WO2018088487A1 - シリンダブロックとそれを備えた斜板形液圧回転装置 - Google Patents
シリンダブロックとそれを備えた斜板形液圧回転装置 Download PDFInfo
- Publication number
- WO2018088487A1 WO2018088487A1 PCT/JP2017/040458 JP2017040458W WO2018088487A1 WO 2018088487 A1 WO2018088487 A1 WO 2018088487A1 JP 2017040458 W JP2017040458 W JP 2017040458W WO 2018088487 A1 WO2018088487 A1 WO 2018088487A1
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- Prior art keywords
- cylinder block
- cylinder
- cooling
- side end
- insertion side
- Prior art date
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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
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0639—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally 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
- 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
- F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
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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
- F01B3/0052—Cylinder barrel
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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
- 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
- F01B3/0076—Connection between cylinder barrel and inclined swash 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
- F01B31/00—Component parts, details, or accessories not provided for in, or of interest apart from, other groups
- F01B31/08—Cooling of steam engines; Heating; Heat insulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally 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
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0644—Component parts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0644—Component parts
- F03C1/0652—Cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0678—Control
- F03C1/0686—Control by changing the inclination of the swash plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
- F03C1/24—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders
- F03C1/2407—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders
- F03C1/2423—Reciprocating-piston liquid engines with movable cylinders or cylinder in which the liquid exclusively displaces one or more pistons reciprocating in rotary cylinders having cylinders in star or fan arrangement, the connection of the pistons with an actuated element being at the outer ends of the cylinders with two or more series radial piston-cylinder units
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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
- F04B1/2014—Details or component parts
- F04B1/2035—Cylinder barrels
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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
- 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
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash 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
- 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
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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
- 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
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
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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
- 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
- F04B53/18—Lubricating
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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 cylinder block in which pistons inserted into a plurality of cylinder bores formed around a rotating shaft are reciprocally slid in the cylinder bore, and a swash plate type hydraulic rotating device including the same. It is.
- a cylinder block of such a hydraulic device is formed with a plurality of cylinder bores into which pistons can be respectively inserted from openings on the end surface on the piston insertion side.
- the inserted pistons reciprocally slide in the cylinder bore. There is something to do.
- a swash plate type hydraulic device as in Patent Document 1 is known.
- the swash plate type hydraulic device of Patent Document 1 (hereinafter referred to as “swash plate type hydraulic rotating device”) includes a rotating shaft, and a cylinder block is integrally attached to the rotating shaft. Cylinder bores 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 bore. A shoe is attached to an end protruding from the cylinder bore, and this shoe is disposed on a support surface of a swash plate disposed in an inclined manner.
- the cylinder block is rotated by reciprocating the piston in the cylinder bore. Then, high pressure hydraulic oil is supplied to the cylinder bore and the piston is reciprocated to rotate the cylinder block, thereby rotating the rotating shaft integrally provided with the cylinder block. That is, the swash plate type hydraulic rotating device works as a hydraulic motor.
- the piston reciprocates in the cylinder bore by rotating the cylinder block. And by rotating a cylinder block with a rotating shaft, low pressure hydraulic fluid can be sucked and high pressure hydraulic fluid can be discharged. That is, the swash plate type hydraulic rotating device can be operated as a hydraulic pump.
- Patent Document 2 As another prior art, there is a hydraulic rotating machine provided with a detected recess for detection by an electromagnetic pickup type rotation sensor around a cylinder block (see Patent Document 2).
- the swash plate type hydraulic rotating device having the configuration as in Patent Document 1 was mainly used at low-speed and medium-speed rotation, but in order to cope with the high rotation in the drive device of construction machinery and industrial machinery, It is desired that the swash plate type hydraulic rotating device can be used even at high speed.
- the cylinder block of the swash plate type hydraulic rotating device is rotated at a high speed, the influence of the centrifugal force acting on the piston and the shoe increases, and unlike the low rotation, the influence of the centrifugal force cannot be ignored.
- the contact pressure corresponds to the pressure of hydraulic oil that is mainly supplied or discharged, so that the amount of heat generated on the sliding surface is relatively small. Therefore, a clearance for allowing 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 centrifugal force affects the contact pressure rather than the hydraulic pressure.
- the higher the rotation speed the greater the contact pressure and the amount of heat generated on the sliding surface.
- the temperature of the sliding surface rises, and in particular, it becomes difficult to cool with the hydraulic oil leaking from the clearance, so that the temperature rise near the opening of the cylinder bore becomes significant.
- the centrifugal force increases, the piston is pushed outward, so that the clearance width on the radially outer side becomes narrower than that on the radially inner side of the cylinder block. If it does so, it will become difficult to flow the hydraulic fluid in the outer clearance which became narrow, and hydraulic fluid will be heated in the part of the clearance.
- the portion of the cylinder block that is expected to have a cooling effect differs depending on the number of cylinder bores, the number of rotations, the application, etc. of the swash plate type hydraulic rotating device. It is rare.
- patent document 2 describes providing a recessed part around a cylinder block, this recessed part is only a function as a to-be-detected recessed part of a rotation sensor, and cannot cool a cylinder block.
- an object of the present invention is to provide a cylinder block capable of improving the cooling effect of the sliding surface in accordance with the number of cylinder bores, the number of rotations, and the like, and a swash plate type hydraulic rotating device including the cylinder block. .
- the cylinder block according to the present invention has a plurality of cylinder bores having openings on the piston insertion side end face, and when rotated, the pistons inserted into the cylinder bores reciprocally slide.
