US20150064030A1 - Fluid pressure drive unit - Google Patents

Fluid pressure drive unit Download PDF

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Publication number
US20150064030A1
US20150064030A1 US14/389,319 US201314389319A US2015064030A1 US 20150064030 A1 US20150064030 A1 US 20150064030A1 US 201314389319 A US201314389319 A US 201314389319A US 2015064030 A1 US2015064030 A1 US 2015064030A1
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United States
Prior art keywords
fluid pressure
electric motor
rotation shaft
motor
gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/389,319
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English (en)
Inventor
Kazunari Suzuki
Shinji Yakabe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KYB Corp
Original Assignee
Kayaba Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kayaba Industry Co Ltd filed Critical Kayaba Industry Co Ltd
Assigned to KAYABA INDUSTRY CO., LTD. reassignment KAYABA INDUSTRY CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SUZUKI, KAZUNARI, YAKABE, SHINJI
Publication of US20150064030A1 publication Critical patent/US20150064030A1/en
Assigned to KYB CORPORATION reassignment KYB CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: KAYABA INDUSTRY CO., LTD.
Abandoned legal-status Critical Current

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Classifications

    • 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
    • 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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/128—Driving means
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • 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
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • 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 fluid pressure drive unit for adapted to supply a working fluid to and driving a fluid pressure actuator.
  • a hybrid structure in which a power generator is rotated by an extra output of an engine and emission energy of an actuator, electric power generated by the power generator is stored, and actuation of the actuator is assisted by using the stored electric power is used.
  • a fluid pressure drive unit including an electric motor to be rotated with the stored electric power, and an assist pump to be driven and rotated by the electric motor, the assist pump for discharging a working fluid and assisting the actuation of the actuator by a main pump is used.
  • JP2011-127569A discloses an assist regeneration device including a motor generator to be actuated and rotated with electric energy, a regeneration motor for driving and rotating the motor generator with energy of a working fluid, and an assist pump to be driven and rotated by the motor generator, the assist pump for discharging the working fluid.
  • the present invention is achieved in consideration with the above problem, and an object thereof is to simplify a cooling mechanism of an electric motor in a hydraulic pressure drive unit.
  • a fluid pressure drive unit adapted to supply a working fluid to and driving a fluid pressure actuator.
  • the fluid pressure drive unit includes a fluid pressure pump that is configured to suction and discharge the working fluid, an electric motor that is configured to drive and rotate the fluid pressure pump, a power transmission mechanism that is configured to transmit a power between a rotation shaft of the fluid pressure pump and a rotation shaft of the electric motor, and a circulation mechanism that is configured to be driven by the power transmitted by the power transmission mechanism, the circulation mechanism that is configured to guide a lubricating fluid in the power transmission mechanism and cool the electric motor.
  • FIG. 1 is a front view showing a part of a fluid pressure drive unit according to an embodiment of the present invention in a sectional view.
  • FIG. 2 is a sectional view by line II-II of a fluid pressure pump motor in FIG. 1 .
  • FIG. 3 is a sectional view of a plate, a power transmission mechanism, and a circulation mechanism in FIG. 1 .
  • hydraulic drive unit 100 serving as a fluid pressure drive unit according to an embodiment of the present invention will be described.
  • working oil is used as a working fluid.
  • other fluids such as working water may be used as the working fluid.
  • the hydraulic drive unit 100 is to supply the working oil to and drive a hydraulic actuator (not shown) serving as a fluid pressure actuator.
  • the hydraulic drive unit 100 is applied to a hybrid construction machine such as a power shovel for driving the hydraulic actuator with the working oil discharged from a main hydraulic pump (not shown) which is driven by a prime mover.
