WO2012066593A1 - シリンダブロックの冷却構造、及びそれを有する斜板形液圧装置 - Google Patents
シリンダブロックの冷却構造、及びそれを有する斜板形液圧装置 Download PDFInfo
- Publication number
- WO2012066593A1 WO2012066593A1 PCT/JP2010/006721 JP2010006721W WO2012066593A1 WO 2012066593 A1 WO2012066593 A1 WO 2012066593A1 JP 2010006721 W JP2010006721 W JP 2010006721W WO 2012066593 A1 WO2012066593 A1 WO 2012066593A1
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- Prior art keywords
- cylinder block
- cylinder
- piston
- pressure
- sliding surface
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
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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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
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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
- F01B3/0035—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/02—Cylinders; Cylinder heads having cooling means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/26—Cylinder heads having cooling 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
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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
- F04B1/22—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 having two or more sets of cylinders or pistons
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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
- F04B25/00—Multi-stage pumps
- F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
- F04B39/066—Cooling by ventilation
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/08—Cooling; Heating; Preventing freezing
Definitions
- the present invention provides a cylinder block in which a plurality of cylinders into which pistons can be respectively inserted are formed from openings on an end face on the piston insertion side, and the pistons that are inserted reciprocately slide the cylinders when rotated.
- the present invention relates to a cooling structure of a cylinder block of a swash plate type hydraulic device.
- swash plate type hydraulic pressure a swash plate type hydraulic motor / pump
- Appatus a swash plate type hydraulic device
- the swash plate type hydraulic device of Patent Document 1 includes a rotating shaft, and a cylinder block is integrally attached to the rotating shaft. Cylinders are formed on the end face of the cylinder block at equal intervals in the circumferential direction, and a piston is inserted into each cylinder. A shoe is attached to an end projecting from the cylinder, and the shoe is disposed on a support surface of a swash plate disposed to be inclined.
- the cylinder block rotates by reciprocating the piston in the cylinder, and the piston is reciprocated by supplying high-pressure hydraulic oil to the cylinder.
- the cylinder block rotates, and the rotation shaft provided integrally with the cylinder block can be rotated.
- the swash plate type hydraulic device functions as a hydraulic motor.
- the swash plate type hydraulic device is configured such that the piston moves reciprocally in the cylinder by rotating the cylinder block. Hydraulic oil can be discharged. That is, the swash plate type hydraulic device can be operated as a hydraulic pump.
- the swash plate type hydraulic device having the configuration as in Patent Document 1 has been mainly used for low-speed and medium-speed rotation.
- the influence of the centrifugal force acting on the piston and the shoe becomes large, and unlike the low rotation, the influence of the centrifugal force cannot be ignored.
- the contact pressure corresponds to the pressure of the hydraulic oil that is mainly supplied or discharged, so that the heat generated on the sliding surface is relatively small. Therefore, a clearance for allowing the hydraulic oil to escape is formed between the sliding surface and the piston, and the sliding surface can be sufficiently cooled only by the hydraulic oil leaking from the clearance.
- the lubricating performance of the hydraulic oil is degraded. Along with this, the amount of heat generated on the sliding surface further increases, and the cylinder and the piston may burn.
- increasing the clearance width it is possible to prevent the lubrication performance and seizure of the hydraulic oil from decreasing, but increasing the clearance width greatly increases the amount of hydraulic oil leakage. As a result, the performance of the hydraulic system is lowered and the pressure of the hydraulic device is limited.
- an object of the present invention is to provide a cylinder block cooling structure capable of improving the cooling performance of the sliding surface.
- the cylinder block cooling structure includes a cylinder block in which a plurality of cylinders having openings are formed on an end surface on the piston insertion side, and the pistons inserted into the cylinders reciprocally slide when rotated.
- a plurality of cooling grooves formed on the outer peripheral surface of the cylinder block, the cooling grooves extending from the piston insertion side end surface to a partition wall between two adjacent cylinders, and It is formed by reducing the thickness of the partition so as to reduce the thickness between the sliding surface on which the piston slides and the outer peripheral surface of the cylinder block.
