US20200011326A1 - Vane pump - Google Patents
Vane pump Download PDFInfo
- Publication number
- US20200011326A1 US20200011326A1 US16/347,586 US201716347586A US2020011326A1 US 20200011326 A1 US20200011326 A1 US 20200011326A1 US 201716347586 A US201716347586 A US 201716347586A US 2020011326 A1 US2020011326 A1 US 2020011326A1
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- United States
- Prior art keywords
- hollow shaft
- shaft
- vane pump
- rotor
- hollow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 31
- 230000002093 peripheral effect Effects 0.000 claims description 47
- 239000000314 lubricant Substances 0.000 claims description 26
- 238000007789 sealing Methods 0.000 claims description 20
- 230000033001 locomotion Effects 0.000 claims description 10
- 238000003780 insertion Methods 0.000 claims description 5
- 230000037431 insertion Effects 0.000 claims description 5
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 abstract description 80
- 230000008878 coupling Effects 0.000 abstract description 18
- 238000010168 coupling process Methods 0.000 abstract description 18
- 238000005859 coupling reaction Methods 0.000 abstract description 18
- 238000010276 construction Methods 0.000 description 19
- 239000012530 fluid Substances 0.000 description 12
- 238000003825 pressing Methods 0.000 description 12
- 239000007787 solid Substances 0.000 description 11
- 230000000694 effects Effects 0.000 description 10
- 239000004519 grease Substances 0.000 description 8
- 238000002485 combustion reaction Methods 0.000 description 7
- 238000003754 machining Methods 0.000 description 7
- 230000004323 axial length Effects 0.000 description 6
- 238000005304 joining Methods 0.000 description 5
- 238000005096 rolling process Methods 0.000 description 5
- 238000003860 storage Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 239000003566 sealing material Substances 0.000 description 1
Images
Classifications
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
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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
- 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
- F04C14/223—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 using a movable cam
- F04C14/226—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 using a movable cam by pivoting the cam around an eccentric axis
-
- 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
-
- 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
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/52—Bearings for assemblies with supports on both sides
-
- 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
- F04C2240/00—Components
- F04C2240/60—Shafts
-
- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C27/009—Shaft sealings specially adapted for pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B21/00—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings
- F16B21/10—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts
- F16B21/16—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft
- F16B21/18—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft with circlips or like resilient retaining devices, i.e. resilient in the plane of the ring or the like; Details
Definitions
- the present invention relates to a vane pump.
- Patent Literature 1 Various types of a vane pump, which includes a cam ring with an internal space having a non-circular sectional shape and a rotor having a circular sectional shape and a vane (blade) moving freely in a radial groove being machined into a rotor, have been proposed (see Patent Literature 1, for example).
- Such vane pump is applied in a manner that a vane pump is mounted on a transmission device, in some cases.
- a second shaft 104 for driving the vane pump 100 (or the gear pump) is provided in the transmission device 101 , in addition to an input shaft 103 to which power is transmitted from a driving source 102 (such as an engine, for example). And the shaft 103 and the second shaft 104 are offset.
- an output shaft 105 of the driving source 102 is coupled with the input shaft 103 of the transmission device 101 by a first coupling 106 .
- a gear 107 is coupled with the input shaft 103
- the gear 107 is engaged with a gear 108
- the gear 108 is coupled with the second shaft 104 .
- the second shaft 104 supplies power to the vane pump 100 by a second coupling 109 .
- the gears 107 , 108 construct a gear mechanism in which the second shaft 104 offset the input shaft 103 .
- the present invention was proposed in view of the above-mentioned problem of the prior art and an object of present invention is to provide a vane pump which can prevent lowering of power transmission efficiency when the vane pump is used in combination with a transmission device, for example.
- a vane pump ( 10 , 20 , 50 , 60 , 70 , 80 , 90 ) of the present invention is characterized in that:
- the pump comprises a hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ),
- the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) is constructed such that a rotation driving shaft (the input shaft 103 of the transmission device 101 as shown in FIG. 1 , for example: including an input shaft to which an input is directly transmitted so that the driving force is transmitted to the transmission device from the driving source 102 without through a coupling) of a driving source ( 102 ) can be inserted into a hollow portion, and that
- the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) and the rotation driving shaft ( 103 ) are coupled (connected or engaged) by a mechanism for transmitting a torque but transmitting no thrust.
- a rotor ( 2 , 22 ) is preferably mounted on the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ).
- the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) and the rotor ( 2 , 22 ) are mounted in a manner that relative rotation is not possible and movement in an axial direction is limited by a wire ring ( 3 , 23 ), and that the wire ring ( 3 , 23 ) is disposed across a shaft-side recess portion ( 1 A) and a rotor-side stepped portion ( 2 A) in a state that the shaft-side recess portion ( 1 A) formed on the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) and the rotor-side stepped portion ( 2 A) formed on the rotor ( 2 , 22 ) are aligned.
- the rotor-side stepped portion ( 2 A) is formed on both side surfaces of the rotor ( 2 , 22 ), and a depth dimension (d 1 ) of the rotor-side stepped portion ( 2 A) is preferably larger than a diameter (D 1 ) of a wire material of the wire ring ( 3 , 23 ).
- mechanical seal ( 4 A, 4 B, 24 A, 24 B) is provided on both end portions in the axial direction of the hollow shaft ( 1 , 21 ), and a circuit ( 5 , 25 : relief circuit for protection) for communicating the mechanical seals ( 4 A, 4 B, 24 A, 24 B) on the both end portions each other.
- the rotor ( 2 ) and a cam ring ( 6 ) may be provided one respectively or may be provided in plural (two each, for example).
- the mechanism for transmitting a torque but transmitting no thrust may be a female spline and a male spline formed on an inner peripheral surface of the hollow shaft ( 1 , 21 , 51 , 81 , 91 ) and an outer peripheral surface of the rotation driving shaft ( 103 ), or may be a key ( 52 ) and a keyway ( 53 ).
- the mechanism for transmitting a torque but transmitting no thrust preferably may be constructed by an engagement groove ( 61 B) penetrating the hollow shaft ( 61 ), a through hole of the rotation driving shaft ( 103 ) and a spring pin ( 62 ) being capable of insertion into the engagement groove ( 61 B) and the through hole.
- a spherical member ( 72 : engagement ball) and a radial direction pressing member ( 73 : pressing bolt) for pressing the spherical member ( 72 ) inwardly in the radial direction are accommodated in the accommodating portion ( 71 B), and a plurality of the spherical members ( 72 : engagement ball) is pressed inwardly in the radial direction so that the hollow shaft ( 71 ) and the rotation driving shaft ( 103 ) can be coupled.
- the mechanism for transmitting a torque but transmitting no thrust is constructed by splines formed on the outer peripheral surface of the rotation driving shaft ( 103 ) and the inner peripheral surface of the hollow shaft ( 81 ), the splines are formed only in regions (regions immediately below the vane) in the vicinity of the vane in the axial direction of the rotation driving shaft ( 103 ) and the hollow shaft ( 81 ), a region where the splines are not provided in the rotation driving shaft ( 103 ) and the hollow shaft ( 81 ) constructs a lubricant-oil filling space (large diameter portion) in which a lubricant oil (grease oil, for example) is filled, and a sealing member ( 82 : a square ring, for example) for the lubricant oil is provided in a region on a side separated from a cover portion ( 7 ).
- the mechanism for transmitting a torque but transmitting no thrust is constructed by splines formed on the whole region in the axial direction of the outer peripheral surface of the rotation driving shaft ( 103 ) and the inner peripheral surface of the hollow shaft ( 91 ), a sealing member ( 92 : a spline seal) for the lubricant oil is disposed in a region on a side separated from the cover portion ( 7 ), the sealing member ( 92 ) has projections and recesses formed on an outer periphery thereof, and that the projections and recesses are formed so as to correspond to the spline (female spline) formed on the inner peripheral surface of the hollow shaft ( 91 ).
- the hollow shaft ( 51 , 61 , 71 , 81 , 91 ) is preferably supported by a supporting member disposed on a side being separated from the cover portion ( 7 ) and a supporting member disposed in the vicinity of the cover portion ( 7 ).
- circuit ( 5 , 25 : relief circuit for protection) communicating the mechanical seal ( 4 A, 4 B, 24 A, 24 B) on the both end portions in the axial direction of the hollow shaft ( 1 , 21 ) each other it is preferably to provide a circuit ( 55 ) communicating the mechanical seal ( 4 B, 24 B) on the cover portion ( 7 , 27 ) side with an intake portion (intake port 14 ).
- the vane pump ( 10 , 20 , 50 , 60 , 70 , 80 , 90 ) of the present invention includes the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ), by inserting the rotation driving shaft (the input shaft 103 of the transmission device 101 , for example) of the driving source ( 102 ) into the hollow portion of the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ), and by coupling the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) and the rotation driving shaft ( 103 ) by the mechanism (splines, key and keyway and the like) for transmitting a torque but transmitting no thrust, the vane pump ( 10 , 20 , 50 , 60 , 70
- the vane pump ( 10 , 20 , 50 , 60 , 70 , 80 , 90 ) is used in a manner that the vane pump is attached to another device (the transmission device 101 , for example), for example, since the vane pump ( 10 , 20 , 50 , 60 , 70 , 80 , 90 ) is directly rotated/driven by the input shaft ( 103 ) of the transmission device ( 101 ), for example, it is not necessary to provide a gear mechanism (the gear mechanisms 107 , 108 inside the transmission device 101 shown in FIG. 12 ) for transmitting rotation driving force or a shaft (the second shaft 104 , for example: see FIG.
- the shaft (the second shaft 104 : see FIG. 12 ) for rotating/driving vane pump
- a bearing for supporting/bearing the shaft for rotating/driving vane pump is not necessary, the gear mechanism for transmitting rotation driving force is not necessary either, the number of constructional components of a device on which the vane pump ( 10 , 20 , 50 , 60 , 70 , 80 , 90 ) of the present invention is mounted is largely reduced, and then component management becomes extremely easy.
- the power transmission shaft (the input shaft 103 of the transmission device 101 , for example) is inserted into the hollow portion of the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) of the vane pump ( 10 , 20 , 50 , 60 , 70 , 80 , 90 ), a labor and/or cost for assembling is remarkably reduced.
- the rotation driving shaft (a solid shaft: the input shaft 103 of the transmission device 101 shown in FIG. 1 , for example) of the driving source ( 102 ) is inserted into the hollow portion of the inner side in the radial direction of the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ), even if a force (a force in a thrust direction) in the rotation shaft direction operates on the rotation driving shaft ( 103 , input shaft), the rotation driving shaft ( 103 ) merely slides on the hollow portion of the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ), and the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) does not load (receive) the force in the axial direction.
- a fastening force operating when the vane pump is attached to the driving source does not transmit to the driving source ( 102 ) through the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ).
- the driving source ( 102 ) is an internal combustion engine
- the driving source ( 102 ) is an electric motor
- the rotor ( 2 , 22 ) by mounting the rotor ( 2 , 22 ) on the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ), it is possible to prevent a situation such that the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) is removed from the vane pump ( 10 , 20 , 50 , 60 , 70 , 80 , 90 ).
- the rotation driving shaft (solid shaft: the input shaft 103 of the transmission device 101 shown in FIG. 1 , for example) of the driving source ( 102 ) is inserted into the hollow portion on the inner side in the radial direction of the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ), even if the force (a force in the thrust direction) operates in the rotation shaft direction on the rotation driving shaft ( 103 ), the rotation driving shaft ( 103 ) merely slides on the hollow portion of the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ), and the hollow shaft ( 1 , 21 , 51 , 61 , 71 , 81 , 91 ) does not load the force in the axial direction.
- the rotor-side stepped portion ( 2 A) is formed on both side surfaces of the rotor ( 2 , 22 ), and if the depth dimension (d 1 ) of the rotor-side stepped portion ( 2 A) is larger than the diameter (D 1 ) of the wire rod of the wire ring ( 3 , 23 ), the wire ring ( 3 , 23 ) can be accommodated inside the rotor ( 2 , 22 ), the rotor ( 2 , 22 ) is prevented to interfere with the wire ring ( 3 , 23 ), and design of pump construction on the both side surfaces of the rotor ( 2 , 22 ) become easy.
- the mechanical seal ( 4 A, 4 B, 24 A, 24 B) are disposed on both end portions in the axial direction of the vane pump ( 10 , 20 ).
- the mechanical seal is provided only on one side (an end portion being close to an equipment supplying power, for example) in the axial direction, but the mechanical seal is not provided on the other (the end portion being separated from the equipment supplying power, for example).
- a relief circuit for relieving a pressure operating on the mechanical seal is also provided only on the end portion on a side to which the mechanical seal is provided, while the relief circuit is not formed on the other (the end portion being separated from the equipment supplying power, for example), and thus, in a case that the constructions of the prior-art vane pump is applied to the present invention, it is possible that the mechanical seal provided on the other is broken.
- the present invention by providing a circuit ( 5 , 25 : relief circuit for protection) communicating the mechanical seal ( 4 B, 24 B) on the other (the end portion being separated from the equipment supplying power, for example) with the mechanical seal ( 4 A, 24 A) on the one (the end portion close to the equipment supplying power, for example), the pressure operating on the other mechanical seal ( 4 B, 24 B) can be relieved to the relief circuit ( 9 , 29 ) for mechanical seal through the circuit ( 5 , 25 ).
- the hollow shaft ( 51 , 61 , 71 , 81 , 91 ) is supported by the supporting member disposed on a side separated from the cover portion ( 7 ) and the supporting member disposed in the vicinity of the cover portion ( 7 ), since the hollow shaft ( 51 , 61 , 71 , 81 , 91 ) is supported at two spots being separated in the axial direction, that is, the hollow shaft is supported by a manner so-called both-end supporting, and thus, the hollow shaft ( 51 , 61 , 71 , 81 , 91 ) can be accurately centered with the rotation driving shaft ( 103 ) and pump efficiency can be improved, as compared with the case of supporting with a single supporting member.
- the supporting member may be a bearing bush ( 19 , 54 ) or may be constructed as direct receiving by forming a film of a material which improves abrasion resistance on a surface of an insertion hole for the hollow shaft ( 51 , 61 , 71 , 81 , 91 ) of the case ( 8 ) or the cover portion ( 7 ).
- the circuit (relief circuit 5 , 25 for protection in the hollow shaft 1 , 21 ) communicating the mechanical seals ( 4 A, 4 B, 24 A, 24 B) on the both end portions in the axial direction of the hollow shaft ( 51 , 61 , 71 , 81 , 91 ) each other cannot be constructed any more.
- the pressure operating on the mechanical seal ( 4 B, 24 B) on the cover portion side can be relieved to the intake portion (intake port 14 ) by the circuit ( 55 ).
