WO2016152402A1 - Dispositif de pompage - Google Patents

Dispositif de pompage Download PDF

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Publication number
WO2016152402A1
WO2016152402A1 PCT/JP2016/056161 JP2016056161W WO2016152402A1 WO 2016152402 A1 WO2016152402 A1 WO 2016152402A1 JP 2016056161 W JP2016056161 W JP 2016056161W WO 2016152402 A1 WO2016152402 A1 WO 2016152402A1
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WO
WIPO (PCT)
Prior art keywords
pump
drive shaft
gear
shaft
pump device
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.)
Ceased
Application number
PCT/JP2016/056161
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English (en)
Japanese (ja)
Inventor
郁也 尾根田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Publication of WO2016152402A1 publication Critical patent/WO2016152402A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

Definitions

  • the present invention relates to a pump device.
  • Patent Document 1 discloses a gear pump including two gears that mesh with each other. When the gear rotates, the hydraulic fluid is sent from the low pressure suction side space to the high pressure discharge space, thereby driving as a pump.
  • the pump drive shaft connected to the motor rotation shaft of the electric motor via the joint is supported at the shaft support portion of the pump housing via the fluid bearing. did.
  • the pump drive shaft is supported on the shaft support portion of the pump housing via a fluid bearing.
  • vibration and noise can be suppressed.
  • FIG. 1 is a cross-sectional view of a pump device of Example 1.
  • FIG. 1 is a cross-sectional view of a pump device of Example 1.
  • FIG. 1 is a cross-sectional view of a pump device of Example 1.
  • FIG. 1 is a view showing a side plate of Example 1.
  • FIG. 3 is a diagram showing a side plate, a drive shaft, and a driven shaft when the pump device of Example 1 is driven.
  • FIG. 3 is a diagram illustrating a pump element housing portion, a drive gear, and a driven gear when the pump device according to the first embodiment is driven.
  • FIG. 3 is a diagram illustrating a drive gear, a driven gear, a drive shaft, and a driven shaft according to the first embodiment.
  • FIG. 3 is a diagram showing the relationship between the hydrodynamic bearing generating groove and the flow of hydraulic fluid in Example 1.
  • FIG. 3 is a diagram showing a state when the pump device of Example 1 is driven.
  • FIG. 3 is a diagram illustrating a side plate, a drive shaft, and a driven shaft according to the first embodiment.
  • FIG. 4 is a cross-sectional view of a pump device of Example 2.
  • FIG. 4 is a cross-sectional view of a pump device of Example 2.
  • FIG. 6 is a diagram showing a state when the pump device of Example 2 is driven.
  • FIG. 1 is a partial cross-sectional view of the pump device 1.
  • 2 is a cross-sectional view taken along the line AA in FIG.
  • FIG. 3 is a cross-sectional view taken along the line BB in FIG.
  • the pump device 1 includes an electric motor 2 and a pump 3.
  • the electric motor 2 rotates the motor rotating shaft 2a during driving.
  • the pump 3 is an external gear pump that is driven by the electric motor 2.
  • the outside of the pump 3 is covered with a pump case 30.
  • the pump case 30 includes a first pump case 30a and a second pump case 30b.
  • a pump unit 31 is accommodated in a low pressure chamber 30c inside the pump case 30.
  • the pump unit 31 has a pump housing 32.
  • the pump housing 32 has a space for a pump element accommodating portion 32a and a high pressure chamber 32b therein.
  • the pump element accommodating portion 32a is formed so as to penetrate in the axial direction (motor rotating shaft direction) of the pump housing 32.
  • An opening on one side in the axial direction of the pump element accommodating portion 32a is closed by a pump cover 33.
  • the opening on the other axial end side of the pump element housing portion 32a is closed by the second pump case 30b.
  • the pump element accommodating portion 32a communicates with the low pressure chamber 30c.
  • the high pressure chamber 32 b is open on the pump cover 33 side, and the opening is closed by the pump cover 33.
  • the high pressure chamber 32b communicates with a discharge port 34 formed in the second pump case 30b.
  • the high pressure chamber 32b communicates with the pump element housing portion 32a.
  • a pump element 35 is accommodated in the pump element accommodating portion 32a.
  • the pump element 35 includes a drive gear 36 and a driven gear 37.
  • the drive gear 36 and the driven gear 37 are external gears, and their external teeth mesh with each other.
  • the drive gear 36 is provided with a drive shaft 38 formed integrally with the drive gear 36.
  • the driven gear 37 is provided with a driven shaft 39 formed integrally with the driven gear 37.
  • the drive shaft 38 is connected to the motor rotating shaft 2a via the joint 40.
  • Side plates 41 are provided in both sides of the drive element 36 and the driven gear 37 in the axial direction in the pump element housing portion 32a. Two side plates 41 are provided, but those having the same shape are used.
  • the side plate 41 is formed with two through holes 41a penetrating in the axial direction. A drive shaft 38 and a driven shaft 39 are inserted into the through holes 41a, respectively.
  • the side plate 41 disposed on the pump cover 33 side is in contact with the side surface of the pump cover 33.
  • the side plate 41 disposed on the second pump case 30b side is in contact with the side surface of the second pump case 30b.
  • Seal grooves 41b are formed on the side surface of the pump cover 33 and the surface of the side plate 41 that contacts the side surface of the second pump case 30b.
