EP2848808B1 - Fluid pressure drive unit - Google Patents
Fluid pressure drive unit Download PDFInfo
- Publication number
- EP2848808B1 EP2848808B1 EP13769429.5A EP13769429A EP2848808B1 EP 2848808 B1 EP2848808 B1 EP 2848808B1 EP 13769429 A EP13769429 A EP 13769429A EP 2848808 B1 EP2848808 B1 EP 2848808B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fluid pressure
- electric motor
- drive unit
- fluid
- motor
- 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.)
- Not-in-force
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—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
- 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
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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
-
- 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
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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 fluid pressure drive unit adapted to supply a working fluid to and driving a fluid pressure actuator according to the preamble of claim 1.
- a fluid pressure drive unit as described in the preamble of claim 1 is already known from US 5 320 501 A .
- 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.
- the above and other objects of the invention are achieved by the fluid pressure drive unit according to claim 1. Preferred embodiments are claimed in the dependent claims.
- a fluid pressure drive unit adapted to supply a working fluid to and driving a fluid pressure actuator.
- the fluid pressure drive unit comprises a fluid pressure pump configured to suction and discharge the working fluid, an electric motor configured to drive and rotate the fluid pressure pump, a power transmission mechanism located between a rotation shaft of the fluid pressure pump and a rotation shaft of the electric motor and configured to transmit a power there-between via a rotation thereof; and a circulation mechanism configured to be driven by the power transmitted by the power transmission mechanism and guide a lubricating fluid in the power transmission mechanism to the electric motor to cool the electric motor.
- 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 3a 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 12a are defined between the cylinders and the pistons 13.
- the volume chambers 12a 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 15a 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 12a, and a discharge port 15b 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 12a.
- a region where the pistons 13 are brought into sliding contact with the swash plate 14 and the volume chambers 12a 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 12a are contracted is a discharging region.
- the supply port 15a is formed in correspondence with the suctioning region
- the discharge port 15b 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 25a formed into an arc shape centering on the rotation shaft 2, the supply port 25a providing communication between the return passage 6 and volume chambers 22a, and an emission port 25b similarly formed into an arc shape centering on the rotation shaft 2, the emission port 25b providing communication between the supply and emission passage 4 and the volume chambers 22a.
- a region where the pistons 23 are brought into sliding contact with the swash plate 24 and the volume chambers 22a are extended is a suctioning region, and a region where the pistons 23 are brought into sliding contact with the swash plate 24 and the volume chambers 22a are contacted is an emitting region.
- the supply port 25a is formed in correspondence with the suctioning region, and the emission port 25b 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 40a to which the hydraulic pump motor 1 and the electric motor 30 are attached, and the other surface 40b 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 40a of the plate 40, and the electric motor 30 may be attached to the other surface 40b 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 51a is abutted with the other surface 40b of the plate 40.
- the lubricant oil is charged inside the casing 51.
- the casing 51 has a through hole 51b formed on an end surface on the opposite side of the opening end surface 51a, the through hole 51b into which a rotation shaft of the idle gear 54 is inserted.
- the first gear 52 has a recessed portion 52a 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 52b, and the other end of the rotation shaft is rotatably and axially supported on the casing 51 by a second bearing 52c.
- the second gear 53 has a recessed portion 53a 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 53b, and the other end of the rotation shaft is rotatably and axially supported on the casing 51 by a second bearing 53c.
- 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 54b, and a substantially center part of the rotation shaft is rotatably and axially supported on the casing 51 by a second bearing 54c.
- the other end of the rotation shaft of the idle gear 54 is inserted into the through hole 51b 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 61a 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 54d 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 54c and the third bearing 54d. It should be noted that the impeller 62 may be provided anywhere between the first bearing 54b and the third bearing 54d.
- 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 12a through the supply port 15a of the port plate 15.
- the working oil discharged from the volume chambers 12a is guided to the discharge passage 5 through the discharge port 15b 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 51b 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 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 22a through the supply port 25a 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 22a is emitted to the supply and emission passage 4 through the emission port 25b 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)
Description
- The present invention relates to a fluid pressure drive unit adapted to supply a working fluid to and driving a fluid pressure actuator according to the preamble of
claim 1. - A fluid pressure drive unit as described in the preamble of
claim 1 is already known fromUS 5 320 501 A . Conventionally, in a construction machine such as a power shovel, 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. In such a hybrid structure, 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 - However, in the assist regeneration device of
JP2011-127569A - 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.