- a length dimension and pipe resistance of the circuit ( 55 ) communicating the mechanical seal ( 4 B, 24 B) on the cover portion ( 7 , 27 ) side and the intake portion (intake port 14 ) are smaller than the length dimension and pipe resistance of the circuit ( 5 , 25 ) communicating the mechanical seals ( 4 A, 4 B, 24 A, 24 B) on the both end portions in the axial direction of the hollow shaft ( 1 , 21 ), and thus, the pressure operating on the mechanical seal ( 4 B, 24 B) on the cover portion side can be relieved reliably and an operative effect as the relief circuit is reliably carried on.
- the mechanism for transmitting a torque but transmitting no thrust is constructed by the splines formed on the outer peripheral surface of the rotation driving shaft ( 103 ) and on the inner peripheral surface of the hollow shaft ( 81 )
- the splines is only formed in the region (region immediately below the vane) in the vicinity of the vane in the axial direction of the rotation driving shaft ( 103 ) and the hollow shaft ( 81 )
- the lubricant-oil filling space (large diameter portion) is constructed in which space a lubricant oil (grease oil, for example) is filled in the region where the splines of the rotation driving shaft ( 103 ) and the hollow shaft ( 81 ) are not provided
- the sealing member ( 82 : a square ring, for example) for the lubricant oil in the region on the side separated from the cover portion ( 7 ) is provided, even if the lubricant oil is filled in the lubricant-oil filling space, the lubric
- the driving source is an internal combustion engine
- torque fluctuation being specific to the internal combustion engine generates the collisions of teeth of the male and female splines against each other (teeth are hit by each other) through the rotation driving shaft ( 103 ) and the hollow shaft ( 81 , 91 ), and therefore, a tooth surface of the spline is damaged, however, by filling the lubricant oil in the lubricant-oil filling space, the lubricant oil is interposed between teeth of the male and female splines and a buffer operation is carried on by the lubricant oil as a cushion, and thus, damage on the tooth surface caused by the collision between the teeth is reduced.
- a sealing member for lubricant oil such as a square ring
- the mechanism for transmitting a torque but transmitting no thrust is constructed by the splines formed on the whole regions in the axial direction on the outer peripheral surface of the rotation driving shaft and the inner peripheral surface of the hollow shaft, it is necessary to cut off the spline (of the inner peripheral surface of the hollow shaft) at a place where the sealing member for the lubricant oil should be installed by machining so as to form a cylindrical surface, and then, it is necessary to provide a square ring.
- the sealing member ( 92 : spline seal) of the lubricant oil to be provided in the region on the side being separated from the cover portion ( 7 ) is constructed by a sealing member ( 92 : spline seal) with projections and recesses formed on the outer periphery thereof, the projections and recesses being formed corresponding to the spline (female spline) are formed on the inner peripheral surface of the hollow shaft ( 91 ), without cutting off the spline (of the inner peripheral surface of the hollow shaft) at a place where the sealing member for the lubricant oil should be provided by machining so as to form a cylindrical surface, or without increasing a machining cost of the hollow shaft ( 91 ), the sealing member ( 92 : spline seal) for the lubricant oil can be provided, by assembling the spline seal ( 92 ) from a distal end side (right end side in FIG.
- FIG. 1 is a sectional view showing an outline of an embodiment of the present invention.
- FIG. 2 is a sectional view showing a first embodiment of the present invention.
- FIG. 3 is an A-B line arrow-view sectional view of FIG. 2 .
- FIG. 4 is an explanatory view showing a manner that a rotor is mounted on a hollow shaft by a wire ring.
- FIG. 5 is an explanatory view schematically showing a circuit for relieving a pressure operating on a mechanical seal.
- FIG. 6 is a sectional view showing a second embodiment of the present invention.
- FIG. 7 shows a third embodiment of the present invention, in which FIG. 7(A) is a sectional view and FIG. 7(B) is a partial side view showing a state that a key and a keyway are engaged with each other.
- FIG. 8 shows a fourth embodiment of the present invention, in which FIG. 8(A) is a sectional view and FIG. 8 (B) is a partial plan view showing a state that a spring pin is engaged.
- FIG. 9 shows a fifth embodiment of the present invention, in which FIG. 9(A) is a sectional view and FIG. 9(B) is a partial side view showing a state that an input shaft is fixed to a hollow shaft.
- FIG. 10 is a sectional view showing a sixth embodiment of the present invention.
- FIG. 11 are views showing a variation of the sixth embodiment of the present invention, in which FIG. 11 (A) is a sectional view, and FIG. 11(B) is a partial side view showing the hollow shaft when a spline seal is installed.
- FIG. 12 is an explanatory view schematically showing a state in which a prior-art vane pump is mounted on a transmission device.
- FIG. 1 a summary of the embodiments of the present invention will be described.
- the same members described by referring to FIG. 12 are given the same reference numerals, and description will be omitted.
- the output shaft 105 of the driving source 102 (for example, an internal combustion engine) is coupled with the input shaft 103 of the transmission device 101 through the coupling 106 , and the vane pump 10 (or 20 ) is disposed on an end surface TF on the driving source 102 side of the transmission device 101 .
- the vane pump 10 ( 20 ) includes the hollow shaft 1 (or 21 ) and a female spline is engraved on the inner peripheral surface of the shaft 1 over the axial direction.
- the input shaft 103 (coupled with the rotation driving shaft of the driving source 102 through the coupling 106 ) of the transmission device 101 is inserted.
- the input shaft 103 of the transmission device 101 is reliably supported by a rolling bearing (not shown) on the transmission device 101 side.
- the vane pump 10 ( 20 ) is directly mounted on the input shaft 103 of the transmission device 101 .
- a male spline fitted with the female spline is engraved in the outer peripheral surface overlapped with the hollow shaft 1 ( 21 ) of the vane pump 10 ( 20 ) so that power transmission from the input shaft 103 to the hollow shaft is carried out by spline fitting between the female spline and the male spline.
- the input shaft 103 of the transmission device 101 directly rotates/drives the vane pump 10 ( 20 ).
- the first embodiment shown in FIGS. 2 to 5 is an embodiment according to the vane pump of a type in which a cam ring and a rotor are provided one respectively.
- the hollow shaft 1 is disposed at the center of the vane pump 10 , and as shown in FIG. 3 , the inner peripheral surface of the hollow shaft 1 is constructed so as to be shaped as a female spline shaft. Since a spline shape is constructed in the hollow shaft 1 , in the hollow shaft 1 , vicinities of upper and lower ends are illustrated by three line segments, in FIG. 2 .
- the vane pump 10 is mounted on the transmission device 101 as shown in FIG. 1 , for example, the input shaft 103 (solid shaft: FIG. 1 ) of the transmission device 101 is inserted into the hollow portion of the spline-shaped hollow shaft 1 .
- the surface outward in the radial direction of the spline-shaped hollow shaft 1 is mounted on the inner peripheral surface of the rotor 2 by spline fitting and incapable of relative rotation, then the rotor 2 is rounded by rounds of the hollow shaft 1 .
- the rotor 2 may be mounted on the hollow shaft 1 , incapable of axial movement, but in this embodiment, it is preferable that the rotor 2 is mounted on the shaft 1 so as to limit movement of the rotor 2 in the axial direction, as written hereinafter.
- a plurality of radial vane grooves 11 G ( FIG. 3 ) extending in the radial direction is formed, and the vane 11 is inserted into the vane groove 11 G.
- a vane 11 is constructed movably in the radial direction along the vane groove 11 G, and a part of a pressure oil ejected from an ejection port 16 during driving of the vane pump is supplied to a pressure-oil storage portion 12 for vane through a circuit 17 for pressure loading (pressure loading), whereby the vane 11 is urged outward in the radial direction and protruded, and an end portion outward in the radial direction of the vane 11 slides on the inner peripheral surface of the cam ring 6 .
- the pressure-oil storage portion 12 for vane is formed in the rotor 2 (refer to FIG. 3 ).
- the rotor 2 During driving of the vane pump 10 , the rotor 2 is rotated in an arrow A direction ( FIG. 3 ), and with the rotation of the rotor 2 , a working fluid flows into a pump chamber ⁇ from the intake port 14 in the vane pump 10 through an intake circuit 13 of the cam ring 6 .
- the pump chamber ⁇ is defined by the adjacent vane 11 , the outer surface of the rotor 2 , and the inner peripheral surface of the cam ring 6 .
- a position of the pump chamber ⁇ is changed with the rotation of the rotor 2 (corresponding to a circumferential position of the cam ring 6 ), and a size (volume) of the pump chamber ⁇ is also changed with the rotation of the rotor 2 (corresponding to the circumferential position of the cam ring 6 ).
- the working fluid supplied from the intake port 14 flows into the pump chamber a via the intake circuit 13 . Then, by means of contracting the volume of the pump chamber as, a pressure is applied and the working fluid is ejected from the ejection port 16 via an ejection circuit 15 .
- the vane pump 10 includes a body portion 8 and the cover portion 7 .
- the hollow shaft 1 , the rotor 2 , the vane 11 (movable in the vane groove of the rotor 2 ), and the cam ring 6 are accommodated.
- the pressure plate 18 is disposed in the body portion 8 .
- the circuit 17 for pressure loading supplying the pressure oil to the pressure-oil storage portion 12 for vane is formed on the pressure plate 18 .
- the cover portion 7 is disposed on its opening side (left side in FIG. 2 ), and the cover portion 7 is fixed to the body portion 8 .
- the intake port 14 for the working fluid is provided in the body portion 8 , and the intake port 14 communicates with the intake circuit 13 for the working fluid on the cam ring 6 side (inner side in the radial direction).
- the ejection circuit 15 for the working fluid is provided in the body portion 8 , and the ejection circuit 15 communicates with an outlet port 16 for the working fluid.
- the rotation driving shaft (the input shaft 103 of the transmission device 101 shown in FIG. 1 , for example: not shown in FIG. 2 ) is inserted into the hollow portion on the inner side in the radial direction of the hollow shaft 1 , even if the force in the rotation shaft direction (force in the thrust direction) operates on the rotation driving shaft (input shaft 103 , for example), the rotation shaft only slides on the hollow portion of the hollow shaft 1 . In other words, even if the force in the axial direction (thrust direction) of the input shaft 103 ( FIG. 1 ) of the transmission device 101 operates, for example, the hollow shaft 1 does not load the force in the axial direction (force in the thrust direction).
- the rotor 2 can be mounted on the hollow shaft 1 .
- the male spline is engraved on the surface between the shaft-side recess portions 1 A, 1 A juxtaposed in the axial direction
- the female spline is engraved on the surface between the rotor-side stepped portions 2 A, 2 A juxtaposed in the axial direction similarly, and the rotating power is transmitted from the hollow shaft 1 to the rotor 2 , the shaft 1 and rotor 2 are coupled by spline-fitting the male spline and the female spline as a manner that the shaft 1 and rotor 2 are incapably relating to rotation thereof.
- the rotor-side stepped portion 2 A is formed on the both side surfaces of the rotor 2 .
- the depth dimension d 1 is expressed smaller than the diameter D 1 of the wire rod of the wire ring 3 , but the depth dimension d 1 of the rotor-side stepped portion 2 A is preferably larger than the diameter D 1 of the wire rod of the wire ring 3 (see FIGS. 7 to 11 ).
- the wire ring 3 is accommodated in the rotor 2 , and there is no more concern of interference with the wire ring 3 , and thus, the design of the pump construction on the both side surfaces of the rotor 2 is made easy.
- the gap is generated between the hollow shaft 1 and the rotor 2 .
- an allowance is generated between the rotor 2 and the cover portion 7 or the pressure plate 18 for a portion of the gap, and thus, the collision between the rotor 2 and the cover portion 7 or the pressure plate 18 is prevented by the allowance.
- the hollow shaft 1 does not load the force in the axial direction, but the input shaft 103 merely slides on the hollow portion in the hollow shaft 1 .
- the rotation driving shaft (input shaft 103 of the transmission device 101 ) which is a solid shaft is inserted through the hollow portion in the hollow shaft 1 , the hollow shaft 1 is not biased in the radial direction unless the rotation driving shaft (input shaft 103 of the transmission device 101 ) makes a motion such as precession biased in the radial direction.
- the rotation driving shaft (input shaft 103 of the transmission device 101 , for example) which is a solid shaft is reliably supported by the rolling bearing (not shown) on the transmission device 101 side, it is not biased in the radial direction.
- the bearing bush 19 operates as a sliding bearing, and thus, in the first embodiment shown in FIGS. 2 to 5 , the rolling bearing is omitted and the sliding bearing is merely provided.
- the bearing bush 19 for supporting the hollow shaft 1 in the radial direction is needed.
- the driving source ( 102 ) is an electric motor
- the bearing bush 19 for supporting the hollow shaft 1 in the radial direction can be omitted.
- the rolling bearing is not provided but the hollow shaft 1 is supported on the body portion 8 of the vane pump 10 by the bearing bush 19 , but the bearing bush 19 does not have a function of sealing oil, that is, a working fluid.
- the mechanical seals 4 are disposed on both end portions in the axial direction of the vane pump 10 (the body portion 8 side end portion and the cover portion 7 side end portion: both right and left end portions in FIG. 2 ).
- the mechanical seal on the body portion 8 side end portion is shown by reference numeral “ 4 A”
- the mechanical seal on the cover portion 7 side end portion is shown by reference numeral “ 4 B”.
- the mechanical seal 4 is an expression comprehensively indicating the mechanical seals 4 A and 4 B.
- the rotation driving force is supplied by the shaft 104 , but the shaft 104 does not penetrate the vane pump 100 .
- the mechanical seal (not shown) is provided only on the end portion close to the equipment (transmission device 101 ) for supplying power, and there is little necessity to provide the mechanical seal on the end portion separated from the equipment for supplying the power.
- the mechanical seals 4 A and 4 B are provided on the both end portions in the axial direction.
- the relief circuit 9 for mechanical seal is provided in order to communicate the back portion (left side in FIG. 2 ) of the mechanical seal 4 A on the body portion 8 side end portion (right side in FIG. 2 ) with the intake port 14 .
- the relief circuit 9 for mechanical seal (or a circuit corresponding to that) communicating the back portion (left side in FIG. 2 ) of the mechanical seal 4 A (on the right side) of the body portion 8 side end portion with the intake port 14 is merely provided.
- the relief circuit 9 for mechanical seal is provided which circuit communicates the back portion of the mechanical seal 4 A on the body portion 8 side end portion (right side in FIG. 2 ) with the intake port 14 .
- the back portion of the mechanical seal 4 A and the back portion of the mechanical seal 4 B (mechanical seal on the side separated from the relief circuit 9 for mechanical seal: the mechanical seal on the left side in FIGS. 2 and 5 ) of the cover portion 7 side end portion are communicated through the relief circuit 5 for protection.
- This relief circuit 5 for protection is provided on a boundary portion between the cover portion 7 as well as the body portion 8 and the hollow shaft 1 , and only one relief circuit 5 for protection is provided in FIG. 5 , but a plurality of the relief circuits can be provided.
