JP2014129774A - Hydraulic machine and wind power generation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic machine in which convertible energy is increased while upsizing of the hydraulic machine is restrained, and a wind power generation device.SOLUTION: A hydraulic machine comprises: at least one piston 22; at least one cylinder 24 for guiding the at least one piston so as to allow reciprocation; and a machine element 30 configured to interlock with reciprocation of the piston inside the cylinder. In a region surrounded by the cylinder, a plurality of hydraulic chambers 25A and 25B separated by the piston are formed. The machine element is configured to convert a motion mode between the rotation of the machine element and the reciprocation of the piston accompanied by periodical volume changes in each of the plurality of hydraulic chambers.

Description

  The present disclosure relates to a hydraulic machine and a wind turbine generator including the hydraulic machine.

  Conventionally, hydraulic machines for converting energy between rotational energy (mechanical energy) of a rotating shaft and fluid energy of hydraulic oil are known. For example, the hydraulic pump compresses the hydraulic oil using the rotational energy of the rotary shaft and discharges the high-pressure oil. On the other hand, the hydraulic motor applies torque to the rotating shaft using the fluid energy of the high-pressure oil.

  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 structure in which a piston shoe is provided between a plurality of radially arranged pistons and an eccentric shaft, and the piston can be reciprocated by a force transmitted from the eccentric shaft through the piston shoe. A piston-type hydraulic pump is disclosed.

JP 2010-19192 A US Pat. No. 4,629,401

  However, in the hydraulic machines described in Patent Documents 1 and 2, the periodic volume change of one hydraulic chamber and one piston are interlocked. That is, one hydraulic chamber is provided for one piston. Therefore, in order to increase the energy converted between the rotational energy of the rotating shaft and the fluid energy of the hydraulic oil, either the hydraulic chamber is enlarged or the number of pairs of pistons and hydraulic chambers is increased. The method also increases the size of the hydraulic machine.

  An object of at least one embodiment of the present invention is to provide a hydraulic machine and a wind power generator in which convertible energy is increased while suppressing an increase in size of the hydraulic machine.

A hydraulic machine according to at least one embodiment of the present invention includes:
At least one piston,
At least one cylinder for reciprocally guiding the at least one piston;
A mechanical element configured to interlock with the reciprocating motion of each of the pistons within each of the cylinders;
A plurality of hydraulic chambers separated from each other by the piston are formed in a region surrounded by each cylinder.
The mechanical element is configured to convert a motion mode between a reciprocating motion of each of the pistons with a periodic volume change of each of the plurality of hydraulic chambers and a rotational motion of the mechanical element. Features.

In the hydraulic machine, a plurality of hydraulic chambers separated from each other by a piston are formed in a region surrounded by each cylinder, and the reciprocating motion of the piston accompanied by a periodic volume change of each of the plurality of hydraulic chambers and The motion mode is converted between the rotational motion of the machine elements.
Therefore, regardless of the reciprocal phase of each piston, at least one of the plurality of hydraulic chambers separated by the piston in one cylinder is energy between the rotational energy of the rotating shaft and the fluid energy of the hydraulic oil. Can contribute to conversion. For example, when the hydraulic machine is a hydraulic pump, at least one of a plurality of hydraulic chambers separated by the piston in one cylinder is pressed by the piston to reduce the volume regardless of the phase of the reciprocating motion of the piston. Contributes to boosting hydraulic oil. On the other hand, even in the case where the hydraulic machine is a hydraulic motor, at least one of the plurality of hydraulic chambers separated by the piston in one cylinder has a volume by introduction of high-pressure hydraulic oil, regardless of the phase of the reciprocating motion of the piston. Increases, causing the piston to reciprocate. As described above, the plurality of hydraulic chambers provided for one cylinder can contribute to energy conversion between the rotational energy of the rotating shaft and the fluid energy of the hydraulic oil, thereby increasing the size of the hydraulic machine. Large energy can be converted while suppressing the above.

In some embodiments, the hydraulic machine includes a displacement for regulating displacement of each piston in the piston central axis direction so that each piston reciprocates in synchronization with the rotational movement of the machine element. A regulation part is further provided.
The reciprocating motion of each piston synchronized with the rotational motion of the machine element is reliably performed by the action of the displacement restricting portion. Therefore, a plurality of hydraulic chambers provided for one cylinder surely contribute to energy conversion in the hydraulic machine.
In one embodiment, the hydraulic machine further includes at least one connecting portion that connects the mechanical element and the at least one piston, the mechanical element includes a crankshaft, and the displacement restricting portion includes: The engagement portion between the at least one connection portion and the crankshaft. In another embodiment, the hydraulic machine further includes at least one roller provided between the machine element and the at least one piston, and the machine element has a cam surface that contacts the at least one roller. The displacement restricting portion has a contact surface of a profile corresponding to the cam surface, is disposed on the opposite side of the cam with the at least one roller interposed therebetween, and rotates together with the cam. Composed.

In some embodiments, each of the hydraulic chambers has an oil supply port to which an oil supply passage for supplying hydraulic oil to the hydraulic chamber is connected, and an oil discharge passage for discharging the hydraulic oil from the hydraulic chamber. Is connected to the oil discharge port, and the oil discharge port is located above the oil supply port.
As a result, a flow of hydraulic oil is formed in the hydraulic chamber upward toward the oil discharge port when the volume of the hydraulic chamber is contracted. Therefore, even if bubbles are mixed in the hydraulic chamber, the bubbles can be discharged from the oil discharge port to the oil discharge passage by the flow of hydraulic oil in the hydraulic chamber.
If the oil discharge port is provided above the oil supply port, the degree of freedom of arrangement of the hydraulic chamber in the hydraulic machine is limited, and it may be difficult to increase the number of piston and cylinder pairs. . Even in such a case, the hydraulic machine can convert large energy with a small number of pairs of pistons and cylinders for the reasons described above.

In one embodiment, the angle formed by the central axis of the at least one cylinder with respect to the horizontal direction is within 45 degrees.
Thereby, bubbles can be smoothly discharged from the oil discharge port to the oil discharge passage by the flow of hydraulic oil in the hydraulic chamber.