  • the hydraulic drive unit 100 is provided with a hydraulic pump motor 1 serving as a fluid pressure pump motor which includes a hydraulic pump 10 serving as a fluid pressure pump for suctioning and discharging the working oil, and a hydraulic motor 20 serving as a fluid pressure motor to be driven and rotated with the supplied working oil.
  • a hydraulic pump motor 1 serving as a fluid pressure pump motor which includes a hydraulic pump 10 serving as a fluid pressure pump for suctioning and discharging the working oil, and a hydraulic motor 20 serving as a fluid pressure motor to be driven and rotated with the supplied working oil.
  • the hydraulic drive unit 100 is also provided with an electric motor 30 arranged in parallel to the hydraulic pump motor 1 , a plate 40 having an identical surface to which the hydraulic pump motor 1 and the electric motor 30 are attached, a power transmission mechanism 50 for transmitting a power between a rotation shaft 2 of the hydraulic pump motor 1 and a rotation shaft (not shown) of the electric motor 30 , and a circulation mechanism 60 for guiding lubricant oil serving as a lubricating fluid in the power transmission mechanism 50 and cooling the electric motor 30 .
  • the hydraulic pump 10 and the hydraulic motor 20 forming the hydraulic pump motor 1 are respectively swash-plate-type variable piston pump motors.
  • the hydraulic motor 20 is a piston pump motor of a larger scale than the hydraulic pump 10 .
  • the hydraulic pump motor 1 is provided with a casing 3 for accommodating the hydraulic pump 10 and the hydraulic motor 20 , and the single rotation shaft 2 rotatably and axially supported on the casing 3 and commonly used for the hydraulic pump 10 and the hydraulic motor 20 .
  • the casing 3 has a flange portion 3 a fastened to the plate 40 by bolts.
  • the casing 3 has a supply and emission passage 4 through which the working oil to be supplied to the hydraulic pump 10 flows and the working oil emitted from the hydraulic motor 20 flows, a discharge passage 5 through which the working oil discharged from the hydraulic pump 10 flows, and a return passage 6 through which the working oil returned from the hydraulic actuator, to be supplied to the hydraulic motor 20 flows.
  • the supply and emission passage 4 communicates with a tank (not shown) in which the working oil is stored.
  • the discharge passage 5 and the return passage 6 communicate with the hydraulic actuator.
  • the supply and emission passage 4 is provided to oppose the discharge passage 5 and the return passage 6 .
  • the hydraulic pump 10 and the hydraulic motor 20 are arranged to oppose each other in the axial direction of the rotation shaft 2 across the supply and emission passage 4 , the discharge passage 5 , and the return passage 6 .
  • the hydraulic pump 10 suctions the working oil of the supply and emission passage 4 and discharges to the discharge passage 5 .
  • the hydraulic pump 10 assists drive of the hydraulic actuator by the main hydraulic pump with the discharged working oil.
  • the hydraulic pump 10 is provided with a cylinder block 11 coupled to the rotation shaft 2 , a plurality of pistons 13 respectively accommodated in a plurality of cylinders 12 which is defined in the cylinder block 11 , a swash plate 14 for letting the pistons 13 in sliding contact reciprocate, and a port plate 15 to be brought into sliding contact with an end surface of the cylinder block 11 .
  • the cylinder block 11 is formed into a substantially columnar shape, and rotated integrally with the rotation shaft 2 .
  • the cylinder block 11 is driven and rotated by the rotation shaft 2 .
  • the plurality of cylinders 12 is formed in parallel with the rotation shaft 2 .
  • the cylinders 12 are arranged on an identical circumference of the cylinder block 11 centering on the rotation shaft 2 in an annular manner at fixed intervals.
  • the pistons 13 are inserted into the respective cylinders 12 , and volume chambers 12 a are defined between the cylinders and the pistons 13 .
  • the volume chambers 12 a communicate with the port plate 15 through communication holes.
  • the swash plate 14 is provided in such a manner that the tilting angle is adjustable by a capacity switching actuator (not shown).
  • the swash plate 14 is tiltable into a state shown in FIG. 2 from a state where the swash plate is perpendicular to the rotation shaft 2 with the tilting angle of zero.
  • the tilting angle of the swash plate 14 is steplessly adjusted by the capacity switching actuator.
  • the port plate 15 is formed into a disc shape, and has a through hole into which the rotation shaft 2 is inserted in center thereof.
