WO2013146576A1 - 流体圧駆動ユニット - Google Patents

流体圧駆動ユニット Download PDF

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Publication number
WO2013146576A1
WO2013146576A1 PCT/JP2013/058254 JP2013058254W WO2013146576A1 WO 2013146576 A1 WO2013146576 A1 WO 2013146576A1 JP 2013058254 W JP2013058254 W JP 2013058254W WO 2013146576 A1 WO2013146576 A1 WO 2013146576A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid pressure
electric motor
drive unit
fluid
gear
Prior art date
Application number
PCT/JP2013/058254
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
鈴木　一成
新司 矢加部
Original Assignee
カヤバ工業株式会社
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 カヤバ工業株式会社 filed Critical カヤバ工業株式会社
Priority to CN201380017785.7A priority Critical patent/CN104220750B/zh
Priority to US14/389,319 priority patent/US20150064030A1/en
Priority to EP13769429.5A priority patent/EP2848808B1/en
Priority to KR1020147026743A priority patent/KR101782684B1/ko
Publication of WO2013146576A1 publication Critical patent/WO2013146576A1/ja

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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 that supplies a working fluid to a fluid pressure actuator for driving.
  • a fluid pressure drive unit that includes an electric motor that rotates with stored electric power, and an assist pump that is driven by the electric motor to discharge the working fluid and assist the operation of the actuator by the main pump.
  • JP2011-127569A includes an assist regenerative motor that includes a motor generator that rotates by electric energy, a regenerative motor that rotationally drives the motor generator by the energy of the working fluid, and an assist pump that is driven by the motor generator to discharge the working fluid.
  • An apparatus is disclosed.
  • the motor generator generates heat when it is driven to rotate or when regenerative power is generated. Therefore, a cooling system for cooling the motor generator from the outside by circulating a refrigerant using a pump is required.
  • the present invention has been made in view of the above-described problems, and an object thereof is to simplify a cooling mechanism for an electric motor in a fluid pressure drive unit.
  • a fluid pressure drive unit that supplies and drives a working fluid to a fluid pressure actuator.
  • the fluid pressure drive unit transmits power between a fluid pressure pump that sucks and discharges working fluid, an electric motor that rotationally drives the fluid pressure pump, and a rotation shaft of the fluid pressure pump and a rotation shaft of the motor.
  • a power transmission mechanism that is driven by power transmitted by the power transmission mechanism, and a circulation mechanism that guides a lubricating fluid in the power transmission mechanism and cools the electric motor.
  • FIG. 1 is a front view showing, in section, a part of a fluid pressure drive unit according to an embodiment of the present invention.
  • 2 is a sectional view of the fluid pressure pump motor taken along the line II-II in FIG.
  • FIG. 3 is a cross-sectional view of the plate, the power transmission mechanism, and the circulation mechanism in FIG.
  • hydraulic drive unit 100 as a fluid pressure drive unit according to an embodiment of the present invention will be described with reference to the drawings.
  • working oil is used as the working fluid.
  • other fluids such as working water may be used as the working fluid instead of the working oil.
  • the hydraulic drive unit 100 is driven by supplying hydraulic oil to a hydraulic actuator (not shown) as a fluid pressure actuator.
  • the hydraulic drive unit 100 is applied to a hybrid construction machine such as a power shovel that drives a hydraulic actuator with hydraulic oil discharged from a main hydraulic pump (not shown) driven by a prime mover.
  • the hydraulic drive unit 100 includes a hydraulic pump 10 as a fluid pressure pump that sucks and discharges hydraulic oil, and a hydraulic motor 20 as a fluid pressure motor that is rotationally driven by the supplied hydraulic oil.
  • a hydraulic pump motor 1 as a fluid pressure pump motor is provided.
  • the hydraulic drive unit 100 includes an electric motor 30 arranged in parallel with the hydraulic pump motor 1, a plate 40 on which the hydraulic pump motor 1 and the electric motor 30 are mounted on the same surface, and a rotating shaft 2 of the hydraulic pump motor 1.
  • a power transmission mechanism 50 that transmits power between the motor 30 and a rotating shaft (not shown) of the electric motor 30, and a circulation mechanism 60 that guides lubricating oil as a lubricating fluid in the power transmission mechanism 50 to cool the electric motor 30.
  • the hydraulic pump 10 and the hydraulic motor 20 constituting the hydraulic pump motor 1 are each a swash plate type variable displacement type piston pump motor.
  • the hydraulic motor 20 is a large piston pump motor compared to the hydraulic pump 10.