In some embodiments, the at least one cylinder is arranged in a horizontal direction, and the oil filler port is a lower region of the inner peripheral surface of the cylinder that forms a boundary between the hydraulic chambers. The oil outlet is open to an upper region of the inner peripheral surface of the cylinder.
Thereby, air bubbles can be smoothly discharged from the oil discharge port to the oil discharge passage by the flow of the hydraulic oil in the hydraulic chamber when the volume of the hydraulic chamber is contracted.
In one embodiment, the hydraulic machine is provided in the oil supply passage extending to the oil supply port toward the lower region, and an oil supply valve for switching a supply state of hydraulic oil to each of the hydraulic chambers And an oil discharge valve provided in the oil discharge passage extending to the oil discharge port toward the upper region and for switching the discharge state of the hydraulic oil from each of the hydraulic chambers.

In one embodiment, the at least one piston includes at least one piston group including a plurality of pistons arranged along a radial direction of the hydraulic machine, and an axial direction of the hydraulic machine is along a vertical direction. ing.
Thereby, since several piston is arrange | positioned along the radial direction (horizontal direction) of a hydraulic machine, the number of the cylinders along the horizontal direction which can discharge | emit a bubble smoothly can be increased.

In some embodiments, the hydraulic machine further includes at least one connecting portion that connects the mechanical element and the at least one piston, and the at least one piston is a crankshaft as the mechanical element. Including at least one piston group composed of a plurality of pistons arranged along a radial direction of the hydraulic machine, wherein the at least one connecting portion belongs to each of the piston groups. One main rod for connecting one of the pistons to the crankshaft, and at least one for connecting another piston of the plurality of pistons belonging to each of the piston groups to the main rod. A secondary rod of a book.
As a result, the number of pistons belonging to each piston group and arranged along the radial direction of the hydraulic machine can be increased, and more energy can be converted while suppressing an increase in the size of the hydraulic machine.

In one embodiment, the at least one piston group includes a plurality of piston groups arranged in the axial direction of the hydraulic machine, and the plurality of first pistons belonging to the first group of the plurality of rows are: Among the plurality of rows, the plurality of second pistons belonging to the piston group in the second row adjacent to the first row are displaced from each other in the circumferential direction of the hydraulic machine.
Thus, by arranging a plurality of rows of piston groups in the axial direction of the hydraulic machine, the total number of pistons can be increased, and larger energy can be converted. In addition, since the circumferential positions of the pistons are deviated between the adjacent two rows of piston groups, a large number of pistons can be provided while suppressing an increase in the axial size of the hydraulic machine.

In one embodiment, each piston group is connected to the crankshaft via the main rod or via the main rod and the slave rod, and is paired along a horizontal direction. Each of the hydraulic chambers including a piston is connected to an oil supply port to which an oil supply passage for supplying hydraulic oil to the hydraulic chamber is connected, and an oil discharge passage for discharging the hydraulic oil from the hydraulic chamber. The oil supply port is open to a lower region of the inner peripheral surface of the cylinder that forms a boundary between the hydraulic chambers, and the oil discharge port The upper peripheral area of the inner peripheral surface is opened.
Thereby, air bubbles can be smoothly discharged from the oil discharge port to the oil discharge passage by the flow of the hydraulic oil in the hydraulic chamber when the volume of the hydraulic chamber is contracted.

In some embodiments, the hydraulic machine further includes at least one connecting portion that connects the mechanical element and the at least one piston, and the plurality of hydraulic chambers includes a first hydraulic chamber, A second hydraulic chamber located farther from the mechanical element than the first hydraulic chamber, and each of the connecting portions penetrates at least the first hydraulic chamber, and the first hydraulic chamber is formed by each of the connecting portions. A seal member is provided in the penetrating portion of the hydraulic chamber.
Thereby, the leak of the hydraulic fluid from the penetration part of the 1st hydraulic chamber by a connection part can be prevented. Therefore, it is possible to suppress a decrease in performance of the hydraulic machine due to hydraulic oil leakage.

In one embodiment, the mechanical element includes a crankshaft, and each of the connecting portions is fixed to each of the pistons and has a first rod portion penetrating the first hydraulic chamber and one end of the crankshaft. And a second rod portion whose other end is engaged with the first rod portion, and the engaging portion between the first rod portion and the other end of the second rod portion is the first rod portion. Located outside the hydraulic chamber.
Depending on the phase of the rotational movement of the crankshaft as a mechanical element, the angle formed between the end of the connecting portion connected to the crankshaft and the piston axial direction changes periodically. Therefore, the connecting portion rotates within a predetermined angle range in accordance with the rotational movement of the crankshaft. At this time, it may be desired to maintain the sealing performance of the through portion of the first hydraulic chamber by the connecting portion while allowing the connecting portion to rotate.
In this regard, as described above, the connection portion including the first rod portion and the second rod portion is adopted, and the engaging portion between the first rod portion and the second rod portion is provided outside the first hydraulic chamber. Only the second rod portion on the crankshaft side rotates with respect to the first rod portion on the piston side, and the first rod portion penetrating the first hydraulic chamber moves linearly. Therefore, it becomes easy to maintain the sealing performance of the penetrating portion of the first hydraulic chamber by the linearly moving first rod portion while allowing the second rod portion to rotate.

A wind turbine generator according to at least one embodiment of the present invention,
At least one blade,
A hub to which the at least one blade is mounted;
A hydraulic pump configured to be driven by rotation of the hub;
A hydraulic motor configured to be driven by pressure oil generated by the hydraulic pump;
A generator driven by the hydraulic motor,
At least one of the hydraulic pump and the hydraulic motor includes at least one piston, at least one cylinder for reciprocatingly guiding the at least one piston, and each piston within each cylinder. A mechanical element configured to interlock with reciprocating motion,
A plurality of hydraulic chambers separated from each other by the piston are formed in a region surrounded by each piston and each cylinder.
The mechanical element is configured to convert a motion mode between a reciprocating motion of each of the pistons accompanied by a periodic volume change of each of the plurality of hydraulic chambers and a rotational motion of the mechanical element.

In the wind turbine generator, at least one of the hydraulic pump and the hydraulic motor is formed with a plurality of hydraulic chambers separated from each other by pistons in a region surrounded by each cylinder, and each cycle of the plurality of hydraulic chambers is The motion mode is converted between the reciprocating motion of the piston accompanied by a general volume change and the rotational motion of the mechanical element.
Therefore, each of the plurality of hydraulic chambers provided for one cylinder can contribute to energy conversion between the rotational energy of the rotating shaft and the fluid energy of the hydraulic oil. Large energy can be converted while suppressing one size increase.