- the mechanical seal 4 B (the mechanical seal on the side separated from the relief circuit 9 for mechanical seal) on the cover portion 7 side end portion communicates with the relief circuit 9 for mechanical seal through the relief circuit 5 for protection.
- Reference numeral 16 shown in FIGS. 2 and 5 indicates an ejection port formed on the body portion 8 .
- FIG. 3 in order to mount the cover portion 7 and the body portion 8 on the end surface TF (see FIG. 1 ) of the transmission device 101 , for example, there are bolt holes H at four spots.
- a bolt (not shown) inserting through the cover portion 7 and the body portion 8 into the bolt hole H, the vane pump 10 is mounted on the end surface TF of the transmission device 101 , for example.
- the vane pump 10 is mounted on the end surface TF ( FIG. 1 ) of the transmission device 101 , the vane pump 10 is mounted on the end surface TF in a manner that an end surface 7TS ( FIG. 2 ) on the cover portion 7 side of the vane pump 10 contacts with on the end surface TF side of the transmission device 101 .
- a joining bolt B shown in FIG. 3 is a bolt for joining the body portion 8 and the cover portion 7 of the vane pump 10 . That is, in a state that the body portion 8 and the cover portion 7 are joined by the joining bolt B, it is possible to mount the body portion 8 and the cover portion 7 to the end surface TF of the transmission device 101 , for example, by inserting a bolt, which is not shown, into the bolt hole H.
- the vane pump 10 is mounted on the transmission device 101 , for example, by inserting a bolt, which is not shown, into the bolt hole H, since the body portion 8 and the cover portion 7 of the vane pump 10 are also integrally joined by the bolt which is not shown, the joining bolt B in FIG. 3 can be omitted.
- the vane pump 10 by fitting (or inserting) the rotation driving shaft (input shaft 103 of the transmission device 101 , for example) of the driving source 102 with the hollow portion of the spline-shaped hollow shaft 1 , the vane pump 10 can be directly rotated/driven by the rotation driving shaft 103 without interposing another coupling device.
- the vane pump 10 is used in a manner that the vane pump 10 is mounted on the transmission device 101 , for example, since the vane pump 10 is directly rotated/driven by the input shaft 103 of the transmission device 101 , it is not necessary to provide a gear mechanism for transmitting a rotation driving force and a shaft for rotating/driving a vane pump separately, and also, it is not necessary to provide a coupling mechanism between the vane pump 10 and the driving shaft. Thus, there is no transmission loss by coupling, meshing between the gears and the like, transmission efficiency is improved, and it is possible to become the transmission device 101 smaller.
- the rotation driving shaft (solid shaft: the input shaft 103 of the transmission device 101 shown in FIG. 1 , for example) of the driving source 102 is inserted into the hollow portion of the inner side in the radial direction of the hollow shaft 1 , even if the force in the rotation shaft direction (the force in the thrust direction) operates on the rotation driving shaft 103 (input shaft), the rotation driving shaft 103 only slides on the hollow portion of the hollow shaft 1 , and the hollow shaft 1 does not load the force in the axial direction.
- the hollow shaft 1 is not biased in the radial direction, unless the rotation driving shaft 103 which is a solid shaft makes a motion such as precession biased in the radial direction. And then, in a case that the rotation driving shaft 103 is reliably supported by a rolling bearing or the like on the rotation driven side (the transmission device 101 , for example), the rotation driving shaft 103 is not biased in the radial direction.
- the vane pump 10 of the first embodiment even if the force in the rotation shaft direction (force in the thrust direction) operates on the rotation driving shaft 103 of the driving source 102 , as described above, the hollow shaft 1 does not load the force in the axial direction. Thus, even if the rotor 2 is mounted on the hollow shaft 1 , the force in the axial direction of the rotation shaft 103 of the driving source 102 is not transmitted to the rotor 2 .
- the mechanical seals 4 A, 4 B are disposed on the both end portions in the axial direction (the body portion 8 side end portion and the cover portion 7 side end portion) of the vane pump 10 , and the relief circuit 5 for protection communicating the mechanical seal 4 A of the body portion 8 side end portion with the mechanical seal 4 B of the cover portion 7 side end portion is provided, the mechanical seal 4 A is communicated with the intake port 14 through the relief circuit 9 for mechanical seal, the pressure operating on the mechanical seal 4 B of the cover portion 7 side end portion can be relieved to the relief circuit 9 for mechanical seal via the relief circuit 5 for protection.
- the cam ring and the rotor are provided one respectively, but in the second embodiment shown in FIG. 6 , the cam ring and the rotor are provided two respectively.
- FIG. 6 Constructions shown in FIG. 6 which are different from the first embodiment in FIGS. 2 to 5 will be mainly described hereinafter.
- the hollow shaft 21 constructed so as to be shaped as a spline shaft is disposed at the center of the vane pump 20 , and in a case that the vane pump 20 is mounted on the transmission device 101 as shown in FIG. 1 , for example, the input shaft 103 (see FIG. 1 ) of the transmission device 101 is inserted into the hollow portion of the spline-shaped hollow shaft 21 .
- the vane pump 20 includes the body portion 28 and the cover portion 27 .
- the body portion 28 located on the left side in FIG. 6 accommodates the hollow shaft 21 , the rotor 22 , the vane 31 , and the cam ring 26 .
- the cover portion 27 located on the right in FIG. 6 accommodates the hollow shaft 21 , the rotor 22 , the vane 31 , and the cam ring 26 .
- the cover portion 27 covers an opening side of the body portion 28 and fixes the body portion 28 .
- a bearing bush 39 is disposed in the body portion 28 and the cover portion 27 , respectively, and the hollow shaft 21 is supported in a rotatable manner by the bearing bush 39 .
- the pressure plates 38 , 38 are disposed on the cover portion 27 side (right side in FIG. 6 ) of the rotor 22 and the cam ring 26 accommodated in the body portion 28 and on the opposite side (left side in FIG. 6 ), and an intermediate plate 40 is disposed in the body portion 28 .
- the pressure plates 38 , 38 are disposed on the body portion 28 side (left side in FIG. 6 ) of the rotor 22 and the cam ring 26 accommodated in the cover portion 27 and on the opposite side (right side in FIG. 6 ).
- the rotor 22 and the cam ring 26 accommodated in the body portion 28 and the rotor 22 and the cam ring 26 accommodated in the cover portion 27 are disposed by ensuring an appropriate distance by means of the intermediate plate 40 .
- a pressure loading circuits 37 , 37 are formed, and the pressure loading circuit 37 communicates with a pressure-oil storage portion for vane, not shown, and also communicates with ejection circuits 35 - 1 , 35 - 2 for the working fluid which will be described hereinafter.
- an intake port 34 for the working fluid is provided, and the intake port 34 communicates with a pump chamber (not shown in FIG. 6 ) through an intake circuit 33 of the intermediate plate 40 accommodated in the body portion 28 .
- ejection ports 36 - 1 , 36 - 2 for the working fluid are provided, respectively, and the ejection ports 36 - 1 , 36 - 2 communicate with the ejection circuits 35 - 1 , 35 - 2 for the working fluid on the cam ring 26 side (via a circuit, not shown), respectively.
- the rotors 22 , 22 on the body portion 28 side and the cover portion 27 side are mounted on the hollow shaft 21 by the wire rings 23 , 23 , respectively.
- the mechanical seals 24 , 24 are disposed on the both end portions in the axial direction of the vane pump 20 , that is, on the body portion 28 side end portion (left side in FIG. 6 ) and the cover 27 side end portion (right side in FIG. 6 ), respectively.
- the mechanical seal on the body portion 28 side end portion is shown by reference numeral 24 A
- the mechanical seal on the cover portion 7 side end portion is shown by reference numeral 24 B.
- the mechanical seal 24 is a comprehensive expression indicating the mechanical seals 24 A and 24 B.
- the relief circuit 29 for mechanical seal is formed, and the relief circuit 29 for mechanical seal communicates the back portion of the mechanical seal 24 A of the body portion 28 side end portion (left end portion in FIG. 6 ) with the intake port 34 .
- the back portion of the mechanical seal 24 A (mechanical seal on the left side in FIG. 6 ) of the body portion 28 side end portion (left end portion in FIG. 6 ) and the back portion of the mechanical seal 24 B (mechanical seal on the right side in FIG. 6 ) of the cover 27 side end portion are communicated through the relief circuit 25 for protection.
- one piece of the relief circuit 25 for protection is formed on the boundary portion between the cover 27 as well as the body portion 28 and the hollow shaft 21 , but a plurality of the relief circuit 25 can be formed.
- the mechanical seal 24 B (mechanical seal on the right side in FIG. 6 ) of the cover 27 side end portion communicates with the relief circuit 29 for mechanical seal through the relief circuit 25 for protection and the mechanical seal 24 A (mechanical seal on the left side in FIG. 6 ) of the body portion 28 side end portion (left end portion in FIG. 6 ).
- the third embodiment to the sixth embodiment of the present invention will be described with reference to FIGS. 7 to 11 .
- the third embodiment to the sixth embodiment shown in FIGS. 7 to 11 are embodiments according to a vane pump of a type in which the cam ring and the rotor are provided one respectively similar to the first embodiment shown in FIGS. 1 to 5 .
- FIGS. 7 to 11 the same members as those described with reference to FIGS. 1 to 5 are shown by the same reference numerals respectively, and the explanation thereof will be omitted.
- the input shaft 103 (solid shaft: refer to FIG. 1 ), not shown in FIG. 1 , of the transmission device 101 is inserted into the hollow portion of the hollow shaft 51 of the vane pump 50 .
- the input shaft 103 (rotation driving shaft) and the hollow shaft 51 are connected in a manner that the rotation force (torque) is transmitted but the thrust force is not transmitted by engaging the key 52 and the keyway 53 . That is, in the third embodiment shown in FIG. 7 , the “mechanism for transmitting a torque but transmitting no thrust” is constructed by the key 52 and the keyway 53 .
- the keyway 53 extending in a center axis direction of the hollow shaft is formed over a predetermined length L in a longitudinal direction of the hollow shaft 51 at least at one spot in a circumferential direction.
- the keyway 53 having the predetermined length L similar to the hollow shaft 51 is formed too, on a part of the outer peripheral surface of the region (region covered by the hollow shaft 51 ) which is inserted into the hollow shaft 51 .
- the keyway 53 of the input shaft 103 and the keyway 53 of the hollow shaft 51 are disposed so that the circumferential positions thereof are aligned, and the kay 52 having the width dimension which is the generally the same as the width dimension of the keyway 53 is inserted (or mounted) to the keyway 53 .
- the axial length L of the keyway 53 is designed so that the axial length is equal to or more than the axial length of the key 52 .
- the input shaft 103 (rotation driving shaft) is not shown.
- the input shaft 103 and the hollow shaft 51 become capable of relative movement merely in the axial direction of the hollow shaft 51 for a distance corresponding to a difference in the axial length between the keyway 53 and the key 52 , and the thrust force from the input shaft 103 to the hollow shaft 61 is not transmitted.
- the hollow shaft 51 and the input shaft 103 are not capable of relative rotation, and the torque is transmitted from the input shaft 103 to the hollow shaft 51 .
- the hollow shaft 1 is supported by the bearing bush 19 only.
- the bearing bush 54 for supporting the hollow shaft 51 is provided on the cover 7 side.
- the hollow shaft 51 is supports at two spots in the axial direction by the bearing bush 19 (bearing bush 19 disposed on a side separated from the cover portion 7 ) disposed on the body 8 side and the bearing bush 54 disposed in the vicinity of the cover portion 7 , and a construction so-called “both-end supporting” is constructed, and then, the hollow shaft 51 is supports by said “both-end supporting” construction.
- the hollow shaft 51 By supporting the hollow shaft 51 by the bearing bushes 19 and 54 (supporting members) in the both-end supporting manner, the hollow shaft 51 can be centered in parallel with the input shaft 103 and with high accuracy in a manner that rattling or the like does not happened relative to a case that the hollow shaft 51 is supported by a single bearing bush (supporting member). Thus, pump efficiency can be improved.
- the supporting member may be also constructed by the bearing bushes 19 and 54 as shown in drawings.
- a film of a material improving abrasion resistance may be formed on a surface of the insertion hole of the case 8 or the hollow shaft 51 of the cover portion 7 so as to support the hollow shaft 51 directly (direct bearing).
- the bearing bush is used on one side in the axial direction, while the other side is constructed as the above-mentioned direct bearing manner.
- the relief circuit 5 , 25 for protection as shown in the embodiment in FIGS. 1 to 6 cannot be constructed.
- FIG. 7 of the third embodiment instead of the relief circuit 5 , 25 (refer to FIGS. 2, 5, and 6 : circuit communicating the mechanical seals 4 A, 4 B, 24 A, and 24 B on both end portions in the axial direction of the hollow shaft), a channel 55 for communicating directly the mechanical seal 4 B on the cover portion 7 side (left side in FIG. 7 ) with the intake portion (intake port 14 ) is formed, as the relief circuit for protection.
- this relief circuit 55 for protection relievef circuit for mechanical seal
- the pressure generated on the back portion of the mechanical seal 4 A on the body portion 8 side end portion is relieved to the intake port 14 through the relief circuit 9 for mechanical seal
- the pressure generated on the back portion of the mechanical seal 4 B on the cover portion 7 side end portion is relieved to the intake port 14 through the relief circuit 55 for mechanical seal.
- the relief circuit 55 for protection (relief circuit for mechanical seal) has a length dimension and pipe resistance which are smaller than those of the relief circuits 5 , 25 for protection in the embodiment shown in FIGS. 1 to 6 , and thus, the pressure operating on the mechanical seal 4 B on the cover portion 7 side is reliably relieved, and the operative effect of the relief circuit is exerted reliably.
- the “mechanism which transmits the torque but does not transmit the thrust” is constructed by the engagement groove 61 B penetrating the hollow shaft 61 , a through hole (not shown) of the rotation driving shaft 103 , and the spring pin 62 capable of being inserted into the engagement groove 61 B and the through hole.
- the axial dimension of the hollow shaft 61 is designed so as to be larger than a width of the pump case (the body portion 8 and the cover portion 7 of the vane pump 60 ), and the distal end (right end in FIG. 8 ) of the hollow shaft 61 is protruded (protruding portion 61 A) from the pump case end portion (right end in FIG. 8 : body portion 8 side end portion).
- the engagement groove 61 B into which the spring pin 62 is inserted is formed (opened), and the engagement groove 61 B is formed on the same diameter of the hollow shaft 61 at a pair of positions being symmetrical to the shaft core in the circumferential direction of the hollow shaft 61 .