- the cylinder block includes a cooling portion, and the cooling portion includes a plurality of pistons extending in the axial direction of the cylinder block from the piston insertion side end surface formed between the adjacent cylinder bores. Has cooling holes.
- the surrounding coolant with a relatively low temperature in the cooling hole provided between the cylinder bores, which are the sliding surfaces of the piston that becomes high temperature of the cylinder block) ( Hydraulic fluid) is led.
- the coolant guided to the cooling hole takes the heat of the cylinder block and comes out of the cooling hole, and the cylinder block can be appropriately cooled with this coolant.
- the cooling performance of a cylinder block can be improved and the temperature rise of a sliding surface can be suppressed.
- the cooling hole extends from the piston insertion side end face where the cylinder bore is opened, the temperature rise can be particularly suppressed in the vicinity of the piston insertion side end face of the sliding surface where the temperature rises most markedly.
- cooling hole may be formed obliquely so as to penetrate from the end surface on the piston insertion side toward the outer peripheral surface of the cylinder block.
- the cooling hole includes a linear portion extending in parallel with the cylinder bore, and a through hole portion opened from the position away from the piston insertion side end surface of the linear portion toward the outer peripheral surface of the cylinder block, You may have.
- the cylinder block according to the present invention is a cylinder block in which a plurality of cylinder bores having openings on the piston insertion side end surface are formed, and the pistons inserted into the cylinder bores reciprocally slide when rotated.
- the cylinder block may include a cooling portion, and the cooling portion may have a plurality of cooling holes extending in a radial direction from between the cylinder bores adjacent to the outer peripheral surface of the cylinder block. .
- the surrounding coolant fluid (hydraulic fluid) having a relatively low temperature is introduced from the outer peripheral surface of the cylinder block to the cooling hole extending between the adjacent cylinder bores. It is burned.
- the coolant guided to the cooling hole takes the heat of the cylinder block and comes out of the cooling hole, and the cylinder block can be appropriately cooled by this coolant.
- the cylinder block according to the present invention is a cylinder block in which a plurality of cylinder bores having openings on the piston insertion side end surface are formed, and the pistons inserted into the cylinder bores reciprocally slide when rotated.
- the cylinder block may include a cooling portion, and the cooling portion may have a plurality of cooling holes extending in a radial direction from an outer peripheral surface of the cylinder block.
- the surrounding coolant (hydraulic fluid) having a relatively low temperature is guided to the cooling hole extending in the radial direction from the outer peripheral surface of the cylinder block.
- the coolant guided to the cooling hole takes the heat of the cylinder block and comes out of the cooling hole, and the cylinder block can be appropriately cooled by this coolant.
- the cylinder bore may include an insert bush, and the cooling hole may be formed from an outer peripheral surface of the cylinder block to an outer surface position of the insert bush.
- the coolant can be guided to the position of the insert bush of the cylinder bore, and the position close to the cylinder bore that becomes high temperature can be appropriately cooled.
- the cylinder block according to the present invention is a cylinder block in which a plurality of cylinder bores having openings on the piston insertion side end surface are formed, and the pistons inserted into the cylinder bores reciprocally slide when rotated.
- the cylinder block includes a cooling portion, and the cooling portion includes an annular notch formed at an edge of the piston insertion side end surface of the cylinder block, and the cylinder block from the annular notch. And a plurality of cooling grooves formed on the outer peripheral surface of the cylinder block so as to extend in the axial direction.
- the surrounding coolant having a relatively low temperature (hydraulic oil) is inserted into the piston by the annular notch formed in the edge of the piston insertion side end surface of the cylinder block.
- the cylinder block is guided by guiding the coolant from the notch to a plurality of cooling grooves formed on the outer periphery of the cylinder block, and taking the heat of the cylinder block with this coolant. Can be cooled properly.
- the cylinder block according to the present invention is a cylinder block in which a plurality of cylinder bores having openings on the piston insertion side end surface are formed, and the pistons inserted into the cylinder bores reciprocally slide when rotated.
- the cylinder block includes a cooling unit, and the cooling unit is positioned between adjacent cylinder bores and extends from the piston insertion side end surface in the axial direction of the cylinder block. A plurality of cooling grooves formed on the surface.
- the surrounding coolant (hydraulic fluid) having a relatively low temperature is introduced to the cooling groove extending in the axial direction of the cylinder block from the piston insertion side end surface of the cylinder block. It is burned.
- the coolant guided to the cooling groove takes the heat of the cylinder block and goes out of the cooling groove, and the cylinder block can be appropriately cooled by this coolant.
- the swash plate type hydraulic rotating device is connected to a low-pressure side passage through which a low-pressure hydraulic fluid flows and a high-pressure side passage through which a high-pressure hydraulic fluid flows, and the hydraulic fluid passes through the high-pressure side passage.
- the cylinder block is rotated by being supplied to the cylinder bore and discharged from the cylinder bore to the low pressure side passage, or the hydraulic fluid is sucked into the cylinder bore from the low pressure side passage by rotating the cylinder block, and further compressed.
- a swash plate type hydraulic rotating device that discharges to the high-pressure side passage after that, and includes any one of the cylinder blocks.
- a clearance is provided between the sliding surface of the cylinder bore and the outer peripheral surface of the piston, and in the swash plate type hydraulic rotating device that uses hydraulic oil leaking from the clearance as lubricating oil, the piston of the cylinder block Temperature rise on the sliding surface can be suppressed. Therefore, an increase in the oil temperature of the lubricating oil leaking from the clearance can be suppressed, and the lubricating oil can be prevented from transferring. Thereby, the fall of the lubricating performance of lubricating oil can be prevented and it can maintain moving a piston smoothly.
