JP2014129776A - Hydraulic machine and wind power generation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic machine that can be downsized by improving the layout of valves, and a wind power generation device including the same.SOLUTION: A hydraulic machine comprises: pistons; cylinders; oil supply valves 60A for switching the state of supply of hydraulic oil to hydraulic chambers 25 respectively; and oil discharge valves 60B for switching the state of discharge of hydraulic oil from the hydraulic chambers respectively. Each oil supply valve and each oil discharge valve include: valve elements 62A and 62B; movable shafts 63A and 63B connected to the valve elements; and drive parts 64A and 64B configured to move the movable shafts respectively. A first movable shaft, which is one of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve, is inserted into a through-hole 69 provided in a second movable shaft, which is the other of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve. The first movable shaft and the second movable shaft are configured to be able to be moved by the drive parts independently of each other.

Description

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

Conventionally, hydraulic machines such as a hydraulic pump and a hydraulic motor are 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 type hydraulic machine that functions as a drive train of 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

By the way, the hydraulic machine described above includes an oil supply valve for supplying hydraulic oil to the cylinder and an oil discharge valve for discharging hydraulic oil from the cylinder. The layout of these valves is a very important problem in reducing the size of the hydraulic machine itself.
In this regard, Patent Documents 1 and 2 do not describe measures for reducing the size of the hydraulic machine.

  The present invention has been made in view of the above-described conventional problems, and an object of the present invention is to provide a hydraulic machine that can be miniaturized by devising a valve layout and a wind turbine generator having the hydraulic machine. There is.

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;
At least one oil supply valve for switching a supply state of hydraulic oil to at least one hydraulic chamber respectively formed by the at least one piston and the at least one cylinder;
And at least one oil discharge valve for switching a discharge state of the hydraulic oil from the at least one hydraulic chamber,
Each of the oil supply valves and each of the oil discharge valves includes a valve body, a movable shaft connected to the valve body, and a drive unit configured to move the movable shaft,
The first movable shaft that is one of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve is a second movable shaft that is the other of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve. And the first movable shaft and the second movable shaft are configured to be movable independently of each other by the driving unit.

  In the hydraulic machine, the first movable shaft that is one movable shaft of the oil supply valve and the oil discharge valve is inserted through a through hole provided in the second movable shaft that is the other movable shaft. The first movable shaft and the second movable shaft are configured to be movable by the drive unit independently of each other. Thus, by arranging the first movable shaft and the second movable shaft concentrically so as to be movable independently of each other, a compact series arrangement of the oil supply valve and the oil discharge valve becomes possible, and the hydraulic machine It can be miniaturized.

In some embodiments, the drive unit includes a solenoid for generating a magnetic force that moves the movable shaft.
In this case, at least one of the oil supply valve and the oil discharge valve is configured as an electromagnetic valve that moves the movable shaft by the magnetic force generated by the solenoid. Since the solenoid valve is excellent in responsiveness, the supply state and discharge state of the hydraulic oil in the hydraulic chamber can be switched instantaneously.

In another embodiment, the drive unit includes a pilot valve for moving the movable shaft by applying a hydraulic pressure to a hydraulic pressure receiving portion provided on the movable shaft.
In this case, since at least one of the oil supply valve and the oil discharge valve is configured to move the movable shaft by the oil pressure, the oil pressure of the hydraulic oil can be effectively used.

In some embodiments, the solenoid arrangement region where the solenoid of the oil supply valve and the solenoid of the oil discharge valve are arranged includes the valve body of the oil supply valve and the valve body of the oil discharge valve. It is provided separately from the valve element arrangement region.
Thus, by providing the solenoid arrangement area where the solenoid is arranged and the valve element arrangement area where the valve element is arranged separately, the maintainability for both the solenoid and the valve element is improved.

In some embodiments, the solenoid arrangement area is arranged farther from the hydraulic chamber than the valve element arrangement area.
Thus, by arranging the solenoid arrangement area farther from the hydraulic chamber than the valve element arrangement area, it is possible to improve the maintainability of the solenoid and also facilitate the arrangement of the electric wiring connected to the solenoid.

In some embodiments, the solenoid placement region includes a single solenoid chamber in which the solenoids of both the oil supply valve and the oil discharge valve are accommodated.
Thus, by providing one solenoid chamber in which the solenoids of both the oil supply valve and the oil discharge valve are accommodated, the maintainability for the solenoid is further improved, and the arrangement of the electric wiring connected to the solenoid is further facilitated. .

In another embodiment, the solenoid arrangement region is provided separately from the oil supply solenoid chamber in which the solenoid of the oil supply valve is accommodated and the oil supply solenoid chamber, and the solenoid of the oil discharge valve is accommodated in the solenoid arrangement region. And a solenoid chamber for oil drainage.
As described above, if the oil supply solenoid chamber in which the solenoid of the oil supply valve is accommodated and the oil discharge solenoid chamber in which the oil discharge valve is accommodated are provided separately, one solenoid in which both solenoids are accommodated is provided. Since each solenoid chamber can be made smaller than the case where a large solenoid chamber is provided, the layout of the solenoid chamber is improved.

In some embodiments, the fuel supply solenoid chamber or the oil discharge solenoid chamber is further provided with a communication path for communicating at least one of the oil supply solenoid chamber or the oil discharge solenoid chamber with the valve element arrangement region. At least one of the solenoid chambers is provided with a magnetic force receiving portion that is provided on the movable shaft so as to extend radially outward of the movable shaft and receives the magnetic force from the solenoid.
According to such a configuration, the hydraulic pressure is applied to the magnetic force receiving portion provided in the solenoid chamber by the hydraulic oil introduced into the solenoid chamber via the communication path, and the back pressure is applied to the movable shaft. By utilizing this back pressure, the electromagnetic force required to move the movable shaft can be reduced.

In some embodiments, the pressure receiving area of the magnetic force receiving portion from the hydraulic oil inside the at least one of the oil supply solenoid chamber or the oil discharge solenoid chamber is A, and the magnetic force receiving portion is provided. When the pressure receiving area from the hydraulic fluid of the valve body connected to the movable shaft is A ₀ , the pressure receiving area ratio A / A ₀ is 0.8 or more and 1.2 or less.
As described above, when A / A ₀ is 0.8 or more and 1.2 or less, the hydraulic pressure acting on the valve body and the back pressure acting on the magnetic force receiving portion are substantially balanced and are necessary for moving the movable shaft. Electromagnetic force can be reduced.

In some embodiments, the solenoid for moving the first movable shaft is disposed in a first solenoid chamber that is one of the oil supply solenoid chamber and the oil discharge solenoid chamber, and the oil supply solenoid. The solenoid for moving the second movable shaft is disposed in a second solenoid chamber located between the first solenoid chamber and the hydraulic chamber, which is the other of the chamber and the oil discharge solenoid chamber. ing.
The second movable shaft is disposed on the outer peripheral side of the first movable shaft. For this reason, it is reasonable to arrange the magnetic force receiving portion of the second movable shaft closer to the hydraulic chamber than the magnetic force receiving portion of the first movable shaft.
Therefore, the second solenoid chamber in which the solenoid for moving the second movable shaft is disposed is disposed closer to the hydraulic chamber than the first solenoid chamber in which the solenoid for moving the first movable shaft is disposed. As a result, the layout can be improved and the overall configuration of the hydraulic machine can be reduced in size.