  According to at least one embodiment of the present invention, a plurality of hydraulic chambers provided for one cylinder can contribute to energy conversion between the rotational energy of the rotating shaft and the fluid energy of the hydraulic oil, respectively. . Therefore, large energy can be converted while suppressing an increase in size of at least one of the hydraulic machines.

It is a figure which shows the wind power generator which concerns on one Embodiment. 1 is a schematic view of a radial piston hydraulic machine according to an embodiment. 1 is a schematic view of a radial piston hydraulic machine according to an embodiment. 1 is a schematic view of a radial piston hydraulic machine according to an embodiment. It is a schematic sectional drawing along the radial direction of the hydraulic machine concerning one embodiment. It is a schematic sectional drawing along the axial direction of the hydraulic machine which concerns on one Embodiment. 1 is a schematic view of a hydraulic machine according to an embodiment. 1 is a schematic view of a hydraulic machine according to an embodiment. 1 is a schematic view of a hydraulic machine according to an embodiment. FIG. 10 is a schematic external view of the hydraulic machine shown in FIG. 9. It is a fragmentary sectional view along the radial direction of the hydraulic machine concerning one embodiment. It is a fragmentary sectional view along the axial direction of the hydraulic machine shown in FIG. FIG. 12 is a perspective view of the vicinity of a displacement restricting portion of the hydraulic machine shown in FIG. 11.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, and the like 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 an embodiment.
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 one embodiment, a hydraulic pump 8 is connected to the rotor 3 via a rotating shaft 6. A hydraulic motor 10 is connected to the hydraulic pump 8 via a high pressure oil line 12 and a low pressure oil line 14. Specifically, the outlet of the hydraulic pump 8 is connected to the inlet of the hydraulic motor 10 via the high-pressure oil line 12, and the inlet of the hydraulic pump 8 is connected to the outlet of the hydraulic motor 10 via the low-pressure oil line 14. The hydraulic pump 8 is driven by the rotary shaft 6 to increase the pressure of the hydraulic oil and generate high-pressure hydraulic oil (pressure oil). The pressure oil generated by the hydraulic pump 8 is supplied to the hydraulic motor 10 via the high-pressure oil line 12, and the hydraulic motor 10 is driven by this pressure oil. The low-pressure hydraulic oil after the work is performed by the hydraulic motor 10 is returned again to the hydraulic pump 8 via the low-pressure oil line 14 provided between the outlet of the hydraulic motor 10 and the inlet of the hydraulic pump 8.
A generator 16 is connected to the hydraulic motor 10. In one embodiment, the generator 16 is a synchronous generator that is 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 one embodiment, 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 to 4 are schematic views of a radial piston hydraulic machine according to the embodiment.
As shown in FIGS. 2 to 4, the hydraulic machine 20 includes at least one piston 22 and at least one cylinder 24 for guiding the piston 22. Each piston 22 is guided by a corresponding cylinder 24 and can reciprocate in the cylinder 24. Further, the hydraulic machine 20 includes a mechanical element 30 configured to be interlocked with the reciprocating motion of each piston 22. The machine element 30 rotates with the rotating shaft of the hydraulic machine 20. The motion mode is converted between the reciprocating motion of the piston 22 and the rotational motion of the mechanical element 30.

  In some embodiments, a plurality of hydraulic chambers 25 (25A, 25B) separated by at least one piston 22 are formed in the region surrounded by each cylinder 24. When each piston 22 reciprocates within the cylinder 24, the volumes of the plurality of hydraulic chambers (25A, 25B) separated by the piston 22 within one cylinder 24 change periodically.

In the exemplary embodiment shown in FIG. 2, one piston 22 is provided in a region surrounded by the cylinder 24, and a pair of hydraulic chambers 25 </ b> A and 25 </ b> B are formed on both sides of the piston 22.
In another embodiment, as shown in FIG. 3, two pistons 22 </ b> A and 22 </ b> B are provided in a region surrounded by the cylinder 24. Specifically, the area surrounded by the cylinder 24 is divided into two spaces by a partition wall 24A of the cylinder 24, and one of the piston 22A and the piston 22B is provided in each space. A pair of hydraulic chambers 25 are formed on both sides of each piston 22A, 22B, and four hydraulic chambers 25A to 25D are provided as the entire cylinder 24.
In still another embodiment, as shown in FIG. 4, two pistons 22 </ b> A and 22 </ b> B are provided in a region surrounded by the cylinder 24. Specifically, the area surrounded by the cylinder 24 is divided into two spaces by a partition wall 24A of the cylinder 24, and one of the piston 22A and the piston 22B is provided in each space. One hydraulic chamber 25A is formed on one side of the piston 22A near the mechanical element 30, and a pair of hydraulic chambers 25B and 25C are formed on both sides of the other piston 22B. The cylinder 24 as a whole has three hydraulic chambers 25A. ~ 25C are provided.

  When the hydraulic machine 20 is a hydraulic pump, the rotary motion of the machine element 30 that rotates together with the rotary shaft of the hydraulic machine 20 is converted into the reciprocating motion of the piston 22, and periodic volume changes of the plurality of hydraulic chambers 25 occur. 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 each hydraulic chamber 25, and the reciprocating motion is converted into the rotational motion of the mechanical element 30. The rotating shaft of the hydraulic machine 20 rotates together with the machine element 30.

  Thus, the mechanical element 30 converts the energy between the kinetic energy (mechanical energy) of the rotating shaft of the hydraulic machine 20 and the fluid energy of the hydraulic oil, and the hydraulic machine 20 is used as a hydraulic pump or a hydraulic motor. It has come to play the role of the period.

At this time, by providing a plurality of hydraulic chambers 25 for one cylinder 24, the energy exchanged between the kinetic energy of the rotating shaft of the hydraulic machine 20 and the fluid energy of the hydraulic oil increases. In other words, at least one of the plurality of hydraulic chambers 25 separated by the piston 22 in one cylinder 24 is free from the rotational energy of the rotating shaft of the hydraulic machine 20 and the hydraulic oil regardless of the phase of the reciprocating motion of the piston 22. It can contribute to energy conversion with fluid energy. That is, the hydraulic machine is operated by at least one of the plurality of hydraulic chambers 25 regardless of whether the piston 22 is in a period from the bottom dead center to the top dead center or whether the piston 22 is in a period from the top dead center to the bottom dead center. Energy conversion at 20 is performed.
For example, when the hydraulic machine 20 is a hydraulic pump, at least one of a plurality of hydraulic chambers 25 separated by the piston 22 in one cylinder 24 is pressed by the piston 22 regardless of the phase of the reciprocating motion of the piston 22. As a result, the volume is reduced, which contributes to pressurization of the hydraulic oil. On the other hand, even when the hydraulic machine 20 is a hydraulic motor, at least one of the plurality of hydraulic chambers 25 separated by the piston 22 in one cylinder 24 operates at a high pressure regardless of the phase of the reciprocating motion of the piston 22. The introduction of oil increases the volume, causing the piston 22 to reciprocate.