- the cooling effect of the cylinder block can be appropriately improved according to conditions such as the number of cylinder bores, the number of revolutions, and the application. It becomes possible.
- FIG. 1 is a cross-sectional view showing a swash plate type hydraulic rotating device including a cylinder block according to a first embodiment of the present invention.
- FIG. 2 is a drawing showing only the cylinder block according to the first embodiment shown in FIG. 1, wherein (A) is a perspective view, (B) is a sectional view, and (C) is a schematic diagram showing the flow of hydraulic oil. is there.
- 3 is a drawing showing only a cylinder block according to a second embodiment of the swash plate type hydraulic rotating device shown in FIG. 1, wherein (A) is a perspective view and (B) is a sectional view.
- FIG. 4 is a drawing showing only a cylinder block according to a third embodiment of the swash plate type hydraulic rotating device shown in FIG.
- FIG. 1 is a drawing showing only a cylinder block according to a fourth embodiment of the swash plate type hydraulic rotating device shown in FIG. 1, wherein (A) is a perspective view and (B) is a sectional view.
- 6 is a drawing showing only a cylinder block according to a fifth embodiment of the swash plate type hydraulic rotating device shown in FIG. 1, wherein (A) is a perspective view and (B) is a sectional view.
- FIG. 7 is a drawing showing only a cylinder block according to a sixth embodiment of the swash plate type hydraulic rotating device shown in FIG. 1, wherein (A) is a perspective view and (B) is a sectional view.
- FIG. 1 is a drawing showing only a cylinder block according to a sixth embodiment of the swash plate type hydraulic rotating device shown in FIG. 1, wherein (A) is a perspective view and (B) is a sectional view.
- FIG. 8 is a drawing showing only the cylinder block according to the seventh embodiment of the swash plate type hydraulic rotating device shown in FIG. 1, wherein (A) is a perspective view and (B) is a cross-sectional view.
- FIG. 9 is a drawing showing only the cylinder block according to the eighth embodiment in the swash plate type hydraulic rotating device shown in FIG. 1, wherein (A) is a perspective view and (B) is a sectional view.
- FIG. 10 is a drawing showing only the cylinder block according to the ninth embodiment in the swash plate type hydraulic rotating device shown in FIG. 1, wherein (A) is a perspective view and (B) is a sectional view.
- cylinder blocks 12A to 12I in the swash plate type hydraulic rotating device 1 will be described as an example.
- the left direction shown in FIG. 1 will be described as “front direction” and the right direction will be described as “rear direction”.
- FIG. 1 is a cross-sectional view showing a swash plate type hydraulic rotating device 1 including a cylinder block 12A according to the first embodiment.
- a swash plate type hydraulic rotating device 1 is provided.
- the swash plate type hydraulic rotating device 1 is a so-called swash plate type motor / pump. It has the function of a hydraulic pump that supplies and moves the actuator.
- the working fluid to be handled is assumed to be hydraulic oil
- the swash plate type hydraulic rotating device 1 is assumed to be a hydraulic motor 10.
- the hydraulic motor (swash plate type hydraulic rotating device 1) 10 includes a rotating shaft 11 and is a high-speed rotating type hydraulic motor that can rotate the rotating shaft 11 at a high speed.
- the hydraulic motor 10 also includes a cylinder block 12A, 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 ⁇ / b> A is inserted into an intermediate portion of the rotating shaft 11.
- the cylinder block 12A is generally formed in a cylindrical shape.
- the axis of the cylinder block 12A coincides with the axis L1 of the rotary shaft 11.
- the cylinder block 12 ⁇ / b> A is integrally coupled to the rotating shaft 11 by spline coupling, and rotates integrally with the rotating shaft 11.
- a plurality of cylinder bores 20 are formed in the cylinder block 12A.
- the cylinder bores 20 are arranged at equal intervals in the circumferential direction of the cylinder block 12A around the axis L1 (FIG. 2), and extend parallel to the axis L1.
- the cylinder bore 20 is a hole defined by a sliding surface having a circular cross section and a bottom surface, and has an opening on the piston insertion side end surface 12c (front side end surface) of the cylinder block 12A.
- the pistons 13 are inserted into the cylinder bores 20 through the openings.
- the piston 13 has a substantially cylindrical shape, and reciprocates in the front-rear direction while sliding on the sliding surface 12b that defines the cylinder bore 20.
- the cylinder bore 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 sleeve is not fitted will be described, but the same applies to the case where the sleeve is fitted.
- the outer diameter of the piston 13 is slightly smaller than the inner diameter of the cylinder bore 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 bore 20 regardless of the position of the piston 13.
- the outer surface of the spherical holding portion 13a is formed in a substantially spherical shape, and a shoe 14 is attached to the spherical holding portion 13a.
- 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 rotary shaft 11 penetrates the vicinity of the center thereof.
- the swash plate 15 is disposed in front of the cylinder block 12A and has a support plate 21 on the cylinder block 12A side.
- the support plate 21 has an annular shape, and a plurality of shoes 14 are arranged on the support plate 21 at equal intervals in the circumferential direction. Further, the plurality of shoes 14 are provided with a presser plate 22 for pressing these shoes 14 against the support plate 21.
- the presser plate 22 has a generally annular shape, and the rotation shaft 11 is inserted through the center of the presser 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 12A.
