WO2011121883A1 - バルブプレート、並びにこれを備えたアキシャルピストン式油圧ポンプ・モータ - Google Patents
バルブプレート、並びにこれを備えたアキシャルピストン式油圧ポンプ・モータ Download PDFInfo
- Publication number
- WO2011121883A1 WO2011121883A1 PCT/JP2011/001060 JP2011001060W WO2011121883A1 WO 2011121883 A1 WO2011121883 A1 WO 2011121883A1 JP 2011001060 W JP2011001060 W JP 2011001060W WO 2011121883 A1 WO2011121883 A1 WO 2011121883A1
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- WIPO (PCT)
- Prior art keywords
- valve plate
- port
- axial piston
- motor
- recess
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
- F01B3/0047—Particularities in the contacting area between cylinder barrel and valve plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/128—Driving means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2035—Cylinder barrels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
- F01B3/007—Swash plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/11—Kind or type liquid, i.e. incompressible
Definitions
- the present invention relates to a valve plate, and an axial piston hydraulic pump and an axial piston hydraulic motor provided with the valve plate.
- an axial piston hydraulic pump and an axial piston hydraulic motor are known.
- a swash plate type hydraulic pump and a swash shaft type hydraulic pump are known.
- a swash plate type hydraulic motor a swash plate type hydraulic motor and an oblique axis type hydraulic motor are known.
- a swash plate type hydraulic pump (hereinafter also simply referred to as a swash plate type pump), for example, one disclosed in Patent Document 1 is known.
- a swash plate type hydraulic motor hereinafter also simply referred to as a swash plate type motor
- An oblique axis hydraulic pump / motor disclosed in, for example, Patent Document 3 is known.
- FIG. 11 shows a swash plate pump 61 of Patent Document 1.
- a cylinder block 64 is provided in the pump housing 62 of the swash plate pump 61 and is fixed to the drive shaft 63 and can rotate integrally. The rear end surface of the cylinder block 64 is supported in contact with the valve plate 65.
- a plurality of cylinders 66 are formed around the drive shaft 63 in the cylinder block 64 in parallel with each other.
- a piston 67 is inserted into each cylinder 66. The tip of each piston 67 is connected to a shoe 67a.
- the shoe 67 a is rotatable integrally with the cylinder block 64 and the piston 67 and is slidable with respect to the shoe plate 68 fixed to the swash plate 69.
- the cylinder block 64 When the drive shaft 63 is rotated by a drive device (not shown), the cylinder block 64 also rotates together, and the piston 67 reciprocates in the cylinder 66 due to the reaction from the swash plate 69.
- the cylinder block 64 has its rear end face pressed against the valve plate 65 by the action of the internal pressure of the cylinder 66. Since the cylinder block 64 rotates in this state, frictional heat is generated on the sliding surfaces of the valve plate 65 and the cylinder block 64. In general, while the hydraulic oil is sealed on this sliding surface, the heat balance is maintained by lubricating and cooling with an appropriate amount of drain oil (leakage oil) at the same time.
- the present invention has been made to solve such a problem, and provides a valve plate that can greatly suppress the temperature rise of the valve plate during operation without relying on the adjustment of the amount of leaked oil by the hydraulic balance of the sliding surface.
- An object of the present invention is to provide an axial piston type hydraulic pump and an axial piston type hydraulic motor using the valve plate.
- the valve plate of the present invention is A valve plate used in an axial piston type hydraulic device having a rotating shaft and a rotating cylinder block in a housing, A sliding support surface that contacts and supports the rear end surface of the cylinder block; A back surface that is the opposite surface corresponding to the sliding support surface; A central hole through which the rotating shaft passes; It has a plurality of ports formed so as to penetrate through the central hole as a hydraulic oil entrance and exit, A cooling recess into which hydraulic oil can flow is formed in a region excluding the port on the back surface.
- the hydraulic oil flowing into the cooling recess on the back surface serves as a refrigerant, and takes away frictional heat due to sliding with the cylinder block.
- the cooling action of the valve plate is exhibited. Since the sliding surface temperature is locally higher than the drain oil temperature in the housing, the cooling effect can be achieved by using any of the drain oil in the housing, the oil that passes through the suction port, or the discharge port as the working oil. Is obtained.