  In some embodiments, as shown in FIGS. 2 to 4, each of the hydraulic chambers 25 (25 </ b> A to 25 </ b> D) has an oil supply port 42 (42 </ b> A to 42 </ b> D) to which the oil supply passage 40 (40 </ b> A to 40 </ b> D) is connected, And an oil discharge port 52 (52A to 52D) to which the oil discharge passage 50 (50A to 50D) is connected. The hydraulic oil is supplied to each hydraulic chamber 25 via the oil supply passage 40 and the oil supply port 42, and the hydraulic oil is discharged from each hydraulic chamber 25 via the oil discharge passage 50 and the oil discharge port 52. It has become.

Further, each of the oil supply passages 40 (40A to 40D) is provided with an oil supply valve 44 (44A to 44C) for switching the supply state of the hydraulic oil to each of the hydraulic chambers 25 (25A to 25D). Similarly, each oil drain passage 50 (50A to 50D) is provided with a drain valve 54 (54A to 54C) for switching the discharge state of the hydraulic oil from each hydraulic chamber 25 (25A to 25D). .
The oil supply valve 44 and the oil discharge valve 54 corresponding to each hydraulic chamber 25 are opened and closed based on the phase of the periodic volume change of the hydraulic chamber 25. For example, when the volume of the hydraulic chamber 25 is reduced in conjunction with the reciprocating motion of the piston 22, the oil supply valve 44 is closed and the oil discharge valve 54 is opened. Conversely, when the volume of the hydraulic chamber 25 increases in conjunction with the reciprocating motion of the piston 22, the oil supply valve 44 is opened and the oil discharge valve 54 is closed.

In some embodiments, as shown in FIGS. 2 to 4, the oil discharge port 52 is located above the oil supply port 42 in each hydraulic chamber 25.
Thereby, in the hydraulic chamber 25, a flow of hydraulic oil is formed upward toward the oil discharge port 52 when the volume of the hydraulic chamber 25 is reduced. Therefore, even if bubbles are mixed in the hydraulic chamber 25, the bubbles can be discharged from the oil discharge port 52 to the oil discharge passage 50 by the flow of the hydraulic oil in the hydraulic chamber 25.

  If the oil discharge port 52 is provided above the oil supply port 42, the degree of freedom of the arrangement of the hydraulic chamber 25 inside the hydraulic machine 20 is limited, and the number of pairs of pistons 22 and cylinders 24 is increased. May be difficult. Even in such a case, the hydraulic machine 20 is provided with a plurality of hydraulic chambers 25 for one cylinder 24 as described above, so that a large amount of energy can be obtained with a small number of pairs of pistons 22 and cylinders 24. Can be converted.

  Further, from the viewpoint of smooth discharge of bubbles from the oil discharge port 52 located above the oil supply port 42 to the oil discharge passage 50, the angle formed by the central axis of the cylinder 24 with respect to the horizontal direction may be within 45 degrees. Good.

In one embodiment, the cylinder 24 is disposed along the horizontal direction, and the oil filler port 42 opens to a lower region of the inner peripheral surface 24B of the cylinder 24 that forms the boundary of each hydraulic chamber 25. The oil discharge port 52 is open to the upper region of the inner peripheral surface 24 </ b> B of the cylinder 24.
As a result, bubbles can be smoothly discharged from the oil discharge port 52 to the oil discharge passage 50 by the flow of hydraulic oil in the oil pressure chamber 25 when the volume of the hydraulic chamber 25 is contracted.

In some embodiments, the hydraulic machine 20 includes a displacement for restricting the displacement of each piston 22 in the direction of the piston center axis such that each piston 22 reciprocates in synchronization with the rotational movement of the machine element 30. The regulation part 100 is further provided.
In the exemplary embodiment shown in FIGS. 2 to 4, the hydraulic machine 20 further includes a connecting portion 60 for connecting the crankshaft as the mechanical element 30 and the piston 22, and the displacement restricting portion 100 is connected to the connecting portion 60. And an engaging portion 61 with the crankshaft (specifically, the crankpin 32 of the crankshaft). As shown in FIGS. 2 to 4, the crank pin 32 is provided eccentric to the crankshaft center O. For this reason, while the crankshaft as the mechanical element 30 makes one rotation, the center of the end of the connecting portion 60 engaged with the crankpin 32 in the engaging portion 61 has a circular locus as indicated by reference numeral 33. Draw. As a result, the rotation of the crankshaft as the mechanical element 30 and the reciprocating motion of the piston 22 connected to the crankshaft by the connecting portion 60 are interlocked.
In this way, the reciprocating motion of each piston 22 synchronized with the rotational motion of the crankshaft as the mechanical element 30 is reliably performed by the action of the displacement restricting portion 100 (the engaging portion 61 between the crank pin 32 and the connecting portion 60). . Therefore, the plurality of hydraulic chambers 25 provided for one cylinder 24 surely contribute to energy conversion in the hydraulic machine 20.

In some embodiments, as shown in FIGS. 2 and 3, the connecting portion 60 passes through the first hydraulic chamber 25 </ b> A closest to the mechanical element 30, and the through portion of the first hydraulic chamber 25 </ b> A by the connecting portion 60. Is provided with a seal member 29A.
Thereby, the leak of the hydraulic fluid from the penetration part of 25 A of 1st hydraulic chambers by the connection part 60 can be prevented. Therefore, it is possible to suppress a decrease in performance of the hydraulic machine 20 due to hydraulic oil leakage.

In one embodiment, the connecting portion 60 is fixed to the piston 22 and penetrates the first hydraulic chamber 25A, and one end is engaged with the crankshaft (crank pin 32) and the first rod portion. 62 and a second rod portion 64 with the other end engaged.
Here, in the exemplary embodiment shown in FIGS. 2 and 3, the engaging portion 65 between the first rod portion 62 and the other end of the second rod portion 64 is located outside the first hydraulic chamber 25A. As a result, only the second rod portion 64 on the crankshaft side rotates relative to the first rod portion 62 on the piston 22 side, and the first rod portion 62 penetrating the first hydraulic chamber 25A moves linearly. It becomes like this. Therefore, it is easy to seal the penetrating portion of the first hydraulic chamber 25A by the linearly moving first rod portion 62 with the seal member 29A while allowing the second rod portion 64 to rotate.