In some embodiments, the first solenoid chamber and the second solenoid include a bush provided between the first movable shaft and the second movable shaft, and a bush hole into which the bush is inserted. A partition that partitions the chamber, and a seal member provided between the inner peripheral surface of the bush hole of the partition and the outer peripheral surface of the bush are further provided.
According to such a configuration, the first solenoid chamber and the second solenoid chamber can be liquid-tightly separated by the seal member, so that it is possible to prevent a decrease in performance of the hydraulic machine due to hydraulic oil leakage. . At this time, since the bush is disposed between the first movable shaft and the seal member, the movable shaft and the seal member can be prevented from coming into direct contact.

In some embodiments, the first movable shaft is made of a magnetic material and receives a magnetic force from the solenoid. The first movable shaft is made of a non-magnetic material and penetrates the second movable shaft. And a shaft portion inserted through the hole.
According to such a configuration, since the shaft portion of the first movable shaft that is inserted through the through hole of the second movable shaft is formed of a non-magnetic material, the first movable shaft and the second movable shaft are caused by the magnetic force. It can be prevented from attracting each other.

In some embodiments, the solenoid of at least one of the oil supply valve and the oil discharge valve is housed in a groove of an annular core, and the at least one movable shaft of the oil supply valve and the oil discharge valve is A magnetic force receiving portion arranged to cover at least the opening portion of the groove portion of the annular core and configured to receive the magnetic force from the solenoid accommodated in the groove portion.
According to such a configuration, since the magnetic force receiving portion is disposed so as to cover the opening portion of the groove portion of the annular core, leakage of magnetic force from the solenoid accommodated in the groove portion is prevented. Therefore, magnetic field interference between the solenoid of the oil supply valve and the solenoid of the oil discharge valve can be prevented.

In some embodiments, the solenoid of at least one of the oil supply valve and the oil discharge valve is a plurality of cores respectively accommodated in recesses of a plurality of cores discretely arranged around a central axis of the movable shaft. The at least one movable shaft of the oil supply valve and the oil discharge valve is disposed so as to cover at least an opening portion of the concave portion of the plurality of cores, and is accommodated in each of the concave portions. A magnetic force receiving portion configured to receive the magnetic force from the solenoid;
According to such a configuration, since the magnetic force receiving portion is arranged so as to cover the opening portions of the concave portions of the plurality of discretely arranged cores, leakage of magnetic force from the solenoid accommodated in the concave portion is prevented. . Therefore, magnetic field interference between the solenoid of the oil supply valve and the solenoid of the oil discharge valve can be prevented.

In some embodiments, the movable shafts of the oil supply valve and the oil discharge valve are arranged coaxially with respect to each of the cylinders.
Thus, if the movable shafts of the oil supply valve and the oil discharge valve are arranged coaxially with respect to the cylinder, the layout of the oil supply valve and the oil discharge valve can be simplified.

A wind turbine generator according to at least one embodiment of the present invention,
At least one blade,
A hub to which the at least one blade is mounted;
A hydraulic pump configured to be driven by rotation of the hub;
A hydraulic motor configured to be driven by pressure oil generated by the hydraulic pump;
A wind turbine generator comprising a generator driven by the hydraulic motor,
At least one of the hydraulic pump and the hydraulic motor includes at least one piston, at least one cylinder for reciprocally guiding the at least one piston, the at least one piston, and the at least one cylinder. At least one oil supply valve for switching the supply state of hydraulic oil to at least one hydraulic chamber formed respectively, and at least one for switching the discharge state of the hydraulic oil from the at least one hydraulic chamber, respectively. Including a drain valve,
Each of the oil supply valves and each of the oil discharge valves includes a valve body, a movable shaft connected to the valve body, and a drive unit configured to move the movable shaft,
The first movable shaft that is one of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve is a second movable shaft that is the other of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve. And the first movable shaft and the second movable shaft are configured to be movable independently of each other by the driving unit.

  In the hydraulic machine of the wind power generator, the first movable shaft that is one movable shaft of the oil supply valve and the oil discharge valve is inserted into a through hole provided in the second movable shaft that is the other movable shaft. The first movable shaft and the second movable shaft are configured to be movable by the drive unit independently of each other. Thus, by arranging the first movable shaft and the second movable shaft concentrically so as to be movable independently of each other, a compact series arrangement of the oil supply valve and the oil discharge valve becomes possible, and the hydraulic machine It can be miniaturized.

  According to at least one embodiment of the present invention, a first movable shaft that is one of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve, and a first that is the other of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve. By arranging the two movable shafts concentrically so as to be movable independently of each other, it is possible to provide a hydraulic machine that can be miniaturized and a wind turbine generator equipped with the hydraulic machine.

It is a figure which shows the wind power generator concerning one Embodiment. It is sectional drawing along the radial direction of the hydraulic machine concerning one Embodiment. It is a schematic diagram of the cylinder sleeve concerning one embodiment, and is a sectional view of a cylinder sleeve along the direction orthogonal to the radial direction of a cylinder block. It is a schematic diagram of the cylinder sleeve concerning one embodiment, and is an AA sectional view in Drawing 3A. It is a schematic diagram of the cylinder sleeve concerning one embodiment, and is a BB sectional view in Drawing 3A. It is the figure which showed the cylinder sleeve concerning one Embodiment, Comprising: It is sectional drawing of the cylinder sleeve along the radial direction of a cylinder block. It is the figure which showed typically the example of arrangement | positioning of the drive part concerning one Embodiment. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. It is a partial expanded sectional view along the radial direction of the hydraulic machine concerning one embodiment. It is the figure which showed the cylinder sleeve concerning one Embodiment, Comprising: It is sectional drawing of the cylinder sleeve along the radial direction of a cylinder block. It is the figure which showed the cylinder sleeve concerning one Embodiment, Comprising: It is sectional drawing of the cylinder sleeve along the radial direction of a cylinder block. It is the figure which showed the cylinder sleeve concerning one Embodiment, Comprising: It is sectional drawing of the cylinder sleeve along the radial direction of a cylinder block. It is the figure which showed the cylinder sleeve concerning one Embodiment, Comprising: It is sectional drawing of the cylinder sleeve along the radial direction of a cylinder block. It is the figure which showed the cylinder sleeve concerning one Embodiment, Comprising: It is sectional drawing of the cylinder sleeve along the radial direction of a cylinder block.

  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, but are merely illustrative examples.

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.

FIG. 2 is a cross-sectional view along the radial direction of the hydraulic machine according to the embodiment.
In the exemplary embodiment shown in the figure, the hydraulic machine 20 includes a plurality of pistons 22 arranged along the radial direction of the hydraulic machine 20 and a plurality of pistons 22 for holding the plurality of pistons 22 slidably. And a cylinder block 26 provided with a cylinder 24. Each piston 22 is guided by a cylinder 24 so as to reciprocate along the radial direction of the hydraulic machine 20. The cylinder block 26 includes a plurality of cylinder sleeves 40 each having a plurality of cylinders 24 and a cylinder block body 50 having a plurality of sleeve holes 52 into which the plurality of cylinder sleeves 40 are respectively inserted. In each cylinder sleeve 40, a hydraulic chamber 25 is formed by the piston 22 and the cylinder 24.