  • the port plate 15 has a supply port 15 a formed into an arc shape centering on the rotation shaft 2 , the supply port providing communication between the supply and emission passage 4 and the volume chambers 12 a, and a discharge port 15 b similarly formed into an arc shape centering on the rotation shaft 2 , the discharge port providing communication between the discharge passage 5 and the volume chambers 12 a.
  • a region where the pistons 13 are brought into sliding contact with the swash plate 14 and the volume chambers 12 a are extended is a suctioning region
  • a region where the pistons 13 are brought into sliding contact with the swash plate 14 and the volume chambers 12 a are contracted is a discharging region.
  • the supply port 15 a is formed in correspondence with the suctioning region
  • the discharge port 15 b is formed in correspondence with the discharging region.
  • the hydraulic motor 20 is driven and rotated with the working oil emitted from the hydraulic actuator.
  • the hydraulic motor 20 is provided with a cylinder block 21 coupled to the rotation shaft 2 , a plurality of pistons 23 respectively accommodated in a plurality of cylinders 22 which is defined in the cylinder block 21 , a swash plate 24 for letting the pistons 23 in sliding contact reciprocate, and a port plate 25 to be brought into sliding contact with an end surface of the cylinder block 21 .
  • the cylinder block 21 , the cylinders 22 , the pistons 23 , and the swash plate 24 of the hydraulic motor 20 only have different size from the configurations of the above hydraulic pump 10 but have the same configurations. Thus, description thereof is omitted.
  • the port plate 25 is formed into a disc shape, and has a through hole into which the rotation shaft 2 is inserted in center thereof.
  • the port plate 25 has a supply port 25 a formed into an arc shape centering on the rotation shaft 2 , the supply port 25 a providing communication between the return passage 6 and volume chambers 22 a, and an emission port 25 b similarly formed into an arc shape centering on the rotation shaft 2 , the emission port 25 b providing communication between the supply and emission passage 4 and the volume chambers 22 a.
  • a region where the pistons 23 are brought into sliding contact with the swash plate 24 and the volume chambers 22 a are extended is a suctioning region
  • a region where the pistons 23 are brought into sliding contact with the swash plate 24 and the volume chambers 22 a are contacted is an emitting region.
  • the supply port 25 a is formed in correspondence with the suctioning region
  • the emission port 25 b is formed in correspondence with the emitting region.
  • the electric motor 30 drives and rotates the hydraulic pump 10 , and is capable of generating regenerative electric power by the rotation of the hydraulic motor 20 .
  • the electric power generated in the electric motor 30 is stored in an electric power storage device (not shown).
  • the electric motor 30 drives and rotates the hydraulic pump 10 by using the regenerative electric power regenerated by the rotation of the hydraulic motor 20 and stored in the electric power storage device.
  • the plate 40 is a plate shape member having one surface 40 a to which the hydraulic pump motor 1 and the electric motor 30 are attached, and the other surface 40 b to which a casing 51 of the power transmission mechanism 50 is attached.
  • the power transmission mechanism 50 is provided to oppose the hydraulic pump motor 1 and the electric motor 30 across the plate 40 .
  • a through hole (not shown) through which the rotation shaft 2 of the hydraulic pump motor 1 passes, a through hole (not shown) through which a rotation shaft of the electric motor 30 passes, and a reflux port 42 (refer to FIG. 3 ) through which the lubricant oil after cooling the electric motor 30 is refluxed are formed.
  • the hydraulic pump motor 1 and the electric motor 30 are arranged in a U shape through the plate 40 and the power transmission mechanism 50 . Therefore, as the hydraulic pump motor 1 and the electric motor 30 are arranged in parallel, the entire length of the hydraulic drive unit 100 can be shortened. Thus, mountability of the hydraulic drive unit 100 to the hybrid construction machine can be improved.
  • the hydraulic pump motor 1 may be attached to the one surface 40 a of the plate 40
  • the electric motor 30 may be attached to the other surface 40 b of the plate 40 .
  • the hydraulic pump motor 1 and the electric motor 30 may be arranged in series across the plate 40 .