In the exemplary embodiment shown in FIG. 2, an extension rod 66 is provided along the axial direction of the cylinder 24 on the opposite side of the connecting portion 60 (first rod portion 62) across the piston 22. A sealing member 29B is provided in the penetrating portion of the second hydraulic chamber 25B.
Thereby, the reciprocating motion of the piston 22 in the cylinder 24 is stabilized by the extension rod 66, and the leakage of hydraulic oil from the penetrating portion of the second hydraulic chamber 25B by the extension rod 66 can be prevented.

In the exemplary embodiment shown in FIGS. 3 and 4, a first extension rod 66A is provided along the axial direction of the cylinder 24 on the opposite side of the connecting portion 60 (first rod portion 62) across the piston 22A. A sealing member 29C is provided at a portion where the partition wall 24A is penetrated by the first extension rod 66A. Further, a second extension rod 66B is provided along the axial direction of the cylinder 24 on the opposite side of the first extension rod 66A across the piston 22B, and the hydraulic chamber 25 farthest from the machine element 30 (the hydraulic chamber in FIG. 3). 25D and a hydraulic member 25C in FIG. 4) is provided with a seal member 29D in a through portion of the second extension rod 66B.
In this way, it is possible to prevent leakage of hydraulic oil from the through portion of the partition wall 24A by the first extension rod 66A and the through portion of the hydraulic chamber 25 by the second extension rod 66B.

  Further, a piston group composed of a plurality of pistons 22 arranged along the radial direction of the hydraulic machine 20 is provided around a crankshaft as the machine element 30, and the plurality of pistons are interlocked with the rotation of the crankshaft. You may make it 22 reciprocate.

FIG. 5 is a schematic cross-sectional view along the radial direction of the hydraulic machine 20 according to the embodiment. FIG. 6 is a schematic cross-sectional view along the axial direction of the hydraulic machine 20 according to the embodiment. 5 and 6, the same parts as those in FIGS. 2 to 4 are denoted by the same reference numerals, and the description thereof is omitted here.
In some embodiments, the hydraulic machine 20 has at least one piston group composed of a plurality of pistons 22 arranged around the crankshaft (crankpin 32) along the radial direction of the hydraulic machine 20. In the exemplary embodiment shown in FIG. 5, a piston comprising six pistons 22 arranged at angular positions shifted by 60 degrees with respect to the crankshaft center O (that is, the central axis of the rotating shaft 21 of the hydraulic machine 20). A group is provided. In the exemplary embodiment shown in FIG. 6, the piston group composed of a plurality of pistons 22 arranged around the crankpin 32 along the radial direction of the hydraulic machine 20 includes two pistons in the axial direction of the hydraulic machine 20. A column is provided.

By the way, in the case of a star engine, the explosion process in each cylinder is performed only once per two rotations of the crankshaft (characteristic of a 4-stroke engine). Therefore, the star engine is designed such that the explosion process in the cylinder is skipped with the rotation of the crankshaft, and the explosion process in all the cylinders is completed while the crankshaft rotates twice. For this reason, the number of pistons in each piston group in a typical star engine is an odd number.
On the other hand, since the hydraulic machine 20 does not have the above-described problem in the star engine, the number of pistons 22 belonging to each piston group may be an even number (for example, six as shown in FIG. 5).

  In one embodiment, as shown in FIGS. 5 and 6, at least one connecting portion 60 for connecting at least one piston 22 to a crankshaft (crank pin 32) as a mechanical element 30 is provided as one main part. A rod 70 and at least one slave rod 80 are included.

Only one main rod 70 is provided for each piston group. Through the main rod 70, one piston among the plurality of pistons 22 belonging to each piston group is connected to the crankshaft (crank pin 32).
In one embodiment, the crankshaft 32 of the crankshaft is inserted into a crankpin hole 72 formed at one end of the main rod 70. A plain bearing may be provided between the crankpin hole 72 and the crankpin 32. The other end of the main rod 70 is connected to the first rod portion 62 that is fixed to the piston 22 and penetrates the first hydraulic chamber 25A. In one embodiment, the main rod 70 is connected to the first rod portion 62 by a pin 74 that is inserted into an end portion of the first rod portion 62 and a pin hole provided in the other end of the main rod 70.

Of the plurality of pistons 22 belonging to each piston group, pistons other than the piston connected to the crankpin 32 of the crankshaft via the main rod 70 are connected to the main rod 70 via the slave rod 80.
In one embodiment, one end of each sub rod 80 is connected to the main rod 70 by a pin 78 inserted into a pin hole 76 formed in the one end of the main rod 70 (the end where the crank pin hole 72 is provided). Connected. A sliding bearing may be provided between the main rod 70 and the pin 78. The other end of each slave rod 80 is connected to a first rod portion 62 that is fixed to the piston 22 and penetrates the first hydraulic chamber 25A. In one embodiment, the slave rod 80 is connected to the first rod portion 62 by a pin 84 that is inserted into an end portion of the first rod portion 62 and a pin hole 82 provided in the other end of the slave rod 80.

  In this way, by connecting a plurality of pistons 22 belonging to each piston group to the crankshaft (crank pin 32) via one main rod 70 and at least one sub rod 80, at the same axial position. The number of pistons 22 that can be arranged along the radial direction of the hydraulic machine 20 can be increased. Therefore, it is possible to convert larger energy while suppressing an increase in size of the hydraulic machine 20.

In one embodiment, the engaging portion 65 (see FIG. 6) between the main rod 70 and the first rod portion 62 is located outside the first hydraulic chamber 25A, and the main rod 70 is the first around the pin 74. The first rod portion 62 is configured to move linearly with respect to the rod portion 62. Similarly, the engaging portion 85 (see FIG. 6) between the slave rod 80 and the first rod 62 is located outside the first hydraulic chamber 25A, and the slave rod 80 is centered on the pin 84 and the first rod portion 62 is located. The first rod portion 62 is configured to move linearly.
Thereby, it becomes easy to seal the penetration part of 25 A of 1st hydraulic chambers by the 1st rod part 62 with 29 A of sealing members.