The above and other objects of the invention are achieved by the fluid pressure drive unit according toclaim 1. Preferred embodiments are claimed in the dependent claims. - According to
claim 1, a fluid pressure drive unit adapted to supply a working fluid to and driving a fluid pressure actuator is provided. The fluid pressure drive unit comprises a fluid pressure pump configured to suction and discharge the working fluid, an electric motor configured to drive and rotate the fluid pressure pump, a power transmission mechanism located between a rotation shaft of the fluid pressure pump and a rotation shaft of the electric motor and configured to transmit a power there-between via a rotation thereof; and a circulation mechanism configured to be driven by the power transmitted by the power transmission mechanism and guide a lubricating fluid in the power transmission mechanism to the electric motor to cool the electric motor. - The details as well as other features and advantages of the present invention are set forth in the remainder of the specification and are shown in the accompanying drawings.
-
- [
Fig. 1] 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] Fig. 2 is a sectional view by line II-II of a fluid pressure pump motor inFig. 1 . - [
Fig. 3] Fig. 3 is a sectional view of a plate, a power transmission mechanism, and a circulation mechanism inFig. 1 . - Hereinafter, referring the drawings, a
hydraulic drive unit 100 serving as a fluid pressure drive unit according to an embodiment of the present invention will be described. In thehydraulic drive unit 100, working oil is used as a working fluid. It should be noted that instead of the working oil, other fluids such as working water may be used as the working fluid. - Firstly, referring to
Figs. 1 to 3 , a configuration of thehydraulic drive unit 100 will be described. - 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. Thehydraulic 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. - As shown in
Fig. 1 , thehydraulic drive unit 100 is provided with ahydraulic pump motor 1 serving as a fluid pressure pump motor which includes ahydraulic pump 10 serving as a fluid pressure pump for suctioning and discharging the working oil, and ahydraulic 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 anelectric motor 30 arranged in parallel to thehydraulic pump motor 1, aplate 40 having an identical surface to which thehydraulic pump motor 1 and theelectric motor 30 are attached, apower transmission mechanism 50 for transmitting a power between arotation shaft 2 of thehydraulic pump motor 1 and a rotation shaft (not shown) of theelectric motor 30, and acirculation mechanism 60 for guiding lubricant oil serving as a lubricating fluid in thepower transmission mechanism 50 and cooling theelectric motor 30. - The
hydraulic pump 10 and thehydraulic motor 20 forming thehydraulic pump motor 1 are respectively swash-plate-type variable piston pump motors. Thehydraulic motor 20 is a piston pump motor of a larger scale than thehydraulic pump 10. - As shown in
Fig. 2 , thehydraulic pump motor 1 is provided with acasing 3 for accommodating thehydraulic pump 10 and thehydraulic motor 20, and thesingle rotation shaft 2 rotatably and axially supported on thecasing 3 and commonly used for thehydraulic pump 10 and thehydraulic motor 20. - The
casing 3 has aflange portion 3a fastened to theplate 40 by bolts. Thecasing 3 has a supply andemission passage 4 through which the working oil to be supplied to thehydraulic pump 10 flows and the working oil emitted from thehydraulic motor 20 flows, adischarge passage 5 through which the working oil discharged from thehydraulic pump 10 flows, and areturn passage 6 through which the working oil returned from the hydraulic actuator, to be supplied to thehydraulic motor 20 flows. - The supply and
emission passage 4 communicates with a tank (not shown) in which the working oil is stored. Thedischarge passage 5 and thereturn passage 6 communicate with the hydraulic actuator. The supply andemission passage 4 is provided to oppose thedischarge passage 5 and thereturn passage 6. - The
hydraulic pump 10 and thehydraulic motor 20 are arranged to oppose each other in the axial direction of therotation shaft 2 across the supply andemission passage 4, thedischarge passage 5, and thereturn passage 6. - The
