferential direction of the hydraulic machine 20. Provided. 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 portion 51 are respectively provided with oil supply grooves 42A and oil discharge grooves of the plurality of cartridges 38 inserted into the plurality of cartridge holes 52 belonging to the respective axial hole rows 53. 42B, 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 20, 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. 20 is a plan view schematically showing the cylinder block 26.

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.
Thereby, 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 cartridge 38, and the oil supply path 30A and the oil discharge path 30B in the cylinder block body 50 are provided. Each connection 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 cartridge 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. 21 shows an arrangement of the oil supply passages 30 </ b> A when the axial hole row 53 is constituted by four cartridge holes 52. In this configuration, the hydraulic chamber 25 in the upstream group communicates with more oil passages 30A than the hydraulic chambers 25 in the downstream group, and therefore the oil passage 30A upstream of the hydraulic chambers 25 in the upstream group is connected. 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. 21, the plurality of oil supply passages 30 </ b> A include 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. 22 shows a configuration of the oil supply passage 30 </ b> A in the case where the axial hole row 53 is configured by four cartridge 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. 22, the plurality of oil supply passages 30 </ b> A are directed from the upstream end in the oil supply flow direction of the cylinder block 26 to at least one hydraulic chamber 25 in 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. 21 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 cartridge 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. 21, in some embodiments, the plurality of oil drain passages 30 </ b> B are provided with through holes provided in the cylinder block 26 so as to communicate with all of the m hydraulic chambers 25, and downstream. 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 30B, so that the flow path of the oil exhaust passage 30B downstream from the hydraulic chamber 25 in the downstream group can be achieved with a simple configuration. 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. 22 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 cartridge 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. 22, the plurality of oil discharge passages 30 </ b> B are connected to at least one hydraulic chamber 25 in the downstream group from the downstream end of the cylinder block 26 in the oil discharge flow direction. 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, the plurality of cylinders 24 arranged in the circumferential direction of the hydraulic machine 20 form an annular cylinder group, and when the plurality of cylinder groups are arranged in the axial direction of the hydraulic machine, As shown in FIGS. 23, 24, and 25, adjacent cylinder groups may be arranged with a phase difference from each other. That is, when the plurality of cylinders 24 and the cartridge holes 52 are arranged in the axial direction and the circumferential direction of the hydraulic machine 20, it is not always necessary to arrange them in the axial direction.

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.

In some embodiments, one of the first communication path and the second communication path includes an outer peripheral flow path provided on the outer peripheral surface of each cartridge 38.
When the flow path is provided inside the cartridge, it is necessary to increase the thickness of the cartridge around the flow path so as to withstand the pressure of the hydraulic oil to ensure strength, and it is necessary to enlarge the cartridge 38. On the other hand, when the outer peripheral flow path is provided on the outer peripheral surface of the cartridge 38, the flow paths formed inside the cartridge 38 can be reduced, and the wall thickness of the cartridge 38 is increased by the reduced amount of the internal flow path. Can be reduced. For this reason, the cartridge 38 can be downsized. Alternatively, if the cartridge 38 is the same size, the pressure resistance of the cartridge 38 can be increased.

  Here, FIG. 26 is a schematic cross-sectional view of a cylinder assembly 43 according to some embodiments, and FIG. 27 is a schematic cross-sectional view of the cylinder assembly 43 of FIG. 28 is a schematic cross-sectional view taken along line XXVIII-XXVIII in FIG. 26, FIG. 29 is a schematic cross-sectional view taken along line XXIX-XXIX in FIG. 26, and FIG. 26 is a perspective view schematically showing the cylinder assembly 26 of FIG. 26 together with the cartridge hole 52 in a state where the piston 22 and the roller 23A are removed from the cylinder sleeve 80. FIG.

In the cylinder assembly 43 shown in FIGS. 26 to 30, the first communication passage that connects the oil supply passage 30 </ b> A and the hydraulic chamber 25 via the oil supply valve 60 </ b> A includes the outer peripheral flow passage 98.
Specifically, the outer peripheral flow path 98 is formed by a half-pipe-shaped recess formed on the outer peripheral surface of the cylinder sleeve 80. The outer peripheral flow path 98 extends along the radial direction of the hydraulic machine 20. In other words, the outer peripheral flow path 98 extends along the axis of the cylinder sleeve 80.