- the spherical bush 23 is urged toward the support plate 21 by a plurality of pressing springs 27 provided in the cylinder block 12 ⁇ / b> A, 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 bore 20 can be changed.
- the oil chamber 20 a is a space behind the rear end surface of the piston 13 in the cylinder bore 20.
- a cylinder port 26 communicating with the oil chamber 20a is formed in the cylinder block 12A.
- One cylinder port 26 is provided for each cylinder bore 20 and corresponds to the cylinder bore 20 on a one-to-one basis.
- the cylinder port 26 opens at the rear end face of the cylinder block 12A, and the valve plate 16 is provided on the rear end face.
- the valve plate 16 is an annular plate-like member, and is located between the cylinder block 12A 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 12A side is connected to several cylinder ports 26.
- the connection destination of the cylinder port 26 is alternately switched between the suction port 16a and the discharge port 16b.
- the opening of the suction port 16a is connected to a high-pressure side passage (not shown), and the opening of the discharge port 16b is connected to a low-pressure side passage (not shown).
- the cylinder bore 12 is alternately connected to the high-pressure side passage and the low-pressure side passage by rotating the cylinder block 12A.
- 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 piston 13 is most retracted to the cylinder bore 20 and moves from the top dead center located at the innermost part to the bottom dead center where the piston 13 protrudes most from the cylinder bore 20.
- the hydraulic oil flowing through the high-pressure side passage 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 downward on the swash plate 15 and revolves around the axis L1 in one circumferential direction.
- a rotational force about the axis L1 is applied to the cylinder block 12A, and the cylinder block 12A and the rotary shaft 11 rotate about the axis L1.
- the piston 13 when the piston 13 is located between the bottom dead center and the top dead center, the oil chamber 20a is connected to the low pressure side passage through the discharge port 16b.
- the cylinder block 12A rotates, the shoe 14 slides upward on the swash plate 15, 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 through the discharge port 16b.
- the piston 13 in the hydraulic motor 10, the piston 13 is reciprocated in the front-rear direction by sucking and discharging the hydraulic oil, and the cylinder block 12A and the rotating shaft 11 are rotated about the axis L1.
- the swash plate type hydraulic rotating device 1 When the swash plate type hydraulic rotating device 1 is a hydraulic pump, the hydraulic oil is sucked into the cylinder bore 20 from the low pressure side passage by rotating the cylinder block 12A, and the hydraulic oil compressed in the cylinder bore 20 is discharged. It is discharged into the high-pressure side passage.
- the cylinder block 12A is provided with a structure for cooling the cylinder block 12A.
- the illustrated cylinder block 12 ⁇ / b> A according to the first embodiment has a plurality of cooling holes 51 as the cooling unit 50.
- the cooling unit 50 includes a cooling groove 55 as shown in FIGS. 8 to 10 described later, in addition to the cooling hole 51.
- an embodiment of a cylinder block including the cooling unit 50 will be described.
- the axis of the cylinder block 12A will be described as the axis L1. Further, the same components in each embodiment will be described with the same reference numerals.
- (Cylinder block according to the first embodiment) 2 is a drawing showing only the cylinder block 12A according to the first embodiment shown in FIG. 1, wherein (A) is a perspective view, (B) is a sectional view, and (C) is a schematic diagram showing the flow of hydraulic oil. It is.
- the cylinder block 12 ⁇ / b> A has a cooling hole 51 as the cooling unit 50.
- the section of the cooling hole 51 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- a cooling hole 51 extending in the direction of the axis L1 from the piston insertion side end surface 12c is provided at a position close to the outer peripheral surface 12a between the adjacent cylinder bores 20.
- the cooling hole 51 of this embodiment is provided between adjacent cylinder bores 20 at a position closer to the outer peripheral surface 12a of the cylinder block 12A than the center of the cylinder bore 20.
- the axial depth H1 of the cooling hole 51 is formed in the range of the depth H2 from the piston insertion side end face 12c to the deepest position where the piston 13 enters the cylinder bore 20. That is, the cooling hole 51 is in a range from the piston insertion side end surface 12c to the position of the innermost part (the innermost part of the piston 13 when the piston 13 is located at the top dead center) where the piston 13 enters the cylinder bore 20. It is formed.
- the axial depth H1 in this embodiment is formed in a range of about 1 ⁇ 2 from the piston insertion end face 12c in the range of the position H2 from the piston insertion end face 12c to the innermost part where the piston 13 enters the cylinder bore 20. Has been.
- the diameter D of the cooling hole 51 can be formed in a range of 5% to 100% with respect to the diameter of the piston 13.
- the cooling hole 51 capable of appropriately cooling the cylinder block 12A can be formed under various conditions. it can.
- the diameter D of the cooling hole 51 is such that the hydraulic oil entering the cooling hole 51 from the piston insertion side end face 12c moves inside the cooling hole 51 to cool the cylinder block 12A, and from the piston insertion side end face 12c. It is set to the size that comes out.
- the cooling hole 51 may have a diameter D of about 3 mm to 10 mm.
- the cylinder block 12A of this embodiment is rotated so that the cylinder block 12A is provided at a position close to the sliding surface 12b of the piston 13 that becomes a high temperature of the cylinder block 12A.
- the surrounding hydraulic oil O having a relatively low temperature is introduced into the cooling hole 51.
- the hydraulic oil O that has caused the flow of the hydraulic oil O inside the cooling hole 51 to take the temperature of the cylinder block 12A out of the cooling hole 51 allows the cylinder block 12A to be appropriately used. Can be cooled.