- the cooling recess is formed on at least one of the upper and lower sides of the center hole where the port is not formed, and
- the bottom of the recess may be the sliding support surface.
- a groove for circulating hydraulic oil can be formed on the back surface, which communicates with at least one of the inner central hole and the outer housing space from the cooling recess. By doing so, hydraulic oil flows between the recess and the inner central hole and / or the outer housing space, so that an improvement in cooling effect can be expected.
- the cooling recess may be constituted by a groove communicating with the inner central hole on the back surface and the outer housing space. If it carries out like this, the distribution
- this valve plate is for an axial piston type hydraulic pump
- a groove for circulating hydraulic fluid is formed on the back surface, which communicates from the cooling recess to the port that is on the hydraulic oil suction side of the port. May be. By doing so, a large amount of hydraulic oil flows through the recess, so that the cooling effect of the valve plate is improved.
- the groove may be the recess itself. That is, the recess may be formed so as to communicate with the port on the hydraulic oil suction side.
- valve plate When this valve plate is for an axial piston type hydraulic motor, a hydraulic oil supply passage communicating with a port on the hydraulic oil discharge side of the ports may be connected to the cooling recess. By doing so, the cooling fluid is positively fed into the recess from the oil discharge side port, so that the cooling effect is improved.
- the hydraulic pump of the present invention is An axial piston hydraulic pump with a valve plate,
- the valve plate is any one of the valve plates described above,
- the rotating shaft is a driving shaft for rotating the cylinder block;
- the plurality of ports are a hydraulic oil suction port and a discharge port.
- the hydraulic motor of the present invention is An axial piston hydraulic motor with a valve plate,
- the valve plate is any one of the valve plates described above,
- the rotating shaft is a motor shaft that is rotationally driven by the rotation of the cylinder block;
- the plurality of ports are a hydraulic oil supply port and a discharge port that are switched to each other by switching the rotation direction of the motor.
- the hydraulic oil flowing into the cooling recess on the back surface of the valve plate serves as a refrigerant and takes away frictional heat due to sliding with the cylinder block. This effectively cools the valve plate. Accordingly, the rotational speed of the cylinder block can be increased and the hydraulic pressure can be increased without causing problems such as seizure on the sliding surface with the cylinder block.
- FIG. 1 is a longitudinal sectional view showing a main part of a swash plate type axial piston hydraulic motor having a valve plate according to an embodiment of the present invention.
- FIG. 2 is a cross-sectional view taken along the line II in FIG. 1, showing the back surface of the valve plate incorporated in the axial piston hydraulic motor of FIG.
- FIG. 3 is a view corresponding to the view taken along the line II of FIG. 1, showing another embodiment of a valve plate for an axial piston hydraulic motor.
- FIG. 4 is a view corresponding to the view taken along the line II in FIG. 1, showing still another embodiment of a valve plate for an axial piston hydraulic motor.
- FIG. 5 is a view corresponding to a view taken along the line II of FIG.
- FIG. 6 is a view corresponding to the view taken along the line II of FIG. 1, showing still another embodiment of a valve plate for an axial piston hydraulic motor.
- FIG. 7 is a view corresponding to a view taken along the line II of FIG. 1, showing still another embodiment of a valve plate for an axial piston hydraulic motor.
- FIG. 8 is a view corresponding to the view taken along the line II in FIG. 1, showing an embodiment of a valve plate for an axial piston hydraulic pump.
- FIG. 9 is a view corresponding to a view taken along the line II of FIG. 1, showing still another embodiment of a valve plate for an axial piston hydraulic pump.
- FIG. 10 is a view corresponding to the view taken along the line II of FIG. 1, showing still another embodiment of the valve plate for the axial piston hydraulic pump.
- FIG. 11 is a longitudinal sectional view showing a swash plate type axial piston hydraulic pump provided with a conventional valve plate.
- valve plate of the present invention Embodiments of a valve plate of the present invention, and an axial piston hydraulic motor and an axial piston hydraulic pump provided with the valve plate will be described with reference to the accompanying drawings.