- the engagement groove 61 B has a long hole shape (or a groove state) which long hole is opened in the body portion 8 side end portion (right side in FIG. 8 ), a width dimension (dimension in the circumferential direction of the hollow shaft) of the engagement groove 61 B is designed so as to be substantially equal to the diameter of the spring pin 62 when the pin 62 is contracted, and an axial dimension (dimension in the axial direction of the hollow shaft 61 ) of the engagement groove 61 B is designed so as to be larger than the diameter of the spring pin.
- the spring pin 62 is formed having a hollow cylindrical shape having a notch portion 62 A extending in the axial direction, and the diameter of the spring pin 62 is changed (enlarged) by an elastic repulsive force.
- the spring pin 62 is fitted in a state that the diameter of the spring pin 62 is contracted when the pin 62 is inserted into the engagement groove 61 B and a through port, not shown, of the rotation driving shaft 103 .
- the axial length of the spring pin is designed so as to be larger than the diameter of the hollow shaft.
- a pin hole (through port), not shown, is formed, and said pin hole is formed at a position aligned with the position of the engagement groove 61 when the input shaft 103 is inserted into the hollow shaft 61 .
- the pinhole is a through hole (not shown) into which the spring pin 62 can be inserted, and an inner diameter of the pin hole is designed so as to be substantially equal to the diameter of the spring pin 62 being contracted.
- the spring pin 62 is inserted and fitted into one of the engagement grooves 61 B, 61 B of the hollow shaft 61 , the pin hole of the input shaft 103 (not shown in FIG. 8 ), and the other engagement groove 61 B of the hollow shaft 61 .
- the input shaft 103 and the hollow shaft 61 are made capable to move relatively each other in the axial direction of the hollow shaft 61 B for a distance corresponding to the axial length of the engagement groove 61 B, and the thrust force from the input shaft 103 is not transmitted to the hollow shaft 61 .
- the hollow shaft 61 and the input shaft 103 are incapable of relative rotation, and therefore, it is possible to transmit the torque from the input shaft 103 to the hollow shaft 61 .
- the elastic repulsive force operates to the spring pin 62 so as to enlarge outwardly in the radial direction, and the spring pin 62 presses one of the engagement grooves 61 B of the hollow shaft 61 , the pin hole of the input shaft 103 (not shown in FIG. 8 ), and the other engagement groove 61 B of the hollow shaft 61 .
- the spring pin 62 is prevented to be removed from the input shaft 103 or the hollow shaft 61 .
- the fifth embodiment will be described with reference to FIG. 9 .
- the axial dimension of the hollow shaft 71 is designed so as to be larger than the width of the pump case (the body portion 8 and the cover portion 7 of the vane pump 70 ), and the distal end (right end in FIG. 9 ) of the hollow shaft 71 is protruded (protruding portion 71 A) from the pump case end portion (right end in FIG. 9 , the body portion 8 side).
- the plurality of accommodating portions 71 B for accommodating the engagement balls 72 and the pressing bolts 73 are disposed at the same interval in the circumferential direction.
- the accommodating portions 71 B are formed at the same intervals in the circumferential direction at three spots in total so that a center angle is a 120° interval.
- Each of the accommodating portions 71 B is formed integrally with the hollow shaft 71 , is formed cylindrically, and protrudes outwardly from the outer peripheral surface of the hollow shaft 71 .
- the hollow portion of the accommodating portion 71 B is formed so as to extend in the radial direction of the hollow shaft 71 , and a female screw being screwed with the pressing bolt 73 is formed in the inner peripheral surface of the hollow portion.
- a sectional area of an opening in the inner end portion in the radial direction of the accommodating portion 71 B is designed so as to be smaller 1 than a sectional area of the engagement ball 72 .
- a distal end side (an end portion in the radial direction of the hollow shaft 71 ) of the engagement ball 72 merely protrudes to the inner peripheral surface side of the hollow shaft 71 from the opening but the entire engagement ball 72 does not moved to the inner peripheral surface side of the hollow shaft 71 .
- the engagement ball 72 is pressed inwardly in the radial direction by the pressing bolt 73 , and a distal end of the engagement ball 72 protrudes uniformly to the outer peripheral surface of the input shaft 103 (see FIG. 1 ) from the inner peripheral surface of the hollow shaft 71 , presses the input shaft 103 and connects (couples) the input shaft 103 and the hollow shaft 71 .
- the input shaft 103 and the hollow shaft 71 are not relatively moved (without rattling) in the circumferential direction and in the radial direction of the hollow shaft 71 and coupled in a manner that the shaft cores of the input shaft 103 and the hollow shaft 71 are matched or aligned.
- the number of accommodating portions is not limited to three.
- the accommodating portions may be provided in two if they are disposed at an equal interval in the circumferential direction of the hollow shaft 71 , or may be provided in four or more. However, as shown in FIG. 9 , if three accommodating portions 71 B are provided, it is excellent as regard a balance of power and efficiency of tightening.
- the number of accommodating portions is not particularly limited if the shaft cores of the input shaft 103 and the hollow shaft 71 are not offset.
- the accommodating portion 71 B may be formed integrally with the hollow shaft 71 as shown in FIG. 9 , but may be formed separately from the hollow shaft 71 .
- FIG. 9 The other constructions and operative effects of the fifth embodiment in FIG. 9 are similar to those in each of the embodiments shown in FIGS. 1 to 6 , FIG. 7 , and FIG. 8 .
- the mechanism in which the rotation force (torque) is transmitted but the thrust force is not transmitted is constructed by a spline formed on the outer peripheral surface of the input shaft 103 (rotation driving shaft) and the inner peripheral surface of the hollow shaft 81 .
- the spline (a spline portion 81 A of the hollow shaft 81 ) is formed on the inner peripheral surface in a region in the vicinity immediately below the vane 11 (rotor 2 ) located in the vicinity of the center in the axial direction of the hollow shaft 81 merely, and a portion (spline portion) of the hollow shaft 81 in which the spline is formed is indicated by reference character 81 A.
- the spline is formed only on the outer peripheral surface of the input shaft 103 corresponding to the region (the spline portion 81 A of the hollow shaft 81 ) in the vicinity immediately below the vane of the hollow shaft 81 , and the portion (input shaft spline portion) in which the spline of the input shaft 103 is formed is indicated by reference character 103 A.
- the hollow shaft 81 there are large diameter portions 81 B and 81 C, in which the spline is not formed, on a distal end side (the vane pump body portion 8 side: right end side in FIG. 10 ) and on a rear end side (the cover portion 7 side, the left end side in FIG. 10 ), respectively.
- the input shaft 103 on regions in the axial direction corresponding to the large diameter portions 81 B and 81 C in which the spline of the hollow shaft 81 is not formed, there are regions 103 B and 103 C (non-spline portions) in which the spline is not formed, respectively.
- the large diameter portions 81 B and 81 C of the hollow shaft 81 and the non-spline portions 103 B and 103 C of the input shaft 103 construct a lubricant-oil filling space (large diameter portion) in which the lubricant oil (grease oil, for example) is filled.
- lubricant oil grey oil, for example
- the square ring 82 (made of resin or oil-resistant rubber, for example), which is a ring having a square sectional shape, is provided as a sealing member for the lubricant oil on the large diameter portion 81 B on the distal end side (the side separated from the cover portion 7 : right end side in FIG. 10 ).
- the inner diameter of the square ring 82 is substantially equal to the outer diameter of the input shaft 103 .
- the space of the large diameter portion 81 C on the rear end side (the left end side in FIG. 10 ) is closed by a housing of the transmission device 101 , and the grease oil can be sealed.
- the space of the large diameter portion 81 B on the distal end side (right end side in FIG. 10 ) is sealed by providing the square ring 82 on the outer peripheral surface of the non-spline portion 103 B on which no spline is engraved in the input shaft 103 , and the grease-filled state can be maintained.
- the torque fluctuation specific to the internal combustion engine operates to the splines through the input shaft, the teeth of the male and female splines collide against each other (teeth are hit by each other), and there, surfaces of the teeth of the splines are damaged.
- FIG. 10 The other constructions and operative effects of the sixth embodiment shown in FIG. 10 are similar to those in each of the embodiments shown in FIGS. 1 to 6 , FIG. 7 , FIG. 8 , and FIG. 9 .
- the square ring 82 can be installed as it is.
- FIG. 11(A) in a case that the spline is formed on the whole region in the axial direction of the hollow shaft 91 of the vane pump 90 , in order to provide the square ring 82 for sealing as shown in FIG. 10 , it is necessary to cut off the spline (on the inner peripheral surface of the hollow shaft) on (the distal end side (right end side in FIG. 11 ) of the hollow shaft 91 ) the region in which the square ring 82 should be installed by machining so as to form a cylindrical surface, and to install the square ring 82 at the spot after the machining.
- the spline seal 92 (made of resin) is used as a sealing member for the lubricant oil, and then, on the outer periphery surface of the spline seal 92 , there are plurality of projection-and-recess which corresponds to the female spline on the inner peripheral surface of the hollow shaft 91 .
- the spline seal 92 is assembled from the distal end side (right end side in FIG. 11 ) of the hollow shaft 91 , the outer peripheral surface of the input shaft 103 is inserted into the space on the inner side in the radial direction of the spline seal 92 , and then, the male spline of the input shaft 103 and the female spline on the inner peripheral surface of the hollow shaft 91 are engaged.
- the spline seal 92 has the projection-and-recess surface formed on the outer periphery corresponding to the female spline of the hollow shaft 91 , the male spline of the input shaft 103 and the female spline of the hollow shaft 91 can be sealed. Therefore, it is not necessary to cut off the spline (on the inner peripheral surface of the hollow shaft 91 ) by machining in order to form the cylindrical surface, at the spot where the spline seal 92 should be installed. And while the female spline is formed over the entire length of the hollow shaft 91 , the lubricant oil can be sealed therein without increasing a machining cost.
- the input shaft 103 of the transmission device 101 is inserted into the hollow portion of the hollow shafts 1 , 21 , 51 , 61 , 71 , 81 , 91 , however, the output shaft 105 of the motor 102 (driving source) such as a motor can be inserted into the hollow portion of the hollow shafts 1 , 21 , 51 , 61 , 71 , 81 , 91 , for example.
- driving source such as a motor
Abstract
Description
- The present invention relates to a vane pump.
- Various types of a vane pump, which includes a cam ring with an internal space having a non-circular sectional shape and a rotor having a circular sectional shape and a vane (blade) moving freely in a radial groove being machined into a rotor, have been proposed (see
Patent Literature 1, for example). - Such vane pump is applied in a manner that a vane pump is mounted on a transmission device, in some cases.
- In the prior art, as shown in
FIG. 12 , in a case that the vane pump 100 (or a gear pump) in the prior art is used so as to be mounted on thetransmission device 101, asecond shaft 104 for driving the vane pump 100 (or the gear pump) is provided in thetransmission device 101, in addition to aninput shaft 103 to which power is transmitted from a driving source 102 (such as an engine, for example). And theshaft 103 and thesecond shaft 104 are offset. - In
FIG. 12 , anoutput shaft 105 of thedriving source 102 is coupled with theinput shaft 103 of thetransmission device 101 by afirst coupling 106. Inside thetransmission device 101, agear 107 is coupled with theinput shaft 103, thegear 107 is engaged with agear 108, and thegear 108 is coupled with thesecond shaft 104. And thesecond shaft 104 supplies power to thevane pump 100 by asecond coupling 109. - The
gears second shaft 104 offset theinput shaft 103. - However, in constructions shown in
FIG. 12 , there are mechanical losses in each of a spot in which theshaft 103 is coupled with thegear 107, a engaged portion between thegear 107 and thegear 108, a coupled spot between thegear 108 and thesecond shaft 104, a spot in which thesecond shaft 104 is coupled with thevane pump 100 and the like, and there is a problem that efficiency in a portion, in which the transmitted power to theshaft 103 is further transmitted to thevane pump 100, is lowered. - Moreover, it is necessary to carryout a step for matching the
second shaft 104 with a rotation center axis of thevane pump 100, that is, a so-called “centering” step. -
-
Patent Literature 1 - Non-examined Japanese Patent Application Publication No. 2012-163040
- The present invention was proposed in view of the above-mentioned problem of the prior art and an object of present invention is to provide a vane pump which can prevent lowering of power transmission efficiency when the vane pump is used in combination with a transmission device, for example.
- A vane pump (10, 20, 50, 60, 70, 80, 90) of the present invention is characterized in that:
- the pump comprises a hollow shaft (1, 21, 51, 61, 71, 81, 91),
- the hollow shaft (1, 21, 51, 61, 71, 81, 91) is constructed such that a rotation driving shaft (the
input shaft 103 of thetransmission device 101 as shown inFIG. 1 , for example: including an input shaft to which an input is directly transmitted so that the driving force is transmitted to the transmission device from thedriving source 102 without through a coupling) of a driving source (102) can be inserted into a hollow portion, and that - the hollow shaft (1, 21, 51, 61, 71, 81, 91) and the rotation driving shaft (103) are coupled (connected or engaged) by a mechanism for transmitting a torque but transmitting no thrust.
- In the present invention, a rotor (2, 22) is preferably mounted on the hollow shaft (1, 21, 51, 61, 71, 81, 91).
- Here, it is preferable that the hollow shaft (1, 21, 51, 61, 71, 81, 91) and the rotor (2, 22) are mounted in a manner that relative rotation is not possible and movement in an axial direction is limited by a wire ring (3, 23), and that the wire ring (3, 23) is disposed across a shaft-side recess portion (1A) and a rotor-side stepped portion (2A) in a state that the shaft-side recess portion (1A) formed on the hollow shaft (1, 21, 51, 61, 71, 81, 91) and the rotor-side stepped portion (2A) formed on the rotor (2, 22) are aligned.
- In this case, the rotor-side stepped portion (2A) is formed on both side surfaces of the rotor (2, 22), and a depth dimension (d1) of the rotor-side stepped portion (2A) is preferably larger than a diameter (D1) of a wire material of the wire ring (3, 23).
- Moreover, in the present invention, it is preferable that mechanical seal (4A, 4B, 24A, 24B) is provided on both end portions in the axial direction of the hollow shaft (1, 21), and a circuit (5, 25: relief circuit for protection) for communicating the mechanical seals (4A, 4B, 24A, 24B) on the both end portions each other.
- In carrying out of the present invention, the rotor (2) and a cam ring (6) may be provided one respectively or may be provided in plural (two each, for example).
- In the present invention, the mechanism for transmitting a torque but transmitting no thrust may be a female spline and a male spline formed on an inner peripheral surface of the hollow shaft (1, 21, 51, 81, 91) and an outer peripheral surface of the rotation driving shaft (103), or may be a key (52) and a keyway (53).
- Moreover, the mechanism for transmitting a torque but transmitting no thrust preferably may be constructed by an engagement groove (61B) penetrating the hollow shaft (61), a through hole of the rotation driving shaft (103) and a spring pin (62) being capable of insertion into the engagement groove (61B) and the through hole.