  On the other hand, the first communication passage has an oil supply orthogonal flow path 100 extending from the upper part of the hydraulic chamber 25 along a direction orthogonal to the radial direction of the hydraulic machine 20. The oil supply orthogonal flow path 100 passes through the first segment 40 of the cartridge 38 and opens at the bottom surface of the outer peripheral flow path 98. Therefore, the outer peripheral flow path 98 and the hydraulic chamber 25 communicate with each other via the oil supply orthogonal flow path 100.

  On the other hand, the first communication passage has an oil supply orthogonal flow path 102 extending from the valve chamber 87 of the oil supply valve 60 </ b> A along a direction orthogonal to the radial direction of the hydraulic machine 20. The oil supply orthogonal flow path 102 passes through the first segment 40 of the cartridge 38 and opens at the bottom surface of the outer peripheral flow path 98. Accordingly, the outer peripheral flow path 98 and the valve chamber 87 communicate with each other via the oil supply orthogonal flow path 102. Thus, the oil supply orthogonal flow path 100 and the oil supply orthogonal flow path 102 that are separated from each other in the radial direction of the hydraulic machine 20 communicate with each other through the outer peripheral flow path 98, and the valve chamber 87 and the hydraulic chamber 25 communicate with each other.

  In some embodiments, the first flow path includes two peripheral flow paths 98, and the two peripheral flow paths 98 are spaced apart in the diameter direction of the cylinder sleeve 80 and are provided with two orthogonal fuel supply flow paths 100. In addition, two oil supply orthogonal flow paths 102 extend in the diameter direction of the cylinder sleeve 80. The two oil supply orthogonal flow paths 47 and the two oil discharge orthogonal flow paths 72 extend along a direction orthogonal to the separation direction of the outer peripheral flow path 98.

  The oil supply orthogonal flow path 47 and the oil discharge orthogonal flow path 72 have openings on the outer peripheral surface of the cartridge 38, and a seal member 104 is disposed around the openings. The seal member 104 seals the gap between the cartridge 38 and the cartridge hole 52. The seal member 44 is an O-ring made of an elastic material, for example.

  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 machines 20 and 120 used as at least one of the hydraulic pump 8 or the hydraulic motor 10 of the wind turbine generator 1 have been described, but the application of the hydraulic machine 20 is not limited thereto.

  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 line 14 Low pressure 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 28 Rotating shaft 29 Machine element 29A Cam 30 Internal oil passage 30A Oil supply passage 30B Oil discharge passage 34 End plate 35A, 35B Annular collecting passage 36A, 36B External piping 38 Cartridge 40 First segment 41 Oil groove 42 Annular groove 42A Oil supply groove 42B Oil discharge groove 43 Cylinder assembly 44 Seal member 46 Communication path 46A Oil supply communication path 46B Oil discharge communication path 47 Oil supply orthogonal flow path (third flow path, fourth flow path)
48 Radial flow path for oil supply (first flow path)
DESCRIPTION OF SYMBOLS 50 Cylinder block main body 51 Forging part 52 Cartridge hole 52A 1st part 52B 2nd part 53 Axial hole row 54 Engagement screw 55 Engagement groove 56 Engagement plate 57 Closure member 58 Snap ring 59 Arm part 60 Valve 60A Oil supply valve 60B Oil drain valve 62A Valve body 62B Valve body 72 Oil drain orthogonal flow path (second flow path, fifth flow path)
74 Valve hole 75 Valve chamber 76 Energizing member 78 Common flow path 80 Cylinder sleeve 80A First sleeve portion 80B Second sleeve portion 81 Valve block 82 Bottom surface 83 Sleeve 84 End portion 85 Second segment 87 Valve chamber 88 Valve hole 89 Armature 90 Core 92 Solenoid 94 Energizing member 95 Closure member 96 Accumulator 98 Peripheral flow path 100 Oil supply orthogonal flow path 102 Oil supply orthogonal flow path 104 Seal member

Claims (11)