FIG. 7 is a schematic view of a hydraulic machine according to another embodiment. In FIG. 7, the same parts as those in FIGS. 5 and 6 are denoted by the same reference numerals, and the description thereof is omitted here.
In some embodiments, a plurality of piston groups including a plurality of pistons 22 provided around the crankshaft at the same axial position are provided in the axial direction of the hydraulic machine 20. In the exemplary embodiment shown in FIG. 7, the plurality of first pistons 122 (and the corresponding cylinders 124) belonging to the first row of piston groups among the plurality of rows are arranged in the second row adjacent to the first row. The circumferential positions of the plurality of second pistons 222 (and the corresponding cylinders 224) belonging to the piston group are shifted. In FIG. 7, the first row of piston groups including six first pistons 122 is shown on the front side of the drawing, and the second row of piston groups including six second pistons 22 is illustrated as the first row of pistons. Shown on the back side of the group.
By arranging a plurality of piston groups in the axial direction of the hydraulic machine 20, the total number of pistons 22 (the first piston 122 and the second piston 222) can be increased, and while suppressing an increase in the size of the hydraulic machine 20, Big energy can be converted. In addition, since the circumferential positions of the pistons 122 and 222 are shifted between the adjacent two rows of piston groups, the large number of pistons 22 (the first piston 122 and the second piston 22 are controlled while suppressing the axial size of the hydraulic machine 20). A piston 222) can be provided.

FIG. 8 is a schematic view of a hydraulic machine according to another embodiment. In FIG. 8, the same parts as those in FIGS. 2 to 7 are denoted by the same reference numerals, and the description thereof is omitted here.
In one embodiment, as shown in FIG. 8, each piston group includes a pair of pistons 22 arranged along the horizontal direction. The pair of pistons 22 is connected to the crankpin 32 of the crankshaft through the main rod 70 or through the main rod 70 and the sub rod 80. Each hydraulic chamber 25 (25A, 25B) corresponding to each piston 22 is connected to an oil supply passage 40 (40A, 40B) for supplying hydraulic oil to the hydraulic chamber 25 (25A, 25B). An oil supply port 42 (42A, 42B) and an oil discharge port 52 (52A, 52B) to which an oil discharge passage 50 (50A, 50B) for discharging hydraulic oil from the hydraulic chamber 25 (25A, 25B) is connected. Have The oil supply port 42 (42A, 42B) is open to a lower region of the inner peripheral surface 24B of the cylinder 24 that forms the boundary of each hydraulic chamber 25 (25A, 25B). On the other hand, the oil discharge port 52 (52A, 52B) is open to the upper region of the inner peripheral surface 24B of the cylinder 24.
Thereby, bubbles can be smoothly discharged from the oil discharge port 52 to the oil discharge passage 50 by the flow of the hydraulic oil in the hydraulic chamber 25 (25A, 25B).

In some embodiments, the hydraulic machine 20 is arranged such that the axial direction of the hydraulic machine 20 is along the vertical direction.
FIG. 9 is a schematic diagram of a hydraulic machine according to an embodiment. FIG. 10 is a schematic external view of the hydraulic machine shown in FIG. 9 and 10, the same parts as those in FIGS. 2 to 8 are denoted by the same reference numerals, and description thereof is omitted here.
In some embodiments, as shown in FIGS. 9 and 10, the rotating shaft 21 of the hydraulic machine 20 is arranged along the vertical direction, and each piston group is horizontal along the radial direction of the hydraulic machine 20. Includes a plurality of pistons 22 disposed on each other. The plurality of pistons 22 belonging to each piston group are connected to the crankpin 32 of the crankshaft via the main rod 70 or via the main rod 70 and the secondary rod 80. Each hydraulic chamber 25 (25A, 25B) corresponding to each piston 22 is connected to an oil supply passage 40 (40A, 40B) for supplying hydraulic oil to the hydraulic chamber 25 (25A, 25B). An oil supply port 42 (42A, 42B) and an oil discharge port 52 (52A, 52B) to which an oil discharge passage 50 (50A, 50B) for discharging hydraulic oil from the hydraulic chamber 25 (25A, 25B) is connected. Have The oil supply port 42 (42A, 42B) is open to a lower region of the inner peripheral surface 24B of the cylinder 24 that forms the boundary of each hydraulic chamber 25 (25A, 25B). On the other hand, the oil discharge port 52 (52A, 52B) is open to the upper region of the inner peripheral surface 24B of the cylinder 24.
Thereby, bubbles can be smoothly discharged from the oil discharge port 52 to the oil discharge passage 50 by the flow of the hydraulic oil in the hydraulic chamber 25 (25A, 25B).

  In one embodiment, as shown in FIG. 10, the hydraulic machine 20 is a hydraulic motor configured to rotate the rotary shaft 21 by high-pressure oil introduced into the hydraulic chamber 25, and the rotary shaft of the hydraulic machine 200 21 is connected to a driven device 400 represented by a generator.

As described above, according to the above-described embodiment, in the hydraulic machine 20, the plurality of hydraulic chambers 25 (25 </ b> A to 25 </ b> D) separated from each other by the piston 22 are formed in the region surrounded by each cylinder 24. The The motion mode is converted between the reciprocating motion of the piston 22 and the rotational motion of the mechanical element 30 accompanied by the periodic volume change of each of the plurality of hydraulic chambers 25 (25A to 25D). For this reason, at least one of the plurality of hydraulic chambers 25 (25A to 25D) separated by the piston 22 in one cylinder 24 does not depend on the phase of the reciprocating motion of each piston 22, and the rotational energy of the rotary shaft and the hydraulic oil. It can contribute to energy conversion between fluid energy.
In this way, the plurality of hydraulic chambers 25 provided for one cylinder 24 can contribute to energy conversion between the rotational energy of the rotary shaft 21 and the fluid energy of the hydraulic oil, respectively. Large energy can be converted while suppressing the size increase of 20.