- FIG. 1 shows a main part of an axial piston type hydraulic motor (hereinafter referred to as a swash plate type motor) according to an embodiment of the present invention.
- a cylinder block 3 is provided in the motor housing 2 of the swash plate motor 1.
- a motor shaft 4 as an output shaft is fixed to the cylinder block 3 along the central axis CL.
- the motor shaft 4 also rotates integrally.
- the rear end surface 3r of the cylinder block 3 is supported in a state of being in contact with the front surface 5f of the valve plate 5. Therefore, this front surface is also referred to as a sliding support surface 5f.
- valve plate 5 Since the valve plate 5 has a central through hole 5a through which the motor shaft 4 penetrates at the center thereof, the valve plate 5 has an annular shape as a whole (see FIG. 2).
- the valve plate 5 is supported in a state where its rear end portion is fitted in a circular fitting recess 2 a formed on the inner wall surface of the motor housing 2.
- the outer peripheral side of the rear end face (back face) of the valve plate 5 is cut shallowly so that a gap G is formed between the face of the motor housing 2.
- the hydraulic pressure balance on the back surface of the valve plate 5 is set by the area of the back surface that is in contact with the surface of the motor housing 2 (referred to as the support surface 5s).
- a detent pin 11 for preventing rotation of the valve plate 5 is implanted in the inner wall surface of the motor housing 2.
- a plurality of cylinders 6 are formed in parallel with each other around the central through hole 5a.
- a piston 7 is inserted into each cylinder 6.
- the spherical portion of each piston 7 is connected to a shoe 7a.
- the shoe 7a is pressed against the shoe plate 9a fixed to the swash plate 9 by the presser plate 8, and can rotate integrally with the cylinder block 3 and the piston 7, and can slide with respect to the swash plate 9 and the shoe plate 9a.
- a port 6 a for supplying and discharging hydraulic oil to and from the cylinder 6 is formed.
- a plurality of ports 10 penetrating the valve plate 5 and communicating with the respective ports 6 a of the cylinder block 3 are formed.
- three ports 10 ⁇ / b> L and 10 ⁇ / b> R are formed between the top dead center U and the bottom dead center L, respectively, along the circumferential direction.
- the number of ports is not limited to three.
- the rear end surface 3r of the cylinder block 3 is pressed against the sliding support surface 5f of the valve plate 5 by the pressure of the hydraulic oil inside the cylinder 6, and the cylinder block 3 rotates in that state.
- the sliding support surface 5f is a portion corresponding to the support surface 5s on the back surface described above.
- groove-like recesses 12 are formed in the vicinity of the top dead center U and the bottom dead center L on the support surface 5 s of the valve plate 5. These recesses 12 are provided for cooling the valve plate 5 with the hydraulic oil flowing therein.
- Each recess 12 includes an arcuate groove 12a formed along the outer circumference in the vicinity of the outer periphery of the valve plate 5 and a radial groove 12b for communicating the arcuate groove 12a with the central through hole 5a. Has been.
- the bottom surface of the recess 12 is formed such that the surface on the cylinder block 3 side is included in the sliding support surface 5f.
- the recess 12 is filled with oil in the motor housing 2. Since the oil in the housing 2 is lower than the sliding surface temperature, a cooling effect can be obtained.
- the arc-shaped groove 12a and the radial groove 12b have slightly different depths, but the configuration is not limited thereto. Both grooves may be the same depth, or the radial groove 12b may be deeper.
- FIGS. 2 to 8 show other differently shaped cooling recesses 23, 24, 25, 26, 27, 28 formed in the valve plates 13, 14, 15, 16, 17, 18 respectively. Yes.
- the valve plates shown in FIGS. 2 to 8 are all for swash plate type motors.
- These cooling recesses 12, 23 to 28 including the recess 12 of FIG. 2 are formed at the top dead center U and the bottom dead center L of the valve plates 13 to 18. This is because the ports 10 are not formed at the top dead center U and the bottom dead center L, so that the frictional heat is not easily dissipated and the temperature is likely to rise as compared with other portions.
- the top dead center U and the bottom dead center L have a sufficient space for forming a recess.