- the thickness between the sliding surface and the outer peripheral surface is reduced. Since the sliding surface near the outer periphery that generates heat due to centrifugal force under high-speed rotation is higher than the temperature of the drain oil in the surrounding case, the heat generated on the sliding surface is quickly transferred to the outer peripheral surface and dissipated from the outer peripheral surface. can do. Thereby, the cooling performance of a sliding surface can be improved and the temperature rise of a sliding surface can be suppressed. Further, since the cooling groove extends from the piston insertion side end surface where the cylinder opening is located, it is possible to particularly suppress an increase in the surface temperature in the vicinity of the piston insertion side end surface of the sliding surface where the temperature rises most remarkably. Therefore, the occurrence of seizure of the sliding surface can be suppressed.
- a clearance is provided between the sliding surface and the outer peripheral surface of the piston, and hydraulic oil leaking from the clearance is used as the lubricating oil. Is done.
- By suppressing the temperature rise of the sliding surface it is possible to suppress an increase in the oil temperature of the lubricating oil and prevent the lubricating oil from being transferred. Thereby, since the fall of the lubricating performance of lubricating oil can be prevented, it can maintain moving a piston smoothly, and can reduce the emitted-heat amount in a sliding face.
- the piston slides back and forth between the top dead center and the bottom dead center of the cylinder, the cooling groove extends in parallel with the cylinder from the piston insertion side end surface, and the tip thereof is at the bottom dead center. It is preferable that the piston is formed so as to be positioned closer to the piston insertion side end surface than the vicinity of the end surface in the cylinder of the piston.
- the cooling groove has a minimum thickness tmin between the outer peripheral surface of the cylinder block and the sliding surface of 0.02D ⁇ tmin ⁇ 0.3D with respect to the inner diameter D of the cylinder. It is preferable to be formed as described above.
- the rigidity in the region on the outer peripheral surface side of the sliding surface can be ensured while improving the cooling effect. Thereby, the seizure of the cylinder block and the damage on the opening side can be prevented.
- the swash plate type hydraulic device of the present invention is connected to a low pressure side passage through which low pressure hydraulic fluid flows and a high pressure side passage through which high pressure hydraulic fluid flows, and the hydraulic fluid is supplied from the high pressure side passage to the cylinder.
- the cylinder block is rotated by discharging from the cylinder to the low pressure side passage, or the hydraulic fluid is sucked into the cylinder from the low pressure side passage by rotating the cylinder block, and further compressed, and then the high pressure side passage.
- a clearance is provided between the sliding surface and the outer peripheral surface of the piston, and hydraulic oil leaking from the clearance is used as lubricating oil. If the said structure is followed, the raise of the oil temperature of the lubricating oil which leaks from clearance will be suppressed by suppressing the temperature rise of a sliding surface, and it can prevent that lubricating oil makes a transfer. Thereby, the fall of the lubricating performance of lubricating oil can be prevented, a piston can be kept moving smoothly, and the emitted-heat amount in a sliding surface can be reduced.
- a casing for accommodating the cylinder block is provided, the inside of the casing is connected to the low-pressure side passage through a communication passage, and the low-pressure hydraulic oil in the low-pressure side passage is introduced into the casing. It is preferable that
- the outer peripheral surface of the cylinder block can be exposed to the low-pressure and low-temperature hydraulic fluid introduced into the casing, so that the outer peripheral surface can be cooled by the hydraulic fluid.
- the cooling performance of the sliding surface can be improved.
- FIG. 3 is a cross-sectional view of the cylinder block taken along the cutting line AA shown in FIG.
- FIG. 3 is an example of a hydraulic circuit diagram around the swash plate type hydraulic device.
- (A) is a figure which shows the piston in a bottom dead center
- (b) is a graph which shows the surface temperature of each position of the sliding surface of a cylinder block in the state of (a)
- (c) is It is a graph which shows the oil_pressure
- a swash plate type hydraulic device 1 according to an embodiment of the present invention will be described with reference to the drawings described above.
