WO2006095673A1 - Pompe a palettes - Google Patents

Pompe a palettes Download PDF

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Publication number
WO2006095673A1
WO2006095673A1 PCT/JP2006/304245 JP2006304245W WO2006095673A1 WO 2006095673 A1 WO2006095673 A1 WO 2006095673A1 JP 2006304245 W JP2006304245 W JP 2006304245W WO 2006095673 A1 WO2006095673 A1 WO 2006095673A1
Authority
WO
WIPO (PCT)
Prior art keywords
plate
side plate
rotor
vane
side plates
Prior art date
Application number
PCT/JP2006/304245
Other languages
English (en)
Japanese (ja)
Inventor
Yoshikazu Ishii
Original Assignee
Toyota Jidosha Kabushiki Kaisha
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 Toyota Jidosha Kabushiki Kaisha filed Critical Toyota Jidosha Kabushiki Kaisha
Priority to EP06728664A priority Critical patent/EP1857679A1/fr
Priority to US11/885,783 priority patent/US20080159898A1/en
Publication of WO2006095673A1 publication Critical patent/WO2006095673A1/fr

Links

Classifications

    • 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
    • F04C2/3446—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 the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid

Definitions

  • the present invention relates to a vane pump having a pair of side plates on both sides of a rotor.
  • Pumps that generate fluid pressure include trochoid pumps, gear pumps, piston pumps, and the like.
  • a vane pump known as one form of such a pump is used, for example, as a pump for supplying pressurized fluid to a power steering device of an automobile.
  • This vane pump generally has a cam ring in which an elliptical through hole is formed.
  • the cam ring houses a rotor that is rotated by a drive shaft.
  • the rotor is provided with a plurality of vane grooves arranged radially, and the vanes are slidably accommodated in the vane grooves.
  • Patent Document 1 proposes the following technique! According to Patent Document 1, in a vane pump having a movable side plate on one side, a pressurized fluid having a pressure Pout discharged from the working chamber is caused to flow into a vane back pressure chamber provided at the bottom of the vane groove in the pump suction section. The pressurized fluid at the pressure Pout is further pressurized to the pressure Pv when each vane is pressed against the inner peripheral surface of the cam ring in the pump discharge section. After that, pressurizing fluid of this pressure Pv is applied to the movable side plate. Let it flow into the back pressure chamber. In this vane pump, since the pressure Pv is larger than the pressure Poul :, the movable side plate is urged from the back pressure chamber side to the rotor and vane side. As a result, the side clearance can be reduced and maintained.
  • Patent Document 1 Japanese Patent Laid-Open No. 6-207587
  • the shape of the back pressure chamber is often determined in consideration of ease of processing. Therefore, the side clearance is relatively wide because the effect of urging the movable side plate becomes insufficient. This is because if the target is specialized for high-viscosity fluids or specialized for low-pressure use, it can be established as a pump if some degree of side plate stagnation is acceptable. However, if a low-viscosity fluid such as light oil is pressurized with such a vane pump and the pressure is increased, the movable side plate will stagnate and a large amount of fluid will leak. For this reason, it is impossible to pump the fluid whose pressure has been increased by the pump.
  • the fixed side plate may be deformed by the internal pressure of the pump when the pump is operated. If the side clearance increases due to this deformation, the amount of leak of pressurized fluid will increase. Therefore, similarly, the fluid made into high pressure with a pump cannot be supplied.
  • the present invention has been made in view of the above problems, and suppresses the stagnation of the side plate at the time of assembly and minimizes the deformation of the side plate even when the pump is operated.
  • An object of the present invention is to provide a vane pump that can be maintained at a low temperature.
  • a vane pump according to the present invention is housed in a casing, in each of a cam ring, a rotatable rotor disposed in the cam ring, and a plurality of vane grooves formed radially in the rotor.
  • a vane pump comprising a plurality of vanes that slide along the cam surface of the cam ring as it rotates, and side plates disposed on both sides of the rotor and vanes, wherein the side plates are moved relative to the rotor. It has the same rigidity and symmetrical arrangement.
  • the side plates fixed to both side surfaces of the rotor and the vane have a symmetrical structure with the rotor interposed therebetween. Therefore, it occurs when fixed to the side of the cam ring with bolts Small deformation near the shaft center and deformation due to the internal pressure of the pump are symmetrical with the rotor sandwiched between the side plates.
  • the pressure distribution of the pressurized fluid exerted on both sides of the rotor and the vane can be maintained symmetrically. Therefore, the deformation of the rotor and the vane can be suitably suppressed, and the seizure of the high surface pressure state caused by the contact of the rotor and the vane with the side plate can be suppressed.
  • each of the combination side plates may be formed of the same member and in the same shape. As a result, the symmetry between the pair of first plates deformed by the pump internal pressure or the like can be further enhanced.
  • the present invention provides a back pressure chamber in which each of the side plates is a combined side plate made up of a first plate and a second plate, and a pressurized fluid flows between the first plate and the second plate. You may have.
  • the side plate can be processed separately as two parts, the first plate and the second plate, so that the side plate forming the back pressure chamber can be easily processed at low cost.
  • the vane pump according to the present invention is housed in each of a cam ring, a rotatable rotor arranged in the cam ring, and a plurality of vane grooves arranged radially in the rotor.