- Alternatively, it is possible to form a plurality of accommodating portions (71B) at an equal interval in a circumferential direction of the hollow shaft (71), a spherical member (72: engagement ball) and a radial direction pressing member (73: pressing bolt) for pressing the spherical member (72) inwardly in the radial direction are accommodated in the accommodating portion (71B), and a plurality of the spherical members (72: engagement ball) is pressed inwardly in the radial direction so that the hollow shaft (71) and the rotation driving shaft (103) can be coupled.
- In the present invention, it is preferable that the mechanism for transmitting a torque but transmitting no thrust is constructed by splines formed on the outer peripheral surface of the rotation driving shaft (103) and the inner peripheral surface of the hollow shaft (81), the splines are formed only in regions (regions immediately below the vane) in the vicinity of the vane in the axial direction of the rotation driving shaft (103) and the hollow shaft (81), a region where the splines are not provided in the rotation driving shaft (103) and the hollow shaft (81) constructs a lubricant-oil filling space (large diameter portion) in which a lubricant oil (grease oil, for example) is filled, and a sealing member (82: a square ring, for example) for the lubricant oil is provided in a region on a side separated from a cover portion (7).
- Alternatively, it is preferable that the mechanism for transmitting a torque but transmitting no thrust is constructed by splines formed on the whole region in the axial direction of the outer peripheral surface of the rotation driving shaft (103) and the inner peripheral surface of the hollow shaft (91), a sealing member (92: a spline seal) for the lubricant oil is disposed in a region on a side separated from the cover portion (7), the sealing member (92) has projections and recesses formed on an outer periphery thereof, and that the projections and recesses are formed so as to correspond to the spline (female spline) formed on the inner peripheral surface of the hollow shaft (91).
- Moreover, in the present invention, the hollow shaft (51, 61, 71, 81, 91) is preferably supported by a supporting member disposed on a side being separated from the cover portion (7) and a supporting member disposed in the vicinity of the cover portion (7).
- In this case, instead of the circuit (5, 25: relief circuit for protection) communicating the mechanical seal (4A, 4B, 24A, 24B) on the both end portions in the axial direction of the hollow shaft (1, 21) each other, it is preferably to provide a circuit (55) communicating the mechanical seal (4B, 24B) on the cover portion (7, 27) side with an intake portion (intake port 14).
- According to the vane pump (10, 20, 50, 60, 70, 80, 90) of the present invention comprising the above-mentioned constructions, the vane pump (10, 20, 50, 60, 70, 80, 90) includes the hollow shaft (1, 21, 51, 61, 71, 81, 91), by inserting the rotation driving shaft (the
input shaft 103 of thetransmission device 101, for example) of the driving source (102) into the hollow portion of the hollow shaft (1, 21, 51, 61, 71, 81, 91), and by coupling the hollow shaft (1, 21, 51, 61, 71, 81, 91) and the rotation driving shaft (103) by the mechanism (splines, key and keyway and the like) for transmitting a torque but transmitting no thrust, the vane pump (10, 20, 50, 60, 70, 80, 90) is rotated/driven by the rotation driving shaft (105) of the driving source (102) without interposing a coupling separately. - As a result, when the vane pump (10, 20, 50, 60, 70, 80, 90) is used in a manner that the vane pump is attached to another device (the
transmission device 101, for example), for example, since the vane pump (10, 20, 50, 60, 70, 80, 90) is directly rotated/driven by the input shaft (103) of the transmission device (101), for example, it is not necessary to provide a gear mechanism (thegear mechanisms transmission device 101 shown inFIG. 12 ) for transmitting rotation driving force or a shaft (thesecond shaft 104, for example: seeFIG. 12 ) for rotating/driving the vane pump separately, and it is not necessary to provide a coupling mechanism between the vane pump (10, 20, 50, 60, 70, 80, 90) and the driving shaft. Thus, there is not various transmission losses in coupling (thesecond coupling 109 inFIG. 12 ), an engaged portion between the input shaft and the gear, engaged portions between the gears and the like, transmission efficiency of the rotation driving force input into the vane pump (10, 20, 50, 60, 70, 80, 90) of the present invention is improved, and the transmission device (101) can be made smaller. - Moreover, since it is not necessary to separately provide the shaft (the second shaft 104: see
FIG. 12 ) for rotating/driving vane pump, a bearing for supporting/bearing the shaft for rotating/driving vane pump is not necessary, the gear mechanism for transmitting rotation driving force is not necessary either, the number of constructional components of a device on which the vane pump (10, 20, 50, 60, 70, 80, 90) of the present invention is mounted is largely reduced, and then component management becomes extremely easy. - And then, since it is only necessary that the power transmission shaft (the
input shaft 103 of thetransmission device 101, for example) is inserted into the hollow portion of the hollow shaft (1, 21, 51, 61, 71, 81, 91) of the vane pump (10, 20, 50, 60, 70, 80, 90), a labor and/or cost for assembling is remarkably reduced. - Moreover, according to the present invention, since the rotation driving shaft (a solid shaft: the
input shaft 103 of thetransmission device 101 shown inFIG. 1 , for example) of the driving source (102) is inserted into the hollow portion of the inner side in the radial direction of the hollow shaft (1, 21, 51, 61, 71, 81, 91), even if a force (a force in a thrust direction) in the rotation shaft direction operates on the rotation driving shaft (103, input shaft), the rotation driving shaft (103) merely slides on the hollow portion of the hollow shaft (1, 21, 51, 61, 71, 81, 91), and the hollow shaft (1, 21, 51, 61, 71, 81, 91) does not load (receive) the force in the axial direction. Thus, in the present invention, a fastening force operating when the vane pump is attached to the driving source does not transmit to the driving source (102) through the hollow shaft (1, 21, 51, 61, 71, 81, 91). - Here, in a case that the driving source (102) is an internal combustion engine, it is necessary to provide a bearing (a bearing bush, for example) for supporting the hollow shaft (1, 21, 51, 61, 71, 81, 91) in the radial direction. However, in a case that the driving source (102) is an electric motor, it is possible to delete (omit) such a bearing (a bearing bush, for example) for supporting the hollow shaft (1, 21, 51, 61, 71, 81, 91) in the radial direction.
- In the present invention, by mounting the rotor (2, 22) on the hollow shaft (1, 21, 51, 61, 71, 81, 91), it is possible to prevent a situation such that the hollow shaft (1, 21, 51, 61, 71, 81, 91) is removed from the vane pump (10, 20, 50, 60, 70, 80, 90).
- Here, since the rotation driving shaft (solid shaft: the
input shaft 103 of thetransmission device 101 shown inFIG. 1 , for example) of the driving source (102) is inserted into the hollow portion on the inner side in the radial direction of the hollow shaft (1, 21, 51, 61, 71, 81, 91), even if the force (a force in the thrust direction) operates in the rotation shaft direction on the rotation driving shaft (103), the rotation driving shaft (103) merely slides on the hollow portion of the hollow shaft (1, 21, 51, 61, 71, 81, 91), and the hollow shaft (1, 21, 51, 61, 71, 81, 91) does not load the force in the axial direction. Thus, even if the rotor (2, 22) is mounted on the hollow shaft (1, 21, 51, 61, 71, 81, 91), the force in the axial direction of the rotation driving shaft (103) of the driving source (102) is not transmitted to the rotor (2, 22). - Then, by mounting the hollow shaft (1, 21, 51, 61, 71, 81, 91) and the rotor (2, 22) so that the relative rotation is impossible and that the movement in the axial direction is limited by the wire ring (3, 23), and by disposing (positioning) the wire ring (3, 23) in the mode that the wire ring across the shaft-side recess portion (1A) and the rotor-side stepped portion (2A) in a state in which the shaft-side recess portion (1A) formed on the hollow shaft (1, 21, 51, 61, 71, 81, 91) and the rotor-side stepped portion (2A) formed on the rotor (2, 22) are aligned, a gap is generated in a mounting portion of the hollow shaft (1, 21, 51, 61, 71, 81, 91) and the rotor (2, 22), and even if the hollow shaft (1, 21, 51, 61, 71, 81, 91) is moved in the axial direction, the rotor (2, 22) is not moved for the gap portion, and the rotor (2, 22) is prevented to collide against to the cover portion (7, 27), a pressure plate (18, 38) or an intermediate plate (40).
- Here, the rotor-side stepped portion (2A) is formed on both side surfaces of the rotor (2, 22), and if the depth dimension (d1) of the rotor-side stepped portion (2A) is larger than the diameter (D1) of the wire rod of the wire ring (3, 23), the wire ring (3, 23) can be accommodated inside the rotor (2, 22), the rotor (2, 22) is prevented to interfere with the wire ring (3, 23), and design of pump construction on the both side surfaces of the rotor (2, 22) become easy.
- In the present invention, in some cases, the mechanical seal (4A, 4B, 24A, 24B) are disposed on both end portions in the axial direction of the vane pump (10, 20).
- However, in the prior-art vane pump, the mechanical seal is provided only on one side (an end portion being close to an equipment supplying power, for example) in the axial direction, but the mechanical seal is not provided on the other (the end portion being separated from the equipment supplying power, for example). Then, a relief circuit for relieving a pressure operating on the mechanical seal is also provided only on the end portion on a side to which the mechanical seal is provided, while the relief circuit is not formed on the other (the end portion being separated from the equipment supplying power, for example), and thus, in a case that the constructions of the prior-art vane pump is applied to the present invention, it is possible that the mechanical seal provided on the other is broken.
- On the other hand, in the present invention, by providing a circuit (5, 25: relief circuit for protection) communicating the mechanical seal (4B, 24B) on the other (the end portion being separated from the equipment supplying power, for example) with the mechanical seal (4A, 24A) on the one (the end portion close to the equipment supplying power, for example), the pressure operating on the other mechanical seal (4B, 24B) can be relieved to the relief circuit (9, 29) for mechanical seal through the circuit (5, 25).
- In the present invention, in a case that the hollow shaft (51, 61, 71, 81, 91) is supported by the supporting member disposed on a side separated from the cover portion (7) and the supporting member disposed in the vicinity of the cover portion (7), since the hollow shaft (51, 61, 71, 81, 91) is supported at two spots being separated in the axial direction, that is, the hollow shaft is supported by a manner so-called both-end supporting, and thus, the hollow shaft (51, 61, 71, 81, 91) can be accurately centered with the rotation driving shaft (103) and pump efficiency can be improved, as compared with the case of supporting with a single supporting member. The supporting member may be a bearing bush (19, 54) or may be constructed as direct receiving by forming a film of a material which improves abrasion resistance on a surface of an insertion hole for the hollow shaft (51, 61, 71, 81, 91) of the case (8) or the cover portion (7).
- In this case, by providing the supporting member (bearing bush 54) disposed in the vicinity of the cover portion (7), the circuit (
relief circuit hollow shaft 1, 21) communicating the mechanical seals (4A, 4B, 24A, 24B) on the both end portions in the axial direction of the hollow shaft (51, 61, 71, 81, 91) each other cannot be constructed any more. - However, in the present invention, in a case that the circuit (55) communicating the mechanical seal (4B, 24B) on the cover portion (7, 27) side and the intake portion (intake port 14) is provided, the pressure operating on the mechanical seal (4B, 24B) on the cover portion side can be relieved to the intake portion (intake port 14) by the circuit (55). And a length dimension and pipe resistance of the circuit (55) communicating the mechanical seal (4B, 24B) on the cover portion (7, 27) side and the intake portion (intake port 14) are smaller than the length dimension and pipe resistance of the circuit (5, 25) communicating the mechanical seals (4A, 4B, 24A, 24B) on the both end portions in the axial direction of the hollow shaft (1, 21), and thus, the pressure operating on the mechanical seal (4B, 24B) on the cover portion side can be relieved reliably and an operative effect as the relief circuit is reliably carried on.
- In the present invention, in a case that the mechanism for transmitting a torque but transmitting no thrust is constructed by the splines formed on the outer peripheral surface of the rotation driving shaft (103) and on the inner peripheral surface of the hollow shaft (81), the splines is only formed in the region (region immediately below the vane) in the vicinity of the vane in the axial direction of the rotation driving shaft (103) and the hollow shaft (81), the lubricant-oil filling space (large diameter portion) is constructed in which space a lubricant oil (grease oil, for example) is filled in the region where the splines of the rotation driving shaft (103) and the hollow shaft (81) are not provided, and the sealing member (82: a square ring, for example) for the lubricant oil in the region on the side separated from the cover portion (7) is provided, even if the lubricant oil is filled in the lubricant-oil filling space, the lubricant oil is sealed by the sealing material (82) and the state in which the lubricant oil is filled can be maintained.
- In a case that the driving source is an internal combustion engine, torque fluctuation being specific to the internal combustion engine generates the collisions of teeth of the male and female splines against each other (teeth are hit by each other) through the rotation driving shaft (103) and the hollow shaft (81, 91), and therefore, a tooth surface of the spline is damaged, however, by filling the lubricant oil in the lubricant-oil filling space, the lubricant oil is interposed between teeth of the male and female splines and a buffer operation is carried on by the lubricant oil as a cushion, and thus, damage on the tooth surface caused by the collision between the teeth is reduced.
- Here, in a case that a sealing member for lubricant oil such as a square ring should be installed, for example, if the mechanism for transmitting a torque but transmitting no thrust is constructed by the splines formed on the whole regions in the axial direction on the outer peripheral surface of the rotation driving shaft and the inner peripheral surface of the hollow shaft, it is necessary to cut off the spline (of the inner peripheral surface of the hollow shaft) at a place where the sealing member for the lubricant oil should be installed by machining so as to form a cylindrical surface, and then, it is necessary to provide a square ring.