- the swash plate type hydraulic device 1 described below is only one embodiment of the present invention, and the present invention is not limited to the above-described embodiment, and is added, deleted, and deleted without departing from the spirit of the invention. It can be changed.
- the swash plate type hydraulic device 1 is a so-called swash plate type motor / pump, which supplies a hydraulic fluid to a function of a hydraulic motor for rotating a rotating object provided in an industrial machine or a ship or an actuator provided in an industrial machine or a ship.
- a hydraulic pump that moves the actuator.
- the fluid to be handled is assumed to be hydraulic oil
- the swash plate type hydraulic device 1 is assumed to be a hydraulic motor.
- a hydraulic motor 1 that is a swash plate type hydraulic device 1 is a high-speed rotation type hydraulic motor that includes a rotating shaft 11 as shown in FIG. 1 and can rotate the rotating shaft 11 at a high speed.
- the hydraulic motor 1 includes a cylinder block 12, a plurality of pistons 13, a plurality of shoes 14, a swash plate 15, and a valve plate 16 in addition to the rotating shaft 11, and these components are accommodated in a casing 17. Yes.
- the rotating shaft 11 extends in the front-rear direction so as to penetrate the casing 17, and is rotatably supported by bearings 18 and 19 at the front end portion and the rear end portion of the casing 17.
- a cylinder block 12 is fitted into the intermediate portion of the rotating shaft 11 on the rear end side.
- the cylinder block 12 is generally formed in a cylindrical shape, and is positioned such that its axis coincides with the axis L1 of the rotary shaft 11.
- the cylinder block 12 is integrally coupled to the rotating shaft 11 by spline coupling, and is not rotatable relative to the rotating shaft 11.
- the front end portion of the outer peripheral surface 12a of the cylinder block 12 is thinned radially inward over the entire circumferential direction, and a cooling structure 30 is further formed. Details of the structure of the cooling structure 30 will be described later.
- a plurality of cylinders 20 are formed in the cylinder block 12.
- the cylinders 20 are arranged at equal intervals in the circumferential direction as shown in FIG. 2, and extend parallel to the axis L1 as shown in FIG.
- the cylinder 20 is a hole defined by a sliding surface having a circular cross section and a bottom surface, and has an opening on the front end surface (piston insertion side end surface) of the cylinder block 12.
- the pistons 13 are inserted into the respective cylinders 20 through the openings.
- the piston 13 has a substantially columnar shape, and reciprocates in the front-rear direction while sliding on the sliding surface 12b that defines the cylinder 20.
- the cylinder 20 may be fitted with a cylindrical sleeve (not shown) such as a copper bush.
- the piston 13 slides on the inner peripheral surface of the sleeve, and the sliding surface on which the piston 13 slides means the inner peripheral surface of the sleeve.
- the outer diameter of the piston 13 is slightly smaller than the inner diameter of the cylinder 20, and a clearance is formed around the piston 13 between the piston 13 and the sliding surface 12b. Further, the piston 13 has a spherical holding portion 13 a at its front end, and the spherical holding portion 13 a protrudes from the cylinder 20 regardless of the position of the piston 13.
- the outer surface of the spherical holding portion 13a is formed on a substantially spherical surface, and a shoe 14 is attached thereto.
- the shoe 14 has a generally bottomed cylindrical shape, and its inner surface has a partial spherical shape corresponding to the spherical holding portion 13a.
- the spherical holding portion 13a of the piston 13 is fitted in the shoe 14, and the piston 13 is rotatable about the center of the spherical holding portion 13a.
- the shoe 14 has a flange 14a projecting radially outward at the bottom thereof, and is disposed on the swash plate 15 with the bottom abutting against the swash plate 15.
- the swash plate 15 is formed in a substantially disc shape.
- the swash plate 15 is provided in the casing 17 with its upper side tilted rearward, and the rotating shaft 11 passes through the vicinity of the center thereof.