  In one embodiment, the cylinder block body 50 has an annular cross section. A rotating shaft 28 is rotatably arranged on the inner peripheral side of the annular cross section. An eccentric cam 28 a is connected to the rotary shaft 28. The eccentric cam 28a is in contact with contacts of a plurality of machine elements 27, and each of the plurality of machine elements 27 is connected to the plurality of pistons 22 described above. Each cylinder block body 50 is formed with at least one oil passage 30 extending in the axial direction as shown in FIG. In some embodiments, the at least one oil passage 30 includes an oil supply passage 30A communicating with each of the hydraulic chambers 25 via an oil supply valve 60A described later, and a hydraulic chamber 25 via an oil discharge valve 60B described later. And an oil discharge passage 30B communicating with the.

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. Such a reciprocating motion of the piston 22 accompanied by a periodic change in the volume of the hydraulic chamber 25 is such that the motion mode is converted via the mechanical element 27.
For example, when the hydraulic machine 20 is a hydraulic pump, the rotational motion of the mechanical element 27 that rotates together with the eccentric cam 28 a connected to the rotary shaft 28 of the hydraulic machine 20 is converted into the reciprocating motion of the piston 22, and the cycle of the hydraulic chamber 25. A volume change occurs, and 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 27. 27 and the rotating shaft 28 of the hydraulic machine 20 rotate.
Thus, energy is converted between the rotational energy (mechanical energy) of the rotary shaft 28 of the hydraulic machine 20 and the fluid energy of the hydraulic oil by the action of the machine element, 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.

  In the following embodiment, a case where the hydraulic machine 20 is the hydraulic motor 10 will be described as an example.

  3A to 3C are schematic views of a cylinder sleeve according to an embodiment, and FIG. 3A is a cross-sectional view of the cylinder sleeve along a direction orthogonal to the radial direction of the cylinder block. 3B is a cross-sectional view taken along line AA in FIG. 3A. 3C is a cross-sectional view taken along the line BB in FIG. 3A. 4 to 6B are views showing a cylinder sleeve according to an embodiment, and FIG. 4 is a cross-sectional view of the cylinder sleeve along the radial direction of the cylinder block. 6A is a cross-sectional view taken along the line AA of FIG. 6B is a cross-sectional view taken along the line BB in FIG. FIG. 7 is a partially enlarged cross-sectional view along the radial direction of the hydraulic machine according to the embodiment.

  As shown in FIGS. 3B and 3C, the cylinder sleeve 40 is provided with a valve 60 for switching the supply state or the discharge state of the hydraulic oil with respect to the hydraulic chamber 25. In some embodiments, the valve 60 switches the supply state of the high-pressure hydraulic oil supplied to the hydraulic chamber 25 and the discharge state of the low-pressure hydraulic oil discharged from the hydraulic chamber 25. And an oil discharge valve 60B for the purpose. The oil supply valve 60A and the oil discharge valve 60B are respectively configured to move the valve bodies 62A and 62B, the movable shafts 63A and 63B connected to the valve bodies 62A and 62B, and the movable shafts 63A and 63B. 64A, 64B.

In the cylinder sleeve 40A of the exemplary embodiment shown in FIG. 4, the driving portions 64A and 64B include solenoids 66A and 66B and cores 65A and 65B for generating a magnetic force for moving the movable shafts 63A and 63B. The solenoid 66A is mounted in the groove portion of the annular core 65A having a U-shaped cross section in a state of being wound through the annular bobbin 61A. The solenoid 66B is wound around the rod-shaped core 65B. As schematically shown in FIG. 5, the drive unit 64B is discretely arranged around the central axis CL of the movable shafts 63A and 63B.
In this case, at least one of the oil supply valve 60A and the oil discharge valve 60B is configured as an electromagnetic valve that moves the movable shafts 63A and 63B by the magnetic force generated by the solenoids 66A and 66B. Since the solenoid valve is excellent in responsiveness, the supply state and discharge state of the hydraulic oil in the hydraulic chamber 25 can be instantaneously switched.

When a current flows through the solenoid 66A, a magnetic flux is generated, and the magnetic force receiving portions 67A connected to the ends of the core 65A and the movable shaft 63A are magnetized to generate magnetic forces that attract each other. Then, the movable shaft 63A is attracted to the core 65A against the spring force of the biasing spring 68A. Then, the valve element 62A is separated from the seat surface 72A, and the hydraulic chamber 25 and the oil supply valve element arrangement region 38A in which the valve element 62A is arranged communicate with each other.
Similarly, when a current flows through the solenoid 66B, a magnetic flux is generated, and the magnetic force receiving portions 67B connected to the ends of the core 65B and the movable shaft 63B are magnetized to generate magnetic forces that attract each other. The movable shaft 63B is attracted to the core 65B against the spring force of the biasing spring 68B. Then, the valve body 62B comes into contact with the seat surface 72B, and the hydraulic chamber 25 and the oil drain valve body arrangement region 38B in which the valve body 62B is arranged are closed.

  In the exemplary embodiment shown in FIG. 4, the movable shaft 63A (first movable shaft) of the oil supply valve 60A is inserted into a through hole 69 provided in the movable shaft 63B (second movable shaft) of the oil discharge valve 60B. It is inserted. In one embodiment, the magnetic force receiving portion 67B and the shaft portion 69B of the movable shaft 63B are configured separately. Then, the shaft portion 69A of the movable shaft 63A is inserted into the through hole 69 of the movable shaft 63B, and the nut 53 is tightened in a state where the plate-like magnetic force receiving portion 67B is aligned with the stepped portion of the shaft portion 69B. 63A (first movable shaft) and the movable shaft 63B (second movable shaft) are concentrically arranged so as to be movable independently of each other. The shaft portion 69A and the valve body 62A are fastened by, for example, a bolt 54a.

  With this configuration, a compact series arrangement of the oil supply valve 60A and the oil discharge valve 60B becomes possible. That is, when the oil supply valve 60A and the oil discharge valve 60B are simply arranged in series, the shape (radial length) of the cylinder sleeve 40 needs to be increased by the length of the movable shaft 63B overlapping in the axial direction. At the same time, the drive portion 64A for moving the movable shaft 63A needs to be disposed between the two movable shafts 63A and 63B, so that the shape (the length in the radial direction) of the cylinder sleeve 40 needs to be further increased. On the other hand, by arranging the two movable shafts 63A and 63B concentrically so as to be movable independently of each other as described above, such a problem can be solved, and the oil supply valve 60A and the oil discharge valve 60B Therefore, the hydraulic machine 20 can be reduced in size.

  In one embodiment, the shaft portion 69A of the movable shaft 63A and the magnetic force receiving portion 67A are configured separately. In one embodiment, the shaft portion 69A is made of a nonmagnetic material such as austenitic stainless steel such as SUS304. Then, it is integrated with a magnetic force receiving portion 67A made of a magnetic material such as SUM22 by a method such as welding. According to such a configuration, it is possible to prevent the shaft portion 69A of the first movable shaft 63A and the shaft portion 69B of the second movable shaft 63B from being attracted by magnetic force.