  • the hydraulic pump motor 1 is commonly used by the casing 3 that accommodates the hydraulic pump 10 and the hydraulic motor 20, and rotatably supported by the casing 3. And a single rotating shaft 2.
  • the supply / discharge passage 4 communicates with a tank (not shown) in which hydraulic oil is stored.
  • the discharge passage 5 and the return passage 6 communicate with the hydraulic actuator.
  • the supply / discharge passage 4 is provided to face the discharge passage 5 and the return passage 6.
  • the hydraulic pump 10 and the hydraulic motor 20 are arranged to face each other in the axial direction of the rotary shaft 2 with the supply / discharge passage 4, the discharge passage 5, and the return passage 6 interposed therebetween.
  • the hydraulic pump 10 sucks hydraulic oil in the supply / discharge passage 4 and discharges it to the discharge passage 5.
  • the hydraulic pump 10 assists the drive of the hydraulic actuator by the main hydraulic pump with the discharged hydraulic oil.
  • the hydraulic pump 10 includes a cylinder block 11 coupled to the rotary shaft 2, a plurality of pistons 13 respectively accommodated in a plurality of cylinders 12 defined in the cylinder block 11, and a swash plate that reciprocates the pistons 13 that are in sliding contact with each other. 14 and a port plate 15 in which the end face of the cylinder block 11 is in sliding contact.
  • the cylinder block 11 is formed in a substantially cylindrical shape and rotates integrally with the rotary shaft 2.
  • the cylinder block 11 is rotationally driven by the rotary shaft 2.
  • a plurality of cylinders 12 are formed in the cylinder block 11 in parallel with the rotation shaft 2.
  • the cylinders 12 are arranged in a ring at regular intervals on the same circumference around the rotation axis 2 of the cylinder block 11.
  • a piston 13 is inserted into each cylinder 12, and a volume chamber 12 a is defined between the cylinders 13.
  • the volume chamber 12a communicates with the port plate 15 through the communication hole.
  • the piston 13 is in sliding contact with the swash plate 14 when the cylinder block 11 rotates together with the rotary shaft 2. Thereby, the piston 13 reciprocates in the cylinder 12 according to the tilt angle of the swash plate 14, and expands and contracts the volume chamber 12a.
  • the swash plate 14 is provided such that the tilt angle can be adjusted by a capacity switching actuator (not shown).
  • the swash plate 14 can be tilted from a state where the tilt angle perpendicular to the rotation shaft 2 is zero to the state shown in FIG.
  • the tilt angle of the swash plate 14 is adjusted steplessly by the capacity switching actuator.
  • the port plate 15 is formed in a disc shape, and has a through hole through which the rotary shaft 2 is inserted.
  • the port plate 15 is formed in an arc shape centered on the rotation shaft 2 and is formed in an arc shape centered on the rotation shaft 2 and discharged, similarly to the supply port 15a communicating the supply / discharge passage 4 and the volume chamber 12a. It has a discharge port 15b for communicating the passage 5 and the volume chamber 12a.
  • a region where the piston 13 slides on the swash plate 14 and the volume chamber 12a expands is a suction region
  • a region where the piston 13 slides on the swash plate 14 and the volume chamber 12a contracts is a discharge region.
  • the supply port 15a is formed corresponding to the suction area
  • the discharge port 15b is formed corresponding to the discharge area.
  • the hydraulic motor 20 is rotationally driven by hydraulic oil discharged from the hydraulic actuator.
  • the hydraulic motor 20 includes a cylinder block 21 connected to the rotary shaft 2, a plurality of pistons 23 accommodated in a plurality of cylinders 22 defined in the cylinder block 21, and a swash plate that reciprocates the pistons 23 that are in sliding contact with each other. 24 and a port plate 25 in which the end face of the cylinder block 21 is in sliding contact.
  • the cylinder block 21, the cylinder 22, the piston 23, and the swash plate 24 of the hydraulic motor 20 have the same configuration except for the configuration of the hydraulic pump 10 described above, and thus the description thereof is omitted here.
  • the port plate 25 is formed in a disc shape and has a through hole through which the rotary shaft 2 is inserted.
  • the port plate 25 is formed in an arc shape with the rotation shaft 2 as the center, and the supply port 25a that connects the return passage 6 and the volume chamber 22a. It has a discharge port 25b for communicating the passage 4 and the volume chamber 22a.
  • a region where the piston 23 slides on the swash plate 24 and the volume chamber 22a expands is a suction region
  • a region where the piston 23 slides on the swash plate 24 and the volume chamber 22a contracts is a discharge region.
  • the supply port 25a is formed corresponding to the suction area
  • the discharge port 25b is formed corresponding to the discharge area.