- On the other hand, in the present invention, if the sealing member (92: spline seal) of the lubricant oil to be provided in the region on the side being separated from the cover portion (7) is constructed by a sealing member (92: spline seal) with projections and recesses formed on the outer periphery thereof, the projections and recesses being formed corresponding to the spline (female spline) are formed on the inner peripheral surface of the hollow shaft (91), without cutting off the spline (of the inner peripheral surface of the hollow shaft) at a place where the sealing member for the lubricant oil should be provided by machining so as to form a cylindrical surface, or without increasing a machining cost of the hollow shaft (91), the sealing member (92: spline seal) for the lubricant oil can be provided, by assembling the spline seal (92) from a distal end side (right end side in
FIG. 11 ) of the hollow shaft (91) in a manner that sealing the male and female splines in a state where the spline of the rotation driving shaft (103) and the spline of the hollow shaft (91) are engaged with each other, and by inserting the outer peripheral surface of the rotation driving shaft (103) into the space inward in the radial direction of the spline seal (92). -
FIG. 1 is a sectional view showing an outline of an embodiment of the present invention. -
FIG. 2 is a sectional view showing a first embodiment of the present invention. -
FIG. 3 is an A-B line arrow-view sectional view ofFIG. 2 . -
FIG. 4 is an explanatory view showing a manner that a rotor is mounted on a hollow shaft by a wire ring. -
FIG. 5 is an explanatory view schematically showing a circuit for relieving a pressure operating on a mechanical seal. -
FIG. 6 is a sectional view showing a second embodiment of the present invention. -
FIG. 7 shows a third embodiment of the present invention, in whichFIG. 7(A) is a sectional view andFIG. 7(B) is a partial side view showing a state that a key and a keyway are engaged with each other. -
FIG. 8 shows a fourth embodiment of the present invention, in whichFIG. 8(A) is a sectional view andFIG. 8 (B) is a partial plan view showing a state that a spring pin is engaged. -
FIG. 9 shows a fifth embodiment of the present invention, in whichFIG. 9(A) is a sectional view andFIG. 9(B) is a partial side view showing a state that an input shaft is fixed to a hollow shaft. -
FIG. 10 is a sectional view showing a sixth embodiment of the present invention. -
FIG. 11 are views showing a variation of the sixth embodiment of the present invention, in whichFIG. 11 (A) is a sectional view, andFIG. 11(B) is a partial side view showing the hollow shaft when a spline seal is installed. -
FIG. 12 is an explanatory view schematically showing a state in which a prior-art vane pump is mounted on a transmission device. - Embodiments of the present invention will be described below by referring to the attached drawings.
- First, by referring to
FIG. 1 , a summary of the embodiments of the present invention will be described. The same members described by referring toFIG. 12 are given the same reference numerals, and description will be omitted. - In
FIG. 1 , theoutput shaft 105 of the driving source 102 (for example, an internal combustion engine) is coupled with theinput shaft 103 of thetransmission device 101 through thecoupling 106, and the vane pump 10 (or 20) is disposed on an end surface TF on the drivingsource 102 side of thetransmission device 101. - The vane pump 10 (20) includes the hollow shaft 1 (or 21) and a female spline is engraved on the inner peripheral surface of the
shaft 1 over the axial direction. Into the hollow portion of the hollow shaft 1 (21), the input shaft 103 (coupled with the rotation driving shaft of the drivingsource 102 through the coupling 106) of thetransmission device 101 is inserted. - Though not shown clearly in drawings, the
input shaft 103 of thetransmission device 101 is reliably supported by a rolling bearing (not shown) on thetransmission device 101 side. - As shown in
FIG. 1 , the vane pump 10 (20) is directly mounted on theinput shaft 103 of thetransmission device 101. And in the input shaft 103 (the rotation driving shaft of the driving source 102) of thetransmission device 101, a male spline fitted with the female spline is engraved in the outer peripheral surface overlapped with the hollow shaft 1 (21) of the vane pump 10 (20) so that power transmission from theinput shaft 103 to the hollow shaft is carried out by spline fitting between the female spline and the male spline. - Thus, without providing other coupling (such as the
second coupling 109 inFIG. 12 , for example), theinput shaft 103 of thetransmission device 101 directly rotates/drives the vane pump 10 (20). - Moreover, in the embodiment shown in
FIG. 1 , since the vane pump 10 (20) is directly rotated/driven by theinput shaft 103 of thetransmission device 101, it is not necessary to provide a gear mechanism (gears 107, 108 inFIG. 12 ) or the second shaft 104 (FIG. 12 ) inside thetransmission device 101. - That is, in the embodiment, there is no loss in engagement portions between the
shaft 103 and thegear 107, thesecond shaft 104 and thegear 108, and thegear 107 and thegear 108 generated in the case of the prior art inFIG. 12 , and there is no loss, either, in the coupling (thesecond coupling 109 inFIG. 12 ) which couple the vane pump 10 (20) with thesecond shaft 104. Therefore, the transmission efficiency is improved and the transmission device (101) can be made smaller. - Moreover, in the embodiment shown in
FIG. 1 , since the second shaft 104 (shown inFIG. 12 illustrating the prior art) is not provided, a bearing for supporting the second shaft 104 (FIG. 12 ) is not needed either, and since it is not necessary to provide the gear mechanism inside thetransmission device 101 either, as described above, the number of constructional components is reduced largely, and component management becomes extremely easy. - Furthermore, since it is merely necessary that the
input shaft 103 of thetransmission device 101 is inserted into (fitted with) the hollow shaft 1 (21) of the vane pump 10 (20), centering of the hollow shaft 1 (21) and theinput shaft 103 of thetransmission device 101 is not necessary. Thus, working cost of the assembling process is remarkably reduced. - Next, by referring to
FIGS. 2 to 5 , the first embodiment of the present invention will be explained. - The first embodiment shown in
FIGS. 2 to 5 is an embodiment according to the vane pump of a type in which a cam ring and a rotor are provided one respectively. - In
FIGS. 2 and 3 , thehollow shaft 1 is disposed at the center of thevane pump 10, and as shown inFIG. 3 , the inner peripheral surface of thehollow shaft 1 is constructed so as to be shaped as a female spline shaft. Since a spline shape is constructed in thehollow shaft 1, in thehollow shaft 1, vicinities of upper and lower ends are illustrated by three line segments, inFIG. 2 . - In a case that the
vane pump 10 is mounted on thetransmission device 101 as shown inFIG. 1 , for example, the input shaft 103 (solid shaft:FIG. 1 ) of thetransmission device 101 is inserted into the hollow portion of the spline-shapedhollow shaft 1. - In
FIGS. 2 and 3 , the surface outward in the radial direction of the spline-shapedhollow shaft 1 is mounted on the inner peripheral surface of therotor 2 by spline fitting and incapable of relative rotation, then therotor 2 is rounded by rounds of thehollow shaft 1. Therotor 2 may be mounted on thehollow shaft 1, incapable of axial movement, but in this embodiment, it is preferable that therotor 2 is mounted on theshaft 1 so as to limit movement of therotor 2 in the axial direction, as written hereinafter. - On the
rotor 2, a plurality ofradial vane grooves 11G (FIG. 3 ) extending in the radial direction is formed, and thevane 11 is inserted into thevane groove 11G. - A
vane 11 is constructed movably in the radial direction along thevane groove 11G, and a part of a pressure oil ejected from anejection port 16 during driving of the vane pump is supplied to a pressure-oil storage portion 12 for vane through acircuit 17 for pressure loading (pressure loading), whereby thevane 11 is urged outward in the radial direction and protruded, and an end portion outward in the radial direction of thevane 11 slides on the inner peripheral surface of thecam ring 6. Here, the pressure-oil storage portion 12 for vane is formed in the rotor 2 (refer toFIG. 3 ). - During driving of the
vane pump 10, therotor 2 is rotated in an arrow A direction (FIG. 3 ), and with the rotation of therotor 2, a working fluid flows into a pump chamber α from theintake port 14 in thevane pump 10 through anintake circuit 13 of thecam ring 6. Here, the pump chamber α is defined by theadjacent vane 11, the outer surface of therotor 2, and the inner peripheral surface of thecam ring 6. - A position of the pump chamber α is changed with the rotation of the rotor 2 (corresponding to a circumferential position of the cam ring 6), and a size (volume) of the pump chamber α is also changed with the rotation of the rotor 2 (corresponding to the circumferential position of the cam ring 6).
- That is, the working fluid supplied from the
intake port 14 flows into the pump chamber a via theintake circuit 13. Then, by means of contracting the volume of the pump chamber as, a pressure is applied and the working fluid is ejected from theejection port 16 via anejection circuit 15. - As shown in
FIG. 2 , thevane pump 10 includes abody portion 8 and thecover portion 7. - In the
body portion 8, thehollow shaft 1, therotor 2, the vane 11 (movable in the vane groove of the rotor 2), and thecam ring 6 are accommodated. - Then, in
FIG. 2 , thepressure plate 18 is disposed in thebody portion 8. As described above, thecircuit 17 for pressure loading supplying the pressure oil to the pressure-oil storage portion 12 for vane is formed on thepressure plate 18. - In the
body portion 8 accommodating therotor 2, thecam ring 6 and the like, thecover portion 7 is disposed on its opening side (left side inFIG. 2 ), and thecover portion 7 is fixed to thebody portion 8. - As shown in
FIG. 2 , theintake port 14 for the working fluid is provided in thebody portion 8, and theintake port 14 communicates with theintake circuit 13 for the working fluid on thecam ring 6 side (inner side in the radial direction). - Moreover, the
ejection circuit 15 for the working fluid is provided in thebody portion 8, and theejection circuit 15 communicates with anoutlet port 16 for the working fluid. - Since the rotation driving shaft (the
input shaft 103 of thetransmission device 101 shown inFIG. 1 , for example: not shown inFIG. 2 ) is inserted into the hollow portion on the inner side in the radial direction of thehollow shaft 1, even if the force in the rotation shaft direction (force in the thrust direction) operates on the rotation driving shaft (input shaft 103, for example), the rotation shaft only slides on the hollow portion of thehollow shaft 1. In other words, even if the force in the axial direction (thrust direction) of the input shaft 103 (FIG. 1 ) of thetransmission device 101 operates, for example, thehollow shaft 1 does not load the force in the axial direction (force in the thrust direction). Thus, even if therotor 2 is mounted on thehollow shaft 1, the force in the axial direction (force in the thrust direction) operating on the rotation driving shaft (input shaft 103 of the transmission device 101) is not transmitted to therotor 2, and an inconvenience such as damage on therotor 2 by the force (force in the thrust direction) does not happened. Therefore, therotor 2 can be mounted on thehollow shaft 1. - Here, by mounting the
rotor 2 on thehollow shaft 1, there is an operative effect that thehollow shaft 1 is prevented to be removed from thevane pump 10. - In order to rotate the
rotor 2, it is necessary to be a gap (approximately 10 μm, for example) between therotor 2 and thecover portion 7 adjacent to therotor 2 or thepressure plate 18. Here, if therotor 2 and thehollow shaft 1 are completely fixed (incapable of relative rotation and incapable of axial movement), in a case that thehollow shaft 1 is moved in the axial direction, there is inconvenience that therotor 2 collides against thecover portion 7 or thepressure plate 18. - Reversely, in the embodiments shown in drawings, as a manner that the
rotor 2 is mounted on thehollow shaft 1 by thewire ring 3 so as to limit movement in the axial direction, as shown inFIG. 4 , on thecover portion 7 side and on thepressure plate 18 side with respect to therotor 2, the shaft-side recess portion 1A is formed on thehollow shaft 1 side and the steppedportion 2A is formed on therotor 2 side. And in the state in which the hollow shaft-side recess portion 1A and the rotor-side steppedportion 2A are aligned, thewire ring 3 is disposed so as to be place across the hollow shaft-side recess portion 1A and the rotor-side steppedportion 2A. Moreover, the male spline is engraved on the surface between the shaft-side recess portions portions hollow shaft 1 to therotor 2, theshaft 1 androtor 2 are coupled by spline-fitting the male spline and the female spline as a manner that theshaft 1 androtor 2 are incapably relating to rotation thereof. - Here, the rotor-side stepped
portion 2A is formed on the both side surfaces of therotor 2. InFIG. 4 , the depth dimension d1 is expressed smaller than the diameter D1 of the wire rod of thewire ring 3, but the depth dimension d1 of the rotor-side steppedportion 2A is preferably larger than the diameter D1 of the wire rod of the wire ring 3 (seeFIGS. 7 to 11 ). That is because, if the depth dimension d1 of the rotor-side steppedportion 2A is larger than the diameter D1 of the wire rod of thewire ring 3, thewire ring 3 is accommodated in therotor 2, and there is no more concern of interference with thewire ring 3, and thus, the design of the pump construction on the both side surfaces of therotor 2 is made easy. - By being constructed as the manner shown in
FIG. 4 , when thehollow shaft 1 and therotor 2 are mounted by thewire ring 3, the gap is generated between thehollow shaft 1 and therotor 2. By means of the presence of such the gap, even if thehollow shaft 1 is moved in the axial direction, an allowance is generated between therotor 2 and thecover portion 7 or thepressure plate 18 for a portion of the gap, and thus, the collision between therotor 2 and thecover portion 7 or thepressure plate 18 is prevented by the allowance. - As described above, in
FIG. 2 , even if the force in the axial direction (the force in the thrust direction) of the input shaft 103 (FIG. 1 ) of thetransmission device 101 operates, for example, thehollow shaft 1 does not load the force in the axial direction, but theinput shaft 103 merely slides on the hollow portion in thehollow shaft 1. - Moreover, since the rotation driving shaft (
input shaft 103 of the transmission device 101) which is a solid shaft is inserted through the hollow portion in thehollow shaft 1, thehollow shaft 1 is not biased in the radial direction unless the rotation driving shaft (input shaft 103 of the transmission device 101) makes a motion such as precession biased in the radial direction. And then, though not shown clearly, since the rotation driving shaft (input shaft 103 of thetransmission device 101, for example) which is a solid shaft is reliably supported by the rolling bearing (not shown) on thetransmission device 101 side, it is not biased in the radial direction. - However, in a case that such a situation occurs that the
hollow shaft 1 is biased in the radial direction, inconvenience situation is happened in thevane pump 10. Therefore, in preparation for such situation (the situation in which thehollow shaft 1 is biased in the radial direction), as shown inFIG. 2 , by disposing the bearing bush 19 (sliding bearing) on thebody portion 8 side and by supporting thehollow shaft 1 by means of the bearingbush 19, thehollow shaft 1 is prevented from being biased in the radial direction. - The bearing
bush 19 operates as a sliding bearing, and thus, in the first embodiment shown inFIGS. 2 to 5 , the rolling bearing is omitted and the sliding bearing is merely provided. - Here, in a case that the driving
source 102 is an internal combustion engine, the bearingbush 19 for supporting thehollow shaft 1 in the radial direction is needed. However, in a case that the driving source (102) is an electric motor, the bearingbush 19 for supporting thehollow shaft 1 in the radial direction can be omitted. - As described above, in the first embodiment shown in