  In one embodiment, as shown in FIG. 4, the magnetic force receiving portion 67A of the oil supply valve 60A is formed in a bottomed cylindrical shape that opens upward. And the drive part 64A mentioned above is arrange | positioned inside the bottomed cylindrical shape. In one embodiment, the magnetic force receiving portion 67B of the oil discharge valve 60B is provided at the end of the shaft portion 69B so as to extend outward in the radial direction of the movable shaft 63A.

  The solenoid 66A of the oil supply valve 60A is accommodated in the groove portion of the annular core 65A. And the magnetic force receiving part 67A of the oil supply valve 60A described above is arranged so as to cover at least the opening part of the groove part of the annular core 65A. According to such a configuration, since the magnetic force receiving portion 67A is disposed so as to cover the opening portion of the groove portion of the annular core 65A, leakage of magnetic force from the solenoid 66A accommodated in the groove portion is prevented. Therefore, magnetic field interference between the solenoid 66A of the oil supply valve 60A and the solenoid 66B of the oil discharge valve 60B can be prevented.

  In the exemplary embodiment shown in FIG. 4, the valve body 62A of the oil supply valve 60A is formed in an umbrella shape, and a through hole 62a is formed in the peripheral surface thereof. With this configuration, the pressure difference between the inside and the outside of the valve body 62A is eliminated, and the operability of the valve body 62A is improved.

  As shown in FIG. 2 and the like, the cylinder sleeve 40 includes a hydraulic chamber surrounding portion 40a that surrounds the hydraulic chamber 25 and a valve accommodating portion 40b that accommodates the valve 60 described above. The valve accommodating portion 40b is located farther in the radial direction from the piston 22 than the hydraulic chamber surrounding portion 40a. In some embodiments, the oil supply valve 60A and the oil discharge valve 60B described above are accommodated in the valve accommodating portion 40b.

The cylinder sleeve 40A of the exemplary embodiment shown in FIG. 4 is configured by combining a lid member 41, an upper member 42, an outer peripheral member 43, and a lower member 44.
The lid member 41 is formed in a U-shaped cross section that opens downward. The lid member 41 is fastened by the upper member 42 and the bolt 51 a with the concave portion oriented to the upper member 42. And between the cover member 41 and the upper member 42, the solenoid arrangement | positioning area | region 70 in which solenoid 66A, 66B mentioned above is arrange | positioned is formed. In one embodiment, the solenoid arrangement region 70 includes one solenoid chamber 70 in which the drive portions 64A and 64B including the solenoids 66A and 66B of both the oil supply valve 60A and the oil discharge valve 60B and the magnetic force receiving portions 67A and 67B are accommodated. Configured as

  The outer peripheral member 43 is formed in a cylindrical shape. The above-described upper member 42 is inserted from one end side of the cylindrical outer peripheral member 43 and fastened to the outer peripheral member 43 by a bolt 51b. And it fixes to the outer periphery member 43 so that the one end side of the outer periphery member 43 may be obstruct | occluded. An O-ring 81 is interposed between the outer peripheral member 43 and the upper member 42 to seal the connection portion between both members in a liquid-tight manner. The lower member 44 is inserted from the other end side of the cylindrical outer peripheral member 43. The outer peripheral member 43 is fastened and fixed by fastening means (not shown).

  Vertical holes 35 </ b> A and 35 </ b> B are drilled in the outer cylinder portion of the outer peripheral member 43 along the radial direction. After the vertical holes 35A and 35B are drilled, the obstructions 39A and 39B are welded and closed at predetermined locations of the vertical holes 35A and 35B, thereby forming internal channels 35A and 35B, which will be described later, as shown in FIG. Further, a partition wall member 45 is interposed between the upper member 42 and the lower member 44, whereby the oil drainage in which the valve body 62 </ b> B of the oil drainage valve 60 </ b> B described above is disposed inside the upper member 42. The valve body arrangement region 38B is formed, and the oil supply valve body arrangement region 38A in which the valve body 62A of the above-described oil supply valve 60A is arranged is formed in the lower member 44.

  A connection path 36 </ b> B that communicates with the vertical hole 35 </ b> B is provided inside the upper member 42. A connection path 36 </ b> A that communicates with the vertical hole 35 </ b> A is provided inside the lower member 44. In addition, the above-described hydraulic chamber 25 is formed inside the lower member 44, and a bypass flow path that connects the hydraulic chamber 25 and the oil drain valve body arrangement region 38 </ b> B of the upper member 42 is formed. In some embodiments, as shown in FIG. 4, the bypass flow path includes a bypass internal flow path 35 </ b> C (described later) provided inside the lower member 44.

  In some embodiments, as shown in FIG. 4, the solenoid placement region 70 is provided separately from the valve body placement regions 38A and 38B. As described above, the solenoid arrangement area 70 where the solenoids 66A and 66B are arranged and the valve element arrangement areas 38A and 38B where the valve bodies 62A and 62B are arranged are provided separately, so that the solenoids 66A and 66B and the valve bodies are arranged. Since 62A and 62B can be maintained separately, the maintainability of both the solenoids 66A and 66B and the valve bodies 62A and 62B is improved.

In some embodiments, as shown in FIG. 4, the solenoid arrangement region 70 is arranged farther from the hydraulic chamber 25 than the valve element arrangement regions 38A and 38B. Thus, the solenoid arrangement area 70 can be arranged on the end side of the cylinder sleeve 40A by arranging the solenoid arrangement area 70 farther from the hydraulic chamber 25 than the valve body arrangement areas 38A and 38B. Thereby, the maintainability for the solenoids 66A and 66B can be improved, and the arrangement of the electric wiring connected to the solenoids 66A and 66B is facilitated.
Further, as described above, the provision of the single solenoid chamber 70 in which the solenoids 66A and 66B of both the oil supply valve 60A and the oil discharge valve 60B are accommodated further improves the maintainability of the solenoids 66A and 66B, and the solenoid 66A. , 66B can be more easily arranged.

  In some embodiments, as shown in FIG. 4, the annular core 65 </ b> A is fixedly attached to the lid member 41. According to such a structure, since the drive part 64A can be integrally removed simultaneously with removing the cover member 41, the maintainability is further improved.

In some embodiments, as shown in FIG. 7, the movable shafts 63 </ b> A and 63 </ b> B of the oil supply valve 60 </ b> A and the oil discharge valve 60 </ b> B are arranged coaxially with the cylinder 24.
Thus, if the movable shafts 63A and 63B of the oil supply valve 60A and the oil discharge valve 60B are arranged coaxially with respect to the cylinder 24, the layout of the oil supply valve 60A and the oil discharge valve 60B can be simplified, and the cylinder sleeve 40A The shape can be simplified.