A radial piston type hydraulic machine,
A plurality of pistons arranged along a radial direction of the hydraulic machine so as to be located along a circumferential direction of the hydraulic machine;
A plurality of cylinders for respectively guiding the plurality of pistons so as to reciprocate along a radial direction of the hydraulic machine;
A low-pressure line capable of communicating with a plurality of hydraulic chambers respectively formed by the plurality of pistons and the plurality of cylinders;
A high-pressure line capable of communicating with the plurality of hydraulic chambers;
A plurality of low-pressure valves provided between the plurality of hydraulic chambers and the low-pressure line, respectively, for switching a communication state between the plurality of hydraulic chambers and the low-pressure line;
A plurality of high pressure valves provided between the plurality of hydraulic chambers and the high pressure line, respectively, and a plurality of high pressure valves for switching communication states between the plurality of hydraulic chambers and the high pressure line;
Each of the low pressure valves and a cylinder block including a cylinder block body in which a plurality of cartridge holes into which cartridges including the high pressure valves are inserted are formed,
Each of the cartridges is configured to be insertable / removable along the radial direction with respect to each of the cartridge holes of the cylinder block body,
In the cylinder block main body, at least one low pressure oil passage for communicating the plurality of hydraulic chambers with the low pressure line, and at least one for communicating the plurality of hydraulic chambers with the high pressure line are provided. A high-pressure oil passage is formed,
Each of the plurality of cartridges includes a low-pressure communication passage for communicating the plurality of hydraulic chambers with the at least one low-pressure oil passage via the plurality of low-pressure valves, and the plurality of cartridges via the plurality of high-pressure valves. A high-pressure communication passage for communicating the hydraulic chamber of the at least one high-pressure oil passage,
At least one of the low-pressure communication path or the high-pressure communication path extends along the radial direction from each of the hydraulic chambers toward a part of the valve body of each of the low-pressure valve or the high-pressure valve. It includes a radial passage having a significantly smaller cross-section, wherein a portion Ri Oh closest portion to the hydraulic chamber,
The plurality of low pressure valves are provided at positions farther from the plurality of hydraulic chambers than the plurality of high pressure valves, and the valve bodies of the low pressure valves, the valve bodies of the high pressure valves, and the The hydraulic chambers are arranged in this order in the radial direction,
The low-pressure communication path includes at least one radial flow path extending along the radial direction from each hydraulic chamber toward a valve body of each low-pressure valve;
The high-pressure communication path is orthogonal to the at least one radial flow path so as to avoid the at least one radial flow path from the valve body of each high-pressure valve toward the high-pressure oil path. Including at least one orthogonal flow path extending along the direction;
The radial flow path extends from the hydraulic chamber in the radial direction through the valve body of the high pressure valve toward the valve body of the low pressure valve,
The radial piston hydraulic machine, wherein the orthogonal flow path is located between the valve body of the low pressure valve and the hydraulic chamber in the radial direction . Each of the plurality of cartridges includes a plurality of cylinder sleeves forming the cylinder;
Each of the plurality of cylinder sleeves includes an end stop for restricting the piston from coming out of the plurality of cylinder sleeves, and the plurality of pistons can be engaged with the plurality of cylinder sleeves by the end stop. Yes,
2. The radial piston according to claim 1, wherein each of the plurality of cartridges, together with each of the plurality of pistons, is configured to be detachable along the radial direction with respect to each of the cartridge holes of the cylinder block body. Hydraulic machine. A plurality of rollers provided rotatably on each of the plurality of pistons;
A ring cam having a plurality of lobes arranged along a circumferential direction of the hydraulic machine, the lobes configured to contact the plurality of rollers;
The cartridge, together with at least each piston and each roller, is removable from the cartridge hole of each of the cylinder block bodies along the radial direction to the opposite side of the ring cam, and from the opposite side of the ring cam. 3. The radial piston hydraulic machine according to claim 1, wherein the radial piston hydraulic machine is configured to be insertable into each cartridge hole of the cylinder block body along the radial direction. 4.   4. The radial piston hydraulic machine according to claim 3, wherein each of the plurality of rollers is engageable with the plurality of pistons so as to be prevented from coming out of the plurality of pistons in a piston axial direction.   The radial piston hydraulic machine according to claim 3 or 4, wherein each of the plurality of cartridge holes has a size larger than that of the plurality of rollers.   