FIGS. 2 to 5 , the rolling bearing is not provided but thehollow shaft 1 is supported on thebody portion 8 of thevane pump 10 by the bearingbush 19, but the bearingbush 19 does not have a function of sealing oil, that is, a working fluid. Thus, as shown inFIG. 2 , themechanical seals 4 are disposed on both end portions in the axial direction of the vane pump 10 (thebody portion 8 side end portion and thecover portion 7 side end portion: both right and left end portions inFIG. 2 ). Here, inFIG. 2 , the mechanical seal on thebody portion 8 side end portion is shown by reference numeral “4A”, and the mechanical seal on thecover portion 7 side end portion is shown by reference numeral “4B”. In other words, “themechanical seal 4” is an expression comprehensively indicating themechanical seals - In the case of the prior-art vane pump, as shown in
FIG. 12 , the rotation driving force is supplied by theshaft 104, but theshaft 104 does not penetrate thevane pump 100. Thus, in the case of the prior-art vane pump 100 shown inFIG. 12 , it is not necessary to provide a mechanical seal on a side (right side inFIG. 12 ) separated from thetransmission device 101 in theshaft 104 in thevane pump 100. That is, in the prior art vane pump, the mechanical seal (not shown) is provided only on the end portion close to the equipment (transmission device 101) for supplying power, and there is little necessity to provide the mechanical seal on the end portion separated from the equipment for supplying the power. - Reversely, in the
vane pump 10 according to the first embodiment in which the solid shaft (not shown inFIG. 2 ) penetrates thehollow shaft 1, themechanical seals - Also, in the
body portion 8, therelief circuit 9 for mechanical seal is provided in order to communicate the back portion (left side inFIG. 2 ) of themechanical seal 4A on thebody portion 8 side end portion (right side inFIG. 2 ) with theintake port 14. - Here, in the case of the prior-art vane pump, since the mechanical seal is provided only on one end portion in the axial direction, it is necessary to provide the relief circuit merely on the end portion on the side where the mechanical seal is provided, which relief circuit prevents a situation that a pressure exceeding an allowable value operates to the mechanical seal. Thus, in the prior art, as described above with reference to
FIG. 2 , therelief circuit 9 for mechanical seal (or a circuit corresponding to that) communicating the back portion (left side inFIG. 2 ) of themechanical seal 4A (on the right side) of thebody portion 8 side end portion with theintake port 14 is merely provided. - However, in the embodiments shown in drawings in which the
mechanical seals body portion 8 side end portion and thecover portion 7 side end portion), it is required to provide a mechanism for relieving the pressure operating on themechanical seal 4B (mechanical seal on the end portion separated from the equipment for supplying power: the mechanical seal considered to have little necessity to be provided in the prior art) on the other end portion in the axial direction (left end portion inFIG. 2 and thecover portion 7 side end portion). - Because there is a possibility that a back pressure of the
mechanical seal 4B provided on the other end portion in the axial direction (the left end portion inFIG. 2 and thecover portion 7 side end portion) exceeds an allowable pressure. - In the embodiments shown in drawings, as shown in
FIGS. 2 and 5 , there is a mechanism for relieving the back pressure of themechanical seal 4B on the side where therelief circuit 9 for mechanical seal is not provided. - In
FIGS. 2 and 5 , as described above, therelief circuit 9 for mechanical seal is provided which circuit communicates the back portion of themechanical seal 4A on thebody portion 8 side end portion (right side inFIG. 2 ) with theintake port 14. And the back portion of themechanical seal 4A and the back portion of themechanical seal 4B (mechanical seal on the side separated from therelief circuit 9 for mechanical seal: the mechanical seal on the left side inFIGS. 2 and 5 ) of thecover portion 7 side end portion are communicated through therelief circuit 5 for protection. Thisrelief circuit 5 for protection is provided on a boundary portion between thecover portion 7 as well as thebody portion 8 and thehollow shaft 1, and only onerelief circuit 5 for protection is provided inFIG. 5 , but a plurality of the relief circuits can be provided. - In other words, the
mechanical seal 4B (the mechanical seal on the side separated from therelief circuit 9 for mechanical seal) on thecover portion 7 side end portion communicates with therelief circuit 9 for mechanical seal through therelief circuit 5 for protection. -
Reference numeral 16 shown inFIGS. 2 and 5 indicates an ejection port formed on thebody portion 8. - In
FIGS. 2 and 5 , the pressure operating on the back portion of themechanical seal 4B (mechanical seal on the left side) of thecover portion 7 side end portion is transmitted to therelief circuit 9 for mechanical seal through therelief circuit 5 for protection and themechanical seal 4A (mechanical seal on the right side) of thebody portion 8 side end portion and is relieved into theintake port 14. - Thus, in
FIGS. 2 and 5 , even if a large pressure is generated on the back portion of themechanical seal 4B (mechanical seal on the left side) of thecover portion 7 side end portion, the large pressure is immediately relieved into theintake port 14 through therelief circuit 5 for protection, themechanical seal 4A (mechanical seal on the right side) of thebody portion 8 side end portion and therelief circuit 9 for mechanical seal. Thus, even if the large pressure operates on the back portion of themechanical seal 4B (mechanical seal on the left side) of thecover portion 7 side end portion, breakage of themechanical seal 4B is prevented. - In
FIG. 3 , in order to mount thecover portion 7 and thebody portion 8 on the end surface TF (seeFIG. 1 ) of thetransmission device 101, for example, there are bolt holes H at four spots. By inserting a bolt (not shown) inserting through thecover portion 7 and thebody portion 8 into the bolt hole H, thevane pump 10 is mounted on the end surface TF of thetransmission device 101, for example. When thevane pump 10 is mounted on the end surface TF (FIG. 1 ) of thetransmission device 101, thevane pump 10 is mounted on the end surface TF in a manner that an end surface 7TS (FIG. 2 ) on thecover portion 7 side of thevane pump 10 contacts with on the end surface TF side of thetransmission device 101. - Here, a joining bolt B shown in
FIG. 3 is a bolt for joining thebody portion 8 and thecover portion 7 of thevane pump 10. That is, in a state that thebody portion 8 and thecover portion 7 are joined by the joining bolt B, it is possible to mount thebody portion 8 and thecover portion 7 to the end surface TF of thetransmission device 101, for example, by inserting a bolt, which is not shown, into the bolt hole H. - However, in a case that the
vane pump 10 is mounted on thetransmission device 101, for example, by inserting a bolt, which is not shown, into the bolt hole H, since thebody portion 8 and thecover portion 7 of thevane pump 10 are also integrally joined by the bolt which is not shown, the joining bolt B inFIG. 3 can be omitted. - In the
vane pump 10 according to the embodiment inFIGS. 1 to 5 , by fitting (or inserting) the rotation driving shaft (input shaft 103 of thetransmission device 101, for example) of the drivingsource 102 with the hollow portion of the spline-shapedhollow shaft 1, thevane pump 10 can be directly rotated/driven by therotation driving shaft 103 without interposing another coupling device. - As a result, in a case that the
vane pump 10 is used in a manner that thevane pump 10 is mounted on thetransmission device 101, for example, since thevane pump 10 is directly rotated/driven by theinput shaft 103 of thetransmission device 101, it is not necessary to provide a gear mechanism for transmitting a rotation driving force and a shaft for rotating/driving a vane pump separately, and also, it is not necessary to provide a coupling mechanism between thevane pump 10 and the driving shaft. Thus, there is no transmission loss by coupling, meshing between the gears and the like, transmission efficiency is improved, and it is possible to become thetransmission device 101 smaller. - And then, since the gear mechanism for transmitting a rotation driving force or the like is not necessary, the number of constructional components is largely reduced, and component management becomes extremely easy.
- Moreover, since it is only necessary to insert the power transmission shaft (
input shaft 103 of thetransmission device 101, for example) into the hollow portion of thehollow shaft 1 of thevane pump 10, centering of the power transmission shaft and the hollow portion of thehollow shaft 1 are not necessary, and therefore, a labor cost for assembling work of thevane pump 10 is remarkably reduced. - Moreover, according to the
vane pump 10 of the first embodiment, since the rotation driving shaft (solid shaft: theinput shaft 103 of thetransmission device 101 shown inFIG. 1 , for example) of the drivingsource 102 is inserted into the hollow portion of the inner side in the radial direction of thehollow shaft 1, even if the force in the rotation shaft direction (the force in the thrust direction) operates on the rotation driving shaft 103 (input shaft), therotation driving shaft 103 only slides on the hollow portion of thehollow shaft 1, and thehollow shaft 1 does not load the force in the axial direction. - Moreover, the
hollow shaft 1 is not biased in the radial direction, unless therotation driving shaft 103 which is a solid shaft makes a motion such as precession biased in the radial direction. And then, in a case that therotation driving shaft 103 is reliably supported by a rolling bearing or the like on the rotation driven side (thetransmission device 101, for example), therotation driving shaft 103 is not biased in the radial direction. - Furthermore, according to the
vane pump 10 of the first embodiment, even if the force in the rotation shaft direction (force in the thrust direction) operates on therotation driving shaft 103 of the drivingsource 102, as described above, thehollow shaft 1 does not load the force in the axial direction. Thus, even if therotor 2 is mounted on thehollow shaft 1, the force in the axial direction of therotation shaft 103 of the drivingsource 102 is not transmitted to therotor 2. - And then, since the
hollow shaft 1 and therotor 2 are mounted by thewire ring 3, and thewire ring 3 is disposed in the manner that the wire ring extends across the shaft-side recess portion 1A and the rotor-side steppedportion 2A in the state that the shaft-side recess portion 1A formed on thehollow shaft 1 and the rotor-side steppedportion 2A formed on therotor 2 are aligned, there is a gap in a portion in which thehollow shaft 1 and therotor 2 are mounted, and even if thehollow shaft 1 is moved in the axial direction, the allowance is formed corresponding to the portion of the gap, and therotor 2 is not moved due to the portion of the allowance, and therotor 2 is prevented to collide against thecover portion 7 or thepressure plate 18. - In addition, according to the
vane pump 10 of the first embodiment, since themechanical seals body portion 8 side end portion and thecover portion 7 side end portion) of thevane pump 10, and therelief circuit 5 for protection communicating themechanical seal 4A of thebody portion 8 side end portion with themechanical seal 4B of thecover portion 7 side end portion is provided, themechanical seal 4A is communicated with theintake port 14 through therelief circuit 9 for mechanical seal, the pressure operating on themechanical seal 4B of thecover portion 7 side end portion can be relieved to therelief circuit 9 for mechanical seal via therelief circuit 5 for protection. - Thus, even if an excessive pressure operates on the
mechanical seal 4B of thecover portion 7 side end portion, breakage of themechanical seal 4B is prevented. - Subsequently, the second embodiment of the present invention will be explained hereinafter with reference to
FIG. 6 . - In the first embodiment shown in
FIGS. 2 to 5 , the cam ring and the rotor are provided one respectively, but in the second embodiment shown inFIG. 6 , the cam ring and the rotor are provided two respectively. - Constructions shown in
FIG. 6 which are different from the first embodiment inFIGS. 2 to 5 will be mainly described hereinafter. - In
FIG. 6 , thehollow shaft 21 constructed so as to be shaped as a spline shaft is disposed at the center of thevane pump 20, and in a case that thevane pump 20 is mounted on thetransmission device 101 as shown inFIG. 1 , for example, the input shaft 103 (seeFIG. 1 ) of thetransmission device 101 is inserted into the hollow portion of the spline-shapedhollow shaft 21. - The
vane pump 20 includes thebody portion 28 and thecover portion 27. - The
body portion 28 located on the left side inFIG. 6 accommodates thehollow shaft 21, therotor 22, thevane 31, and thecam ring 26. On the other hand, thecover portion 27 located on the right inFIG. 6 accommodates thehollow shaft 21, therotor 22, thevane 31, and thecam ring 26. Thecover portion 27 covers an opening side of thebody portion 28 and fixes thebody portion 28. - A bearing
bush 39 is disposed in thebody portion 28 and thecover portion 27, respectively, and thehollow shaft 21 is supported in a rotatable manner by the bearingbush 39. - The
pressure plates cover portion 27 side (right side inFIG. 6 ) of therotor 22 and thecam ring 26 accommodated in thebody portion 28 and on the opposite side (left side inFIG. 6 ), and anintermediate plate 40 is disposed in thebody portion 28. - The
pressure plates body portion 28 side (left side inFIG. 6 ) of therotor 22 and thecam ring 26 accommodated in thecover portion 27 and on the opposite side (right side inFIG. 6 ). - The
rotor 22 and thecam ring 26 accommodated in thebody portion 28 and therotor 22 and thecam ring 26 accommodated in thecover portion 27 are disposed by ensuring an appropriate distance by means of theintermediate plate 40. - On the
pressure plates pressure loading circuits pressure loading circuit 37 communicates with a pressure-oil storage portion for vane, not shown, and also communicates with ejection circuits 35-1, 35-2 for the working fluid which will be described hereinafter. - On the
body portion 28 of thevane pump 20, anintake port 34 for the working fluid is provided, and theintake port 34 communicates with a pump chamber (not shown inFIG. 6 ) through anintake circuit 33 of theintermediate plate 40 accommodated in thebody portion 28. - On the
body portion 28 and thecover portion 27, ejection ports 36-1, 36-2 for the working fluid are provided, respectively, and the ejection ports 36-1, 36-2 communicate with the ejection circuits 35-1, 35-2 for the working fluid on thecam ring 26 side (via a circuit, not shown), respectively. - As shown in
FIG. 6 , therotors body portion 28 side and thecover portion 27 side are mounted on thehollow shaft 21 by the wire rings 23, 23, respectively. - The mechanical seals 24, 24 are disposed on the both end portions in the axial direction of the
vane pump 20, that is, on thebody portion 28 side end portion (left side inFIG. 6 ) and thecover 27 side end portion (right side inFIG. 6 ), respectively. Here, inFIG. 6 , the mechanical seal on thebody portion 28 side end portion is shown byreference numeral 24A, and the mechanical seal on thecover portion 7 side end portion is shown by reference numeral 24B. In other words, the mechanical seal 24 is a comprehensive expression indicating themechanical seals 24A and 24B. - On the
body portion 28, therelief circuit 29 for mechanical seal is formed, and therelief circuit 29 for mechanical seal communicates the back portion of themechanical seal 24A of thebody portion 28 side end portion (left end portion inFIG. 6 ) with theintake port 34. - Further, the back portion of the
mechanical seal 24A (mechanical seal on the left side inFIG. 6 ) of thebody portion 28 side end portion (left end portion inFIG. 6 ) and the back portion of the mechanical seal 24B (mechanical seal on the right side inFIG. 6 ) of thecover 27 side end portion are communicated through therelief circuit 25 for protection. InFIG. 6 , one piece of therelief circuit 25 for protection is formed on the boundary portion between thecover 27 as well as thebody portion 28 and thehollow shaft 21, but a plurality of therelief circuit 25 can be formed. - The mechanical seal 24B (mechanical seal on the right side in
FIG. 6 ) of thecover 27 side end portion communicates with therelief circuit 29 for mechanical seal through therelief circuit 25 for protection and themechanical seal 24A (mechanical seal on the left side inFIG. 6 ) of thebody portion 28 side end portion (left end portion inFIG. 6 ). - The other constructions and operative effects of the second embodiment shown in