Further, in the above-described embodiment, the force by the hydraulic oil applied to the piston 22 is obtained by multiplying the pressure difference between the hydraulic chambers 25 on both sides of the piston 22 by the area of the pressure receiving surface of the piston 22. On the other hand, in the case of a conventional hydraulic machine in which one hydraulic chamber is formed by one piston in one cylinder, the force by the hydraulic oil acting on the piston is different from the pressure in the hydraulic chamber and the outside of the hydraulic chamber. This is the difference from the pressure (typically atmospheric pressure) multiplied by the area of the piston pressure receiving surface. Therefore, according to the hydraulic machine 20, the force by the hydraulic oil applied to the piston 22 is smaller than that of the conventional hydraulic machine. Therefore, the load on the hydraulic machine 20 due to the pressure of the hydraulic oil is relatively small.
That is, according to the hydraulic machine 20, the region in one cylinder 24 is separated from the plurality of hydraulic chambers 25 by the piston 22, and thus acts on the piston 22 due to the pressures of the hydraulic chambers 25 on both sides of the piston 22. Since the force is partially offset, the load on the hydraulic machine 20 due to the hydraulic oil pressure is small.

  Furthermore, according to the above-described embodiment, by providing a plurality of hydraulic chambers 25 that are formed by separating the region in one cylinder 24 by the piston 22, the piston 22 moves downward in the reciprocating motion cycle of the piston 22. In both the period from the dead center to the top dead center and the period in which the piston 22 moves from the top dead center to the bottom dead center, one of the hydraulic chambers 25 has the fluid energy of the hydraulic oil and the rotary shaft of the hydraulic machine 20. Contributes to conversion between kinetic energy. Therefore, the rotation of the rotary shaft 21 of the hydraulic machine 20 can be made smooth.

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

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

  In the exemplary embodiments shown in FIGS. 2 to 8, the displacement of the engaging portion 61 between the crankshaft as the mechanical element 30 and the connecting portion 60 for restricting the displacement of each piston 22 in the piston central axis direction. Although functioning as the restricting unit 100, the configuration of the displacement restricting unit 100 is not limited to this example.

FIG. 11 is a partial cross-sectional view along the radial direction of the hydraulic machine according to the embodiment. FIG. 12 is a partial cross-sectional view along the axial direction of the hydraulic machine shown in FIG. 11. FIG. 13 is a perspective view of the periphery of the displacement restricting portion 100 of the hydraulic machine shown in FIG.
As shown in FIGS. 11 to 13, in some embodiments, the hydraulic machine 300 includes a plurality of pistons 322 disposed along a radial direction of the hydraulic machine 300 and a plurality of pistons 322 slidably held. And a cylinder block 312 provided with a plurality of cylinders 324. Each piston 322 is guided by a cylinder 324 so as to reciprocate along the radial direction of the hydraulic machine 320. In a region surrounded by the cylinder 324, a plurality of hydraulic chambers 325 (325A, 325B) separated from each other by the pressure receiving portion 330 of the piston 324 are formed.

  The displacement restricting portion 100 of the hydraulic machine 300 is disposed so as to face the cam surface of the cam 310 as the machine element 30, and has a contact surface 63 having a profile in phase with the cam surface of the cam 310. That is, the contact surface 63 of the displacement restricting portion 100 has a curved surface corresponding to the cam surface of the cam 310. Further, the displacement restricting portion 100 is configured to rotate together with the cam 310. In one embodiment, as shown in FIG. 12, the displacement restricting portion 100 is connected to a cam 310 via a connecting portion 312 and rotates together with the cam 310. Note that a pair of displacement restricting portions 100 may be provided on both sides of the lower portion 324 of the piston 322 as shown in FIGS.

A roller 326 is provided between the cam 310 and each piston 322. In the exemplary embodiment shown in FIGS. 11-13, the roller 326 is engaged with the lower portion 323 of the piston 322 and is configured to be rotatable about the central axis of the roller 326. The roller 326 is sandwiched between the cam 310 and the displacement restricting portion 100 and is in contact with both the cam surface of the cam 310 and the abutting surface 63 of the displacement restricting portion 100.
Thus, the displacement of each piston 322 in the piston central axis direction is regulated by the displacement regulating unit 100, and each piston 322 reciprocates in synchronization with the rotational movement of the cam 310 as the mechanical element 30. It is like that.

  In the exemplary embodiment shown in FIGS. 11 to 13, one piston 322 is provided in each cylinder 324, and the area in the cylinder 324 is divided into two hydraulic chambers 325 </ b> A and 325 </ b> B by one piston 322. It is separated by. However, a plurality of pistons 322 may be provided in each cylinder 324, and a region in each cylinder 324 may be divided into three or more hydraulic chambers 325 by the plurality of pistons 322.

In some embodiments, the piston 322 includes a pressure receiving portion 330 that separates the plurality of hydraulic chambers 325 (325A, 325B), and a small diameter portion 332 provided between the pressure receiving portion 330 and the lower portion 323 of the piston 322. . The small diameter portion 332 has a smaller diameter than the pressure receiving portion 330 and passes through the first hydraulic chamber 325 </ b> A closest to the cam 310 as the mechanical element 30. A seal member 329A is provided in a portion where the small diameter portion 332 penetrates the first hydraulic chamber 325A.
Thereby, the leakage of the hydraulic fluid from the penetration part of the 1st hydraulic chamber 325A by the small diameter part 332 can be prevented. Therefore, it is possible to suppress a decrease in performance of the hydraulic machine 300 due to hydraulic oil leakage.

In some embodiments, an extension rod 334 having a smaller diameter than the pressure receiving portion 330 is provided along the axial direction of the cylinder 324 on the opposite side of the small diameter portion 332 across the pressure receiving portion 330. The extension rod 334 passes through the second hydraulic chamber 325B that is farther from the cam 310 than the first hydraulic chamber 325A. A seal member 329B is provided in a portion where the extension rod 334 penetrates the second hydraulic chamber 325B.
Thereby, the reciprocating motion of the piston 322 in the cylinder 324 is stabilized by the extension rod 334, and leakage of hydraulic oil from the penetrating portion of the second hydraulic chamber 325B by the extension rod 334 can be prevented.