  As described above, the valve accommodating portion 40b of the cylinder sleeve 40 is provided with the internal flow path 35 (35A, 35B) extending along the radial direction. In some embodiments, the internal flow path 35 is an oil supply internal flow path 35A provided between the oil supply valve 60A and the oil supply path 30A, and an oil discharge provided between the oil discharge valve 60B and the oil discharge path 30B. And an internal flow path 35B. In some embodiments, the internal flow path 35 communicates with an oil path 30 (30A, 30B) formed in the cylinder block body 50, as shown in FIG. Further, as shown in FIG. 6A, the oil drain internal flow path 35B and the oil drain valve element arrangement region 38B communicate with each other through the connection path 36B described above, and the oil supply internal flow path 35A and the oil supply valve element arrangement area 38A are As shown to FIG. 6B, it connects by the connection path 36A mentioned above. Thus, the oil passage 30 (30A, 30B) and the hydraulic chamber 25 are communicated with each other via the valve 60 (60A, 60B) accommodated in the valve accommodating portion 40b.

  If such an internal flow path 35 (35A, 35B) is provided inside the cylinder sleeve 40, the hydraulic chamber 25 and the oil path 30 (30A, 30B) of the cylinder block body 50 are accommodated in the valve accommodating portion 40b. The internal flow path 35 (35A, 35B) communicates with the valve 60 (60A, 60B). For this reason, the cylinder block main body 50 can be reduced in size irrespective of the shape (radial length) of the cylinder sleeve 40.

In some embodiments, as shown in FIG. 7, a part 40 p of the valve accommodating portion 40 b of the cylinder sleeve 40 </ b> A protrudes from the cylinder block body 50. The at least one internal flow path 35 described above extends in the radial direction from the portion 40p protruding from the cylinder block body 50 in the valve housing portion 40b toward the at least one oil path 30 described above.
If such an internal flow path 35 is provided inside the cylinder sleeve 40, the hydraulic chamber 25 and the oil path 30 of the cylinder block body 50 are connected with the valve housing portion 40 b protruding from the cylinder block body 50. It is possible to communicate with the internal flow path 35 via the valve 60 accommodated in the valve accommodating portion 40b. For this reason, the cylinder block main body 50 can be reduced in size irrespective of the shape (radial length) of the cylinder sleeve 40.

In some embodiments, as shown in FIG. 7, at least the internal flow path 35 (35A, 35B) described above is provided across the valve accommodating portion 40b and the hydraulic chamber surrounding portion 40a.
Thus, if the internal flow path 35 (35A, 35B) extending from the valve accommodating portion 40b to the hydraulic chamber surrounding portion 40a is provided, the entire valve accommodating portion 40b protrudes from the cylinder block main body 50. The hydraulic chamber 25 and the oil passage 30 (30A, 30B) of the cylinder block body 50 are communicated with each other by the internal flow path 35 (35A, 35B) via the valve 60 (60A, 60B) accommodated in the valve accommodating portion 40b. Can do. For this reason, the cylinder block main body 50 can be reduced in size irrespective of the shape (radial length) of the cylinder sleeve 40.

  Further, according to the above-described configuration, in the hydraulic machine 20 in which the oil supply valve 60A and the oil discharge valve 60B are respectively accommodated in the valve accommodating portion 40b of the cylinder sleeve 40, the oil supply passage 30A of the hydraulic chamber 25 and the cylinder block body 50 and The oil discharge passage 30B is communicated with the oil supply internal flow path 35A and the oil discharge internal flow path 35B through the oil supply valve 60A and the oil discharge valve 60B accommodated in the valve accommodating portion 40b, respectively. Therefore, even when both the oil supply valve 60A and the oil discharge valve 60B are accommodated in the valve accommodating portion 40b of the cylinder sleeve 40, the cylinder block body 50 is independent of the shape (radial length) of the cylinder sleeve 40. Can be miniaturized.

  Further, according to the above-described configuration, in the hydraulic machine 20 in which the oil supply valve 60A and the oil discharge valve 60B are respectively accommodated in the valve accommodating portion 40b of the cylinder sleeve 40, the oil supply passage 30A of the hydraulic chamber 25 and the cylinder block body 50 and The oil discharge passage 30B is communicated with the oil supply internal flow path and the oil discharge internal flow path through the oil supply valve 60A and the oil discharge valve 60B accommodated in the valve accommodating portion 40b, respectively. Therefore, even when both the oil supply valve 60A and the oil discharge valve 60B are accommodated in the valve accommodating portion 40b of the cylinder sleeve 40, the cylinder block body 50 is independent of the shape (radial length) of the cylinder sleeve 40. Can be miniaturized.

  In some embodiments, as shown in FIG. 7, the oil supply passage 30 </ b> A is provided at a different radial position from the oil discharge passage 30 </ b> B. According to such a configuration, since the radial positions of the oil supply passage 30A and the oil discharge passage 30B are different, the oil supply passage 30A and the oil discharge passage 30B provided in the cylinder block body 50 and the cylinder sleeve 40 are provided. Connection space between the oil supply internal flow path 35A and the oil discharge internal flow path 35B can be secured.

In some embodiments, a plurality of sets of oil supply internal flow paths 35A and oil discharge internal flow paths 35B are not adjacent to each other, and oil discharge internal flow paths belonging to different sets are not adjacent to each other. The cylinder sleeves 40 are arranged in the circumferential direction so as not to be adjacent to each other. That is, as shown in FIG. 3A, for example, in two internal flow channel sets 35a and 35b, the oil supply internal flow channels 35A and 35A and the oil discharge internal flow channels 35B and 35B are arranged so as not to be adjacent to each other. .
According to such a configuration, coupled with the configuration in which the oil supply passage 30 </ b> A and the oil discharge passage 30 </ b> B are different from each other in the radial direction, a wide distance between the oil passages 30 connected to the internal flow passages 35 is ensured. be able to.

  That is, by separating the circumferential position of the piston sleeve of the same type of internal flow path 35 (oil supply internal flow path 35A or oil discharge internal flow path 35B), the distance between the oil paths 30 at the same radial position is increased. Can be secured. In addition, the distance between the oil passages 30 connected to the adjacent internal flow passages 35 is widely ensured by the configuration in which the radial positions of the oil supply passage 30A and the oil discharge passage 30B described above are different. In addition, as a result, as shown in FIG. 7, the oil supply passage 30 </ b> A and the oil discharge passage 30 </ b> B are arranged in a staggered manner in the cylinder block main body 50, and the rigidity against twisting of the cylinder block main body 50 is ensured.

In some embodiments, as schematically shown in FIG. 3C, for example, in the valve accommodating portion 40b of the cylinder sleeve 40, the oil supply valve 60A and the oil discharge valve 60B are arranged side by side in the radial direction. In the cylinder sleeve 40, a bypass flow path is provided between the valve body 62 </ b> B of the oil discharge valve 60 </ b> B and the hydraulic chamber 25 that are located away from the hydraulic chamber 25 in the radial direction. This bypass flow path includes a bypass internal flow path 35C provided inside the valve accommodating portion 40b so as to extend along the radial direction.
According to such a configuration, since the bypass flow path is formed between the oil discharge valve 60B and the hydraulic chamber 25, the oil supply valve 60A and the oil discharge valve 60B can be arranged in series in the radial direction. it can. For this reason, the size (diameter) of the cylinder sleeve 40 can be reduced. Thereby, the cylinder block main body 50 can be reduced in size.
In FIG. 3C, the bypass internal flow path 35C is disposed on the same circumference as the oil supply internal flow path 35A and the oil discharge internal flow path 35B, but is not limited thereto. As shown in FIG. 4, the bypass internal flow path 35C may be disposed on the inner peripheral side with respect to the oil supply internal flow path 35A and the oil discharge internal flow path 35B.