  • a vane pump comprising a plurality of vanes that slide along the cam surface of the cam ring as the rotor rotates, and side plates disposed on both sides of the rotor and the vane. It is characterized by inserting a bolt into at least one central hole.
  • a compressive force can be applied to the first plate by tightening the connecting bolt that fastens the first plate and the second plate.
  • the rigidity of the first plate can be increased, so that deformation of the first plate due to the internal pressure of the pump can be suppressed.
  • each of the side plates is a connection-type combination side plate in which a first plate and a second plate are integrated with a connection bolt, and the connection bolt is inserted into a center hole of the second plate. Further, it may be fastened to a female screw formed in the center hole of the first plate. As a result, the rigidity in the vicinity of the center hole of the first plate can be increased.
  • the connecting bolt may be a hollow bolt. This allows the rotor to A combination side plate can be arranged on the vane pump while avoiding interference with the coupled drive shaft.
  • the present invention may further include a back pressure chamber for allowing a pressurized fluid to flow between the first plate and the second plate.
  • a back pressure chamber for allowing a pressurized fluid to flow between the first plate and the second plate.
  • connection-type combination side plate and the cam ring are fastened with fixing bolts arranged on an outer peripheral portion, and the connection bolt is tightened to bring the first plate near the center hole.
  • a compressive force may be applied in advance.
  • the coupled combination side plate is bolted to the side of the force muffling near the outer periphery, the vicinity of the center hole of the first plate tends to deform toward the rotor due to the influence of the tightening force.
  • both of the side plates may be the connection type combination side plates.
  • these side plates When both side plates are connected combination side plates, these side plates have a symmetrical structure with the rotor in between. Therefore, it is possible to maintain the symmetry of the pressure distribution of the fluid acting on both sides of the rotor and vane.
  • one of the side plates may be the connection-type combination side plate, and the other may be the combination side plate.
  • the symmetry of the distribution can be ensured.
  • the deformation of the rotor and the vane can be preferably suppressed, and the rotor and the vane coming into contact with each first plate can suppress the seizure in a high surface pressure state.
  • one of the side plates may be the connection-type combination side plate, and the other may be a movable side plate that is slidable in the axial direction.
  • the flatness of the contact surface between the movable side plate and the rotor and the vane can also be set to be deviated.
  • one of the side plates is a movable combination side plate that is slidable in the axial direction
  • the other may be the combination side plate. Due to the above structure, the movable combination side plate can increase the rigidity in the vicinity of the shaft center and suppress the deformation of the first plate, like the connection type combination side plate. Further, the flatness of the contact surface between the movable combination side plate and the rotor and vane can be set to be offset.
  • one of the side plates may be a movable combination side plate that is slidable in the axial direction, and the other may be the coupled combination side plate.
  • the amount of tightening of the connecting bolt 9 can also be set on the combination side plate side, so the degree of freedom for changing the rigidity is high.
  • one of the side plates may be a movable combination side plate that is slidable in the axial direction, and the other may be the movable side plate.
  • the flatness of the contact surface with the rotor and vane can also be set to be offset.
  • one of the side plates may be a movable combination side plate that is slidable in the axial direction. Further, in this case, since these side plates have a symmetrical structure with the rotor interposed therebetween, the symmetry of the pressure distribution of the fluid acting on both sides of the mouth and the vane can be maintained.
  • FIG. 1 is an external view of a vane pump according to the present invention.
  • FIG. 2 is a cross-sectional view of a vane pump according to the present invention.
  • FIG. 3 is a cross-sectional view showing an example in which both of a pair of side plates of the boosting section of the vane pump according to the present invention are combined side plates.
  • FIG. 4 is a cross-sectional view taken along the line AA in FIG. 3, of the pressure increasing part of the vane pump according to the present invention.
  • FIG. 5 is an explanatory view of a combination side plate of the vane pump according to the present invention.
  • FIG. 6 is a cross-sectional view showing an example in which both side plates of the pressure increasing portion of the vane pump according to the present invention are connected to combined side plates.
  • FIG. 7 is a cross-sectional view showing an example in which one of the side plates of the booster section of the vane pump according to the present invention is a coupled combination side plate and the other is a combination side plate.
  • FIG. 8 is a cross-sectional view showing an example in which one of the side plates of the boosting section of the vane pump according to the present invention is a coupled combination side plate and the other is a movable side plate.
  • FIG. 9 is a cross-sectional view showing an example in which one of the side plates is a movable combination side plate and the other side plate is a combination side plate of the pressure increasing unit of the vane pump according to the present invention.
  • FIG. 10 is a cross-sectional view showing an example in which one of the side plates is a movable combination side plate and the other is a coupled combination side plate of the pressure increasing portion of the vane pump according to the present invention.
  • FIG. 11 is a cross-sectional view showing an example in which one of the side plates is a movable combination side plate and the other is a movable side plate of the pressure increasing unit of the vane pump according to the present invention.