- a recess may be formed between the left and right ports 10L and 10R instead of the top and bottom dead centers U and the bottom dead center L. This is because a cooling effect is exhibited even if a recess is formed in any part of the support surface.
- An arc-shaped groove 23 a formed along the outer circumference circle and a short radial groove 23 b for communicating the arc-shaped groove 23 a with the motor housing 2 outside the valve plate 13 are configured.
- the arc-shaped groove 23 a is formed in the vicinity of the outer periphery of the valve plate 13. The hydraulic oil in the low pressure port discharged from the cylinder 6 flows into the recess 23 through the hydraulic oil supply passage 19. Then, it flows out into the housing 2 through the radial groove 23b.
- the recess 24 of the valve plate 14 in FIG. 4 is obtained by adding one second radial groove 24c directed inward with respect to the recess 23 in FIG. Since other shapes are the same as the recess 23 of FIG. 3 including the first radial groove 24b, similar portions are denoted by similar reference numerals and detailed description thereof is omitted.
- the second radial groove 24c extends from the center of the arc-shaped groove 24a toward the inner central through hole 14a, but does not reach the central through hole 14a.
- the second radial groove 24c is provided in order to effectively expand the cooling area.
- the recess 25 of the valve plate 15 in FIG. 5 is obtained by adding a plurality of second radial grooves 25c similar to those described in FIG. 4 to the recess 23 in FIG.
- Other shapes, such as the arcuate groove 25a and the first radial groove 25b are the same as those in the recesses of FIGS. 3 and 4, so that similar parts are denoted by similar reference numerals and detailed description thereof. Is omitted. All the second radial grooves 25c do not reach the central through hole 15a.
- the plurality of second radial grooves 25c are also provided in order to effectively expand the cooling area.
- the recess 26 of the valve plate 16 in FIG. 6 is a larger enlargement of the width of the arc-shaped groove 23a in the recess 23 in FIG. Since other shapes, for example, the radial groove 26b are the same as those of the recess 23 in FIG. 3, similar parts are denoted by the same reference numerals, and detailed description thereof is omitted.
- the width of the arc-shaped groove 26a is about 1.5 to 2 times the width of the arc-shaped grooves 12a, 23a, 24a, and 25a shown in FIGS.
- the recess 27 of the valve plate 17 in FIG. 7 employs a plurality of circular recesses 27a aligned along the outer circumference in the vicinity of the outer circumference of the valve plate 17 in place of the arc-shaped groove 23a in FIG. Yes.
- a short radial groove 27b for communicating the circular recess 27a at both ends into the motor housing 2 outside the valve plate 17 is formed.
- the recess 28 of the valve plate 18 in FIG. 8 is formed by forming only one recess 28a similar to the circular recess shown in FIG. 7 at the top dead center U and the bottom dead center L instead of a plurality. is there.
- a short radial groove 28b similar to that shown in FIG. 2 is formed from each circular recess 28a so as to communicate with the central through hole 18a of the valve plate 18.
- the recesses of the swash plate type motor valve plates 5 and 13 to 18 are illustrated in FIGS. 2 to 8, but the present invention is not limited to such a configuration.
- the recess may be communicated with both the outer motor housing 2 and the central through holes 5a, 13a to 18a, instead of communicating with only one of them.
- the recess may be formed only from the radial groove that directly communicates the inside of the outer motor housing 2 and the central through holes 5a and 13a to 18a without providing the arc-shaped groove.
- hydraulic oil is provided in the recesses.
- This dedicated passage is shown in broken lines in FIG. That is, the hydraulic oil supply passage 19 is formed in a tunnel shape in the wall of the motor housing 2.
- the hydraulic oil supply passage 19 is connected to the low-pressure side port 10L or 10R described above, although not shown. Then, hydraulic oil can be exchanged with a port on the oil drain side by a switching valve (not shown).
- the cooling effect is improved by positively feeding the cooling hydraulic oil into the recess.
- the cooling recess is not communicated with the port in order to increase the cooling effect unlike the swash plate type pump described later.
- the left and right ports may alternately become high-pressure side oil supply ports by changing the rotation direction.