FIG. 8 is a cross-sectional view of the cylinder sleeve along the radial direction of the cylinder block according to another embodiment.
Note that the present embodiment has basically the same configuration as the above-described embodiment, and the same components are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the cylinder sleeve 40B of the exemplary embodiment shown in FIG. 8, a partition wall 46 is disposed between the lid member 41 and the upper member 42, and the partition portion 46 allows the above-described solenoid arrangement region 70 to be connected to the drive unit 64A. Is divided into an oil supply solenoid chamber 70 </ b> A (first solenoid chamber) for storing the oil and an oil discharge solenoid chamber 70 </ b> B (second solenoid chamber) for storing the drive portion 64 </ b> B. A bush hole 46a is opened in the partition wall 46, and one end side of the bush 45A is inserted into the bush hole 46a. As shown in FIG. 8, the bush 45A is interposed between the shaft portion 69A of the oil supply valve 60A and the shaft portion 69B of the oil discharge valve 60B. The other end of the bush 45A is bent and extends in the horizontal direction. The horizontal portion of the bush 45A also serves as the partition wall 45 that partitions the oil supply valve element arrangement region 38A and the oil discharge valve element arrangement region 38B.

The valve body 62 of the oil supply valve 60A is formed in a plate shape. And it is connected with the nut 54b by the one end part of the shaft part 69A of the movable shaft 63A.
The shaft portion 69A of the oil supply valve 60A is perforated through the center in the axial direction, and a communication passage 74A that connects the oil supply solenoid chamber 70A and the oil supply valve body arrangement region 38A is formed. A recess 72a is formed on the inner peripheral side of the seat surface 72A with which the valve element 62A of the oil supply valve 60A abuts. A plurality of through holes 62a are formed in the valve body 62A. And even if the valve body 62A is closed through the communication passage 74A, the recess 72a, and the through hole 62a, the refueling solenoid chamber 70A and the refueling valve body arrangement region 38A are communicated with each other. It has become.
According to such a configuration, hydraulic pressure is applied to the magnetic force receiving portion 67A provided in the oil supply solenoid chamber 70A by the hydraulic oil introduced into the oil supply solenoid chamber 70A via the communication passage 74A, and the movable shaft 63A is moved to the back. Pressure is applied. By utilizing this back pressure, the electromagnetic force required to move the movable shaft 63A can be reduced.

Further, the upper member 42 of the cylinder sleeve 40B is formed with a communication passage 74B that communicates the oil discharge solenoid chamber 70B and the oil discharge valve body arrangement region 38B. The communication passage 74B allows the oil discharge valve body arrangement region 38B and the oil discharge solenoid chamber 70B to always communicate with each other regardless of the operating state of the oil discharge valve 60B.
According to such a configuration, hydraulic pressure acts on the magnetic force receiving portion 67B provided in the oil exhaust solenoid chamber 70B by the hydraulic oil introduced into the oil exhaust solenoid chamber 70B via the communication passage 74B, and the movable shaft 63B. The back pressure acts on the. By utilizing this back pressure, the electromagnetic force required to move the movable shaft 63B can be reduced.

In the exemplary embodiment shown in FIG. 8, the pressure receiving area of the magnetic force receiving portion 67A from the working oil inside the oil supply solenoid chamber 70A is A1, and the pressure receiving pressure from the working oil of the valve body 62A connected to the movable shaft 63A. when the area was A1 _0, the pressure receiving area ratio A1 / A1 ₀ is 0.8 to 1.2. Similarly, the pressure receiving area of the magnetic force receiving portion 67B from the inside of the working oil discharge oil solenoid chamber 70B and A2, when the pressure receiving area of the hydraulic oil of the valve body 62A which is connected to the movable shaft 63A to the A2 ₀ , the pressure receiving area ratio A2 / A2 ₀ is 0.8 to 1.2.
If comprised in this way, the hydraulic pressure which acts on valve body 62A, 62B and the back pressure which acts on magnetic force receiving part 67A, 67B will be substantially balanced, and the electromagnetic force required to move movable shaft 63A, 63B can be made small. .

  In the exemplary embodiment shown in FIG. 8, an O-ring 82 is interposed as a seal member between the inner peripheral surface of the bush hole 46a of the partition wall 46 and the outer peripheral surface of the bush 45A. According to such a configuration, the oil supply solenoid chamber 70 </ b> A and the oil discharge solenoid chamber 70 </ b> B can be liquid-tightly separated by the O-ring 82. For this reason, it is possible to prevent a decrease in performance of the hydraulic machine 20 due to leakage of hydraulic oil from the oil supply solenoid chamber 70A into which high-pressure hydraulic oil is introduced into the oil discharge solenoid chamber 70B. At this time, since the bush 45A is disposed between the shaft portion 69A of the oil supply valve 60A and the O-ring 82, the movable shaft 63A and the O-ring 82 are not in direct contact with each other. For this reason, a general O-ring 82 can be adopted without using a special sliding member for sliding.

  An O-ring 83 is interposed between the lid member 41 and the partition wall 46 so as to surround the oil supply solenoid chamber 70A. Further, an O-ring 84 is interposed between the partition wall 46 and the upper member 42 so as to surround the oil draining solenoid chamber 70B. These O-rings 83 and 84 prevent the performance of the hydraulic machine 20 from being degraded due to leakage of hydraulic oil.

  In addition, as described above, if the oil supply solenoid chamber 70A in which the solenoid 66A of the oil supply valve 60A is accommodated and the oil discharge solenoid chamber 70B in which the oil discharge valve 60B is accommodated are provided separately, FIG. As shown in the embodiment shown in FIG. 4, each of the solenoid chambers 70 </ b> A and 70 </ b> B can be made smaller as compared with the case where one large solenoid chamber 70 in which both solenoids 66 </ b> A and 66 </ b> B are accommodated. Thereby, the layout of the solenoid chambers 70A and 70B is improved, and the degree of freedom in designing the cylinder sleeve 40 is increased.

In the exemplary embodiment shown in FIG. 8, a solenoid 66A for moving the movable shaft 63A (first movable shaft) is arranged in the solenoid chamber 70A (first solenoid chamber) for refueling. The movable shaft 63B (second movable shaft) is moved to the oil draining solenoid chamber 70B (second solenoid chamber) located between the oil supply solenoid chamber 70A (first solenoid chamber) and the hydraulic chamber 25. A solenoid 66B is provided for this purpose.
The movable shaft 63B (second movable shaft) is disposed on the outer peripheral side of the movable shaft 63A (first movable shaft). For this reason, it is reasonable to arrange the magnetic force receiving portion 67B of the movable shaft 63B closer to the hydraulic chamber 25 than the magnetic force receiving portion 67A of the movable shaft 63A.
Accordingly, the oil discharge solenoid chamber 70B in which the solenoid 66B for moving the movable shaft 63B is disposed is more hydraulically hydraulic than the oil supply solenoid chamber 70A in which the solenoid 66A for moving the movable shaft 63A is disposed. By arranging the cylinder sleeve 40 on the side, the layout of the cylinder sleeve 40 can be improved, and the overall configuration of the hydraulic machine 20 can be reduced in size.