  • FIG. 12 is a cross-sectional view showing an example in which both side plates of the pressure increasing section of the vane pump according to the present invention are movable combination side plates.
  • FIG. 1 is an external view of the vane pump 100.
  • the casing of the vane pump 100 is formed by fixing the head flange cover 10 to the center case 11 by press-fitting or bolt fastening or the like, and fixing the case rear cover 12 to the center case 11 by fastening bolts 13 or the like.
  • FIG. 2 is a cross-sectional view of the vane pump 100 of FIG.
  • the vane pump 100 houses a booster in the housing.
  • FIG. 3 is a cross-sectional view of the boosting unit, and shows a part surrounded by a circle in FIG.
  • a front combination side plate 3a and a rear combination side plate 7a are arranged on both sides of the cam ring 18.
  • the front cover 15 is arranged on the side surface of the front combination side plate 3a.
  • the rear cover 16 is disposed on the side surface of the rear combination side plate 7a.
  • the front combination side plate 3a includes a first front plate la and a second front plate 2a.
  • the rear combination side plate 7a includes a first rear plate 5a and a second rear plate 6a.
  • FIG. 4 is a cross-sectional view taken along the line AA of the booster in FIG. As shown in FIG. 4, the cam ring 18 has a through hole formed in an elliptical shape, and a rotor 19 is accommodated in the cam ring 18.
  • a plurality of grooves formed radially in the radial direction are arranged on the outer circumferential surface at equal intervals in the circumferential direction.
  • Each groove accommodates a vane 20 that is slidable in the radial direction.
  • the vane 20 is constantly pressed against the inner peripheral surface of the cam ring 18 by being urged in the radial direction by centrifugal force or the like.
  • the rotor 19 is connected to the drive shaft 21 by fitting a drive shaft 21 having a corresponding spline shaft into a spline hole formed at the center of rotation, and the drive shaft 21 is connected to a power source of an internal combustion engine or the like. It is rotated by.
  • a working chamber 23 is formed in a space surrounded by the two adjacent vanes 20 and the cam ring 18. As shown in FIG. 3, the axial wall surfaces of the working chamber 23 are the first front plate la and the first rear plate 5a. Since the inner peripheral surface of the through hole having the elliptical shape of the cam ring 18 constitutes a part of the wall surface of the working chamber 23, the volume of the working chamber 23 is expanded or contracted with rotation.
  • the first rear plate 5a is formed with a suction port 24 for sucking fluid into the vane pump and a discharge port 25 for discharging pressurized fluid to the outside.
  • the suction port 24 is formed at a position corresponding to the working chamber 23 in the radial direction at a position where a suction force is generated by expanding the volume of the working chamber 23 in the circumferential direction.
  • the discharge port 25 is formed at a position where pressure is generated by reducing the volume of the working chamber 23 in the circumferential direction, and is formed at a position corresponding to the working chamber 23 in the radial direction.
  • the front combination side plate 3a and the rear combination side plate 7a are fixed to the side surfaces of the cam ring 18 with the fastening bolts 17 respectively, the first front plate la is shown in FIG. As shown in (a), the vicinity of the center hole 26 may be deformed to the rotor side. The same applies to the first rear plate 5a. Further, when the pump is operated, the first front plate la and the first rear plate 5a may be deformed by the pump internal pressure.
  • the front combination side plate 3a and the rear combination side plate 7a have a symmetrical structure with the rotor 19 interposed therebetween. Furthermore, these combination side plates are made of the same material and have the same shape and the same rigidity.
  • a through hole having a step portion on the inner peripheral surface is formed in the second front plate 2a.
  • the front back pressure chamber 4 is formed by the cylindrical space formed by the step portion on the inner peripheral surface and the wall surface of the first front plate la on the second front plate 2a side.
  • a through hole having a step portion is also formed in the second rear plate 6a, and a cylindrical rear back pressure chamber 8 is formed.
  • the front back pressure chamber 4 and the rear back pressure chamber 8 are not illustrated in the discharge port 25 of FIG. 4 respectively. They are communicated with each other through a communication passage, and a pressurized fluid is introduced into each back pressure chamber.
  • the back pressure chambers 4 and 8 are respectively connected to the first side plates. Since the front plate la and the second front plate 2a or the first rear plate 5a and the second rear plate 6a can be processed separately, the side plate forming the back pressure chamber can be easily and inexpensively manufactured.
  • FIG. 6 is a cross-sectional view of the booster, which can be accommodated in the circled part of FIG. 2 in place of the booster shown in FIG.
  • the front combination side plate 3b includes a first front plate lb and a second front plate 2b.
  • the rear combination side plate 7b is composed of a first rear plate 5b and a second rear plate 6b.
  • the second front plate 2b is formed with a through hole having a step portion on the inner peripheral surface.
  • the front back pressure chamber 4 is formed by the cylindrical space formed by the step on the inner peripheral surface and the wall surface of the first front plate lb on the second front plate 2b side.
  • a through hole having a stepped portion is formed in the second rear plate 6b to form a cylindrical rear back pressure chamber 8.
  • the front back pressure chamber 4 and the rear back pressure chamber 8 are respectively connected to the discharge port 25 of FIG. 4 through a communication path (not shown), and pressurized fluid having a high pressure flows into each back pressure chamber.
  • a through hole is formed in the shaft center of each of the first front plate lb and the first rear plate 5b, and a female screw 14 is formed in the through hole.