hydraulic pump 10 suctions the working oil of the supply andemission passage 4 and discharges to thedischarge passage 5. Thehydraulic pump 10 assists drive of the hydraulic actuator by the main hydraulic pump with the discharged working oil. Thehydraulic pump 10 is provided with acylinder block 11 coupled to therotation shaft 2, a plurality ofpistons 13 respectively accommodated in a plurality ofcylinders 12 which is defined in thecylinder block 11, aswash plate 14 for letting thepistons 13 in sliding contact reciprocate, and aport plate 15 to be brought into sliding contact with an end surface of thecylinder block 11. - The
cylinder block 11 is formed into a substantially columnar shape, and rotated integrally with therotation shaft 2. Thecylinder block 11 is driven and rotated by therotation shaft 2. In thecylinder block 11, the plurality ofcylinders 12 is formed in parallel with therotation shaft 2. - The
cylinders 12 are arranged on an identical circumference of thecylinder block 11 centering on therotation shaft 2 in an annular manner at fixed intervals. Thepistons 13 are inserted into therespective cylinders 12, andvolume chambers 12a are defined between the cylinders and thepistons 13. Thevolume chambers 12a communicate with theport plate 15 through communication holes. - When the
cylinder block 11 is rotated together with therotation shaft 2, thepistons 13 are brought into sliding contact with theswash plate 14. Thereby, thepistons 13 reciprocate in thecylinders 12 in accordance with a tilting angle of theswash plate 14, and hence extend and contract thevolume chambers 12a. - The
swash plate 14 is provided in such a manner that the tilting angle is adjustable by a capacity switching actuator (not shown). Theswash plate 14 is tiltable into a state shown inFig. 2 from a state where the swash plate is perpendicular to therotation shaft 2 with the tilting angle of zero. The tilting angle of theswash 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 therotation shaft 2 is inserted in center thereof. Theport plate 15 has asupply port 15a formed into an arc shape centering on therotation shaft 2, the supply port providing communication between the supply andemission passage 4 and thevolume chambers 12a, and adischarge port 15b similarly formed into an arc shape centering on therotation shaft 2, the discharge port providing communication between thedischarge passage 5 and thevolume chambers 12a. - In the
hydraulic pump 10, a region where thepistons 13 are brought into sliding contact with theswash plate 14 and thevolume chambers 12a are extended is a suctioning region, and a region where thepistons 13 are brought into sliding contact with theswash plate 14 and thevolume chambers 12a are contracted is a discharging region. Thesupply port 15a is formed in correspondence with the suctioning region, and thedischarge port 15b is formed in correspondence with the discharging region. Thereby, in accordance with rotation of thecylinder block 11, the working oil is suctioned into thevolume chambers 12a facing thesupply port 15a, and the working oil is discharged from thevolume chambers 12a facing thedischarge port 15b. - The
hydraulic motor 20 is driven and rotated with the working oil emitted from the hydraulic actuator. Thehydraulic motor 20 is provided with acylinder block 21 coupled to therotation shaft 2, a plurality ofpistons 23 respectively accommodated in a plurality of cylinders 22 which is defined in thecylinder block 21, aswash plate 24 for letting thepistons 23 in sliding contact reciprocate, and a port plate 25 to be brought into sliding contact with an end surface of thecylinder block 21. Thecylinder block 21, the cylinders 22, thepistons 23, and theswash plate 24 of thehydraulic motor 20 only have different size from the configurations of the abovehydraulic 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 25a formed into an arc shape centering on therotation shaft 2, the supply port 25a providing communication between thereturn passage 6 and volume chambers 22a, and anemission port 25b similarly formed into an arc shape centering on therotation shaft 2, theemission port 25b providing communication between the supply andemission passage 4 and the volume chambers 22a. - In the