  • the electric motor 30 can drive the hydraulic pump 10 to rotate and can generate regenerative power by the rotation of the hydraulic motor 20.
  • the electric power generated by the electric motor 30 is stored in a power storage device (not shown).
  • the electric motor 30 rotationally drives the hydraulic pump 10 using the regenerative power regenerated by the rotation of the hydraulic motor 20 and stored in the power storage device.
  • the plate 40 is a plate-like member in which the hydraulic pump motor 1 and the electric motor 30 are attached to one surface 40 a and the casing 51 of the power transmission mechanism 50 is attached to the other surface 40 b.
  • the power transmission mechanism 50 is provided to face the hydraulic pump motor 1 and the electric motor 30 with the plate 40 interposed therebetween.
  • the plate 40 is recirculated with a through hole (not shown) through which the rotary shaft 2 of the hydraulic pump motor 1 passes, a through hole (not shown) through which the rotary shaft of the electric motor 30 passes, and lubricating oil that has cooled the electric motor 30.
  • the reflux port 42 (see FIG. 3) is formed.
  • the hydraulic pump motor 1 and the electric motor 30 are arranged in a U shape via the plate 40 and the power transmission mechanism 50. Therefore, the total length of the hydraulic drive unit 100 can be shortened by the amount that the hydraulic pump motor 1 and the electric motor 30 are arranged in parallel. Therefore, the mountability of the hydraulic drive unit 100 on the hybrid construction machine can be improved.
  • the hydraulic pump motor 1 may be attached to one surface 40a of the plate 40 and the electric motor 30 may be attached to the other surface 40b of the plate 40 instead of the U-shaped arrangement. Further, the hydraulic pump motor 1 and the electric motor 30 may be arranged in series with the plate 40 interposed therebetween.
  • the power transmission mechanism 50 includes a casing 51 fixed to the plate 40, a first gear 52 that rotates integrally with the rotating shaft 2 of the hydraulic pump motor 1, and a rotating shaft of the electric motor 30.
  • a rotating second gear 53 and an idle gear 54 provided between the first gear 52 and the second gear 53 for transmitting power are provided.
  • the casing 51 accommodates a first gear 52, a second gear 53, and an idle gear 54.
  • the casing 51 is bolted in a state where the open end surface 51 a is in contact with the other surface 40 b of the plate 40.
  • the casing 51 is filled with lubricating oil.
  • the casing 51 has a through hole 51b formed on the end surface opposite to the opening end surface 51a and through which the rotation shaft of the idle gear 54 is inserted.
  • the first gear 52 has a recess 52a formed on the rotating shaft and into which the rotating shaft 2 of the hydraulic pump motor 1 is fitted. Thereby, the first gear 52 rotates integrally with the rotary shaft 2 of the hydraulic pump motor 1.
  • one end of the rotating shaft is rotatably supported on the plate 40 by the first bearing 52b, and the other end of the rotating shaft is rotatably supported on the casing 51 by the second bearing 52c.
  • the second gear 53 has a concave portion 53a formed on the rotation shaft and into which the rotation shaft of the electric motor 30 is inserted. As a result, the second gear 53 rotates integrally with the rotating shaft of the electric motor 30.
  • one end of the rotating shaft is rotatably supported on the plate 40 by the first bearing 53b, and the other end of the rotating shaft is rotatably supported on the casing 51 by the second bearing 53c.
  • the idle gear 54 meshes with each of the first gear 52 and the second gear 53 to transmit power to each other.
  • one end of a rotating shaft is rotatably supported on the plate 40 by a first bearing 54b, and the approximate center of the rotating shaft is rotatably supported on the casing 51 by a second bearing 54c.
  • the other end of the rotating shaft of the idle gear 54 is inserted into the casing 61 of the circulation mechanism 60 through the through hole 51b.
  • the power transmission mechanism 50 can be reduced in size, and the entire hydraulic drive unit 100 can be reduced in size.
  • the reduction ratio between the hydraulic pump motor 1 and the electric motor 30 can be set to an appropriate value.
  • the circulation mechanism 60 has a casing 61 whose inside communicates with the inside of the casing 51 of the power transmission mechanism 50, an impeller 62 as a rotating member that rotates integrally with the idle gear 54 in the casing 61, and the impeller 62 lifted up.
  • a supply flow path 63 that guides the lubricating fluid to the electric motor 30 and a return flow path 64 that returns the lubricating fluid guided to the electric motor 30 into the power transmission mechanism 50 are provided.
  • the casing 61 is fixed in a state in which the opening end surface 61 a is in contact with the casing 51 of the power transmission mechanism 50. Lubricating oil filled in the casing 51 of the power transmission mechanism 50 flows into the casing 61.