  • a counterbore 32 that accommodates the bolt head of the connecting bolt 9 is formed on the shaft center of the side surface of the front cover 15 of the second front plate 2b.
  • a counterbore 32 for receiving the bolt head of the connecting bolt 9 is formed on the shaft center side surface of the second cover plate 6b on the side of the rear cover 16.
  • the connecting bolt 9 integrally connects the first front plate lb and the second front plate 2b. Similarly, the connecting bolt 9 integrally connects the first rear plate 5b and the second rear plate 6b.
  • the connecting bolt 9 is hollow, and the drive shaft 21 is accommodated in the connecting bolt 9.
  • the first front plate lb and the rear combination side plate 7b are fixed to the side surfaces of the cam ring 18 with the fastening bolts 17 respectively, if there is no connecting bolt 9, the first front plate lb and In the same manner as the deformation shown in FIG. 5 (a), the first rear plate 5b may be deformed in the vicinity of the center hole 26 toward the rotor 19 side.
  • the symmetry of the fluid pressure exerted on both sides of the rotor 19 and the vane 20 may be lost, and as a result, the rotor 19 and the vane 20 are tilted around the center hole 26 as a fulcrum. There is a case.
  • the position and amount of the gap between the rotor 19 and the vane 20 and each side plate are unclear.
  • the position and amount of this gap change with the rotation of the rotor 19 and the vane 20 when the pump is operated, and thus cannot be grasped.
  • the rotor 19 and the vane 20 may come into contact with the first front plate lb or the first rear plate 5b, resulting in high surface pressure and seizure.
  • the connecting bolt 9 is tightened in the vicinity of the center hole 26 of the first front plate lb and the first rear plate 5b in the direction opposite to the above deformation.
  • the deformation can be suppressed to a certain level.
  • the symmetry of the first side clearance 22a and the second side clearance 22b on both sides of the rotor 19 can be ensured at a certain level.
  • the distribution of fluid pressure exerted on both side surfaces of the rotor 19 and the vane 20 can be maintained symmetrically, and seizure of the rotor 19 and the vane 20 can be suppressed.
  • the first side clearance 22a and the second clearance 22b can be obtained. It is possible to set the tightening amount of the connecting bolt 9 that can guarantee a certain amount. Further, by applying a compressive force by tightening the connecting bolt 9, it is possible to increase the rigidity of the central hole vicinity 26 of the first front plate lb and the first rear plate 5b.
  • the first side clearance 22a and the second side clearance 22b are made somewhat wide to prevent seizure between the side plate and the rotor 19 and the vane 20.
  • these side clearances can be further reduced where necessary.
  • the connection bolt 9 is tightened. Since the rigidity of the first front plate lb and the first rear plate 5b, which are part of the side plate, can be changed depending on the amount of insertion, there is a high degree of freedom in changing the side plate stiffness.
  • the front combination side plate 3b and the rear combination side plate 7b sandwiching the rotor 19 have a symmetrical structure. Therefore, in this embodiment as well, the both sides of the rotor 19 and the vane 20 are covered. The distribution of the fluid pressure can be secured symmetrically, and seizure of the rotor can be prevented.
  • Example 1 since the first front side plate 3b can be separated into two members, ie, the first front plate lb and the second front plate 2b, parts processing for forming the front back pressure chamber 4 is easy. The same applies to the first rear side plate 7b. For this reason, parts are inexpensive and suitable for mass production.
  • the front combination side plate 3b and the rear combination side plate 7b may be the same member and have the same rigidity.
  • the connecting bolt 9 may be an appropriate bolt instead of a hollow bolt according to the structure of the vane pump to be applied!
  • FIG. 7 is a cross-sectional view of a boosting unit including a front combination side plate 3b in one of a pair of side plates.
  • This booster can be accommodated in the circled portion of FIG. 2 in place of the booster shown in FIG. Further, this boosting unit is obtained by replacing the front combination side plate 3a of the boosting unit shown in FIG. 3 with the front combination side plate 3b of the boosting unit of the second embodiment.
  • the second embodiment is different from the second embodiment in contrast to the deformation shown in FIG. 5 (a).
  • the deformation of the vicinity of the center hole 26 of the front plate lb can be suppressed by tightening the connecting bolt 9.
  • the tightening of the connecting bolt 9 can increase the rigidity of the vicinity of the center hole 26 and suppress deformation due to the internal pressure of the pump, so that the side clearance 22a can be further reduced.
  • the booster shown in FIG. 8 is provided with a rear ring 29a that can accommodate the front plate 5c on the side surface of the cam ring 18 instead of the rear combination side plate 7a of FIG. It contains 5c.
  • the first rear plate 5c is a movable side plate that is slidable in the axial direction.
  • a second rear plate 6c is provided on the opposite side of the rear ring 29a from the cam ring 18.
  • the second rear plate 6c is a cylindrical member, and a step portion is formed on the inner peripheral surface. The space formed in the step on the inner peripheral surface is opposite to the rotor of the second rear plate 6c.
  • a rear back pressure chamber 8 is formed with the side wall, and pressurized fluid is introduced through a communication path (not shown). Further, the second rear plate 6c accommodates a movable side plate set spring 27a in a cylinder. The first rear plate 5c is urged toward the rotor 19 by the pressure of the movable side plate set spring 27a and the pressurized fluid.