- the swash plate 15 is disposed in front of the cylinder block 12 and has a support plate 21 on the cylinder block 12 side.
- the support plate 21 has an annular shape, and a plurality of shoes 14 are arranged at equal intervals in the circumferential direction. Further, the plurality of shoes 14 are provided with a pressing plate 22 for pressing them against the support plate 21.
- the holding plate 22 has a generally annular shape, and the rotation shaft 11 is inserted through the center of the holding plate 22 so as to be relatively rotatable.
- the holding plate 22 has the same number of mounting holes 22a as the shoes 14, and the mounting holes 22a are arranged at equal intervals in the circumferential direction.
- the holding plate 22 is inserted into the mounting hole 22a through the opening side of the shoe 14 and comes into contact with the flange 14a.
- the holding plate 22 cooperates with the support plate 21 to hold the flange 14a.
- the presser plate 22 has a spherical bush 23 inserted through its inner hole.
- the spherical bush 23 has a substantially cylindrical shape and is externally mounted on the rotary shaft 11 and the cylinder block 12.
- the spherical bush 23 is biased toward the support plate 21 by a plurality of pressing springs 40 provided on the cylinder block 12, and the presser plate 22 is pressed against the support plate 21 by the spherical bush 23. .
- the swash plate 15 in which the plurality of shoes 14 are arranged in this way is connected to a regulator 24 provided at the top of the casing 17 at the top.
- the regulator 24 has a plunger 25 that is movable in the front-rear direction, and the swash plate 15 is connected to the plunger 25. Therefore, by moving the plunger 25 in the front-rear direction, the inclination angle of the swash plate can be changed to adjust the stroke of the piston 13, and the capacity of the oil chamber 20a of the cylinder 20 can be changed.
- the oil chamber 20a is a space behind the rear end face of the piston 13 in the cylinder 20.
- a cylinder port 26 connected to the oil chamber 20a is formed in the cylinder block 12.
- One cylinder port 26 is provided for each cylinder 20 and corresponds to the cylinder 20 on a one-to-one basis.
- the cylinder port 26 opens at the rear end surface of the cylinder block 12, and the valve plate 16 is provided on the rear end surface.
- the valve plate 16 is an annular plate-like member, and is located between the cylinder block 12 and the rear end portion of the casing 17.
- the valve plate 16 is fixed to the casing 17 so as not to be relatively rotatable by a pin member (not shown).
- a rotation shaft 11 is inserted into the inner hole of the valve plate 16, and the rotation shaft 11 and the valve plate 16 are configured to be rotatable relative to each other.
- the valve plate 16 positioned in this way is formed with a suction port 16a and a discharge port 16b.
- the suction port 16a and the discharge port 16b are generally arcuate and are spaced apart from each other in the circumferential direction.
- the suction port 16a and the discharge port 16b penetrate the valve plate 16 in the thickness direction, and the opening on the cylinder block 12 side is connected to several cylinder ports 26, and the cylinder block 12 is rotated.
- the connection destination of the cylinder port 26 is switched alternately between the suction port 16a and the discharge port 16b.
- the opening on the other side of the suction port 16a is connected to the high-pressure side passage 27 shown in FIG. 4, and the opening of the discharge port 16b is connected to the low-pressure side passage 28 shown in FIG.
- the cylinder 20 is alternately connected to the high pressure side passage 27 and the low pressure side passage 28 by rotating the cylinder block 12.
- the positions of the suction port 16a and the discharge port 16b are shifted in the circumferential direction with respect to the actual one.
- the circuit configuration shown in FIG. 4 is an example for further enhancing the cooling effect, and the cooling effect can be obtained by the oil in the case without this configuration.
- a communication passage 29 as shown in FIG. 4 is formed in the casing 17, and the communication passage 29 connects the inside of the casing 17 and the low-pressure side passage 28.
- a certain amount of hydraulic oil flowing through the low pressure side passage 28 can be introduced into the casing 17 via the communication passage 29 and used as a coolant, and the rotary shaft 11 and the cylinder block 12 can be used by the low pressure and low temperature hydraulic oil.