- the recess is communicated with the oil supply port, a part of the high-pressure hydraulic oil to be supplied to the cylinder may flow into the recess and the output efficiency of the motor may be reduced.
- the action of separating the valve plates 5 and 13 to 18 from the motor housing 2 works.
- the cooling effect may be improved by communicating the cooling recess with the port.
- the swash plate pump basically has the same structure as the swash plate motor. However, unlike a swash plate type motor, the swash plate type pump is not a motor shaft but a drive shaft. The cylinder block is rotated by rotating the drive shaft by the drive device. As a result, each piston having the spherical tip connected to the shoe 7a is reciprocated in the cylinder. In this way, the swash plate type pump is completely opposite in input and output to the swash plate type motor. However, it is the same as the swash plate type motor that the cylinder block rotates while being pressed against the valve plate by the action of the internal pressure of the cylinder. As a result, frictional heat is generated on the sliding surface between the valve plate and the cylinder block. The above points are as described in the “Background Art” section of this specification.
- the suction side port 22R has a different shape from the port 10R (FIGS. 2 to 8) of the swash plate type motor. This is because the hydraulic fluid on the suction side has a low pressure, so that even if the long port 22R as shown in the figure is formed, there is no problem with the strength of the valve plates 20 and 21.
- the suction side is always the suction side, and the rotation direction of the drive shaft is not changed to reverse the suction and discharge.
- the high pressure side forms a bridge (portion between the port 22L and the port 22L) so as to maintain the strength of the valve plates 20 and 21.
- cooling recesses are formed at the top dead center U and the bottom dead center L, respectively.
- a recess 30 is formed that is similar to the recess 12 of the motor valve plate 5 shown in FIG. 2.
- the recesses 30 at the top dead center U and the bottom dead center L are formed in the vicinity of the outer periphery of the valve plate 20 along an outer circumferential circle, and the arc-shaped groove 30a communicates with the central through hole 20a.
- a radial groove 30b is formed in the vicinity of the outer periphery of the valve plate 20 along an outer circumferential circle, and the arc-shaped groove 30a communicates with the central through hole 20a.
- a radial groove 30b a radial groove 30b.
- one end side of the arc-shaped groove 30a communicates with the suction side port 22R. Accordingly, the hydraulic fluid flows between the suction side port 22R and the central through hole 20a via the arc-shaped groove 30a and the radial groove 30b.
- the cooling effect of the valve plate 20 is improved by communicating the recess 30 with the port 22R having a large amount of operating oil compared to the case where the recess 30 is communicated only with the outer motor housing 2 or the central through hole 20a.
- the reason why the arc-shaped groove 30a communicates with the suction side port 22R instead of the discharge side port 22L is that the pump efficiency decreases when the arcuate groove 30a communicates with the discharge side port 22L.
- the recess 31 of the valve plate 21 shown in FIG. 10 is composed only of an arc-shaped groove 31a communicating with the suction side port 22R.
- the recesses 30 and 31 of the valve plates 20 and 21 for the swash plate pump are illustrated only in FIGS. 9 and 10, but are not limited to such a configuration.
- the recesses 12 and 23 to 28 of the swash plate type motor valve plates 5 and 13 to 18 shown in FIGS. 2 to 8 may be employed as they are.
- a configuration in which the arc-shaped grooves 23a, 24a, 25a, and 26a shown in FIGS. 3 to 6 are communicated with the suction side port 22R may be employed.
- the second radial grooves 24c and 25c shown in FIGS. 4 and 5 may be connected to the suction port 22R.
- the circular recesses 27a and 28a shown in FIGS. 7 and 8 may be connected to the suction side port 22R.
- a swash plate motor and a swash plate pump are taken as examples. However, it is not limited to these.
- the present invention can be applied to a slant shaft hydraulic motor and a slant shaft hydraulic pump.
- the valve plate can be effectively cooled without relying on the adjustment of the leaked oil amount. Therefore, it is particularly useful for a hydraulic motor and a hydraulic pump that require a further increase in the rotational speed and a further increase in the hydraulic oil pressure.