  • the power transmission mechanism 50 is provided with the casing 51 fixed to the plate 40 , a first gear 52 to be rotated integrally with the rotation shaft 2 of the hydraulic pump motor 1 , a second gear 53 to be rotated integrally with the rotation shaft of the electric motor 30 , and an idle gear 54 provided between the first gear 52 and the second gear 53 , the idle gear 54 for transmitting the power.
  • the casing 51 accommodates the first gear 52 , the second gear 53 , and the idle gear 54 .
  • the casing 51 is fastened by bolts in a state where an opening end surface 51 a is abutted with the other surface 40 b of the plate 40 .
  • the lubricant oil is charged inside the casing 51 .
  • the casing 51 has a through hole 51 b formed on an end surface on the opposite side of the opening end surface 51 a, the through hole 51 b into which a rotation shaft of the idle gear 54 is inserted.
  • the first gear 52 has a recessed portion 52 a formed on a rotation shaft, the recessed portion into which the rotation shaft 2 of the hydraulic pump motor 1 is inserted and fitted. Thereby, the first gear 52 is rotated integrally with the rotation shaft 2 of the hydraulic pump motor 1 .
  • one end of the rotation shaft is rotatably and axially supported on the plate 40 by a first bearing 52 b, and the other end of the rotation shaft is rotatably and axially supported on the casing 51 by a second bearing 52 c.
  • the second gear 53 has a recessed portion 53 a formed on a rotation shaft, the recessed portion into which the rotation shaft of the electric motor 30 is inserted and fitted. Thereby, the second gear 53 is rotated integrally with the rotation shaft of the electric motor 30 .
  • one end of the rotation shaft is rotatably and axially supported on the plate 40 by a first bearing 53 b, and the other end of the rotation shaft is rotatably and axially supported on the casing 51 by a second bearing 53 c.
  • the idle gear 54 is respectively meshed with the first gear 52 and the second gear 53 and transmits the power between the gears.
  • one end of the rotation shaft is rotatably and axially supported on the plate 40 by a first bearing 54 b, and a substantially center part of the rotation shaft is rotatably and axially supported on the casing 51 by a second bearing 54 c .
  • the other end of the rotation shaft of the idle gear 54 is inserted into the through hole 51 b and extended in a casing 61 of the circulation mechanism 60 .
  • the power transmission mechanism 50 can be downsized, and the entire hydraulic drive unit 100 can be downsized.
  • a reduction ratio between the hydraulic pump motor 1 and the electric motor 30 can be set to be a proper value.
  • the circulation mechanism 60 is provided with the casing 61 whose interior communicates with an interior of the casing 51 of the power transmission mechanism 50 , an impeller 62 serving as a rotation member to be rotated integrally with the idle gear 54 in the casing 61 , a supply flow passage 63 for guiding the lubricating fluid stirred up by the impeller 62 to the electric motor 30 , and a reflux flow passage 64 for returning the lubricating fluid guided to the electric motor 30 into the power transmission mechanism 50 .
  • the casing 61 is fixed in a state where an opening end surface 61 a is abutted with the casing 51 of the power transmission mechanism 50 .
  • the lubricant oil charged in the interior of the casing 51 of the power transmission mechanism 50 flows into the interior of the casing 61 .
  • a third bearing 54 d for rotatably and axially supporting the other end of the rotation shaft of the idle gear 54 is provided.
  • the impeller 62 is a rotating part provided coaxially with the idle gear 54 .
  • the impeller 62 is attached to the rotation shaft of the idle gear 54 .
  • the impeller 62 is provided between the second bearing 54 c and the third bearing 54 d. It should be noted that the impeller 62 may be provided anywhere between the first bearing 54 b and the third bearing 54 d.
  • the impeller 62 is rotated when the power transmission mechanism 50 transmits the power between the hydraulic pump motor 1 and the electric motor 30 , and stirs up the lubricant oil in the casing 51 of the power transmission mechanism 50 guided into the casing 61 toward an outer circumference.
  • the rotation number of the impeller 62 is increased. Therefore, in accordance with an increase in a heat generation amount of the electric motor 30 , an amount of the lubricant oil stirred up by the impeller 62 is increased.
  • the impeller may be provided to be rotated integrally with the first gear 52 or the second gear 53 .