- the piston 13 and the like can be cooled.
- the high pressure side passage 27 is provided from the top dead center where the piston 13 is most retracted to the cylinder 20 to the bottom dead center where the piston 13 is projected most from the cylinder 20.
- the flowing hydraulic oil is sucked into the oil chamber 20a through the suction port 16a.
- the piston 13 is pressed forward by the hydraulic oil, and as a result, the shoe 14 is pressed against the swash plate 15. Since the swash plate 15 is tilted, the pressed shoe 14 slides down on the swash plate 15 and revolves around the axis L1 in the circumferential direction. Thereby, a rotational force around the axis L1 is applied to the cylinder block 12, and the cylinder block 12 and the rotary shaft 11 rotate around the axis L1.
- the oil chamber 20a is connected to the low pressure side passage 28 via the discharge port 16b.
- the shoe 14 slides on the swash plate 15 so as to run upward, and revolves around the axis L1 in the circumferential direction.
- the piston 13 is pushed back, and the hydraulic oil in the oil chamber 20a is discharged to the low-pressure side passage 28 via the discharge port 16b.
- the piston 13 is reciprocated in the front-rear direction by sucking and discharging the hydraulic oil, and the cylinder block 12 and the rotary shaft 11 are rotated about the axis L1.
- the piston 13 slides on the sliding surface 12b and reciprocates in the front-rear direction during supply and discharge. Therefore, frictional heat is generated on the sliding surface 12b during sliding, and the surface temperature of the sliding surface 12b, particularly the region on the opening side, rises.
- a clearance is provided between the outer surface of the piston 13 and the sliding surface 12b, and the friction generated on the sliding surface 12b by lubricating the piston 13 using the working oil leaking from the clearance as lubricating oil. While reducing heat, the sliding surface 12b is cooled by the lubricating oil.
- a clearance is provided to suppress an increase in the surface temperature of the sliding surface 12b.
- the hydraulic block 1 further includes a cooling structure 30 for the cylinder block 12 to further suppress the increase in the surface temperature. .
- the cooling structure 30 of the cylinder block 12 has a cooling groove 31.
- the cooling groove 31 is formed in each partition wall 32 between two adjacent cylinders 20, and extends in parallel to the axis L1 from the front end surface of the cylinder block 12 toward the rear end surface.
- the front end of the cooling groove 31 is closer to the front end face side of the cylinder block 12 than the vicinity of the rear end face of the piston 13 located at the bottom dead center, that is, near the rear end face of the piston 13 located at the bottom dead center. It is located on the front side (see FIG. 3).
- the partition wall 32 means the entire wall between straight lines L2 and L3 extending from the center of the cylinder block 12 to the outer peripheral surface 12a through the centers of two adjacent cylinders 20 (in FIG. Area shown in the net).
- 5 (b) and 5 (c) are graphs showing the surface temperature and hydraulic pressure at various values of the sliding surface 12b when the piston 13 is located at the bottom dead center (see FIG. 5 (a)).
- 5B the vertical axis indicates the surface temperature T of the sliding surface 12b
- the horizontal axis indicates the distance d from the front end surface of the cylinder block 12.
- FIG. 5C the vertical axis indicates the sliding surface.
- the hydraulic pressure P acting on 12 b and the horizontal axis indicate the distance d from the front end face of the cylinder block 12.
- the rear side of the piston 13 (that is, between the distance d1 and the distance d2) is cooled by the hydraulic oil in the oil chamber 20a. Therefore, it is kept at a substantially constant temperature.
- the cooling effect by the hydraulic oil that has entered the clearance is small. In the vicinity of the opening, that is, the front end face of the cylinder block 12 is highest.
- the region on the rear side of the rear end surface of the piston 13 of the sliding surface 12b forms the oil chamber 20a.
- the hydraulic pressure acting on the region is substantially the same as the pressure of the hydraulic oil sucked from the suction port 16a.