- the cooling performance of the cylinder block 12A can be improved and the temperature rise of the sliding surface 12b can be suppressed.
- the cooling hole 51 extends from the piston insertion side end surface 12c having the opening of the cylinder bore 20, the temperature rise is particularly suppressed in the vicinity of the piston insertion side end surface 12c of the sliding surface 12b where the temperature rises most markedly. Can do.
- FIG. 3 is a drawing showing only the cylinder block 12B according to the second embodiment of the hydraulic motor (swash plate type hydraulic rotating device 1).
- FIG. 3A is a perspective view and
- FIG. 3B is a sectional view.
- the cylinder block 12 ⁇ / b> B has a cooling hole 51 as the cooling unit 50.
- the section of the cooling hole 51 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- a cooling hole 51 extending from the piston insertion side end face 12c in the direction of the axis L1 of the cylinder block 12B is provided radially outward between the adjacent cylinder bores 20.
- two cooling holes 51 are provided on the outer sides between the adjacent cylinder bores 20 at positions close to the outer peripheral surface 12a of the cylinder block 12B.
- the cooling hole 51 provided at a position close to the sliding surface 12b of the piston 13 at a high temperature of the cylinder block 12B has a relatively low temperature.
- the hydraulic oil can be guided to cool the cylinder block 12B appropriately.
- the cooling performance of the cylinder block 12B can be improved, and the temperature rise of the sliding surface 12b can be suppressed.
- the position closer to the cylinder bore 20 can be cooled compared to the cylinder block 12A of the first embodiment.
- FIG. 4 is a drawing showing only the cylinder block 12C according to the third embodiment of the hydraulic motor (swash plate type hydraulic rotating device 1), wherein (A) is a perspective view and (B) is a sectional view. .
- the cylinder block 12 ⁇ / b> C has a cooling hole 51 as the cooling unit 50.
- the section of the cooling hole 51 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- a cooling hole 51 extending in the direction of the axis L1 from the piston insertion side end surface 12c is provided at a position close to the outer peripheral surface 12a between the adjacent cylinder bores 20.
- the cooling hole 51 of this embodiment is a hole inclined so as to penetrate from the piston insertion side end face 12c toward the outer peripheral face 12a of the cylinder block 12C.
- the cooling hole 51 provided at a position close to the sliding surface 12b of the piston 13 at a high temperature of the cylinder block 12C has a relatively low temperature.
- the hydraulic oil can be guided to properly cool the cylinder block 12C.
- the cooling performance of the cylinder block 12C can be improved, and the temperature rise of the sliding surface 12b can be suppressed.
- the hydraulic oil that has entered the cooling hole 51 from the piston insertion side end face 12c can be discharged to the outer peripheral face 12a of the cylinder block 12C by centrifugal force generated by the rotation of the cylinder block 12C. Therefore, a forced flow is generated in the hydraulic oil in the cooling hole 51, and the cooling effect can be enhanced.
- FIG. 5 is a drawing showing only the cylinder block 12D according to the fourth embodiment of the hydraulic motor (swash plate type hydraulic rotating device 1), wherein (A) is a perspective view and (B) is a sectional view. .
- the cylinder block 12 ⁇ / b> D has a cooling hole 51 as the cooling unit 50.
- the section of the cooling hole 51 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- the cylinder block 12D of this embodiment is provided with a cooling hole 51 extending from the piston insertion side end surface 12c in the direction of the axis L1 at a position close to the outer peripheral surface 12a between adjacent cylinder bores 20.
- the cooling hole 51 has a straight portion extending in parallel with the cylinder bore 20 and a hole that opens from the deep portion of the straight portion away from the piston insertion side end surface 12c toward the outer peripheral surface 12a of the cylinder block 12D. And a hole 52.
- the cooling hole 51 provided at a position close to the sliding surface 12b of the piston 13 at a high temperature of the cylinder block 12D has a relatively low temperature.
- the hydraulic oil can be guided to cool the cylinder block 12D appropriately. Thereby, the cooling performance of cylinder block 12D can be improved and the temperature rise of the sliding face 12b can be suppressed.
- the hydraulic oil that has entered the cooling hole 51 from the piston insertion side end face 12c can be discharged from the punched hole 52 to the outer peripheral face 12a of the cylinder block 12D by centrifugal force generated by the rotation of the cylinder block 12D. Therefore, a forced flow is generated in the hydraulic oil in the cooling hole 51, and the cooling effect can be enhanced.
- FIG. 6 is a drawing showing only the cylinder block 12E according to the fifth embodiment of the hydraulic motor (swash plate type hydraulic rotating device 1), wherein (A) is a perspective view and (B) is a sectional view. .
- the cylinder block 12 ⁇ / b> E has a cooling hole 51 as the cooling unit 50.
- the section of the cooling hole 51 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- a plurality of cooling holes 51 are provided in the radial direction perpendicular to the axis L1 of the cylinder block 12E from the outer peripheral surface 12a of the cylinder block 12E.
- the cooling hole 51 is provided between the adjacent cylinder bores 20 with a radial depth H3 extending from the outer peripheral surface 12a to the cylinder bore 20 to a position at a predetermined distance from the axis L1 of the cylinder block 12E.
- the radial depth H3 at which the cooling hole 51 is provided can be a depth at which a predetermined distance from the axis L1 to a position closest to the axis L1 of the cylinder bore 20 remains.
- cooling hole 51 is further provided at a position where cooling is desired in the direction of the axis L1.
- the number of the cooling holes 51 is not limited to the example illustrated.