  • a seal member 42 is provided in the seal groove 41b. The seal member 42 prevents the hydraulic fluid from flowing from the high pressure chamber 32b to the low pressure chamber 30c side.
  • FIG. 4 is a view showing the side plate 41.
  • FIG. 4 (a) is a view of the side plate 41 as viewed from the pump cover 33 or the second pump case 30b side.
  • FIG. 4B is an axial sectional view of the side plate 41.
  • FIG. 4 (c) is a view of the side plate 41 as viewed from the drive gear 36 and the driven gear 37 side.
  • FIG. 5 is a view showing the side plate 41, the drive shaft 38, and the driven shaft 39 when the pump device 1 is driven.
  • the hydraulic fluid in the low pressure chamber 30c is sent to the high pressure chamber 32b by the rotation of the drive gear 36 and the driven gear 37.
  • the pressure in the high pressure chamber 32b is higher than the pressure in the low pressure chamber 30c. Due to this pressure difference, the drive gear 36 and the driven gear 37 are pressed toward the low pressure chamber 30c, and the drive shaft 38 and the driven shaft 39 formed integrally with the drive gear 36 and the driven gear 37 move toward the low pressure chamber 30c. . Therefore, the gap between the drive shaft 38 and the driven shaft 39 and the through hole 41a has the largest gap (gap C) on the high pressure chamber 32b side and the smallest gap (gap D) on the low pressure chamber 30c side.
  • a hydraulic fluid introduction groove 41c extending in the axial direction is formed on the inner peripheral surface of the through hole 41a.
  • the hydraulic fluid introduction groove 41c is formed at a position shifted in the circumferential direction of the through hole 41a with respect to the position where the gap D is formed.
  • An annular groove 41d is formed over the entire circumference of the through hole 41a at the opening of the through hole 41a on the pump cover 33 or second pump case 30b side. The annular groove 41d communicates with the hydraulic fluid introduction groove 41c.
  • FIG. 6 is a view showing the pump element housing portion 32a, the drive gear 36, and the driven gear 37 when the pump device 1 is driven.
  • the pump device 1 is driven at a low rotation (for example, 2000 [rpm]).
  • a low rotation for example, 2000 [rpm]
  • the drive shaft 38 and the driven shaft 39 are pressed toward the low pressure chamber 30c, and the drive shaft 38 and the driven shaft 39 move toward the low pressure chamber 30c. Therefore, the drive gear 36 and the driven gear 37 also move to the low pressure chamber 30c side.
  • the tooth tips of the drive gear 36 and the driven gear 37 come into contact with the side surface of the pump element accommodating portion 32a on the low pressure chamber 30c side, and the side surfaces are scraped (wiping process).
  • the shape of the side surface of the pump element accommodating portion 32a on the low pressure chamber 30c side can be made to follow the locus of the tooth tips of the drive gear 36 and the driven gear 37.
  • the wipe process is performed not only before the pump device 1 is shipped but also after the vehicle is mounted.
  • the gap between the drive gear 36 and the driven gear 37 and the pump element accommodating portion 32a is the smallest gap (gap E) on the low pressure chamber 30c side.
  • the gap E is set to be smaller than the minimum gap (gap D) between the drive shaft 38 and the driven shaft 39 and the through hole 41a.
  • FIG. 7 shows the drive gear 36, the driven gear 37, the drive shaft 38, and the driven shaft 39.
  • a plurality of hydrodynamic bearing generating grooves 43 are formed on the outer peripheral surfaces of the drive shaft 38 and the driven shaft 39 and in the portion inserted into the through hole 41a of the side plate 41.
  • the hydrodynamic bearing generating groove 43 is formed in a V shape when viewed from the radial direction of the drive shaft 38 and the driven shaft 39.
  • the hydrodynamic bearing generating groove 43 is formed so that the two grooves approach each other in the direction opposite to the rotational direction of the drive shaft 38 and the driven shaft 39, and is connected at the tip thereof.
  • FIG. 8 is a diagram showing the relationship between the hydrodynamic bearing generating groove 43 and the flow of hydraulic fluid.
  • the hydraulic fluid moves along the fluid bearing generation groove 43, and the hydraulic fluid concentrates at the center in the width direction of the fluid bearing generation groove 43.
  • the pressure of the hydraulic fluid at the center portion in the width direction of the hydrodynamic bearing generating groove 43 is higher than the pressure of the hydraulic fluid at portions other than the center portion in the width direction.
  • FIG. 9 is a diagram showing a state when the pump device 1 is driven.
  • the hatching showing the cross section is not drawn, the dark hatching indicates the region of the high-pressure hydraulic fluid, and the thin hatching indicates the region of the low-pressure hydraulic fluid.
  • the arrows indicate the rotation directions of the drive gear 36 and the driven gear 37.
  • FIG. 10 is a view showing the side plate 41, the drive shaft 38, and the driven shaft 39. As shown in FIG. FIG. 10 (a) shows a state when the hydrodynamic bearing is not acting.
  • FIG. 10 (b) shows the state when the hydrodynamic bearing is operating.
  • the hydraulic fluid in the low pressure chamber 30c is sent to the high pressure chamber 32b by the rotation of the drive gear 36 and the driven gear 37. Therefore, the pressure in the high pressure chamber 32b is higher than the pressure in the low pressure chamber 30c. Due to the pressure difference between the high pressure chamber 32b and the low pressure chamber 30c, the drive gear 36 and the driven gear 37 are pressed toward the low pressure chamber 30c.