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

DESCRIPTION OF SYMBOLS 1 Wind power generator 2 Blade 3 Rotor 4 Hub 5 Hub cover 6 Rotating shaft 8 Hydraulic pump 10 Hydraulic motor 12 High pressure oil line 14 Low pressure oil line 16 Generator 18 Nacelle 19 Tower 20 Hydraulic machine 21 Rotating shaft 22 Piston 24 Cylinder 24A In partition 24B Peripheral surface 25 Hydraulic chamber 29A, 29B Seal member 30 Machine element 32 Crank pin 40 Oil supply passage 42 Oil supply port 44 Oil supply valve 50 Oil discharge passage 52 Oil discharge port 54 Oil discharge valve 60 Connecting portion 62 First rod portion 64 Second rod portion 65 engaging portion 66 extension rod 70 main rod 72 crank pin hole 74 pin 76 pin hole 78 pin 80 slave rod 82 pin hole 84 pin 85 engaging portion 122 first piston 222 second piston 300 hydraulic machine 310 cam 312 cylinder block 3 Second piston 324 cylinder 325 hydraulic chambers 326 roller 329A seal member 329B seal member 330 receiving portion 332 small-diameter portion 334 extending rod 400 driven equipment

Claims (15)

At least one piston,
At least one cylinder for reciprocally guiding the at least one piston;
A mechanical element configured to interlock with the reciprocating motion of each of the pistons within each of the cylinders;
A plurality of hydraulic chambers separated from each other by the piston are formed in a region surrounded by each cylinder.
The mechanical element is configured to convert a motion mode between a reciprocating motion of each of the pistons with a periodic volume change of each of the plurality of hydraulic chambers and a rotational motion of the mechanical element. Hydraulic machine featuring.   The displacement regulating part for regulating displacement of each piston in the direction of the central axis of the piston so as to reciprocate each of the pistons in synchronization with the rotational movement of the mechanical element. The hydraulic machine according to 1. And further comprising at least one connecting portion for connecting the mechanical element and the at least one piston, respectively.
The mechanical element includes a crankshaft;
The hydraulic machine according to claim 2, wherein the displacement restricting portion is an engaging portion between the at least one connecting portion and the crankshaft. Each of the hydraulic chambers has an oil supply port to which an oil supply passage for supplying hydraulic oil to the hydraulic chamber is connected, and an oil discharge port to which an oil discharge passage for discharging the hydraulic oil from the hydraulic chamber is connected And
The hydraulic machine according to any one of claims 1 to 3, wherein the oil discharge port is positioned above the oil supply port.   The hydraulic machine according to claim 4, wherein an angle formed by a central axis of the at least one cylinder with respect to a horizontal direction is within 45 degrees. The at least one cylinder is disposed along a horizontal direction;
The fuel filler opening is opened in a lower region of the inner peripheral surface of the cylinder that forms a boundary between the hydraulic chambers,
6. The hydraulic machine according to claim 4, wherein the oil discharge port opens in an upper region of the inner peripheral surface of the cylinder. An oil supply valve provided in the oil supply passage extending to the oil supply port toward the lower region, and for switching a supply state of hydraulic oil to each of the hydraulic chambers;
An oil discharge valve provided in the oil discharge passage extending toward the oil discharge port toward the upper region, and for switching a discharge state of hydraulic oil from each of the hydraulic chambers; The hydraulic machine according to claim 6. The at least one piston includes at least one piston group including a plurality of pistons arranged along a radial direction of the hydraulic machine;
The hydraulic machine according to 6 or 7, wherein an axial direction of the hydraulic machine is along a vertical direction. And further comprising at least one connecting portion for connecting the mechanical element and the at least one piston, respectively.
The at least one piston includes at least one piston group including a plurality of pistons arranged around a crankshaft as the mechanical element along a radial direction of the hydraulic machine,
The at least one connecting portion belongs to one main rod for connecting one of the plurality of pistons belonging to each of the piston groups to the crankshaft, and belongs to each of the piston groups. The hydraulic machine according to any one of claims 1 to 8, further comprising at least one slave rod for connecting another piston among the plurality of pistons to the main rod. The at least one piston group includes a plurality of piston groups arranged in the axial direction of the hydraulic machine,
Among the plurality of rows, the plurality of first pistons belonging to the first row of the piston group includes a plurality of second pistons belonging to the second row of the piston group adjacent to the first row and the hydraulic pressure. The hydraulic machine according to claim 9, wherein a position of the machine in a circumferential direction is shifted. Each of the piston groups includes a pair of pistons that are connected to the crankshaft via the main rod or via the main rod and the slave rod, and arranged along the horizontal direction,
Each of the hydraulic chambers has an oil supply port to which an oil supply passage for supplying hydraulic oil to the hydraulic chamber is connected, and an oil discharge port to which an oil discharge passage for discharging the hydraulic oil from the hydraulic chamber is connected And
The fuel filler opening is opened in a lower region of the inner peripheral surface of the cylinder that forms a boundary between the hydraulic chambers,
The hydraulic machine according to claim 9 or 10, wherein the oil discharge port is opened in an upper region of the inner peripheral surface of the cylinder. And further comprising at least one connecting portion for connecting the mechanical element and the at least one piston, respectively.
The plurality of hydraulic chambers include a first hydraulic chamber and a second hydraulic chamber located farther from the mechanical element than the first hydraulic chamber,
Each of the connecting portions penetrates at least the first hydraulic chamber,
The hydraulic machine according to any one of claims 1 to 11, wherein a seal member is provided in a portion where each of the connecting portions penetrates the first hydraulic chamber. The mechanical element includes a crankshaft;
Each of the connecting portions is fixed to each of the pistons and penetrates the first hydraulic chamber, and one end is engaged with the crankshaft and the other end is engaged with the first rod portion. A second rod portion to be joined,
The hydraulic machine according to claim 12, wherein an engaging portion between the first rod portion and the other end of the second rod portion is located outside the first hydraulic chamber. And at least one roller provided between the machine element and the at least one piston, respectively.
The mechanical element is a cam having a cam surface that contacts the at least one roller;
The displacement restricting portion has a contact surface of a profile corresponding to the cam surface, is disposed on the opposite side of the cam with the at least one roller interposed therebetween, and is configured to rotate together with the cam. The hydraulic machine according to claim 2, characterized in that: At least one blade,
A hub to which the at least one blade is mounted;
A hydraulic pump configured to be driven by rotation of the hub;
A hydraulic motor configured to be driven by pressure oil generated by the hydraulic pump;
A wind turbine generator comprising a generator driven by the hydraulic motor,
At least one of the hydraulic pump and the hydraulic motor includes at least one piston, at least one cylinder for reciprocatingly guiding the at least one piston, and each piston within each cylinder. A mechanical element configured to interlock with reciprocating motion,
A plurality of hydraulic chambers separated from each other by the piston are formed in a region surrounded by each piston and each cylinder.
The mechanical element is configured to convert a motion mode between a reciprocating motion of each of the pistons with a periodic volume change of each of the plurality of hydraulic chambers and a rotational motion of the mechanical element. A featured wind power generator.

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