- the position close to the sliding surface 12b of the piston 13 at a high temperature of the cylinder block 12E is set as the cooling hole 51 by the cooling hole 51 extending between the adjacent cylinder bores 20. It can be properly cooled with the guided relatively low temperature hydraulic fluid. Thereby, the cooling performance of the cylinder block 12E can be improved and the temperature rise of the sliding face 12b can be suppressed.
- FIG. 7 is a drawing showing only the cylinder block 12F according to the sixth embodiment of the hydraulic motor (swash plate type hydraulic rotating device 1), wherein (A) is a perspective view and (B) is a sectional view. .
- the cylinder block 12 ⁇ / b> F has a cooling hole 51 as the cooling unit 50.
- the section of the cooling hole 51 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- the cylinder block 12F of this embodiment is provided with a cooling hole 51 extending radially from the outer peripheral surface 12a toward the outer periphery of the cylinder bore 20.
- the cooling hole 51 is provided with a radial depth H4 extending in a radial direction from the outer peripheral surface 12a of the cylinder block 12F to a position a predetermined distance from the outer periphery of the cylinder bore 20.
- the radial depth H4 of the cooling hole 51 can be, for example, a depth to the outer surface position of the insert bush when an insert bush (not shown) is provided.
- the cooling hole 51 may be provided up to a position near the cylinder bore 20.
- the position close to the sliding surface 12b of the piston 13 at a high temperature of the cylinder block 12F can be appropriately cooled with hydraulic oil having a relatively low temperature led to the cooling hole 51.
- the cooling performance of the cylinder block 12F can be improved and the temperature rise of the sliding face 12b can be suppressed.
- the cooling effect can be enhanced by further providing a cooling hole 51 in the direction of the axis L1 of the cylinder block 12F.
- the number of the cooling holes 51 is not limited to the example shown in the figure, and the cooling holes 51 may be further provided at positions where cooling is desired in the direction of the axis L1.
- FIG. 8 is a drawing showing only the cylinder block 12G according to the seventh embodiment of the hydraulic motor (swash plate type hydraulic rotating device 1), (A) is a perspective view, and (B) is a sectional view. .
- the cylinder block 12 ⁇ / b> G has a cooling groove 55 as the cooling unit 50.
- the section of the cooling groove 55 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- annular notch 56 is provided in the circumferential direction of the edge of the piston insertion side end face 12c of the cylinder block 12G.
- the notch 56 is formed by scraping the corner of the outer peripheral surface 12a in the piston insertion side end surface 12c of the cylinder block 12G into an annular shape.
- channel 55 is provided in the outer peripheral surface 12a of the cylinder block 12G so that it may extend in the direction of the axis line L1 of the cylinder block 12G from this notch part 56.
- An annular notch 56 is provided at the corner of the outer peripheral surface 12a of the cylinder block 12G, and the cooling groove 55 extends from the notch 56, so that the hydraulic oil is cooled from the notch 56. It can flow smoothly into the groove 55.
- the axial depth H1 of the cooling groove 55 is from the piston insertion side end surface 12c to the position of the innermost part where the piston 13 enters the cylinder bore 20 (the innermost part of the piston 13 when the piston 13 is located at the top dead center). Formed in a range of the depth H2.
- the axial depth H1 in this embodiment is about 1 ⁇ 2 from the piston insertion side end surface 12c in the range of the depth H2 from the piston insertion side end surface 12c to the position of the innermost part where the piston 13 enters the cylinder bore 20. Formed in the range.
- the width dimension W of the cooling groove 55 can be formed in a range of 2% to 100% with respect to the diameter of the piston 13.
- the cooling grooves 55 of this embodiment are provided at equal intervals in the circumferential direction on the outer peripheral surface 12a of the cylinder block 12G.
- an uneven surface is formed on the outer peripheral surface 12a of the cylinder block 12G.
- the concave cooling groove 55 and the convex outer peripheral surface 12a therebetween are formed at equal intervals.
- the outer peripheral surface 12a of the cylinder block 12G can be appropriately cooled with hydraulic oil having a relatively low temperature led to the cooling groove 55. Thereby, the cooling performance of the cylinder block 12G can be improved, and the temperature rise of the sliding surface 12b can be suppressed.
- the concave and convex surface formed by the concave cooling groove 55 and the convex outer peripheral surface 12a can also be provided with a function as a detection unit of a rotation sensor (not shown).
- a rotation sensor not shown.
- FIG. 9 is a drawing showing only a cylinder block 12H according to an eighth embodiment of the hydraulic motor (swash plate type hydraulic rotating device 1), wherein (A) is a perspective view and (B) is a sectional view. .
- the cylinder block 12 ⁇ / b> H has a cooling groove 55 as the cooling unit 50.
- the section of the cooling groove 55 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- the cylinder block 12H of this embodiment is provided with a notch 56 that is recessed from the outer peripheral surface 12a in the circumferential direction of the edge of the piston insertion side end surface 12c of the cylinder block 12H, as in FIG.
- a plurality of cooling grooves 55 extending in the axial direction of the cylinder block 12H from the notches 56 are provided.
- the cooling groove 55 of this embodiment is provided radially outward of the cylinder bore 20 so as to extend from the notch portion 56 in the direction of the axis L1 of the cylinder block 12H.
- the cooling groove 55 can also be provided in a range from the piston insertion side end surface 12 c to the position of the innermost part where the piston 13 enters the cylinder bore 20.
- the notch 56 is not necessarily provided.