  • the drive shaft 38 and the driven shaft 39 formed integrally with the drive gear 36 and the driven gear 37 also move to the low pressure chamber 30c side. As the drive shaft 38 moves, the axis of the drive shaft 38 deviates from the axis of the motor rotation shaft 2a.
  • the drive gear 36 and the driven gear 37 are external gears.
  • the tooth tips of the drive gear 36 and the driven gear 37 are pressed against the inner peripheral surface of the pump element housing portion 32a. Accordingly, smooth rotation of the drive gear 36 and the driven gear 37 is hindered, which may lead to an increase in vibration and noise of the pump device 1. Therefore, in the first embodiment, a fluid bearing made of hydraulic fluid is generated between the inner peripheral surface of the through hole 41a of the side plate 41 and the outer peripheral surfaces of the drive shaft 38 and the driven shaft 39, and the drive shaft 38 and The driven shaft 39 is pivotally supported.
  • the hydrodynamic bearing indicates the hydraulic fluid between the inner peripheral surface of the through hole 41a and the outer peripheral surfaces of the drive shaft 38 and the driven shaft 39. Due to the rotation of the drive shaft 38 and the driven shaft 39, the hydraulic fluid moves along the hydrodynamic bearing generating groove 43 due to its own viscosity. Therefore, the hydraulic fluid gathers at the center in the width direction of the hydrodynamic bearing generation groove 43, and the pressure of the hydraulic fluid at the center in the width direction of the hydrodynamic bearing generation groove 43 is higher than the pressure of the hydraulic fluid at the portion other than the center in the width direction. Become.
  • the smallest gap (of the gap between the drive shaft 38 of the drive gear 36 and the through hole 41a in the radial direction of the rotation shaft of the drive shaft 38 ( The gap (D) was made larger than the smallest gap (gap E) among the gaps between the external teeth of the drive gear 36 and the pump element accommodating portion 32a.
  • the gap (D) was made larger than the smallest gap (gap E) among the gaps between the external teeth of the drive gear 36 and the pump element accommodating portion 32a.
  • the clearance between the external teeth of the drive gear 36 and the driven gear 37 and the pump element accommodating portion 32a can be reduced.
  • the leakage of hydraulic fluid from the tooth tips of the drive gear 36 and the driven gear 37 can be suppressed, and the pump efficiency can be improved.
  • the tooth tips of the drive gear 36 and the driven gear 37 abut against the side surface of the pump element housing portion 32a on the low pressure chamber 30c side, and the side surfaces thereof are shaved.
  • the shape of the side surface of the pump element accommodating portion 32a on the low pressure chamber 30c side can be made to follow the locus of the tooth tips of the drive gear 36 and the driven gear 37.
  • the leakage of hydraulic fluid from the tooth tips of the drive gear 36 and the driven gear 37 can be suppressed, and the pump efficiency can be improved.
  • the pump device 1 is driven, the shaft misalignment of the drive shaft 38 and the driven shaft 39 is suppressed by the fluid bearing.
  • a fluid bearing generated by increasing the pressure of the hydraulic fluid by rotating the drive shaft 38 and the driven shaft 39 without depending on an external pump is called a hydrodynamic bearing.
  • the dynamic pressure bearing requires a configuration such as the hydrodynamic bearing generating groove 43 of the drive shaft 38 and the driven shaft 39, but it is not necessary to use an external pump or the like.
  • the depth of the hydrodynamic bearing generation groove 43 is larger than the gap (gap D) at the smallest part of the gap between the drive shaft 38 and the driven shaft 39 on the low pressure chamber 30c side and the through hole 41a.
  • the hydrodynamic bearing generating groove 43 is formed so that the depth of the hydrodynamic bearing generating groove 43 is smaller than the largest gap (gap C) of the gap between the drive shaft 38 and the driven shaft 39 on the high pressure chamber 32b side and the through hole 41a. .
  • the clearance between the drive shaft 38 and the driven shaft 39 on the low pressure chamber 30c side and the through hole 41a is narrower than the clearance between the drive shaft 38 and the driven shaft 39 on the high pressure chamber 32b side and the through hole 41a. Therefore, it is possible to increase the force to push the drive shaft 38 and the driven shaft 39 back toward the high pressure chamber 32b, and to suppress the axial displacement of the drive shaft 38 and the driven shaft 39.
  • the hydraulic fluid introduction groove 41c extending in the axial direction was formed on the inner peripheral surface of the through hole 41a. As a result, the hydraulic fluid can be positively supplied between the drive shaft 38 and the driven shaft 39 and the through hole 41a, and the function of the fluid bearing can be improved.
  • the hydraulic fluid introduction groove 41c is penetrated with respect to a position that is the smallest gap (gap D) among the gaps between the drive shaft 38 and the driven shaft 39 on the low pressure chamber 30c side and the through hole 41a. It was formed at a position shifted in the circumferential direction of the hole 41a.
  • the pressure of the hydraulic fluid in the gap between the drive shaft 38 and the driven shaft 39 on the low pressure chamber 30c side and the through hole 41a is desired to be as high as possible.
  • the hydraulic fluid can be prevented from flowing out of the gap between the drive shaft 38 and the driven shaft 39 on the low pressure chamber 30c side and the through hole 41a from the hydraulic fluid introduction groove 41c.