hydraulic motor 20, a region where thepistons 23 are brought into sliding contact with theswash plate 24 and the volume chambers 22a are extended is a suctioning region, and a region where thepistons 23 are brought into sliding contact with theswash plate 24 and the volume chambers 22a are contacted is an emitting region. The supply port 25a is formed in correspondence with the suctioning region, and theemission port 25b is formed in correspondence with the emitting region. Thereby, in accordance with rotation of thecylinder block 21, the working oil is suctioned into the volume chambers 22a facing the supply port 25a, and the working oil is emitted from the volume chambers 22a facing theemission port 25b. - The
electric motor 30 drives and rotates thehydraulic pump 10, and is capable of generating regenerative electric power by the rotation of thehydraulic motor 20. The electric power generated in theelectric motor 30 is stored in an electric power storage device (not shown). Theelectric motor 30 drives and rotates thehydraulic pump 10 by using the regenerative electric power regenerated by the rotation of thehydraulic motor 20 and stored in the electric power storage device. - As shown in
Fig. 1 , theplate 40 is a plate shape member having onesurface 40a to which thehydraulic pump motor 1 and theelectric motor 30 are attached, and theother surface 40b to which acasing 51 of thepower transmission mechanism 50 is attached. Thereby, thepower transmission mechanism 50 is provided to oppose thehydraulic pump motor 1 and theelectric motor 30 across theplate 40. In theplate 40, a through hole (not shown) through which therotation shaft 2 of thehydraulic pump motor 1 passes, a through hole (not shown) through which a rotation shaft of theelectric motor 30 passes, and a reflux port 42 (refer toFig. 3 ) through which the lubricant oil after cooling theelectric motor 30 is refluxed are formed. - As described above, in the
hydraulic drive unit 100, thehydraulic pump motor 1 and theelectric motor 30 are arranged in a U shape through theplate 40 and thepower transmission mechanism 50. Therefore, as thehydraulic pump motor 1 and theelectric motor 30 are arranged in parallel, the entire length of thehydraulic drive unit 100 can be shortened. Thus, mountability of thehydraulic drive unit 100 to the hybrid construction machine can be improved. - It should be noted that instead of the U shape arrangement, the
hydraulic pump motor 1 may be attached to the onesurface 40a of theplate 40, and theelectric motor 30 may be attached to theother surface 40b of theplate 40. Thehydraulic pump motor 1 and theelectric motor 30 may be arranged in series across theplate 40. - As shown in
Fig. 3 , thepower transmission mechanism 50 is provided with thecasing 51 fixed to theplate 40, afirst gear 52 to be rotated integrally with therotation shaft 2 of thehydraulic pump motor 1, asecond gear 53 to be rotated integrally with the rotation shaft of theelectric motor 30, and anidle gear 54 provided between thefirst gear 52 and thesecond gear 53, theidle gear 54 for transmitting the power. - The
casing 51 accommodates thefirst gear 52, thesecond gear 53, and theidle gear 54. Thecasing 51 is fastened by bolts in a state where an openingend surface 51a is abutted with theother surface 40b of theplate 40. The lubricant oil is charged inside thecasing 51. Thecasing 51 has a throughhole 51b formed on an end surface on the opposite side of the openingend surface 51a, the throughhole 51b into which a rotation shaft of theidle gear 54 is inserted. - The
first gear 52 has a recessedportion 52a formed on a rotation shaft, the recessed portion into which therotation shaft 2 of thehydraulic pump motor 1 is inserted and fitted. Thereby, thefirst gear 52 is rotated integrally with therotation shaft 2 of thehydraulic pump motor 1. In thefirst gear 52, one end of the rotation shaft is rotatably and axially supported on theplate 40 by afirst bearing 52b, and the other end of the rotation shaft is rotatably and axially supported on thecasing 51 by asecond bearing 52c. - Similarly, the
second gear 53 has a recessedportion 53a formed on a rotation shaft, the recessed portion into which the rotation shaft of theelectric motor 30 is inserted and fitted. Thereby, thesecond gear 53 is rotated integrally with the rotation shaft of theelectric motor 30. In thesecond gear 53, one end of the rotation shaft is rotatably and axially supported on theplate 40 by afirst bearing 53b, and the other end of the rotation shaft is rotatably and axially supported on thecasing 51 by asecond bearing 53c. - The