  • a third bearing 54 d that rotatably supports the other end of the rotating shaft of the idle gear 54 is provided in the casing 61.
  • the impeller 62 is an impeller 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 that support the idle gear 54.
  • the impeller 62 may be provided anywhere between the first bearing 54b and the third bearing 54d.
  • the impeller 62 rotates when the power transmission mechanism 50 transmits power between the hydraulic pump motor 1 and the electric motor 30, and the lubricating oil in the casing 51 of the power transmission mechanism 50 guided into the casing 61 is placed on the outer periphery. Scoop up. As the rotational speed of the electric motor 30 increases, the rotational speed of the impeller 62 increases. Therefore, as the amount of heat generated by the electric motor 30 increases, the amount of lubricating oil pumped up by the impeller 62 increases.
  • the impeller 62 may be provided so as to rotate integrally with the first gear 52 or the second gear 53 instead of being provided so as to rotate integrally with the idle gear 54. Further, for example, a plurality of impellers 62 may be provided such that the first gear 52 and the second gear 53 are each provided with an impeller 62. That is, the impeller 62 rotates integrally with at least one of the first gear 52, the second gear 53, and the idle gear 54.
  • impeller 62 instead of the impeller 62, another mechanism such as a cylinder driven by the rotation of the idle gear 54 to scoop up the lubricating oil may be provided. That is, any mechanism can be used as long as it can convert the rotational motion of the idle gear 54 and scoop up the lubricating oil.
  • the supply flow path 63 is a pipe that is pulled out from the casing 61 and connected to the outside of the electric motor 30.
  • the supply flow path 63 is drawn from the surface of the casing 61 that faces the outer periphery of the impeller 62.
  • the lubricating oil guided through the supply flow path 63 is supplied to an oil jacket (not shown) formed inside the electric motor 30 to cool the electric motor 30.
  • the reflux channel 64 is a pipe that is drawn out from the electric motor 30 and connected to the reflux port 42 (see FIG. 3) formed in the plate 40.
  • the recirculation flow path 64 recirculates the lubricating oil discharged from the oil jacket of the electric motor 30 into the casing 51 of the power transmission mechanism 50.
  • the supply flow path 63 and the return flow path 64 may be formed inside the casing of the electric motor 30.
  • the electric motor 30 rotates using the electric power previously stored in the power storage device.
  • the rotation shaft 2 of the hydraulic pump motor 1 is rotationally driven via the power transmission mechanism 50 by the rotation of the electric motor 30.
  • the hydraulic pump 10 is switched to a predetermined value in which the tilt angle of the swash plate 14 is larger than zero by the capacity switching actuator.
  • the piston 13 reciprocates in the cylinder 12 as the cylinder block 11 rotates.
  • the hydraulic oil from the tank is sucked into the volume chamber 12 a through the supply port 15 a of the port plate 15.
  • the hydraulic oil discharged from the volume chamber 12 a is guided to the discharge passage 5 through the discharge port 15 b of the port plate 15.
  • the hydraulic oil discharged from the hydraulic drive unit 100 is used for driving the hydraulic actuator, and assists the drive of the hydraulic actuator by the main hydraulic pump.
  • the lubricating 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 pumped up and supplied to the oil jacket of the electric motor 30 through the supply passage 63.
  • the Therefore, the electric motor 30 can be cooled by heat exchange between the lubricating oil and the electric motor 30.
  • the lubricating oil that has cooled the electric motor 30 is recirculated from the oil jacket of the electric motor 30 into the casing 51 of the power transmission mechanism 50 through the recirculation flow path 64.
  • the impeller 62 rotates with the transmission of power by the power transmission mechanism 50, and the lubricating oil is guided to the electric motor 30. Therefore, it is not necessary to provide a cooling system for cooling the electric motor 30 from the outside, so that the cooling mechanism for the electric motor 30 in the hydraulic drive unit 100 can be simplified.
  • the lubricating oil can be supplied and cooled only when the power transmission mechanism 50 is transmitting power, that is, when the electric motor 30 is rotating and generating heat. Therefore, compared with the case where it always cools using the cooling system which cools the electric motor 30 from the outside, a cooling efficiency can be made high.
  • the lubricating oil pumped up by the impeller 62 cools and recirculates the electric motor 30 so that the lubricating oil in the power transmission mechanism 50 circulates. Therefore, the lubricating oil in the power transmission mechanism 50 flows. Therefore, the bearings that support the first gear 52, the second gear 53, and the idle gear 54 are prevented from seizing due to lack of lubricating oil.