  • the annular groove 41d is formed over the entire circumference of the through hole 41a in the opening of the through hole 41a on the pump cover 33 or the second pump case 30b side.
  • the hydraulic fluid can be sent from the annular groove 41d to the hydraulic fluid introduction groove 41c, and the hydraulic fluid can be positively supplied between the drive shaft 38 and the driven shaft 39 and the through hole 41a, thereby improving the function of the fluid bearing. Can do.
  • a pump housing 32 having a pump element housing portion 32a, a drive shaft 38 (pump drive shaft) rotatably provided in the pump housing 32, and provided in the pump element housing portion 32a and rotated by the drive shaft 38
  • a pump element 35 that is driven and sucks and discharges hydraulic fluid, an electric motor 2 having a motor rotary shaft 2a connected to the drive shaft 38 via a joint 40, and a pump housing 32 are provided via a fluid bearing.
  • the pump element 35 includes a drive gear 36 (first gear) provided on a drive shaft 38 connected to the motor rotation shaft 2a via the joint 40, and a driven gear 37 (second gear) meshed with the drive gear 36.
  • a gear Therefore, the axial deviation between the drive shaft 38 and the motor rotation shaft 2a is suppressed, the pump element 35 is smoothly rotated, and vibration and noise can be suppressed.
  • the drive gear 36 is an external gear
  • the driven gear 37 has external teeth that mesh with the external teeth of the drive gear 36. Therefore, the axial deviation of the drive gear 36 and the driven gear 37 is suppressed, the pump element 35 can rotate smoothly, and vibration and noise can be suppressed.
  • the gap (gap D) in the smallest part of the gap between the gaps is larger than the gap (gap E) in the smallest part of the gap between the external teeth of the drive gear 36 and the pump element accommodating portion 32a. did.
  • the pump housing 32 is formed such that the inner peripheral surface of the pump element housing portion 32a is scraped by the tooth tip of the drive gear 36. Therefore, leakage of the hydraulic fluid from the tooth tip of the drive gear 36 can be suppressed, and the pump efficiency can be improved.
  • the hydrodynamic bearing is a hydrodynamic bearing. Therefore, it is not necessary to use an external pump or the like, and the apparatus can be simplified.
  • a plurality of fluid bearing generation grooves 43 (grooves) provided on the outer peripheral side of the drive shaft 38 of the drive gear 36 or the inner peripheral side of the through hole 41a are provided.
  • a plurality of fluid bearing generating grooves 43 are formed in the fluid bearing generating grooves 43 along the plurality of fluid bearing generating grooves 43 due to the viscosity of the hydraulic fluid as the drive shaft 38 rotates. The pressure is increased at a predetermined location of the plurality of hydrodynamic bearing generating grooves 43. Therefore, it is not necessary to use an external pump or the like, and the apparatus can be simplified.
  • the plurality of hydrodynamic bearing generating grooves 43 are configured so that the drive shaft 38 of the drive gear 36 in the radial direction of the rotation shaft of the drive shaft 38 is obtained when the drive shaft 38 rotates and the pressure of the hydraulic fluid acts on the pump element 35.
  • the plurality of hydrodynamic bearing generating grooves 43 are formed to have a depth larger than the smallest gap (gap D) of the gaps between the through holes 41a. Therefore, the axial deviation of the drive shaft 38 and the driven shaft 39 can be suppressed.
  • the plurality of hydrodynamic bearing generating grooves 43 are configured so that the drive shaft 38 of the drive gear 36 in the radial direction of the rotation shaft of the drive shaft 38 is obtained when the drive shaft 38 rotates and the pressure of the hydraulic fluid acts on the pump element 35.
  • the depth of the plurality of grooves is made smaller than the largest gap (gap C) of the gaps between the through holes 41a. Therefore, it is possible to increase the force for pushing back the drive shaft 38 and the driven shaft 39 from the low pressure chamber 30c side to the high pressure chamber 32b side, and to suppress the axial displacement of the drive shaft 38 and the driven shaft 39.
  • the through hole 41a is provided on the inner peripheral side of the through hole 41a, and has a hydraulic fluid introduction groove 41c that opens toward the drive shaft 38 and into which hydraulic fluid is introduced. Therefore, the function of the fluid bearing can be improved.
  • the pump element 35 includes a drive gear 36 provided on a drive shaft 38 connected to the motor rotation shaft 2a via a joint 40, and a driven gear 37 that meshes with the drive gear 36.
  • the introduction groove 41c is formed between the drive shaft 38 of the drive gear 36 and the through hole 41a in the radial direction of the rotation shaft of the drive shaft 38 in a state where the drive shaft 38 rotates and the pressure of the hydraulic fluid acts on the pump element 35.
  • the gap is provided at a position shifted from the smallest part in the circumferential direction of the rotation axis of the drive shaft 38. Therefore, it is possible to increase the force for pushing back the drive shaft 38 and the driven shaft 39 from the low pressure chamber 30c side to the high pressure chamber 32b side, and to suppress the axial displacement of the drive shaft 38 and the driven shaft 39.
  • the pump element 35 has a drive gear 36 provided on a drive shaft 38 connected to the motor rotation shaft 2a via a joint 40, and a driven gear 37 that meshes with the drive gear 36, and has a through hole.
  • 41a has an annular groove 41d provided at an end portion on the drive gear 36 side in the rotation axis direction of the drive shaft 38 and communicating with the hydraulic fluid introduction groove 41c.