- the hydraulic oil having a relatively low temperature is introduced into the cooling groove 55 provided on the outer peripheral surface 12a of the cylinder block 12H so that the cylinder block 12H is appropriately Can be cooled.
- the cooling performance of the cylinder block 12H can be improved, and the temperature rise of the sliding surface 12b can be suppressed.
- FIG. 10 is a drawing showing only the cylinder block 12I according to the ninth embodiment in the hydraulic motor (swash plate type hydraulic rotating device 1) 10, (A) is a perspective view, and (B) is a sectional view. .
- the cylinder block 12I has a cooling groove 55 as the cooling unit 50. In the sectional view of (B), the section of the cooling groove 55 is shown at the top, and the section of the cylinder bore 20 is shown at the bottom.
- the cylinder block 12I of this embodiment is provided with a plurality of cooling grooves 55 extending from the piston insertion side end face 12c in the direction of the axis L1 of the cylinder block 12I.
- the cooling groove 55 of this embodiment passes between the cylinder bores 20 between the adjacent cylinder bores 20, and extends from the axis L1 of the cylinder block 12I to a position at a predetermined distance.
- the radial depth is H3.
- the radial depth H3 at which the cooling groove 55 is provided can be a depth at which a predetermined distance from the axis L1 to a position closest to the axis L1 of the cylinder bore 20 remains.
- the cooling groove 55 is formed on the outer peripheral surface 12a of the cylinder block 12I so as to extend from the piston insertion side end surface 12c in the direction of the axis L1. Further, the cooling groove 55 of this embodiment is formed in an arc shape that curves from the piston insertion side end surface 12c toward the outer peripheral surface 12a of the cylinder block 12I.
- the axial depth H1 of the cooling groove 55 is formed in the range of the depth H2 from the piston insertion side end face 12c to the position of the innermost part where the piston 13 enters the cylinder bore 20. Note that, as in the eighth embodiment, a notch 56 may be provided.
- the temperature is relatively low at a position close to the sliding surface 12b of the piston 13 where the temperature of the cylinder block 12I becomes high due to the cooling groove 55 provided between the adjacent cylinder bores 20.
- the hydraulic oil can be guided to properly cool the cylinder block 12I.
- the cooling performance of the cylinder block 12I can be improved and the temperature rise of the sliding surface 12b can be suppressed.
- the cooling hydraulic oil 55 can be discharged from the piston insertion side end surface 12c toward the outer peripheral surface 12a of the cylinder block 12I by the arc-shaped cooling groove 55. Therefore, a forced flow is generated in the hydraulic oil in the cooling groove 55, and the cooling effect can be enhanced.
- the cylinder blocks 12A to 12I are suitable according to the specifications such as the number of cylinder bores 20 and the number of rotations of the hydraulic motor (swash plate type hydraulic rotating device 1) 10 and other conditions such as applications. Also, cylinder blocks 12A to 12I can be employed. As a result, appropriate cooling according to the cylinder blocks 12A to 12I becomes possible. Further, by appropriately cooling the cylinder blocks 12A to 12I, it is possible to prevent the temperature of the hydraulic oil from rising and prevent the lubricating performance of the hydraulic oil from deteriorating. Therefore, the swash plate type hydraulic rotating device 1 and the like can be stably operated in a planned manner.
- the hydraulic motor 10 has been described as an example of the swash plate-type hydraulic rotating device 1.
- the hydraulic motor 10 can be used for other hydraulic devices such as a hydraulic pump.
- the present invention is not limited to the embodiment.
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Abstract
Description
図1は、第1実施形態に係るシリンダブロック12Aを備えた斜板形液圧回転装置1を示す断面図である。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回転装置1が設けられている。斜板形液圧回転装置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、扱う作動液を作動油とし、斜板形液圧回転装置1を油圧モータ10として説明する。