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Abstract
Description
回転軸と回転式のシリンダブロックとをハウジング内に備えたアキシャルピストン式の油圧機器に用いられるバルブプレートであって、
前記シリンダブロックの後端面に当接してこれを支持する摺動支持面と、
この摺動支持面に対応した反対側の面である背面と、
前記回転軸が貫通する中心孔と、
この中心孔の周囲に作動油の出入口として貫通するように形成された複数のポートとを有しており、
前記背面における前記ポートを除く領域に、作動油が流入しうる冷却用凹所が形成されている。
バルブプレートを備えたアキシャルピストン式油圧ポンプであって、
前記バルブプレートが前述したうちのいずれかのバルブプレートであり、
前記回転軸が前記シリンダブロックを回転させるための駆動軸であり、
前記複数のポートが作動油の吸い込みポートおよび吐出ポートである。
バルブプレートを備えたアキシャルピストン式油圧モータであって、
前記バルブプレートが前述したうちのいずれかのバルブプレートであり、
前記回転軸が前記シリンダブロックの回転によって回転駆動されるモータシャフトであり、
前記複数のポートが、モータの回転方向の切替によって相互に切り替わる作動油の供給ポートおよび排出ポートである。
2・・・・モータハウジング
3・・・・シリンダブロック
4・・・・モータシャフト
5・・・・バルブプレート
6・・・・シリンダ
7・・・・ピストン
7a・・・・シュー
8・・・・押え板
9・・・・斜板
9a・・・・シュープレート
10・・・・ポート
11・・・・回り止めピン
12・・・・凹所
13~18・・・・バルブプレート
19・・・・作動油供給通路
20、21・・・・バルブプレート
22・・・・ポート
23~28・・・・凹所
30、31・・・・凹所
CL・・・・(シリンダブロックの)中心軸
G・・・・(バルブプレートの背面の隙間)
Claims (8)
- 回転軸と回転式のシリンダブロックとをハウジング内に備えたアキシャルピストン式の油圧機器に用いられるバルブプレートであって、
前記シリンダブロックの後端面に当接してこれを支持する摺動支持面と、
この摺動支持面に対応した反対側の面である背面と、
前記回転軸が貫通する中心孔と、
この中心孔の周囲に作動油の出入口として貫通するように形成された複数のポートとを有しており、
前記背面における前記ポートを除く領域に、作動油が流入しうる冷却用凹所が形成されているバルブプレート。 - 前記ポートが前記中心孔の左右両側に形成されており、前記冷却用凹所が前記中心孔の上下のうち少なくともいずれか一方に形成されており、かつ、当該凹所の底部が前記摺動支持面にしていることを特徴とする請求項1記載のバルブプレート。
- 前記背面に、前記冷却用凹所から内方の前記中心孔および外方のハウジング内空間のうちの少なくとも一方に連通する作動油流通用の溝が形成されている請求項1または2記載のバルブプレート。
- 前記冷却用凹所が、前記背面の内方の前記中心孔および外方のハウジング内空間とを連通する溝から構成されている請求項1記載のバルブプレート。
- 前記油圧機器がアキシャルピストン式の油圧ポンプであり、前記背面に、前記冷却用凹所から前記ポートのうち作動油吸入側とされているポートに連通する作動油流通用の溝が形成されている請求項1記載のバルブプレート。
- 前記油圧機器がアキシャルピストン式の油圧モータであり、前記冷却用凹所に、前記ポートのうち作動油排出側となるポートに連通する作動油供給通路が接続されている請求項1記載のバルブプレート。
- バルブプレートを備えたアキシャルピストン式油圧ポンプであって、
前記バルブプレートが請求項1記載のバルブプレートであり、
前記回転軸が前記シリンダブロックを回転させるための駆動軸であり、
前記複数のポートが作動油の吸い込みポートおよび吐出ポートであるアキシャルピストン式油圧ポンプ。 - バルブプレートを備えたアキシャルピストン式油圧モータであって、
前記バルブプレートが請求項1記載のバルブプレートであり、
前記回転軸が前記シリンダブロックの回転によって回転駆動されるモータシャフトであり、
前記複数のポートが、モータの回転方向の切替によって相互に切り替わる作動油の供給ポートおよび排出ポートであるアキシャルピストン式油圧モータ。
Priority Applications (4)
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US13/582,310 US9175672B2 (en) | 2010-03-31 | 2011-02-24 | Valve plate and axial piston hydraulic pump motor including the same |
CN201180016119.2A CN102812243B (zh) | 2010-03-31 | 2011-02-24 | 阀板及具备该阀板的轴向活塞式油压泵或马达 |
KR1020127015977A KR101390584B1 (ko) | 2010-03-31 | 2011-02-24 | 밸브 플레이트 및 이를 구비한 액시얼 피스톤식 유압 펌프 및 유압 모터 |
EP11762137.5A EP2554842B1 (en) | 2010-03-31 | 2011-02-24 | Valve plate, and axial piston hydraulic pump and axial piston hydraulic motor with same |