  • a plurality of impellers 62 may be provided, for example, impellers 62 are respectively provided in the first gear 52 and the second gear 53 . That is, the impeller 62 is to be rotated integrally with at least any one of the first gear 52 , the second gear 53 , and the idle gear 54 .
  • the impeller 62 instead of the impeller 62 , another mechanism such as a cylinder to be driven by the rotation of the idle gear 54 , the cylinder for stirring up the lubricant oil may be provided. That is, as long as the mechanism is capable of converting rotation motion of the idle gear 54 and stirring up the lubricant oil, any mechanism may be provided.
  • the supply flow passage 63 is a pipe pulled out to an exterior from the casing 61 and coupled to an exterior of the electric motor 30 .
  • the supply flow passage 63 is pulled out from a surface of the casing 61 facing the outer circumference of the impeller 62 .
  • the lubricant oil guided through the supply flow passage 63 is supplied to an oil jacket (not shown) formed inside the electric motor 30 , and cools the electric motor 30 .
  • the reflux flow passage 64 is a pipe pulled out to the exterior from the electric motor 30 and coupled to the reflux port 42 (refer to FIG. 3 ) formed in the plate 40 . Through the reflux flow passage 64 , the lubricant oil emitted from the oil jacket of the electric motor 30 is refluxed into the casing 51 of the power transmission mechanism 50 . It should be noted that instead of the configuration in which the supply flow passage 63 and the reflux flow passage 64 are provided in the exterior of the electric motor 30 , the supply flow passage 63 and the reflux flow passage 64 may be formed inside a casing of the electric motor 30 .
  • the electric motor 30 is rotated by using the electric power preliminarily stored in the electric power storage device. By the rotation of the electric motor 30 , the rotation shaft 2 of the hydraulic pump motor 1 is driven and rotated via the power transmission mechanism 50 .
  • the tilting angle of the swash plate 14 is switched to have a predetermined value which is more than zero by the capacity switching actuator.
  • the pistons 13 reciprocate in the cylinders 12 .
  • the working oil from the tank is suctioned into the volume chambers 12 a through the supply port 15 a of the port plate 15 .
  • the working oil discharged from the volume chambers 12 a is guided to the discharge passage 5 through the discharge port 15 b of the port plate 15 .
  • the working oil discharged from the hydraulic drive unit 100 is supplied for the drive of the hydraulic actuator, and assists the drive of the hydraulic actuator by the main hydraulic pump.
  • the impeller 62 When the impeller 62 is rotated, the lubricant oil in the casing 51 of the power transmission mechanism 50 guided into the casing 61 of the circulation mechanism 60 through the through hole 51 b is stirred up and supplied to the oil jacket of the electric motor 30 through the supply flow passage 63 . Therefore, the electric motor 30 can be cooled by heat exchange between the lubricant oil and the electric motor 30 . The lubricant oil after cooling the electric motor 30 is refluxed from the oil jacket of the electric motor 30 into the casing 51 of the power transmission mechanism 50 through the reflux flow passage 64 .
  • the impeller 62 is rotated in accordance with transmission of the power by the power transmission mechanism 50 , and the lubricant oil is guided to the electric motor 30 . Therefore, since there is no need for providing a cooling system of cooling the electric motor 30 from the exterior, a cooling mechanism of the electric motor 30 in the hydraulic drive unit 100 can be simplified.
  • the power transmission mechanism 50 transmits the power, that is, when the electric motor 30 is rotated and generates heat, the lubricant oil can be supplied and cooling can be performed. Therefore, in comparison to a case where the cooling is always performed by using the cooling system of cooling the electric motor 30 from the exterior, cooling efficiency can be more enhanced.
  • the lubricant oil stirred up by the impeller 62 cools the electric motor 30 and is refluxed, the lubricant oil in the power transmission mechanism 50 is circulated. Therefore, the lubricant oil in the power transmission mechanism 50 flows and moves. Thus, the bearings for axially supporting the first gear 52 , the second gear 53 , and the idle gear 54 are prevented from being burnt out due to shortage of the lubricant oil.