idle gear 54 is respectively meshed with thefirst gear 52 and thesecond gear 53 and transmits the power between the gears. In theidle gear 54, one end of the rotation shaft is rotatably and axially supported on theplate 40 by afirst bearing 54b, and a substantially center part of the rotation shaft is rotatably and axially supported on thecasing 51 by asecond bearing 54c. The other end of the rotation shaft of theidle gear 54 is inserted into the throughhole 51b and extended in acasing 61 of thecirculation mechanism 60. - In such a way, by providing the
idle gear 54 between thefirst gear 52 and thesecond gear 53, even in a case where thehydraulic pump motor 1 and theelectric motor 30 are relatively distant from each other, diameters of thefirst gear 52 and thesecond gear 53 are suppressed from being large. Therefore, thepower transmission mechanism 50 can be downsized, and the entirehydraulic drive unit 100 can be downsized. - By adjusting a gear ratio between the
first gear 52 and thesecond gear 53, a reduction ratio between thehydraulic pump motor 1 and theelectric motor 30 can be set to be a proper value. - The
circulation mechanism 60 is provided with thecasing 61 whose interior communicates with an interior of thecasing 51 of thepower transmission mechanism 50, animpeller 62 serving as a rotation member to be rotated integrally with theidle gear 54 in thecasing 61, asupply flow passage 63 for guiding the lubricating fluid stirred up by theimpeller 62 to theelectric motor 30, and areflux flow passage 64 for returning the lubricating fluid guided to theelectric motor 30 into thepower transmission mechanism 50. - The
casing 61 is fixed in a state where an openingend surface 61a is abutted with thecasing 51 of thepower transmission mechanism 50. The lubricant oil charged in the interior of thecasing 51 of thepower transmission mechanism 50 flows into the interior of thecasing 61. In thecasing 61, athird bearing 54d for rotatably and axially supporting the other end of the rotation shaft of theidle gear 54 is provided. - The
impeller 62 is a rotating part provided coaxially with theidle gear 54. Theimpeller 62 is attached to the rotation shaft of theidle gear 54. Theimpeller 62 is provided between thesecond bearing 54c and thethird bearing 54d. It should be noted that theimpeller 62 may be provided anywhere between thefirst bearing 54b and thethird bearing 54d. - The
impeller 62 is rotated when thepower transmission mechanism 50 transmits the power between thehydraulic pump motor 1 and theelectric motor 30, and stirs up the lubricant oil in thecasing 51 of thepower transmission mechanism 50 guided into thecasing 61 toward an outer circumference. In accordance with an increase in the rotation number of theelectric motor 30, the rotation number of theimpeller 62 is increased. Therefore, in accordance with an increase in a heat generation amount of theelectric motor 30, an amount of the lubricant oil stirred up by theimpeller 62 is increased. - Since the
impeller 62 is rotated integrally with theidle gear 54, rotational fluctuation of theidle gear 54 can be reduced by the flywheel effect. Therefore, noises due to the rotational fluctuation of theidle gear 54 can be reduced. - It should be noted that instead of providing the
impeller 62 to be rotated integrally with theidle gear 54, the impeller may be provided to be rotated integrally with thefirst gear 52 or thesecond gear 53. A plurality ofimpellers 62 may be provided, for example,impellers 62 are respectively provided in thefirst gear 52 and thesecond gear 53. That is, theimpeller 62 is to be rotated integrally with at least any one of thefirst gear 52, thesecond gear 53, and theidle gear 54. - Instead of the
impeller 62, another mechanism such as a cylinder to be driven by the rotation of theidle 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 theidle gear 54 and stirring up the lubricant oil, any mechanism may be provided. - As shown in
Fig. 1 , thesupply flow passage 63 is a pipe pulled out to an exterior from thecasing 61 and coupled to an exterior of theelectric motor 30. Thesupply flow passage 63 is pulled out from a surface of thecasing 61 facing the outer circumference of theimpeller 62. The lubricant oil guided through thesupply flow passage 63 is supplied to an oil jacket (not shown) formed inside theelectric motor 30, and cools theelectric motor 30. - The