- the hydraulic pressure acting on the area on the front side of the rear end face of the piston 13 of the sliding surface 12b is lowered as it advances toward the opening side because the front side of the clearance is connected in the casing 17, and on the opening side, the casing 17 The pressure falls to the internal pressure, that is, the drain pressure.
- the surface temperature of the sliding surface 12b and the hydraulic pressure acting on the sliding surface 12b change with the rear end surface of the piston 13 located at the bottom dead center as a boundary. Further, when the piston 13 is located at the bottom dead center, the high pressure acts on the sliding surface 12b over the widest range.
- the tip of the cooling groove 31 is positioned closer to the front end surface of the cylinder block 12 than the rear end surface of the piston 13, thereby increasing the rigidity of the region where the hydraulic pressure acting on the sliding surface 12b increases.
- the cooling performance in the region where the surface temperature is high can be improved. Thereby, the damage by the seizure of the cylinder 12 and the piston 13 can be prevented without lowering the use limit pressure of the hydraulic oil.
- the cooling groove 31 extending in this way is curved so as to protrude radially inward when viewed from the front as shown in FIG. 2, and is formed between the sliding surface 12b and the outer peripheral surface 12a of the partition wall 32.
- the area between is thinning.
- the cooling groove 31 is formed such that the minimum thickness tmin between the sliding surface 12b and the outer peripheral surface 12b is 0.02D ⁇ tmin ⁇ 0.3D with respect to the inner diameter D of the cylinder 20. More specifically, the thickness t between the outer peripheral surface 12a and the region 12c (corresponding to the outer peripheral surface 12a side of the sliding surface 12b) on the outer side in the radial direction of the sliding surface 12b It is formed so that 0.02D ⁇ t ⁇ 0.3D with respect to the inner diameter D.
- the radially outer region 12c is a radially outer intersection A1 of two points where the straight line L2 and the sliding surface 12b intersect and a region extending from both sides in the circumferential direction.
- the region 12c is, for example, a region in the range of the central angle ⁇ on both sides in the circumferential direction around the intersection A1, and the central angle ⁇ is 30 degrees ⁇ ⁇ ⁇ 180 degrees.
- the cooling performance in the sliding surface 12b can be improved, and an increase in the surface temperature of the sliding surface 12b can be suppressed. it can.
- the temperature rise of the hydraulic fluid (lubricating oil) flowing through the clearance between the sliding surface 12b and the piston 13 can be suppressed, and the hydraulic fluid can be prevented from reaching a high temperature and exceeding the transition temperature. . Therefore, seizure of the sliding surface 12b due to a decrease in the lubricating performance of the hydraulic oil can be prevented.
- the cooling performance The performance of the motor is not degraded while the motor is improved.
- the thickness t it is possible to ensure the rigidity in the vicinity of the opening side of the region 12c on the radially outer peripheral side of the sliding surface 12b, and the piston 13 reciprocates and slides at high speed during operation. However, it is possible to prevent the vicinity of the opening side from being damaged.
- the bottom surface of the cooling groove 31 is curved in an arch shape, but is not necessarily in the arch shape.
- the cooling groove 31A of the cooling structure 30A is sharply formed along the sliding surface 12b, and the thickness t of the entire semicircle on the radially outer side of the sliding surface 12b is uniform. It may be made to become.
- the shape of the cooling groove 31 does not need to be curved, the bottom surface may be flat, and irregularities may be formed to form fins.
- the vicinity of the tip of the bottom surface of the cooling groove 31 is curved so as to be positioned radially outward as the tip is advanced, but it is not necessary to bend and may be flat to the tip (for example, FIG. 3).
- the tip of the cooling groove 31 is between the front end face of the cylinder block 12 and the rear end face of the piston 13 located at the bottom dead center. However, it may extend to the vicinity of the rear end face.
- the swash plate type hydraulic device 1 is a hydraulic motor
- a hydraulic pump may be used as described above.
- the rotating shaft 11 is rotationally driven by an electric motor, an engine or the like to rotate the cylinder block 12.
- the piston 13 reciprocates as the cylinder block 12 rotates.