  • a pump housing 32 having a pump element housing portion 32a, a drive shaft 38 rotatably provided in the pump housing 32, a pump shaft 32 provided in the pump element housing portion 32a, and rotationally driven by the drive shaft 38,
  • the pump element 35 that sucks and discharges the gas and the through hole 41a of the side plate 41 that is provided in the pump housing 32 and supports the drive shaft 38 via a fluid bearing. Therefore, the axial deviation between the drive shaft 38 and the motor rotation shaft 2a is suppressed, the pump element 35 is smoothly rotated, and vibration and noise can be suppressed.
  • FIG. 11 is a cross-sectional view of the pump device 1 in the axial direction.
  • 12 is a cross-sectional view taken along the line AA in FIG.
  • a drive shaft 50, a rotor 51, a cam ring 52, an adapter ring 53, a pressure plate 59 and the like are accommodated in a pump element accommodation portion 55 a in the pump housing 55.
  • the drive shaft 50 is rotatably supported by the pump housing 55.
  • a pulley is connected to the end of the drive shaft 50.
  • the pulley is connected to the drive shaft of the engine via a belt or the like, and the pump device 1 is driven by the drive force of the engine.
  • a rotor 51 is provided on the drive shaft 50 so as to be integrally rotatable.
  • the rotor 51 is formed with a plurality of slits 51a.
  • a plate-like vane 56 having substantially the same width as the axial length of the rotor 51 is inserted into each of the slits 51a so as to advance and retract in the radial direction.
  • a back pressure chamber 51b is provided at the inner diameter side end of each slit 51a. The back pressure chamber 51b is supplied with hydraulic fluid and urges the vane 56 radially outward.
  • the pump housing 55 is formed from a front housing 57 and a rear housing 58.
  • the front housing 57 has a bottomed cup shape.
  • the inner peripheral portion of the front housing 57 having a bottomed cup shape is cylindrical and constitutes a pump element accommodating portion 55a.
  • the bottom of the front housing 57 having a bottomed cup shape constitutes a bottom portion 55b.
  • a disc-shaped pressure plate 59 is accommodated on the bottom 55b.
  • the front housing 57 and the rear housing 58 are fastened and fixed by a plurality of bolts.
  • a rotor 51, a cam ring 52, and an adapter ring 53 are accommodated in the pump element accommodating portion 55a.
  • the rear housing 58 is attached so as to close the opening of the front housing 57.
  • the rear housing 58 is in liquid-tight contact with the rotor 51, the cam ring 52, and the adapter ring 53.
  • the adapter ring 53 is a cylindrical member in which a cam ring housing portion 53a is formed.
  • the adapter ring 53 may have at least an arc-shaped portion so that an accommodation space is formed therein, and the shape viewed from the axial direction is not limited to the O-shape but is a C-shape. It may be formed.
  • a plug member 60 is screwed to the side surface of the front housing 57.
  • a cam spring 61 is held on the plug member 60. The cam spring 61 urges the cam ring 52 in the direction in which the swing amount becomes maximum, and stabilizes the discharge amount (cam ring swing position) at the time of pump start when the pressure is not stable.
  • a cam ring 52 is accommodated in the cam ring accommodating portion 53a of the adapter ring 53.
  • the rotor 51 rotates while the tip of the vane 56 contacts the inner peripheral surface of the cam ring 52 (cam ring inner peripheral surface 52a).
  • the cam ring inner peripheral surface 52a, the rotor 51, and the vane 56 constitute a plurality of pump chambers 70.
  • the rotor 51, the vane 56, and the cam ring 52 constitute a pump element 71.
  • the cam ring 52 is provided in the cam ring housing portion 53a of the adapter ring 53 so as to be movable with respect to the drive shaft 50.
  • a pin 62 is provided between the cam ring 52 and the adapter ring 53.
  • the pin 62 prevents the cam ring 52 and the adapter ring 53 from rotating within the front housing 57.
  • a seal member 63 is provided in the cam ring housing portion 53a of the adapter ring 53.
  • a support plate 64 is provided at a position substantially half a circumference from the position at which the seal member 63 is provided in the cam ring housing portion 53a.
  • the cam ring 52 is swingably provided with a support plate 64 as a fulcrum.
  • the support plate 64 and the seal member 63 separate the first fluid pressure chamber G1 and the second fluid pressure chamber G2 between the cam ring 52 and the adapter ring 53.
  • the first fluid pressure chamber G1 and the second fluid pressure chamber G2 are provided in the cam ring housing portion 53a and on the outer peripheral side of the cam ring 52.
  • the first fluid pressure chamber G1 is provided on the right side in FIG.
  • the second fluid pressure chamber G2 is provided on the left in FIG.
  • the front housing 57 is provided with a control valve 65.
  • the control valve 65 switches the hydraulic fluid supplied into the first fluid pressure chamber G1.
  • the second fluid pressure chamber G2 is always supplied with a working fluid having a suction pressure.
  • the first hydraulic pressure chamber G1 is supplied with hydraulic fluid having a suction pressure.
  • the hydraulic pressure acting on the first fluid pressure chamber G1 and the hydraulic pressure acting on the second fluid pressure chamber G2 are in competition. For this reason, the cam ring 52 swings to the right in FIG. At this time, the discharge capacity per rotation of the pump device 1 increases.