reflux flow passage 64 is a pipe pulled out to the exterior from theelectric motor 30 and coupled to the reflux port 42 (refer toFig. 3 ) formed in theplate 40. Through thereflux flow passage 64, the lubricant oil emitted from the oil jacket of theelectric motor 30 is refluxed into thecasing 51 of thepower transmission mechanism 50. It should be noted that instead of the configuration in which thesupply flow passage 63 and thereflux flow passage 64 are provided in the exterior of theelectric motor 30, thesupply flow passage 63 and thereflux flow passage 64 may be formed inside a casing of theelectric motor 30. - Next, actions of the
hydraulic drive unit 100 will be described. - In a case where the
hydraulic drive unit 100 assists the drive of the hydraulic actuator by the main hydraulic pump, theelectric motor 30 is rotated by using the electric power preliminarily stored in the electric power storage device. By the rotation of theelectric motor 30, therotation shaft 2 of thehydraulic pump motor 1 is driven and rotated via thepower transmission mechanism 50. - Regarding the
hydraulic pump 10, the tilting angle of theswash plate 14 is switched to have a predetermined value which is more than zero by the capacity switching actuator. In thehydraulic pump 10, in accordance with the rotation of thecylinder block 11, thepistons 13 reciprocate in thecylinders 12. By this reciprocation of thepistons 13, the working oil from the tank is suctioned into thevolume chambers 12a through thesupply port 15a of theport plate 15. The working oil discharged from thevolume chambers 12a is guided to thedischarge passage 5 through thedischarge port 15b of theport plate 15. - Thereby, 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. - When the
electric motor 30 drives and rotates thehydraulic pump motor 1, the rotation of thesecond gear 53 is transmitted to theidle gear 54, and the rotation of theidle gear 54 is transmitted to thefirst gear 52. By rotating theidle gear 54, theimpeller 62 of thecirculation mechanism 60 is rotated. - When the
impeller 62 is rotated, the lubricant oil in thecasing 51 of thepower transmission mechanism 50 guided into thecasing 61 of thecirculation mechanism 60 through the throughhole 51b is stirred up and supplied to the oil jacket of theelectric motor 30 through thesupply flow passage 63. Therefore, theelectric motor 30 can be cooled by heat exchange between the lubricant oil and theelectric motor 30. The lubricant oil after cooling theelectric motor 30 is refluxed from the oil jacket of theelectric motor 30 into thecasing 51 of thepower transmission mechanism 50 through thereflux flow passage 64. - As described above, when the
electric motor 30 drives and rotates thehydraulic pump motor 1, theimpeller 62 is rotated in accordance with transmission of the power by thepower transmission mechanism 50, and the lubricant oil is guided to theelectric motor 30. Therefore, since there is no need for providing a cooling system of cooling theelectric motor 30 from the exterior, a cooling mechanism of theelectric motor 30 in thehydraulic drive unit 100 can be simplified. - Only when the
power transmission mechanism 50 transmits the power, that is, when theelectric 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 theelectric motor 30 from the exterior, cooling efficiency can be more enhanced. - Since the lubricant oil stirred up by the
impeller 62 cools theelectric motor 30 and is refluxed, the lubricant oil in thepower transmission mechanism 50 is circulated. Therefore, the lubricant oil in thepower transmission mechanism 50 flows and moves. Thus, the bearings for axially supporting thefirst gear 52, thesecond gear 53, and theidle gear 54 are prevented from being burnt out due to shortage of the lubricant oil. - At this time, the
hydraulic motor 20 is retained in such a manner that a tilting angle of theswash plate 24 becomes zero by the capacity switching actuator. Therefore, since thepistons 23 do not reciprocate in the cylinders 22, a displacement volume by thepistons 23 becomes zero. Thus, since thehydraulic motor 20 does not supply and emit the working oil but only runs idle, a drive loss of thehydraulic motor 20 is suppressed. - Meanwhile, in a case where the regenerative electric power is generated with the working oil emitted from the hydraulic actuator, regarding the