  • the hydraulic motor 20 is retained in such a manner that a tilting angle of the swash plate 24 becomes zero by the capacity switching actuator. Therefore, since the pistons 23 do not reciprocate in the cylinders 22 , a displacement volume by the pistons 23 becomes zero. Thus, since the hydraulic motor 20 does not supply and emit the working oil but only runs idle, a drive loss of the hydraulic motor 20 is suppressed.
  • the tilting angle of the swash plate 24 is switched to be a predetermined value which is more than zero by the capacity switching actuator.
  • the hydraulic motor 20 in accordance with the rotation of the cylinder block 21 , the pistons 23 reciprocate in the cylinders 22 .
  • the pressurized working oil returned from the hydraulic actuator through the return passage 6 flows into the volume chambers 22 a through the supply port 25 a of the port plate 25 .
  • the pistons 23 reciprocate in the cylinders 22 , and the cylinder block 21 is driven and rotated.
  • the working oil flowing into the volume chambers 22 a is emitted to the supply and emission passage 4 through the emission port 25 b of the port plate 25 , and refluxed to the tank.
  • the rotation shaft 2 is rotated integrally with the cylinder block 21 .
  • the rotation of the rotation shaft 2 is transmitted to the rotation shaft of the electric motor 30 via the power transmission mechanism 50 .
  • the electric motor 30 can generate and store the regenerative electric power in the electric power storage device.
  • the hydraulic pump 10 is retained in such a manner that the tilting angle of the swash plate 14 becomes zero by the capacity switching actuator. Therefore, since the pistons 13 do not reciprocate in the cylinders 12 , a displacement volume by the pistons 13 becomes zero. Thus, since the hydraulic pump 10 does not supply and emit the working oil but only runs idle, a drive loss of the hydraulic pump 10 is suppressed.
  • the circulation mechanism 60 for guiding the lubricant oil in the power transmission mechanism 50 by the rotation of the impeller 62 and cooling the electric motor 30 is provided.
  • This impeller 62 is rotated integrally with the idle gear 54 for transmitting the power between the first gear 52 and the second gear 53 . Therefore, when the electric motor 30 drives and rotates the hydraulic pump motor 1 , the impeller 62 is rotated in accordance with the transmission of the power by the power transmission mechanism 50 , and the lubricant oil is guided to the electric motor 30 .
  • the cooling mechanism of the electric motor 30 in the hydraulic drive unit 100 can be simplified.
  • the hydraulic drive unit 100 is to assist the drive of the hydraulic actuator by the main hydraulic pump.
  • the hydraulic actuator may be driven by using only the hydraulic drive unit 100 .
  • Both the hydraulic pump 10 and the hydraulic motor 20 are swash-plate-type piston pump motors. However, as long as the motors are variable motors in which a suction and discharge capacity is adjustable to be zero, the hydraulic pump and the hydraulic motor may be other types.
  • the circulation mechanism 60 may supply the lubricant oil to the hydraulic pump motor 1 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
US14/389,319 2012-03-29 2013-03-22 Fluid pressure drive unit Abandoned US20150064030A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2012075565A JP5767996B2 (ja) 2012-03-29 2012-03-29 流体圧駆動ユニット
JP2012-075565 2012-03-29
PCT/JP2013/058254 WO2013146576A1 (ja) 2012-03-29 2013-03-22 流体圧駆動ユニット

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US20150064030A1 true US20150064030A1 (en) 2015-03-05

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Application Number Title Priority Date Filing Date
US14/389,319 Abandoned US20150064030A1 (en) 2012-03-29 2013-03-22 Fluid pressure drive unit

Country Status (6)

Country Link
US (1) US20150064030A1 (ko)
EP (1) EP2848808B1 (ko)
JP (1) JP5767996B2 (ko)
KR (1) KR101782684B1 (ko)
CN (1) CN104220750B (ko)
WO (1) WO2013146576A1 (ko)

Cited By (11)

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US10358040B1 (en) 2015-06-01 2019-07-23 Hydro-Gear Limited Partnership Drive assembly and system for utility vehicle
US10106027B1 (en) 2015-06-01 2018-10-23 Hydro-Gear Limited Partnership Generator/cooling assembly and system for utility vehicle
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US10391854B1 (en) 2015-06-15 2019-08-27 Hydro-Gear Limited Partnership Drive and cooling system for utility vehicle
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CN104220750A (zh) 2014-12-17
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JP2013204541A (ja) 2013-10-07
CN104220750B (zh) 2016-07-20
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WO2013146576A1 (ja) 2013-10-03
EP2848808A1 (en) 2015-03-18

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