  • the deformation of the first front plate lb as shown in Fig. 5 (a) and the deformation of the first front plate lb and the first rear plate 5c due to the internal pressure of the pump are described above. Similar to the booster shown in FIG. 7, it can be suppressed by tightening the connecting bolt 9. As a result, as in the case described above, it is possible to ensure the symmetry of the distribution of the fluid pressure exerted on both sides of the rotor 19 and the vane 20. 7 and 8, the combination of the pair of side plates sandwiching the rotor 19 may have a structure in which the front side plate and the rear side plate are interchanged.
  • the booster shown in FIG. 9 is provided with a rear ring 29b capable of accommodating a side plate in one of a pair of side plates, and a rear movable combination side plate 7d accommodated in the rear ring 29b.
  • the rear movable combination side plate 7d is configured such that the combination side plate 7b of the booster shown in FIGS. 6 to 8 is slidable in the axial direction.
  • the booster shown in FIG. 9 can be accommodated in the circled part of FIG. 2 in place of the booster shown in FIG. Further, the booster unit replaces the rear combination side plate 7a of the booster unit of Example 1 shown in FIG.
  • a rear movable combination side plate 7d provided in the booster shown in FIG. 9 is obtained by integrally fixing a first rear plate 5d and a second rear plate 6d with a connecting bolt 9.
  • the third rear plate 31 is a cylindrical member that forms a rear back pressure chamber 8 therein and accommodates a movable side plate set spring 27b.
  • a pressurized fluid is allowed to flow into the rear back pressure chamber 8 through a communication path (not shown).
  • the rear movable combination side plate 7d is urged toward the rotor 19 by the pressure of the pressurized fluid and the movable side plate set spring 27b.
  • the deformation of the second rear plate 5d due to the internal pressure of the pump can be suppressed by increasing the rigidity as in the boosting part of FIG. Also, considering the deformation of the first front plate la and the first rear plate 5d on both sides of the rotor 19, tighten the connecting bolt 9 with an appropriate amount. In the same manner, the symmetry of the distribution of the fluid pressure exerted on both sides of the rotor 19 and the vane 20 can be ensured. Further, by providing the rear movable combination side plate 7d operable in the axial direction, the flatness of the contact surface with the rotor 19 and the vane 20 can be set to be offset.
  • the booster shown in FIG. 10 includes a rear movable combination side plate 7d on one side and the above-described front combination side plate 3b on the other side. Even in the case of this booster, deformation of the first front plate lb as shown in FIG. 5 (a) can be suppressed. Further, deformation of the first front plate lb and the first rear plate 5d due to the pump internal pressure can be suppressed with increased rigidity. Also, by tightening the connecting bolt 9 in anticipation of deformation of the first front plate lb and the first rear plate 5d on both sides of the rotor 19, the fluid pressure acting on both sides of the rotor 19 and the vane 20 is similarly reduced. Distribution symmetry can be ensured. Further, similarly to the booster shown in FIG.
  • the flatness of the contact surface with the rotor 19 and the vane 20 can be set to be deviated. Furthermore, since the tightening amount of the connecting bolt 9 can be set by both the first front plate lb and the first rear plate 5d, the degree of freedom in changing the rigidity is high.
  • the booster shown in FIG. 11 is provided with a front movable combination side plate 3d on one side and a first rear plate 5c which is a movable side plate on the other side.
  • This front movable combination side plate 3d is structurally identical to the rear movable combination side plate 7d of the booster shown in FIG. Even in the case of this boosting portion, the deformation of the first front plate Id and the first rear plate 5c on both sides of the rotor 19 is anticipated, and the connecting bolt 9 is tightened with an appropriate amount, so that the rotor 19 and the vane 20 It is possible to ensure the symmetry of the distribution of fluid pressure that covers the both sides of the plate.
  • the boosting unit shown in FIG. 12 is configured such that a pair of side plates sandwiching the rotor 19 are both movable combination side plates. As shown in FIG. 12, these side plates are a front movable combination side plate 3d and a rear movable combination side plate 7d. Even in the case of this booster, the deformation of the first front plate Id and the first rear plate 5d due to the internal pressure of the pump can be suppressed with increased rigidity. It is. In addition, in anticipation of deformation of the first front plate Id and the first rear plate 5d on both sides of the rotor 19, a pressurized fluid is applied to both sides of the rotor 19 by tightening the connecting bolt 9 with an appropriate amount.
  • the symmetry of the pressure distribution can be maintained.
  • the front movable combination side plate 3d and the rear movable combination side plate 7d that are slidable in the axial direction are provided, so that the contact surface with the rotor 19 and the vane 20 can be reduced.
  • the degree of flatness can also be set.
  • the pair of side plates sandwiching the rotor 19 is symmetric, it is possible to further secure the symmetry of the distribution of the fluid pressure exerted on both side surfaces of the rotor 19 and the vane 20.
  • the deformation of the rotor 19 and the vane 20 can be suitably suppressed, and when the rotor 19 and the vane 20 come into contact with the combination side plates 3d and 7d, they are seized in a high surface pressure state. Can be suppressed.
  • the combination side plates 3d and 7d may be formed to have the same shape and the same rigidity by using the same member. In this case, the symmetry of the front combination side plate 3d and the rear combination side plate 7d can be further enhanced. Further, in the boosting section of FIG. 9, FIG. 10 and FIG. 11, the combination of the pair of side plates sandwiching the rotor 19 may have a structure in which the front side and the rear side are interchanged.
  • a vane pump that can suppress the stagnation of the side plate at the time of assembly, minimize the deformation of the side plate even when the pump is operated, and can suitably maintain the side clearance. realizable.