Each of the plurality of cartridge holes includes a first portion having a circular cross section provided in a first region corresponding to each of a plurality of hydraulic chambers formed by the plurality of pistons and the plurality of cylinders, respectively. Provided in the second region closer to the roller than one region, at least notches corresponding to both ends of each roller are added to the circular cross-section having a smaller diameter than the diagonal length of each roller. The radial piston type hydraulic machine according to claim 5, comprising a second portion having a cross-sectional shape.   The radial piston hydraulic machine according to any one of claims 1 to 6, wherein the cartridge includes a valve block that holds each of the low-pressure valves and the high-pressure valves.   The radial piston hydraulic machine according to claim 7, wherein each of the low-pressure valves and each of the high-pressure valves are arranged along the axial direction of the cartridge in the valve block.   The radial piston type according to claim 7, wherein each of the low pressure valves and each of the high pressure valves are arranged in a plane including a circumferential direction of the hydraulic machine and an axial direction of the hydraulic machine in the valve block. Hydraulic machine.   The cylinder block further includes a plurality of lid members that are attached to the cylinder block main body, and that respectively restrict the radial insertion of the cartridges inserted into the cartridge holes from the cylinder block main body. A radial piston hydraulic machine according to any one of claims 1 to 9. 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;
At least one hydraulic motor configured to be driven by pressure oil generated by the hydraulic pump;
A wind turbine generator comprising a generator driven by the at least one hydraulic motor,
At least one of the hydraulic pump and the at least one hydraulic motor is a radial piston type hydraulic machine,
The radial piston type hydraulic machine reciprocates along a radial direction of the hydraulic machine with a plurality of pistons arranged along a radial direction of the hydraulic machine so as to be positioned along a circumferential direction of the hydraulic machine. A plurality of cylinders for guiding each of the plurality of pistons so as to be movable, a low pressure line communicating with a plurality of hydraulic chambers formed by the plurality of pistons and the plurality of cylinders, and the plurality of hydraulic chambers. A plurality of low-pressure valves provided between the plurality of hydraulic chambers and the low-pressure line, respectively, for switching a communication state between the plurality of hydraulic chambers and the low-pressure line; Are provided between the hydraulic chamber and the high-pressure line, respectively, for switching the communication state between the plurality of hydraulic chambers and the high-pressure line, respectively. A high pressure valve, a cylinder block including a cylinder block body cartridge hole is formed with a plurality of the cartridge is inserted that contains each of the each of the low-pressure valve the high pressure valve,
Each of the cartridges is configured to be insertable / removable along the radial direction with respect to each of the cartridge holes of the cylinder block body,
In the cylinder block main body, at least one low pressure oil passage for communicating the plurality of hydraulic chambers with the low pressure line, and at least one for communicating the plurality of hydraulic chambers with the high pressure line are provided. A high-pressure oil passage is formed,
Each of the plurality of cartridges includes a low-pressure communication passage for communicating the plurality of hydraulic chambers with the at least one low-pressure oil passage via the plurality of low-pressure valves, and the plurality of cartridges via the plurality of high-pressure valves. A high-pressure communication passage for communicating the hydraulic chamber of the at least one high-pressure oil passage,
At least one of the low-pressure communication path or the high-pressure communication path extends along the radial direction from each of the hydraulic chambers toward a part of the valve body of each of the low-pressure valve or the high-pressure valve. It includes a radial passage having a significantly smaller cross-section, wherein a portion Ri Oh closest portion to the hydraulic chamber,
The plurality of low pressure valves are provided at positions farther from the plurality of hydraulic chambers than the plurality of high pressure valves, and the valve bodies of the low pressure valves, the valve bodies of the high pressure valves, and the The hydraulic chambers are arranged in this order in the radial direction,
The low-pressure communication path includes at least one radial flow path extending along the radial direction from each hydraulic chamber toward a valve body of each low-pressure valve;
The high-pressure communication path is orthogonal to the at least one radial flow path so as to avoid the at least one radial flow path from the valve body of each high-pressure valve toward the high-pressure oil path. Including at least one orthogonal flow path extending along the direction;
The radial flow path extends from the hydraulic chamber in the radial direction through the valve body of the high pressure valve toward the valve body of the low pressure valve,
The wind power generator, wherein the orthogonal flow path is located between the valve body of the low-pressure valve and the hydraulic chamber in the radial direction .

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