- the discharge port 16b is connected to the high pressure side passage 27, the suction port 16a is connected to the low pressure side passage 28, and the oil is passed through the suction port 16a before moving from the top dead center to the bottom dead center.
- the working oil is sucked into the chamber 20a, and the sucked working oil is compressed and discharged to the high-pressure side passage 27 through the discharge port 16b until it moves from the bottom dead center to the top dead center.
- the swash plate type hydraulic apparatus 1 has been described, but the cooling structure 30 of the cylinder block 12 may be applied to an oblique axis type hydraulic apparatus.
- the surface temperature of the sliding surface 12b does not rise as in the swash plate type hydraulic device 1 even if the speed is increased. In the case of a hydraulic device, it is higher.
- oil is used as the working fluid, other liquids such as water may be used as the working fluid.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Reciprocating Pumps (AREA)
- Hydraulic Motors (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
Description
油圧ショベル、クレーン及びブルドーザ等の建設機械や、油圧ユニット、プレス機、製鉄機械、及び射出成形機等の陸用装置等の産業機械や船舶には、そこに備わる機器やアクチュエータを駆動するために斜板形液圧装置1が設けられている。斜板形液圧装置1は、いわゆる斜板形モータ・ポンプであり、産業機械や船舶に備わる回転対象物を回転させる液圧モータの機能、又は産業機械や船舶に備わるアクチュエータに圧液を供給して該アクチュエータを動かす液圧ポンプの機能を有している。なお、以下の説明では、説明の便宜上、扱う流体を作動油とし、斜板形液圧装置1を油圧モータとして説明する。
シリンダブロック12の冷却構造30は、冷却用溝31を有している。冷却用溝31は、図2に示すように隣接する2つのシリンダ20の間にある隔壁32に夫々形成されており、シリンダブロック12の前側端面から後側端面に向かって軸線L1に平行に延在している。本実施形態において、冷却用溝31の先端は、下死点に位置するピストン13の後端面付近よりもシリンダブロック12の前側端面側、つまり下死点に位置するピストン13の後端面付近よりも前側に位置している(図3参照)。なお、隔壁32は、シリンダブロック12の中心から隣接する2つのシリンダ20の中心を通って外周面12aまで夫々延びる直線L2,L3の間にある壁全体を意味している(図2において菱形の網で示している領域)。
本実施形態では、冷却用溝31の底面がアーチ状に湾曲しているが、必ずしもアーチ状である必要はない。例えば、図6に示すように、冷却構造30Aの冷却用溝31Aを摺動面12bに沿って先鋭状に形成して、摺動面12bの半径方向外側の半円全体の厚みtが均一になるようにしてもよい。また、冷却用溝31の形状も、湾曲させる必要はなく、底面が平坦であってく、また凹凸を作ってフィンのようにしてもよい。更に、冷却用溝31の底面の先端付近が先端に進むにつれて半径方向外側に位置するように湾曲しているが、湾曲する必要はなく、先端まで平坦になっていてもよい(例えば、図3の2点鎖線の符号41参照)更に、本実施形態では、図3に示すように冷却用溝31の先端がシリンダブロック12の前側端面と下死点に位置するピストン13の後端面との間に位置しているが、前記後端面付近まで延びていてもよい。
12 シリンダブロック
12a 外周面
12b 摺動面
12c 領域
13 ピストン
17 ケーシング
20 シリンダ
27 高圧側通路
28 低圧側通路
29 連通路
30 冷却構造
31 冷却用溝
32 隔壁
Claims (5)
- ピストン挿入側端面に開口を有する複数のシリンダが形成され、回転させると前記シリンダに夫々挿入されたピストンが往復摺動するようになっているシリンダブロックであって、
前記シリンダブロックの外周面に形成される複数の冷却用溝を有し、
前記冷却用溝は、隣接する2つの前記シリンダの間にある隔壁に前記ピストン挿入側端面から延在し、且つピストンが摺動する摺動面と前記シリンダブロックの外周面との間の厚みを減らすように前記隔壁を減肉することによって形成されている、シリンダブロックの冷却構造。 - 前記ピストンは、上死点から下死点の間でシリンダ内を往復摺動し、