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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

Une pompe à palettes (100) comprend un anneau de came (18), un rotor rotatif (19) disposé dans l’anneau de came (18) ; une pluralité d'aubes (20) conservées dans une pluralité de rainures d’aubes formées dans le rotor (19) et mobiles par glissement le long de la surface de came (18) par rapport à la rotation du rotor (19) et un flasque latéral de combinaison frontale (3a) et un flasque latéral de combinaison arrière (7a) placés des deux cotés du rotor (19) et les palettes (20), tous ces éléments étant encastrés dans l’anneau. Le flasque latéral de combinaison frontale (3a) est formé d’un premier flasque frontal (1a) et un deuxième flasque frontal (2a), tandis que le flasque latéral de combinaison arrière (7a) est formé d’un premier flasque arrière (5a) et d’un deuxième flasque arrière (6a). Le flasque latéral de combinaison frontale (3a) et le flasque latéral de combinaison arrière (7a) sont disposés symétriquement par rapport au rotor (19) et à la même rigidité.
PCT/JP2006/304245 2005-03-08 2006-03-06 Pompe a palettes WO2006095673A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06728664A EP1857679A1 (fr) 2005-03-08 2006-03-06 Pompe a palettes
US11/885,783 US20080159898A1 (en) 2005-03-08 2006-03-06 Vane Pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-063960 2005-03-08
JP2005063960A JP2006249944A (ja) 2005-03-08 2005-03-08 ベーンポンプ