  • the hydraulic fluid having the discharge pressure is supplied to the first fluid pressure chamber G1.
  • the rear housing 58 is formed with a suction port 66 for sucking hydraulic fluid from the outside.
  • the suction port 66 communicates with a region where the capacity of the pump chamber 70 increases as the rotor 51 rotates.
  • the suction port 66 and the pump chamber 70 are connected by a suction passage 68.
  • the front housing 57 is formed with a discharge port 67 for discharging hydraulic fluid to the outside.
  • the discharge port 67 communicates with a region where the capacity of the pump chamber 70 decreases as the rotor 51 rotates.
  • the discharge port 67 and the pump chamber 70 are connected by a discharge passage 69.
  • a plurality of hydrodynamic bearing generating grooves 43 are formed in the outer peripheral surface of the drive shaft 50 and in a portion inserted into the pump housing 55.
  • the hydrodynamic bearing generating groove 43 is formed in a V shape when viewed from the radial direction of the drive shaft 38.
  • the hydrodynamic bearing generating groove 43 is formed so that the two grooves approach each other in the direction opposite to the rotational direction of the drive shaft 38 and the driven shaft 39, and is connected at the tip thereof.
  • FIG. 13 is a view showing a state when the pump device 1 is driven.
  • the hatching indicating the cross section is not drawn
  • the dark hatching indicates the region of the high-pressure hydraulic fluid
  • the thin hatching indicates the region of the low-pressure hydraulic fluid.
  • the arrow indicates the direction of rotation of the drive shaft 50.
  • the rotor 51 Due to the pressure difference between the hydraulic fluid in the high pressure region and the low pressure region, the rotor 51 is pressed toward the low pressure region.
  • the drive shaft 50 formed integrally with the rotor 51 also moves to the low pressure region side.
  • the axis of the drive shaft 50 deviates from the axis of the engine drive shaft. There is a possibility that the rotation of the drive shaft 50 is hindered due to the shaft misalignment, and the smooth rotation of the drive shaft 50 is hindered, leading to an increase in vibration and noise of the pump device 1.
  • the drive shaft 50 is supported by a fluid bearing.
  • the clearance between the drive shaft 50 and the pump housing 55 is narrower on the low pressure region side than on the high pressure region side. Therefore, the pressure of the hydraulic fluid in the gap between the drive shaft 50 and the pump housing 55 is higher on the low pressure side than on the high pressure side.
  • the drive shaft 50 is pushed back to the high pressure region side by the pressure difference of the hydraulic fluid in the gap between the drive shaft 50 and the pump housing 55. As a result, it is possible to suppress the axial deviation between the drive shaft 50 and the drive shaft of the engine, and to reduce the vibration and noise of the pump device 1.
  • a suction port 66 that opens to a region where the volume increases among the plurality of pump chambers 70 as the 51 rotates, and a region where the volume decreases among the plurality of pump chambers 70 provided in the pump housing 55 as the rotor 51 rotates.
  • a discharge port 67 that opens to the pump housing 55, communicates with the suction port 66, and forms a suction region together with the suction port 66, and a discharge that is provided in the pump housing 55 and communicates with the discharge port 67 Passage 69
  • the first fluid pressure provided in the space formed between the pump element accommodating portion 55a and the cam ring 52, the volume of which decreases as the cam ring 52 moves toward the side where the eccentric amount of the cam ring 52 increases.
  • the second fluid pressure chamber G2 provided on the side where the volume increases as the cam ring 52 moves toward the side where the eccentric amount of the chamber G1 and the cam ring 52 increases, and the first fluid pressure chamber G1 provided in the pump housing 55.
  • a control valve 65 that controls the amount of eccentricity of the cam ring 52 by controlling the pressure of the second fluid pressure chamber G2 is provided. Therefore, the shaft deviation of the drive shaft 50 is suppressed, the rotation of the pump element 71 becomes smooth, and vibration and noise can be suppressed.
  • the pump device 1 of the first embodiment has a pair of gears, it may be a tandem type having two pairs of gears or more.
  • the pump device 1 of the first embodiment it is driven by the electric motor 2, but it may be driven by another drive source such as an engine.
  • the pump device 1 is driven by the engine, but may be driven by another drive source such as an electric motor.
  • the present invention may be configured as follows.
  • the pump device A pump housing having a pump element housing; A pump drive shaft rotatably provided in the pump housing; A pump element that is provided in the pump element accommodating portion, is driven to rotate by the pump drive shaft, and sucks and discharges hydraulic fluid;
  • An electric motor having a motor rotation shaft connected to the pump drive shaft via a joint, A shaft support portion provided in the pump housing and supporting the pump drive shaft via a fluid bearing.
  • the pump element may include a first gear provided on the pump drive shaft connected to the motor rotation shaft via the joint, and a second gear meshing with the first gear. A differential pressure between the suction region and the discharge region in the pump housing acts on the gear which is a pump element of the gear pump, and the gear and the pump drive shaft are biased to the suction side.
  • this bias reduces the clearance of the pump drive shaft portion on the suction side, so that the pressure of the fluid in this portion rises and the pump drive shaft is pushed back to suppress the shaft drive shaft misalignment. it can.
  • the first gear is an external gear
  • the second gear may have external teeth that mesh with external teeth of the first gear.
  • the driven side gear internal gear
  • the axis deviation it will directly change the clearance between the gear and the pump housing, so it is desirable to suppress the axis deviation.