図2は、図1に示す第1実施形態に係るシリンダブロック12Aのみを示す図面であり、(A)は斜視図、(B)は断面図、(C)は作動油の流れを示す模式図である。このシリンダブロック12Aは、冷却部50としての冷却用穴51を有している。(B)の断面図は、冷却用穴51の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
図3は、上記油圧モータ(斜板形液圧回転装置1)10における第2実施形態に係るシリンダブロック12Bのみを示す図面であり、(A)は斜視図、(B)は断面図である。このシリンダブロック12Bは、冷却部50として冷却用穴51を有している。(B)の断面図は、冷却用穴51の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
図4は、上記油圧モータ(斜板形液圧回転装置1)10における第3実施形態に係るシリンダブロック12Cのみを示す図面であり、(A)は斜視図、(B)は断面図である。このシリンダブロック12Cは、冷却部50として冷却用穴51を有している。(B)の断面図は、冷却用穴51の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
図5は、上記油圧モータ(斜板形液圧回転装置1)10における第4実施形態に係るシリンダブロック12Dのみを示す図面であり、(A)は斜視図、(B)は断面図である。このシリンダブロック12Dは、冷却部50として冷却用穴51を有している。(B)の断面図は、冷却用穴51の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
図6は、上記油圧モータ(斜板形液圧回転装置1)10における第5実施形態に係るシリンダブロック12Eのみを示す図面であり、(A)は斜視図、(B)は断面図である。このシリンダブロック12Eは、冷却部50として冷却用穴51を有している。(B)の断面図は、冷却用穴51の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
図7は、上記油圧モータ(斜板形液圧回転装置1)10における第6実施形態に係るシリンダブロック12Fのみを示す図面であり、(A)は斜視図、(B)は断面図である。このシリンダブロック12Fは、冷却部50として冷却用穴51を有している。(B)の断面図は、冷却用穴51の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
図8は、上記油圧モータ(斜板形液圧回転装置1)10における第7実施形態に係るシリンダブロック12Gのみを示す図面であり、(A)は斜視図、(B)は断面図である。このシリンダブロック12Gは、冷却部50として冷却用溝55を有している。(B)の断面図は、冷却用溝55の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
図9は、上記油圧モータ(斜板形液圧回転装置1)10における第8実施形態に係るシリンダブロック12Hのみを示す図面であり、(A)は斜視図、(B)は断面図である。このシリンダブロック12Hは、冷却部50として冷却用溝55を有している。(B)の断面図は、冷却用溝55の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
図10は、上記油圧モータ(斜板形液圧回転装置1)10における第9実施形態に係るシリンダブロック12Iのみを示す図面であり、(A)は斜視図、(B)は断面図である。このシリンダブロック12Iは、冷却部50として冷却用溝55を有している。(B)の断面図は、冷却用溝55の部分の断面を上部に示し、シリンダボア20の部分の断面を下部に示している。
以上のように、上記シリンダブロック12A~12Iによれば、油圧モータ(斜板形液圧回転装置1)10のシリンダボア20の数や回転数などの仕様、その他、用途などの条件に応じて適したシリンダブロック12A~12Iを採用することができる。これにより、シリンダブロック12A~12Iに応じた適切な冷却が可能となる。そして、シリンダブロック12A~12Iを適切に冷却することで、作動油の温度上昇を抑えて作動油の潤滑性能が低下することを防止することが可能となる。よって、斜板形液圧回転装置1などを計画的に安定して運用することが可能となる。
10 油圧モータ
12A~12I シリンダブロック
12a 外周面
12b 摺動面
12c ピストン挿入側端面
13 ピストン
17 ケーシング
20 シリンダボア
50 冷却部
51 冷却用穴
52 抜き穴部
55 冷却用溝
56 切欠き部
L1 軸線
D 直径
H1、H2 軸線方向深さ
H3、H4 半径方向深さ
Claims (9)
- ピストン挿入側端面に開口を有する複数のシリンダボアが形成され、回転させると前記シリンダボアにそれぞれ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は冷却部を備え、
前記冷却部は、隣り合う前記シリンダボアの間に形成された前記ピストン挿入側端面から前記シリンダブロックの軸線方向に延在する複数の冷却用穴を有する、
ことを特徴とするシリンダブロック。 - 前記冷却用穴は、前記ピストン挿入側端面から前記シリンダブロックの外周面に向けて貫通するよう斜めに形成されている、
請求項1に記載のシリンダブロック。 - 前記冷却用穴は、前記シリンダボアと平行に延在する直線部と、前記直線部の前記ピストン挿入側端面から離れた位置から前記シリンダブロックの外周面に向けて開放する抜き穴部と、を有している、
請求項1に記載のシリンダブロック。 - ピストン挿入側端面に開口を有する複数のシリンダボアが形成され、回転させると前記シリンダボアにそれぞれ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は冷却部を備え、
前記冷却部は、前記シリンダブロックの外周面から隣り合う前記シリンダボアの間を通って半径方向に延在する複数の冷却用穴を有している、
ことを特徴とするシリンダブロック。 - ピストン挿入側端面に開口を有する複数のシリンダボアが形成され、回転させると前記シリンダボアにそれぞれ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は冷却部を備え、
前記冷却部は、前記シリンダブロックの外周面から半径方向に延在する複数の冷却用穴を有している、
ことを特徴とするシリンダブロック。 - 前記シリンダボアはインサートブッシュを備え、
前記冷却用穴は、前記シリンダブロックの外周面から前記インサートブッシュの外面位置まで形成されている、
請求項5に記載のシリンダブロック。 - ピストン挿入側端面に開口を有する複数のシリンダボアが形成され、回転させると前記シリンダボアにそれぞれ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は冷却部を備え、
前記冷却部は、前記シリンダブロックの前記ピストン挿入側端面の縁部に形成された環状の切欠き部と、前記環状の切欠き部から前記シリンダブロックの軸線方向に延在するように前記シリンダブロックの外周面に形成された複数の冷却用溝と、を有している、
ことを特徴とするシリンダブロック。 - ピストン挿入側端面に開口を有する複数のシリンダボアが形成され、回転させると前記シリンダボアにそれぞれ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は冷却部を備え、
前記冷却部は、隣り合う前記シリンダボアの間に位置し、且つ、前記ピストン挿入側端面から前記シリンダブロックの軸線方向に延在するように前記シリンダブロックの外周面に形成された複数の冷却用溝と、を有している、
ことを特徴とするシリンダブロック。 - 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ボアに供給されて前記シリンダボア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ボアに前記作動液を吸入し、さらに圧縮してから前記高圧側通路へと吐出する斜板形液圧回転装置であって、
請求項1~8のいずれか1項に記載される前記シリンダブロックを備えている、斜板形液圧回転装置。
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CN201780066380.0A CN109891093B (zh) | 2016-11-10 | 2017-11-09 | 缸体及具备该缸体的斜板型液压旋转装置 |
US16/349,021 US10794185B2 (en) | 2016-11-10 | 2017-11-09 | Cylinder block and swash plate type liquid-pressure rotating apparatus including same |
KR1020197014432A KR102345509B1 (ko) | 2016-11-10 | 2017-11-09 | 실린더 블록 및 그를 구비한 사판형 액압 회전 장치 |
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