Further, in the exemplary embodiment shown in FIG. 8, the solenoid 66B of the oil discharge valve 60B is mounted in a concave portion of a core 65B having a U-shaped cross section that opens downward, for example, in a state of being molded with resin. The drive unit 64B including the solenoid 66B is discretely arranged around the central axis CL of the movable shafts 63A and 63B, as schematically shown in FIG. As shown in FIG. 8, the movable shaft 63B of the oil discharge valve 60B is arranged so as to cover the opening portions of the recesses of the plurality of cores 65B, and receives the magnetic force from the solenoid 66B accommodated in each recess. The magnetic force receiving portion 67B configured as described above is included.
According to such a configuration, since the magnetic force receiving portion 67B is disposed so as to cover the opening portions of the concave portions of the plurality of cores 65B that are discretely arranged, the leakage of the magnetic force from the solenoid 66B accommodated in the concave portion is prevented. Is prevented. Therefore, magnetic field interference between the solenoid 66A of the oil supply valve 60A and the solenoid 66B of the oil discharge valve 60B can be prevented.

9 to 12 are cross-sectional views of the cylinder sleeve along the radial direction of the cylinder block according to another embodiment.
Note that these embodiments have basically the same configuration as the above-described embodiments, and the same components are denoted by the same reference numerals, and detailed description thereof is omitted.

In the cylinder sleeve 40C of the exemplary embodiment shown in FIG. 9, the layout of the valve body 62A of the oil supply valve 60A, the shape of the magnetic force receiving portion 67A, and the like are different from the cylinder sleeve 40B shown in FIG.
That is, in the cylinder sleeve 40C shown in FIG. 9, the seat surface 72A is formed on the upper surface side of the oil supply valve body arrangement region 38A in which the valve body 62A is arranged, and the shaft portion 69A of the movable shaft 63A is a lid member. 41, and the magnetic force receiving portion 67A extends from the upper surface side to the lower side of the oil supply solenoid chamber 70A, and is arranged so as to cover the opening portion of the groove portion of the annular core 65A. Yes.

  As in the above-described embodiment, a magnetic flux is generated by current flowing through the solenoid 66A, and the magnetic force receiving portion 67A connected to the core 65A and the end of the movable shaft 63A is magnetized and attracts each other. Such a magnetic force is generated. Then, the movable shaft 63A is attracted to the core 65A against the spring force of the biasing spring 68A. Then, the valve element 62A is separated from the seat surface 72A, and the hydraulic chamber 25 and the oil supply valve element arrangement region 38A in which the valve element 62A is arranged communicate with each other.

  In the cylinder sleeve 40D of the exemplary embodiment shown in FIG. 10, the shape of the valve body 62A of the oil supply valve 60A is different from the cylinder sleeve 40B shown in FIG. That is, the cylinder sleeve 40D shown in FIG. 10 has the same shape as the valve body 62A in the cylinder sleeve 40A shown in FIG.

  In the cylinder sleeve 40E of the exemplary embodiment shown in FIG. 11, the arrangement of the oil supply valve 60A and the oil discharge valve 60B is interchanged. That is, the oil discharge valve body arrangement region 38B in which the valve body 62B of the oil discharge valve 60B is accommodated is located on the side close to the hydraulic chamber 25, and the valve of the oil supply valve 60A is located on the side far from the hydraulic chamber 25. The oil supply valve body arrangement region 38A in which the body 62A is accommodated is located. Further, an oil discharge solenoid chamber 70B is located on the side close to the hydraulic chamber 25, and an oil supply solenoid chamber 70A is located on the side far from the hydraulic chamber 25.

  Further, the configuration of the drive unit 64B of the oil discharge valve 60B is greatly different from that of the above-described embodiment. That is, an annular core 65B in which an annular groove 61B is formed is disposed in the oil discharge solenoid chamber 70B, and a solenoid 66B molded, for example, with resin is wound around the groove 61B. The partition wall 46 is composed of two members, partition walls 46A and 46B. Further, the shaft portion 69B of the movable shaft 63B extends to the vicinity of the lid member 41, and a magnetic force receiving portion 67B is formed at the end thereof. Then, by passing a current through the solenoid 66B, the movable shaft 63B moves downward against the urging force of the urging spring 68B, and the valve body 62B is in contact with the seat surface 72B.

In the cylinder sleeve 40F of the exemplary embodiment shown in FIG. 12, the drive portion 64′A of the oil supply valve 60A includes an oil supply path 92 that connects the oil chamber 70′A and the internal flow path 35A, and the oil supply path 92. It consists of a pilot valve 94 arranged. As the pilot valve 94, for example, a small general-purpose solenoid valve can be used. Further, the movable shaft 63A of the oil supply valve 60A includes a shaft portion 69A and a plate-like hydraulic pressure receiving portion 67′A connected to the other end portion of the shaft portion 69A. Then, by opening the pilot valve 94, supplying hydraulic oil to the oil chamber 70'A and applying hydraulic pressure to the hydraulic pressure receiving portion 67'A, the valve body 62A connected to one end portion of the shaft portion 69A. Is separated from the seat surface 72A, and the hydraulic chamber 25 and the oil supply valve element arrangement region 38A in which the valve element 62A is arranged communicate with each other.
According to such a configuration, the oil supply valve 60A is configured to move the movable shaft 63A by oil pressure, so that the hydraulic oil pressure can be effectively used.

  As described above, according to the above-described embodiment, the first movable shaft that is one of the movable shaft 62A of the oil supply valve 60A and the movable shaft 62B of the oil discharge valve 60B, and the movable shaft 62A and the oil discharge of the oil supply valve 60A. Provided is a hydraulic machine 20 that can be reduced in size and a wind turbine generator 1 having the same by disposing the second movable shaft, which is the other of the movable shafts 62B of the valve 60B, in a state of being movable independently of each other. be able to.

  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.

  In the above-described embodiment, the case where the hydraulic machine 20 is the hydraulic motor 10 has been described as an example. However, the hydraulic machine 20 of the present invention is not limited to the hydraulic motor 10 and can be configured as the hydraulic pump 8. is there. When the hydraulic machine 20 is configured as the hydraulic pump 8, the flow of hydraulic oil is reversed from that in the above embodiment, and the low-pressure hydraulic oil supplied from the oil supply valve 60 </ b> A to the hydraulic chamber 25 is reciprocated by the piston 22. After the pressure is increased in the hydraulic chamber 25, the oil is discharged from the oil discharge valve 60B. In this case, contrary to the above-described embodiment, it is more efficient to place the oil drain valve 60B near the hydraulic chamber 25 because the high-pressure hydraulic oil does not need to pass through the bypass internal flow path 35C. Oil can be supplied.

  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.

  The radial piston hydraulic machine of at least one embodiment of the present invention is suitably used as a hydraulic pump and a hydraulic motor mounted on a wind power generator.