  • the axis deviation is suppressed and the pump element rotates smoothly.
  • the pump drive shaft and the shaft of the first gear in the radial direction of the rotation shaft of the pump drive shaft in a state where the pump drive shaft rotates and the pressure of the hydraulic fluid acts on the pump element.
  • the smallest gap among the gaps between the support portions may be formed to be smaller than the smallest gap among the gaps between the external teeth of the first gear and the pump element housing portion. .
  • the pump housing may be formed such that an inner peripheral surface of the pump element housing portion is scraped by a tooth tip of the first gear.
  • wiping treatment of the inner peripheral surface of the pump element housing portion with the tooth tip of the first gear it is possible to adjust to the rotation locus of the tooth tip of the first gear and further suppress leakage at the tooth tip portion.
  • the axial displacement is suppressed by the fluid bearing, thereby suppressing excessive shaving of the inner peripheral surface of the pump element housing portion.
  • the fluid bearing may be a dynamic pressure bearing.
  • the pump device includes a plurality of grooves provided on an outer peripheral side of the pump drive shaft of the first gear or an inner peripheral side of the shaft support portion,
  • the fluid bearing is the hydraulic fluid that moves in the plurality of grooves, and the plurality of grooves cause the hydraulic fluid to flow along the plurality of grooves according to the viscosity of the hydraulic fluid as the pump drive shaft rotates. Then, the pressure may be increased toward the predetermined portion of the groove to increase the pressure at the predetermined portion of the plurality of grooves.
  • the fluid bearing can be configured with a simple structure.
  • the plurality of grooves include the pump drive shaft of the first gear in the radial direction of the rotation shaft of the pump drive shaft and the pump drive shaft in a state where the pressure of the hydraulic fluid acts on the pump element.
  • the plurality of grooves may be formed so that the depth of the plurality of grooves is larger than the smallest gap among the gaps of the shaft support portions. The influence of the pressure increase in the plurality of grooves can be relatively increased on the side where the gap is minimized, and the effect of the hydrodynamic bearing can be improved.
  • the plurality of grooves include the pump drive shaft of the first gear in the radial direction of the rotation shaft of the pump drive shaft and the pump drive shaft in a state where the pressure of the hydraulic fluid acts on the pump element.
  • the depth of the plurality of grooves may be smaller than the largest gap among the gaps between the shaft support portions. Increase the biasing force on the pump drive shaft from the minimum side to the maximum side of the gap by making the influence of the pressure rise in the plurality of grooves relatively small on the side where the gap is the maximum compared to the side where the gap is the minimum be able to.
  • the shaft support portion may be provided on an inner peripheral side of the shaft support portion, and may have a hydraulic fluid introduction groove that opens toward the pump drive shaft side and into which the hydraulic fluid is introduced.
  • the fluid bearing function can be improved by positively introducing the working fluid through the working fluid introduction groove.
  • the pump element includes a first gear provided on the pump drive shaft connected to the motor rotation shaft via the joint, and a second gear meshing with the first gear,
  • the hydraulic fluid introduction groove includes the pump drive shaft of the first gear in the radial direction of the rotary shaft of the pump drive shaft in a state where the pump drive shaft rotates and the pressure of the hydraulic fluid acts on the pump element.
  • the pump element includes a first gear provided on the pump drive shaft connected to the motor rotation shaft via the joint, and a second gear meshing with the first gear
  • the shaft support portion may include an annular groove that is provided at an end portion on the first gear side in the rotation axis direction of the pump drive shaft and communicates with the hydraulic fluid introduction groove. The working fluid can be effectively introduced into the working fluid introduction groove through the annular groove.
  • a pump device comprising: A pump housing having a pump element housing; A pump drive shaft rotatably provided in the pump housing; A pump element that is provided in the pump element accommodating portion, is driven to rotate by the pump drive shaft, and sucks and discharges hydraulic fluid; Have A shaft support portion provided in the pump housing and supporting the pump drive shaft via a fluid bearing. The smaller the clearance between the pump drive shaft and the portion of the housing that supports the pump rotation shaft, the higher the fluid pressure, and the pump drive shaft is pushed back in a direction in which the clearance becomes uniform. Therefore, rotation of the pump element becomes smooth and vibration or noise can be suppressed.
  • the pump element may include a first gear provided on the pump drive shaft, and a second gear meshing with the first gear.
  • a differential pressure between the suction region and the discharge region in the pump housing acts on the gear which is a pump element of the gear pump, and the gear and the pump drive shaft are biased to the suction side.
  • this bias reduces the clearance of the pump drive shaft portion on the suction side, so that the pressure of the fluid in this portion rises and the pump drive shaft is pushed back to suppress the shaft drive shaft misalignment. it can.
  • the first gear is an external gear
  • the second gear may have external teeth that mesh with external teeth of the first gear.
  • the smallest gap among the gaps between the support portions may be formed to be smaller than the smallest gap among the gaps between the external teeth of the first gear and the pump element housing portion. .
  • the pump housing may be formed such that an inner peripheral surface of the pump element housing portion is scraped by a tooth tip of the first gear.
  • the axial displacement is suppressed by the fluid bearing, thereby suppressing excessive shaving of the inner peripheral surface of the pump element housing portion.
  • the level difference between the portion to be cut and the portion not to be cut is reduced, and leakage at the tooth tip portion can be further suppressed.