  • the hydraulic motor 20 is held by the capacity switching actuator so that the tilt angle of the swash plate 24 becomes zero. Therefore, since the piston 23 does not reciprocate in the cylinder 22, the displacement volume by the piston 23 becomes zero. Accordingly, since the hydraulic motor 20 only idles without supplying or discharging the hydraulic oil, the drive loss of the hydraulic motor 20 can be suppressed.
  • the hydraulic motor 20 when regenerative electric power is generated by the hydraulic oil discharged from the hydraulic actuator, the hydraulic motor 20 is switched to a predetermined value in which the inclination angle of the swash plate 24 is larger than zero by the capacity switching actuator.
  • the piston 23 reciprocates in the cylinder 22 as the cylinder block 21 rotates. Due to the reciprocating motion of the piston 23, the pressurized hydraulic fluid that has returned from the hydraulic actuator through the return passage 6 flows into the volume chamber 22 a through the supply port 25 a of the port plate 25. Then, the piston 23 reciprocates in the cylinder 22 to rotationally drive the cylinder block 21.
  • the hydraulic oil that has flowed into the volume chamber 22a is discharged to the supply / discharge passage 4 through the discharge port 25b of the port plate 25 and is returned to the tank.
  • Rotating shaft 2 rotates integrally with cylinder block 21.
  • the rotation of the rotating shaft 2 is transmitted to the rotating shaft of the electric motor 30 via the power transmission mechanism 50.
  • the electric motor 30 can generate regenerative power and store it in the power storage device.
  • the hydraulic pump 10 is held by the displacement switching actuator so that the tilt angle of the swash plate 14 becomes zero. Therefore, since the piston 13 does not reciprocate within the cylinder 12, the displacement volume by the piston 13 becomes zero. Therefore, since the hydraulic pump 10 merely idles without supplying or discharging the hydraulic oil, the drive loss of the hydraulic pump 10 can be suppressed.
  • the hydraulic drive unit 100 assists the supply of hydraulic oil to the plurality of hydraulic actuators by the main hydraulic pump, the hydraulic drive unit 100 assists the drive of one hydraulic actuator and the hydraulic oil is recirculated from the other hydraulic actuators. There is also a case.
  • a circulation mechanism 60 that cools the electric motor 30 by guiding the lubricating oil in the power transmission mechanism 50 by the rotation of the impeller 62 is provided.
  • the impeller 62 rotates integrally with an idle gear 54 that transmits power between the first gear 52 and the second gear 53. Therefore, when the electric motor 30 rotationally drives the hydraulic pump motor 1, the impeller 62 rotates as power is transmitted by the power transmission mechanism 50, and the lubricating oil is guided to the electric motor 30. Therefore, it is not necessary to provide a cooling system for cooling the electric motor 30 from the outside, so that the cooling mechanism for the electric motor 30 in the hydraulic drive unit 100 can be simplified.
  • the hydraulic drive unit 100 assists the drive of the hydraulic actuator by the main hydraulic pump, but instead of this, the hydraulic actuator may be driven using only the hydraulic drive unit 100.
  • both the hydraulic pump 10 and the hydraulic motor 20 are swash plate type piston pump motors, but other types may be used as long as they are variable displacement types capable of adjusting the suction / discharge capacity to zero.
  • the circulation mechanism 60 may supply lubricating 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)
PCT/JP2013/058254 2012-03-29 2013-03-22 流体圧駆動ユニット WO2013146576A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201380017785.7A CN104220750B (zh) 2012-03-29 2013-03-22 流体压驱动单元
US14/389,319 US20150064030A1 (en) 2012-03-29 2013-03-22 Fluid pressure drive unit
EP13769429.5A EP2848808B1 (en) 2012-03-29 2013-03-22 Fluid pressure drive unit
KR1020147026743A KR101782684B1 (ko) 2012-03-29 2013-03-22 유체압 구동 유닛

Applications Claiming Priority (2)

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

Publications (1)

Publication Number Publication Date
WO2013146576A1 true WO2013146576A1 (ja) 2013-10-03

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ID=49259831

Family Applications (1)

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

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 (1)

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Publication number Priority date Publication date Assignee Title
CN112879256A (zh) * 2021-03-10 2021-06-01 焦秀智 一种可模拟油藏压力的实验装置

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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JP5934543B2 (ja) * 2012-03-29 2016-06-15 Ｋｙｂ株式会社 流体圧駆動ユニット
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