hydraulic motor 20, the tilting angle of theswash plate 24 is switched to be a predetermined value which is more than zero by the capacity switching actuator. In thehydraulic motor 20, in accordance with the rotation of thecylinder block 21, thepistons 23 reciprocate in the cylinders 22. By this reciprocation of thepistons 23, the pressurized working oil returned from the hydraulic actuator through thereturn passage 6 flows into the volume chambers 22a through the supply port 25a of the port plate 25. Thepistons 23 reciprocate in the cylinders 22, and thecylinder block 21 is driven and rotated. The working oil flowing into the volume chambers 22a is emitted to the supply andemission passage 4 through theemission port 25b of the port plate 25, and refluxed to the tank. - The
rotation shaft 2 is rotated integrally with thecylinder block 21. The rotation of therotation shaft 2 is transmitted to the rotation shaft of theelectric motor 30 via thepower transmission mechanism 50. Thereby, theelectric motor 30 can generate and store the regenerative electric power in the electric power storage device. - When the rotation of the
rotation shaft 2 of thehydraulic pump motor 1 is transmitted to theelectric motor 30, the rotation of thefirst gear 52 is transmitted to theidle gear 54, and the rotation of theidle gear 54 is transmitted to thesecond gear 53. By rotating theidle gear 54, theimpeller 62 of thecirculation mechanism 60 is rotated. Therefore, as well as a case where theelectric motor 30 drives and rotates thehydraulic pump motor 1, theelectric motor 30 can be cooled by the heat exchange between the lubricant oil and theelectric motor 30. - At this time, the
hydraulic pump 10 is retained in such a manner that the tilting angle of theswash plate 14 becomes zero by the capacity switching actuator. Therefore, since thepistons 13 do not reciprocate in thecylinders 12, a displacement volume by thepistons 13 becomes zero. Thus, since thehydraulic pump 10 does not supply and emit the working oil but only runs idle, a drive loss of thehydraulic pump 10 is suppressed. - It should be noted that in a case where the
hydraulic drive unit 100 assists supply of the working oil to a plurality of hydraulic actuators by the main hydraulic pump, there is sometimes a case where drive of one hydraulic actuator is assisted and the working oil is refluxed from other hydraulic actuators. - According to the above embodiment, the following effects are obtained.
- The
circulation mechanism 60 for guiding the lubricant oil in thepower transmission mechanism 50 by the rotation of theimpeller 62 and cooling theelectric motor 30 is provided. Thisimpeller 62 is rotated integrally with theidle gear 54 for transmitting the power between thefirst gear 52 and thesecond gear 53. Therefore, when theelectric motor 30 drives and rotates thehydraulic pump motor 1, theimpeller 62 is rotated in accordance with the transmission of the power by thepower transmission mechanism 50, and the lubricant oil is guided to theelectric motor 30. Thus, since there is no need for providing the cooling system of cooling theelectric motor 30 from the exterior, the cooling mechanism of theelectric motor 30 in thehydraulic drive unit 100 can be simplified. - Embodiments of the present invention were described above, but the above embodiments are merely examples of applications of the present invention, and the technical scope of the present invention is not limited to the specific constitutions of the above embodiments.
- For example, the
hydraulic drive unit 100 is to assist the drive of the hydraulic actuator by the main hydraulic pump. However, instead of this, the hydraulic actuator may be driven by using only thehydraulic drive unit 100. - Both the
hydraulic pump 10 and thehydraulic 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. Thecirculation mechanism 60 may supply the lubricant oil to thehydraulic pump motor 1. - The embodiments of the present invention in which an exclusive property or privilege is claimed are defined as follows:
Claims (9)
- A fluid pressure drive unit (100) adapted to supply a working fluid to and driving a fluid pressure actuator, comprising:a fluid pressure pump (10) configured to suction and discharge the working fluid;an electric motor (30) configured to drive and rotate the fluid pressure pump (10); anda power transmission mechanism (50) located between a rotation shaft (2) of the fluid pressure pump (10) and a rotation shaft of the electric motor (30) and configured to transmit a power there-between via a rotation thereof,characterized bya circulation mechanism (60) configured to be driven by the power transmitted by the power transmission mechanism (50) and guide a lubricating fluid in the power transmission mechanism (50) to the electric motor (30) to cool the electric motor (30).