  • the pump element includes a first gear provided on the pump drive shaft connected to the motor rotation shaft via the joint, and a second gear meshing with the first gear, A plurality of grooves provided on the outer peripheral side of the pump drive shaft of the first gear or on the inner peripheral side of the shaft support portion;
  • the fluid bearing is the hydraulic fluid that moves in the plurality of grooves, and the plurality of grooves causes the hydraulic fluid to flow along the plurality of grooves according to the viscosity of the hydraulic fluid as the pump drive shaft rotates. You may make it move toward the predetermined location of the said groove
  • the fluid bearing can be configured with a simple structure.
  • the plurality of grooves include the pump drive shaft of the first gear in the radial direction of the rotation shaft of the pump drive shaft and the pump drive shaft in a state where the pressure of the hydraulic fluid acts on the pump element. You may form so that the depth of the said some groove
  • the influence of the pressure increase in the plurality of grooves can be relatively increased on the side where the gap is minimized, and the effect of the hydrodynamic bearing can be improved.
  • the plurality of grooves include the pump drive shaft of the first gear in the radial direction of the rotation shaft of the pump drive shaft and the pump drive shaft in a state where the pressure of the hydraulic fluid acts on the pump element.
  • the pump device includes: An annular cam ring movably provided in the pump element accommodating portion; A rotor provided on the pump drive shaft, disposed in the cam ring, and formed by arranging a plurality of slits extending in a substantially radial direction in the circumferential direction; A vane provided in the slit so as to freely advance and retract, and forms a plurality of pump chambers together with the cam ring and the rotor; An inlet provided in the pump housing and opening to a region of the plurality of pump chambers whose volume increases with rotation of the rotor; A discharge port that is provided in the pump housing and opens to a region where the volume of the plurality of pump chambers decreases as the rotor rotates; A suction passage provided in the pump housing, communicating with the suction port, and forming a suction region together with the suction port; A discharge passage provided in the pump housing and communicating with the discharge port; A first fluid pressure chamber provided between the pump element housing portion and the cam
  • variable displacement vane pump has one suction area and one discharge area, and pressure acts on the pump drive shaft from the discharge side to the suction side, resulting in axial displacement of the pump drive shaft. The pump drive shaft is pushed back. As a result, the rotation of the pump becomes smooth, and vibration or noise can be suppressed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne un dispositif de pompage conçu de façon à permettre une réduction des vibrations et du bruit. Un arbre d'entraînement de pompe relié à l'arbre rotatif d'un moteur électrique par l'intermédiaire d'une articulation est supporté au niveau d'une partie de support rotative d'un carter de pompe par l'intermédiaire d'un palier fluide.
PCT/JP2016/056161 2015-03-23 2016-03-01 Dispositif de pompage Ceased WO2016152402A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015059455A JP2016180313A (ja) 2015-03-23 2015-03-23 ポンプ装置
JP2015-059455 2015-03-23

Publications (1)

Publication Number Publication Date
WO2016152402A1 true WO2016152402A1 (fr) 2016-09-29

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Application Number Title Priority Date Filing Date
PCT/JP2016/056161 Ceased WO2016152402A1 (fr) 2015-03-23 2016-03-01 Dispositif de pompage

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JP (1) JP2016180313A (fr)
WO (1) WO2016152402A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021102616A1 (de) * 2021-02-04 2022-08-04 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Lenksystem für Fahrzeug, insbesondere Nutzfahrzeug

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50156006A (fr) * 1974-06-06 1975-12-16
JPS56135780A (en) * 1980-03-27 1981-10-23 Matsushita Electric Ind Co Ltd Compressor
JPH046785U (fr) * 1990-05-08 1992-01-22
JPH09200997A (ja) * 1996-01-22 1997-07-31 Tokyo Parts Ind Co Ltd 小型モータの回転支承構造及びその回転支承部の形成方法
US6213745B1 (en) * 1999-05-03 2001-04-10 Dynisco High-pressure, self-lubricating journal bearings
JP2003520339A (ja) * 2000-01-21 2003-07-02 コルテック・インダストリーズ・インコーポレイテッド ハイブリッド軸受
JP2004346783A (ja) * 2003-05-21 2004-12-09 Hitachi Constr Mach Co Ltd ギアポンプ
JP2008240621A (ja) * 2007-03-27 2008-10-09 Toyota Motor Corp ギヤポンプの慣らし方法及びその装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50156006A (fr) * 1974-06-06 1975-12-16
JPS56135780A (en) * 1980-03-27 1981-10-23 Matsushita Electric Ind Co Ltd Compressor
JPH046785U (fr) * 1990-05-08 1992-01-22
JPH09200997A (ja) * 1996-01-22 1997-07-31 Tokyo Parts Ind Co Ltd 小型モータの回転支承構造及びその回転支承部の形成方法
US6213745B1 (en) * 1999-05-03 2001-04-10 Dynisco High-pressure, self-lubricating journal bearings
JP2003520339A (ja) * 2000-01-21 2003-07-02 コルテック・インダストリーズ・インコーポレイテッド ハイブリッド軸受
JP2004346783A (ja) * 2003-05-21 2004-12-09 Hitachi Constr Mach Co Ltd ギアポンプ
JP2008240621A (ja) * 2007-03-27 2008-10-09 Toyota Motor Corp ギヤポンプの慣らし方法及びその装置

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