前記冷却用溝は、前記ピストン挿入側端面からシリンダと平行に延び、その先端が下死点に位置する前記ピストンのシリンダ内にある端面付近よりも前記ピストン挿入側端面側に位置するように形成されている、シリンダブロックの冷却構造。 - 前記冷却用溝は、前記シリンダブロックの外周面と前記摺動面のとの間の最小の厚みtminが前記シリンダの内径Dに対して0.02D≦tmin≦0.3Dとなるように形成されている、シリンダブロックの冷却構造。
- 低圧の作動液が流れる低圧側通路と高圧の作動油が流れる高圧側通路に接続されており、前記作動液が前記高圧側通路から前記シリンダに供給されて前記シリンダから前記低圧側通路に排出することでシリンダブロックを回転させ、又は前記シリンダブロックを回転させることで前記低圧側通路から前記シリンダに作動液を吸入し、更に圧縮してから高圧側通路へと吐出する斜板形液圧装置であって、
請求項1乃至3の何れか1つに記載される前記シリンダブロックの冷却構造を有する、斜板形液圧装置。 - 前記シリンダブロックを収容するケーシングを有し、
前記ケーシング内は、連通路を介して前記低圧側通路と繋がっており、ケーシング内には、前記低圧側通路の低圧の作動油が導かれている、請求項4に記載の斜板形液圧装置。
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KR1020127005007A KR101330768B1 (ko) | 2010-11-16 | 2010-11-16 | 실린더 블록의 냉각 구조 및 이를 갖는 사판형 액압 장치 |
JP2012516416A JP5444462B2 (ja) | 2010-11-16 | 2010-11-16 | シリンダブロックの冷却構造、及びそれを有する斜板形液圧装置 |
CN2010800361423A CN102630279A (zh) | 2010-11-16 | 2010-11-16 | 缸体的冷却结构及具有该结构的斜板型液压装置 |
US13/635,151 US20130000481A1 (en) | 2010-11-16 | 2010-11-16 | Cooling structure of cylinder block and swash plate type liquid-pressure apparatus including same |
EP10859806.1A EP2642123A4 (en) | 2010-11-16 | 2010-11-16 | Cooling structure for cylinder block and swash plate-type hydraulic device equipped with same |
PCT/JP2010/006721 WO2012066593A1 (ja) | 2010-11-16 | 2010-11-16 | シリンダブロックの冷却構造、及びそれを有する斜板形液圧装置 |
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EP (1) | EP2642123A4 (ja) |
JP (1) | JP5444462B2 (ja) |
KR (1) | KR101330768B1 (ja) |
CN (1) | CN102630279A (ja) |
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JP2014043925A (ja) * | 2012-08-28 | 2014-03-13 | Daihatsu Motor Co Ltd | 油圧式無段変速機 |
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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 |
WO2023189943A1 (ja) * | 2022-03-31 | 2023-10-05 | 川崎重工業株式会社 | 回転斜板式液圧ポンプ |
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JP6080626B2 (ja) * | 2013-03-13 | 2017-02-15 | 川崎重工業株式会社 | アキシャルピストンモータ |
JP6252313B2 (ja) * | 2014-03-31 | 2017-12-27 | 株式会社Gsユアサ | 蓄電装置 |
EP3020966B1 (en) | 2014-11-11 | 2020-01-22 | Danfoss A/S | Axial piston machine |
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 |
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JPWO2012066593A1 (ja) | 2014-05-12 |
EP2642123A4 (en) | 2017-10-04 |
JP5444462B2 (ja) | 2014-03-19 |
US20130000481A1 (en) | 2013-01-03 |
KR20120083876A (ko) | 2012-07-26 |
EP2642123A1 (en) | 2013-09-25 |
KR101330768B1 (ko) | 2013-11-18 |
CN102630279A (zh) | 2012-08-08 |
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