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JP2010-080588 | 2010-03-31 | ||
JP2010080588A JP5444088B2 (ja) | 2010-03-31 | 2010-03-31 | バルブプレート、並びにこれを備えたアキシャルピストン式油圧ポンプ・モータ |
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WO2011121883A1 true WO2011121883A1 (ja) | 2011-10-06 |
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PCT/JP2011/001060 WO2011121883A1 (ja) | 2010-03-31 | 2011-02-24 | バルブプレート、並びにこれを備えたアキシャルピストン式油圧ポンプ・モータ |
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US (1) | US9175672B2 (ja) |
EP (1) | EP2554842B1 (ja) |
JP (1) | JP5444088B2 (ja) |
KR (1) | KR101390584B1 (ja) |
CN (1) | CN102812243B (ja) |
WO (1) | WO2011121883A1 (ja) |
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JP2014126020A (ja) * | 2012-12-27 | 2014-07-07 | Kawasaki Heavy Ind Ltd | アキシャルピストンモータ |
US9657726B1 (en) | 2013-04-19 | 2017-05-23 | Hydro-Gear Limited Partnership | Hydraulic running surface |
DE102014207158A1 (de) * | 2013-12-12 | 2015-06-18 | Robert Bosch Gmbh | Hydrostatische Axialkolbenmaschine |
JP2015166580A (ja) * | 2014-03-04 | 2015-09-24 | 株式会社豊田自動織機 | 圧縮機 |
CN105201816B (zh) * | 2015-09-07 | 2017-03-22 | 福州大学 | 一种斜盘式柱塞泵的缸体自冷却结构 |
SG11201808630WA (en) | 2016-04-15 | 2018-10-30 | Alder Biopharmaceuticals Inc | Humanized anti-pacap antibodies and uses thereof |
JP2018076826A (ja) * | 2016-11-10 | 2018-05-17 | 川崎重工業株式会社 | シリンダブロックとそれを備えた斜板形液圧回転装置 |
CN107965449B (zh) * | 2017-12-28 | 2019-03-29 | 赛克思液压科技股份有限公司 | 一种用于柱塞泵防脱缸的结构 |
JP7374638B2 (ja) | 2019-07-18 | 2023-11-07 | ナブテスコ株式会社 | 流体機械及び建設機械 |
JP7476060B2 (ja) * | 2020-09-14 | 2024-04-30 | 株式会社小松製作所 | バルブプレート、シリンダブロック、油圧モータ |
US11898582B1 (en) | 2023-03-09 | 2024-02-13 | Dana Motion Systems Italia S.R.L. | System for a bent axis motor |
US12031559B1 (en) | 2023-07-07 | 2024-07-09 | Robert Bosch Gmbh | Integrated electro-hydraulic unit |
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Also Published As
Publication number | Publication date |
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EP2554842B1 (en) | 2020-04-15 |
US9175672B2 (en) | 2015-11-03 |
JP5444088B2 (ja) | 2014-03-19 |
EP2554842A1 (en) | 2013-02-06 |
EP2554842A4 (en) | 2018-01-24 |
KR101390584B1 (ko) | 2014-04-30 |
CN102812243B (zh) | 2015-05-06 |
US20130055888A1 (en) | 2013-03-07 |
KR20120096013A (ko) | 2012-08-29 |
CN102812243A (zh) | 2012-12-05 |
JP2011214429A (ja) | 2011-10-27 |
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