Publications (1)

Publication Number Publication Date
WO2006095673A1 true WO2006095673A1 (fr) 2006-09-14

Family

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PCT/JP2006/304245 WO2006095673A1 (fr) 2005-03-08 2006-03-06 Pompe a palettes

Country Status (5)

Country Link
US (1) US20080159898A1 (fr)
EP (1) EP1857679A1 (fr)
JP (1) JP2006249944A (fr)
CN (1) CN101137847A (fr)
WO (1) WO2006095673A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011149334A (ja) * 2010-01-21 2011-08-04 Showa Corp 車両の油圧制御装置
JP6163111B2 (ja) * 2014-01-21 2017-07-12 株式会社ショーワ ベーンポンプユニット
JP2016109029A (ja) * 2014-12-05 2016-06-20 株式会社デンソー ベーン式ポンプ、及び、それを用いる燃料蒸気漏れ検出装置
US9902251B2 (en) * 2016-01-26 2018-02-27 Deere & Company Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5027601B1 (fr) * 1968-08-19 1975-09-09
JPS52106602U (fr) * 1977-02-10 1977-08-13
JPS62116189U (fr) * 1986-01-16 1987-07-23
JP2000145664A (ja) * 1998-09-08 2000-05-26 Ebara Corp ベーン式回転機械
JP2000512714A (ja) * 1997-04-15 2000-09-26 ルーク・ファールツォイク―ヒュドラオリク・ゲーエムベーハー・ウント・コンパニー・カーゲー ベーンポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5027601B1 (fr) * 1968-08-19 1975-09-09
JPS52106602U (fr) * 1977-02-10 1977-08-13
JPS62116189U (fr) * 1986-01-16 1987-07-23
JP2000512714A (ja) * 1997-04-15 2000-09-26 ルーク・ファールツォイク―ヒュドラオリク・ゲーエムベーハー・ウント・コンパニー・カーゲー ベーンポンプ
JP2000145664A (ja) * 1998-09-08 2000-05-26 Ebara Corp ベーン式回転機械

Also Published As

Publication number Publication date
JP2006249944A (ja) 2006-09-21
US20080159898A1 (en) 2008-07-03
EP1857679A1 (fr) 2007-11-21
CN101137847A (zh) 2008-03-05

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