- The fluid pressure drive unit (100) according to claim 1, wherein
the power transmission mechanism (50) includes a first gear (52) configured to rotate integrally with the rotation shaft (2) of the fluid pressure pump (10), a second gear (53) configured to rotate 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) and configured to transmit the power there-between, and
the circulation mechanism (60) has a rotation member configured to rotate integrally with at least any one of the first gear (52), the second gear (53), and the idle gear (54) configured to stir up the lubricating fluid in the power transmission mechanism (50). - The fluid pressure drive unit (100) according to claim 2, wherein
the circulation mechanism (60) includes:a supply flow passage (63) through which the lubricating fluid stirred up by the rotation member is guided to the electric motor (30); anda reflux flow passage (64) through which the lubricating fluid guided to the electric motor (30) is returned into the power transmission mechanism (50). - The fluid pressure drive unit (100) according to claim 2, wherein
the rotation member is an impeller (42) configured to rotate integrally with the idle gear (54). - The fluid pressure drive unit (100) according to claim 1, further comprising:a plate (40) having a common surface to which the fluid pressure pump (10) and the electric motor (30) are attached, wherein the rotation shaft (2) of the fluid pressure pump (10) and the rotation shaft of the electric motor (30) are arranged to pass through the plate (40), andthe electric motor (30) is arranged in parallel to the fluid pressure pump (10).
- The fluid pressure drive unit (100) according to claim 1, further comprising:a fluid pressure motor (20) that is configured to be driven and rotated with the working fluid supplied from the fluid pressure actuator, the fluid pressure motor (20) having a rotation shaft common to the rotation shaft (2) of the fluid pressure pump (10), whereinthe electric motor (30) is configured to generate a regenerative electric power when a rotational force is input from the fluid pressure motor (20) via the power transmission mechanism (50).
- The fluid pressure drive unit (100) according to claim 6, wherein the fluid pressure drive unit (100) is applied to a hybrid construction machine comprising the fluid pressure actuator, a main fluid pressure pump configured to supply the working fluid to the fluid pressure actuator to drive the same, and a prime mover configured to drive the main fluid pressure pump, and wherein the fluid pressure motor (20) is configured to be driven and rotated with the working fluid emitted from the fluid pressure actuator;
the electric motor (30) is configured to generate the regenerative electric power by the rotation of the fluid pressure motor (20), and is configured to drive and rotate the fluid pressure pump (10) by using the regenerative electric power, and
the fluid pressure pump (10) is configured to discharge and supply the working fluid to assist the drive of the fluid pressure actuator by the main fluid pressure pump. - The fluid pressure drive unit (100) according to claim 1, wherein the circulation mechanism (60) is configured to guide the lubricating fluid to the electric motor (30) via a passage (63) disposed on the outside of the electric motor (30).
- The fluid pressure drive unit (100) according to claim 1, wherein the circulation mechanism (60) includes:a supply flow passage (63) through which the lubricating fluid is guided to the electric motor (30); andreflux flow passage (64) through which the lubricating fluid guided to the electric motor (30) is returned into the power transmission mechanism (50).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2012075565A JP5767996B2 (en) | 2012-03-29 | 2012-03-29 | Fluid pressure drive unit |
PCT/JP2013/058254 WO2013146576A1 (en) | 2012-03-29 | 2013-03-22 | Fluid pressure drive unit |
Publications (3)
Publication Number | Publication Date |
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EP2848808A1 EP2848808A1 (en) | 2015-03-18 |
EP2848808A4 EP2848808A4 (en) | 2016-03-30 |
EP2848808B1 true EP2848808B1 (en) | 2018-07-04 |
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Application Number | Title | Priority Date | Filing Date |
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EP13769429.5A Not-in-force EP2848808B1 (en) | 2012-03-29 | 2013-03-22 | Fluid pressure drive unit |
Country Status (6)
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US (1) | US20150064030A1 (en) |
EP (1) | EP2848808B1 (en) |
JP (1) | JP5767996B2 (en) |
KR (1) | KR101782684B1 (en) |
CN (1) | CN104220750B (en) |
WO (1) | WO2013146576A1 (en) |
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Also Published As
Publication number | Publication date |
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EP2848808A4 (en) | 2016-03-30 |
JP5767996B2 (en) | 2015-08-26 |
KR20140129274A (en) | 2014-11-06 |
KR101782684B1 (en) | 2017-09-27 |
US20150064030A1 (en) | 2015-03-05 |
CN104220750A (en) | 2014-12-17 |
CN104220750B (en) | 2016-07-20 |
EP2848808A1 (en) | 2015-03-18 |
WO2013146576A1 (en) | 2013-10-03 |
JP2013204541A (en) | 2013-10-07 |
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