DESCRIPTION OF SYMBOLS 1 Wind power generator 2 Blade 3 Rotor 4 Hub 5 Hub cover 6 Rotating shaft 8 Hydraulic pump 10 Hydraulic motor 12 High pressure oil line 14 Low pressure oil line 16 Generator 18 Nacelle 19 Tower 20 Hydraulic machine 22 Piston 24 Cylinder 25 Hydraulic chamber 26 Cylinder block 27 Machine element 28 Rotating shaft 28a Eccentric cam 30 Oil passage 30A Oil supply passage 30B Oil discharge passage 35 Internal flow passage 35A Oil supply internal flow passage 35B Oil discharge internal flow passage 35a, 35b Internal flow passage set 35C Bypass internal flow passage 36A, 36B Connection passage 38A Oil supply valve body arrangement area 38B Oil discharge valve body arrangement area 39A Blockage 40 Cylinder sleeve 40a Hydraulic chamber surrounding part 40b Valve housing part 41 Lid member 42 Upper member 43 Outer member 44 Lower member 45 Bulkhead member 45A Bushing 46 Bulkhead 46a Bushing hole 50 Cylinder block body 5 a, 51b Bolt 52 Sleeve hole 53 Nut 54a Bolt 54b Nut 60 Valve 60A Oil supply valve 60B Oil drain valve 61A Annular bobbin 61B Groove 62a Through hole 62A, 62B Valve body 63A, 63B Movable shaft 64A, 64B Drive part 65A, 65B Core 66A , 66B Solenoid 67A, 67B Magnetic force receiving portion 67'A Hydraulic receiving portion 68A, 68B Energizing spring 69 Through hole 69A, 68B Shaft portion 70 Solenoid placement area 70A Oil supply solenoid chamber 70B Oil discharge solenoid chamber 70'A Oil chamber 72A , 72B Seat surface 72a Recess 74A, 74B Communication passage 81-84 O-ring 92 Oil supply passage 94 Pilot valve

Claims (16)

At least one piston,
At least one cylinder for reciprocally guiding the at least one piston;
At least one oil supply valve for switching a supply state of hydraulic oil to at least one hydraulic chamber respectively formed by the at least one piston and the at least one cylinder;
And at least one oil discharge valve for switching a discharge state of the hydraulic oil from the at least one hydraulic chamber,
Each of the oil supply valves and each of the oil discharge valves includes a valve body, a movable shaft connected to the valve body, and a drive unit configured to move the movable shaft,
The first movable shaft that is one of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve is a second movable shaft that is the other of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve. A hydraulic machine, wherein the first movable shaft and the second movable shaft are configured to be movable independently of each other by the drive unit.   The hydraulic machine according to claim 1, wherein the driving unit includes a solenoid for generating a magnetic force for moving the movable shaft.   2. The hydraulic machine according to claim 1, wherein the driving unit includes a pilot valve for moving the movable shaft by applying hydraulic pressure to a hydraulic pressure receiving portion provided on the movable shaft.   The solenoid arrangement area where the solenoid of the oil supply valve and the solenoid of the oil discharge valve are arranged is a valve element arrangement area where the valve body of the oil supply valve and the valve body of the oil discharge valve are arranged. The hydraulic machine according to claim 2, wherein the hydraulic machine is provided separately.   The hydraulic machine according to claim 4, wherein the solenoid arrangement area is arranged farther from the hydraulic chamber than the valve element arrangement area.   The hydraulic machine according to claim 5, wherein the solenoid arrangement region includes one solenoid chamber in which the solenoids of both the oil supply valve and the oil discharge valve are accommodated.   The solenoid arrangement area includes an oil supply solenoid chamber in which the solenoid of the oil supply valve is accommodated, and an oil discharge solenoid chamber which is provided separately from the oil supply solenoid chamber and in which the solenoid of the oil discharge valve is accommodated. The hydraulic machine according to claim 5, comprising: A communication path for communicating at least one of the solenoid chamber for oil supply or the solenoid chamber for oil discharge and the valve element arrangement region;
The at least one of the oil supply solenoid chamber or the oil discharge solenoid chamber is provided on the movable shaft so as to extend radially outward of the movable shaft, and receives the magnetic force from the solenoid. The hydraulic machine according to claim 7, wherein a magnetic force receiving portion is accommodated. The pressure receiving area of the magnetic force receiving portion from the hydraulic oil in the at least one of the oil supply solenoid chamber or the oil discharge solenoid chamber is A, and the pressure shaft is connected to the movable shaft provided with the magnetic force receiving portion. when the pressure receiving area from the working oil of the valve body and the a _0, the hydraulic machine of claim 8, the pressure receiving area ratio a / a ₀ is characterized in that 0.8 to 1.2. In the first solenoid chamber, which is one of the oil supply solenoid chamber and the oil discharge solenoid chamber, the solenoid for moving the first movable shaft is disposed,
In the second solenoid chamber located between the first solenoid chamber and the hydraulic chamber, which is the other of the oil supply solenoid chamber and the oil discharge solenoid chamber, the second movable shaft is moved. The hydraulic machine according to any one of claims 7 to 9, wherein a solenoid is disposed. A bush provided between the first movable shaft and the second movable shaft;
A partition having a bush hole into which the bush is inserted, and partitioning the first solenoid chamber and the second solenoid chamber;
The hydraulic machine according to claim 10, further comprising a seal member provided between an inner peripheral surface of the bush hole of the partition wall and an outer peripheral surface of the bush.   The first movable shaft is made of a magnetic material and receives a magnetic force from the solenoid. The shaft portion is made of a non-magnetic material and is inserted into the through hole of the second movable shaft. The hydraulic machine according to any one of claims 2 and 4 to 11, wherein: The solenoid of at least one of the oil supply valve and the oil discharge valve is accommodated in a groove portion of an annular core,
The at least one movable shaft of the oil supply valve and the oil discharge valve is disposed so as to cover at least an opening portion of the groove portion of the annular core, and receives the magnetic force from the solenoid accommodated in the groove portion. The hydraulic machine according to any one of claims 2 and 4 to 12, further comprising a magnetic force receiving portion configured as described above. The solenoid of at least one of the oil supply valve and the oil discharge valve includes a plurality of solenoids respectively housed in recesses of a plurality of cores discretely arranged around a central axis of the movable shaft,
The movable shaft of the at least one of the oil supply valve and the oil discharge valve is disposed so as to cover at least an opening portion of the recess of the plurality of cores, and the solenoid from the solenoid accommodated in each of the recesses The hydraulic machine according to any one of claims 2 and 4 to 12, further comprising a magnetic force receiving portion configured to receive a magnetic force.   The hydraulic machine according to any one of claims 1 to 14, wherein the movable shafts of the oil supply valve and the oil discharge valve are arranged coaxially with respect to each of the cylinders. 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 reciprocally guiding the at least one piston, the at least one piston, and the at least one cylinder. At least one oil supply valve for switching the supply state of hydraulic oil to at least one hydraulic chamber formed respectively, and at least one for switching the discharge state of the hydraulic oil from the at least one hydraulic chamber, respectively. Including a drain valve,
Each of the oil supply valves and each of the oil discharge valves includes a valve body, a movable shaft connected to the valve body, and a drive unit configured to move the movable shaft,
The first movable shaft that is one of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve is a second movable shaft that is the other of the movable shaft of the oil supply valve and the movable shaft of the oil discharge valve. A wind turbine generator, wherein the first movable shaft and the second movable shaft are configured to be movable independently of each other by the drive unit.

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