FIG. 6 are similar to those of the embodiment described with reference toFIGS. 1 to 5 . - The third embodiment to the sixth embodiment of the present invention will be described with reference to
FIGS. 7 to 11 . The third embodiment to the sixth embodiment shown inFIGS. 7 to 11 are embodiments according to a vane pump of a type in which the cam ring and the rotor are provided one respectively similar to the first embodiment shown inFIGS. 1 to 5 . InFIGS. 7 to 11 , the same members as those described with reference toFIGS. 1 to 5 are shown by the same reference numerals respectively, and the explanation thereof will be omitted. - First, the third embodiment of the present invention will be explained with reference to
FIG. 7 . - In a case that the
vane pump 50 is mounted on thetransmission device 101 as shown inFIG. 1 , inFIG. 7 , the input shaft 103 (solid shaft: refer toFIG. 1 ), not shown inFIG. 1 , of thetransmission device 101 is inserted into the hollow portion of thehollow shaft 51 of thevane pump 50. - In
FIG. 7 , the input shaft 103 (rotation driving shaft) and thehollow shaft 51 are connected in a manner that the rotation force (torque) is transmitted but the thrust force is not transmitted by engaging the key 52 and the keyway 53. That is, in the third embodiment shown inFIG. 7 , the “mechanism for transmitting a torque but transmitting no thrust” is constructed by the key 52 and the keyway 53. - In
FIG. 7 , on the inner peripheral surface of thehollow shaft 51, the keyway 53 extending in a center axis direction of the hollow shaft is formed over a predetermined length L in a longitudinal direction of thehollow shaft 51 at least at one spot in a circumferential direction. On the other hand, on the input shaft 103 (rotation driving shaft,FIG. 1 ), the keyway 53 having the predetermined length L similar to thehollow shaft 51 is formed too, on a part of the outer peripheral surface of the region (region covered by the hollow shaft 51) which is inserted into thehollow shaft 51. - In a state shown in
FIG. 7 , the keyway 53 of theinput shaft 103 and the keyway 53 of thehollow shaft 51 are disposed so that the circumferential positions thereof are aligned, and thekay 52 having the width dimension which is the generally the same as the width dimension of the keyway 53 is inserted (or mounted) to the keyway 53. Here, the axial length L of the keyway 53 is designed so that the axial length is equal to or more than the axial length of the key 52. InFIG. 7 , the input shaft 103 (rotation driving shaft) is not shown. - As the result of insertion of the key 52 in the keyway 53, the
input shaft 103 and thehollow shaft 51 become capable of relative movement merely in the axial direction of thehollow shaft 51 for a distance corresponding to a difference in the axial length between the keyway 53 and the key 52, and the thrust force from theinput shaft 103 to thehollow shaft 61 is not transmitted. However, with regard to the circumferential direction, thehollow shaft 51 and theinput shaft 103 are not capable of relative rotation, and the torque is transmitted from theinput shaft 103 to thehollow shaft 51. - In the first embodiment shown in
FIGS. 1 to 5 , thehollow shaft 1 is supported by the bearingbush 19 only. - On the other hand, in the third embodiment in
FIG. 7 , in the vicinity of thecover portion 7 on a rear end side (left side inFIG. 7 ) of thehollow shaft 51, the bearingbush 54 for supporting thehollow shaft 51 is provided on thecover 7 side. By means of this construction, thehollow shaft 51 is supports at two spots in the axial direction by the bearing bush 19 (bearingbush 19 disposed on a side separated from the cover portion 7) disposed on thebody 8 side and the bearingbush 54 disposed in the vicinity of thecover portion 7, and a construction so-called “both-end supporting” is constructed, and then, thehollow shaft 51 is supports by said “both-end supporting” construction. - By supporting the
hollow shaft 51 by the bearingbushes 19 and 54 (supporting members) in the both-end supporting manner, thehollow shaft 51 can be centered in parallel with theinput shaft 103 and with high accuracy in a manner that rattling or the like does not happened relative to a case that thehollow shaft 51 is supported by a single bearing bush (supporting member). Thus, pump efficiency can be improved. - The supporting member may be also constructed by the bearing
bushes case 8 or thehollow shaft 51 of thecover portion 7 so as to support thehollow shaft 51 directly (direct bearing). Moreover, it may be such constructions that the bearing bush is used on one side in the axial direction, while the other side is constructed as the above-mentioned direct bearing manner. - Here, in a case that the bearing
bush 54 is provided, therelief circuit FIGS. 1 to 6 cannot be constructed. - Thus, in
FIG. 7 of the third embodiment, instead of therelief circuit 5, 25 (refer toFIGS. 2, 5, and 6 : circuit communicating themechanical seals channel 55 for communicating directly themechanical seal 4B on thecover portion 7 side (left side inFIG. 7 ) with the intake portion (intake port 14) is formed, as the relief circuit for protection. By means of thisrelief circuit 55 for protection (relief circuit for mechanical seal), the pressure operating on themechanical seal 4B on thecover portion 7 side can be relieved to the intake portion (intake port 14). - In other words, in the third embodiment shown in
FIG. 7 , the pressure generated on the back portion of themechanical seal 4A on thebody portion 8 side end portion is relieved to theintake port 14 through therelief circuit 9 for mechanical seal, and the pressure generated on the back portion of themechanical seal 4B on thecover portion 7 side end portion is relieved to theintake port 14 through therelief circuit 55 for mechanical seal. - The
relief circuit 55 for protection (relief circuit for mechanical seal) has a length dimension and pipe resistance which are smaller than those of therelief circuits FIGS. 1 to 6 , and thus, the pressure operating on themechanical seal 4B on thecover portion 7 side is reliably relieved, and the operative effect of the relief circuit is exerted reliably. - Here, the constructions of both-side supporting of the
hollow shaft 51 by providing the bearingbush 54 in addition to the bearingbush 19 and the constructions of providing therelief circuit 55 for protection communicating directly themechanical seal 4B on thecover portion 7 side with theintake port 14 can be used also in the fourth embodiment, the fifth embodiment, the sixth embodiment and variations thereof which will be described hereinafter. - The other constructions and operative effects of the third embodiment shown in
FIG. 7 are similar to those of the embodiments shown inFIGS. 1 to 6 . - Subsequently, the fourth embodiment of the present invention will be described with reference to
FIG. 8 . - In the fourth embodiment shown in
FIG. 8 , by means of thespring pin 62, the input shaft 103 (solid shaft:FIG. 1 ) of thetransmission device 101, not shown, and thehollow shaft 61 of thevane pump 60 are connected in a manner that the rotation force (torque) is transmitted but the thrust force is not transmitted. As will be described hereinafter, in the fourth embodiment shown inFIG. 8 , the “mechanism which transmits the torque but does not transmit the thrust” is constructed by theengagement groove 61B penetrating thehollow shaft 61, a through hole (not shown) of therotation driving shaft 103, and thespring pin 62 capable of being inserted into theengagement groove 61B and the through hole. - In
FIG. 8 , the axial dimension of thehollow shaft 61 is designed so as to be larger than a width of the pump case (thebody portion 8 and thecover portion 7 of the vane pump 60), and the distal end (right end inFIG. 8 ) of thehollow shaft 61 is protruded (protrudingportion 61A) from the pump case end portion (right end inFIG. 8 :body portion 8 side end portion). - On the protruding
portion 61A of thehollow shaft 61, theengagement groove 61B into which thespring pin 62 is inserted is formed (opened), and theengagement groove 61B is formed on the same diameter of thehollow shaft 61 at a pair of positions being symmetrical to the shaft core in the circumferential direction of thehollow shaft 61. - The
engagement groove 61B has a long hole shape (or a groove state) which long hole is opened in thebody portion 8 side end portion (right side inFIG. 8 ), a width dimension (dimension in the circumferential direction of the hollow shaft) of theengagement groove 61B is designed so as to be substantially equal to the diameter of thespring pin 62 when thepin 62 is contracted, and an axial dimension (dimension in the axial direction of the hollow shaft 61) of theengagement groove 61B is designed so as to be larger than the diameter of the spring pin. - The
spring pin 62 is formed having a hollow cylindrical shape having anotch portion 62A extending in the axial direction, and the diameter of thespring pin 62 is changed (enlarged) by an elastic repulsive force. Thespring pin 62 is fitted in a state that the diameter of thespring pin 62 is contracted when thepin 62 is inserted into theengagement groove 61B and a through port, not shown, of therotation driving shaft 103. And the axial length of the spring pin is designed so as to be larger than the diameter of the hollow shaft. - In the input shaft 103 (see
FIG. 1 ) not shown inFIG. 8 , a pin hole (through port), not shown, is formed, and said pin hole is formed at a position aligned with the position of theengagement groove 61 when theinput shaft 103 is inserted into thehollow shaft 61. And the pinhole is a through hole (not shown) into which thespring pin 62 can be inserted, and an inner diameter of the pin hole is designed so as to be substantially equal to the diameter of thespring pin 62 being contracted. - When the
input shaft 103 and thehollow shaft 61 are to be connected, thespring pin 62 is inserted and fitted into one of theengagement grooves hollow shaft 61, the pin hole of the input shaft 103 (not shown inFIG. 8 ), and theother engagement groove 61B of thehollow shaft 61. As a result, theinput shaft 103 and thehollow shaft 61 are made capable to move relatively each other in the axial direction of thehollow shaft 61B for a distance corresponding to the axial length of theengagement groove 61B, and the thrust force from theinput shaft 103 is not transmitted to thehollow shaft 61. However, with regard to the circumferential direction, thehollow shaft 61 and theinput shaft 103 are incapable of relative rotation, and therefore, it is possible to transmit the torque from theinput shaft 103 to thehollow shaft 61. - In a state that the
input shaft 103 and thehollow shaft 61 are connected, the elastic repulsive force operates to thespring pin 62 so as to enlarge outwardly in the radial direction, and thespring pin 62 presses one of theengagement grooves 61B of thehollow shaft 61, the pin hole of the input shaft 103 (not shown inFIG. 8 ), and theother engagement groove 61B of thehollow shaft 61. Thus, thespring pin 62 is prevented to be removed from theinput shaft 103 or thehollow shaft 61. - The other constructions and operative effects of the fourth embodiment shown in
FIG. 8 are similar to those in each of the embodiments shown inFIGS. 1 to 6 and 7 . - The fifth embodiment will be described with reference to
FIG. 9 . - In the fifth embodiment shown in
FIG. 9 , by means of a plurality of pressingbolts 73, the input shaft 103 (solid shaft:FIG. 1 ) of the transmission device 101 (FIG. 1 ), not shown, and thehollow shaft 71 of thevane pump 70 are connected in the manner that the rotation force (torque) is transmitted but the thrust force is not transmitted. As will be described hereinafter, the “mechanism which transmits the torque but does not transmit the thrust” in the fifth embodiment shown inFIG. 9 has a plurality ofaccommodating portions 71B provided at equal interval in the circumferential direction of thehollow shaft 71, a plurality of engagement balls 72 (spherical members) accommodated in theaccommodating portion 71B and a plurality of pressing bolts 73 (member for pressing in the radial direction). - In
FIG. 9 , the axial dimension of thehollow shaft 71 is designed so as to be larger than the width of the pump case (thebody portion 8 and thecover portion 7 of the vane pump 70), and the distal end (right end inFIG. 9 ) of thehollow shaft 71 is protruded (protrudingportion 71A) from the pump case end portion (right end inFIG. 9 , thebody portion 8 side). - In the protruding
portion 71A of thehollow shaft 71, the plurality ofaccommodating portions 71B for accommodating theengagement balls 72 and thepressing bolts 73 are disposed at the same interval in the circumferential direction. As shown inFIG. 9(B) , in the fifth embodiment shown inFIG. 9 , theaccommodating portions 71B are formed at the same intervals in the circumferential direction at three spots in total so that a center angle is a 120° interval. - Each of the
accommodating portions 71B is formed integrally with thehollow shaft 71, is formed cylindrically, and protrudes outwardly from the outer peripheral surface of thehollow shaft 71. - The hollow portion of the
accommodating portion 71B is formed so as to extend in the radial direction of thehollow shaft 71, and a female screw being screwed with thepressing bolt 73 is formed in the inner peripheral surface of the hollow portion. - Though an inner end portion in the radial direction of the
accommodating portion 71B is opened to an inner peripheral surface side of thehollow shaft 71, a sectional area of an opening in the inner end portion in the radial direction of theaccommodating portion 71B is designed so as to be smaller 1 than a sectional area of theengagement ball 72. Thus, in a case that theengagement ball 72 is disposed in the hollow portion of theaccommodating portion 71B, a distal end side (an end portion in the radial direction of the hollow shaft 71) of theengagement ball 72 merely protrudes to the inner peripheral surface side of thehollow shaft 71 from the opening but theentire engagement ball 72 does not moved to the inner peripheral surface side of thehollow shaft 71. - By tightening the
pressing bolts 73 in each of theaccommodating portions 71B uniformly, theengagement ball 72 is pressed inwardly in the radial direction by thepressing bolt 73, and a distal end of theengagement ball 72 protrudes uniformly to the outer peripheral surface of the input shaft 103 (seeFIG. 1 ) from the inner peripheral surface of thehollow shaft 71, presses theinput shaft 103 and connects (couples) theinput shaft 103 and thehollow shaft 71. As a result, theinput shaft 103 and thehollow shaft 71 are not relatively moved (without rattling) in the circumferential direction and in the radial direction of thehollow shaft 71 and coupled in a manner that the shaft cores of theinput shaft 103 and thehollow shaft 71 are matched or aligned. - Here, the number of accommodating portions (engagement balls, pressing bolts) is not limited to three. The accommodating portions may be provided in two if they are disposed at an equal interval in the circumferential direction of the
hollow shaft 71, or may be provided in four or more. However, as shown inFIG. 9 , if threeaccommodating portions 71B are provided, it is excellent as regard a balance of power and efficiency of tightening. - The number of accommodating portions is not particularly limited if the shaft cores of the
input shaft 103 and thehollow shaft 71 are not offset. - The
accommodating portion 71B may be formed integrally with thehollow shaft 71 as shown inFIG. 9 , but may be formed separately from thehollow shaft 71. - The other constructions and operative effects of the fifth embodiment in
FIG. 9 are similar to those in each of the embodiments shown inFIGS. 1 to 6 ,FIG. 7 , andFIG. 8 . - Subsequently, the sixth embodiment will be described with reference to
FIG. 10 . - In the sixth embodiment shown in
FIG. 10 , the mechanism in which the rotation force (torque) is transmitted but the thrust force is not transmitted is constructed by a spline formed on the outer peripheral surface of the input shaft 103 (rotation driving shaft) and the inner peripheral surface of thehollow shaft 81. - In
FIG. 10 , the spline (aspline portion 81A of the hollow shaft 81) is formed on the inner peripheral surface in a region in the vicinity immediately below the vane 11 (rotor 2) located in the vicinity of the center in the axial direction of thehollow shaft 81 merely, and a portion (spline portion) of thehollow shaft 81 in which the spline is formed is indicated byreference character 81A. Moreover, in theinput shaft 103, the spline is formed only on the outer peripheral surface of theinput shaft 103 corresponding to the region (thespline portion 81A of the hollow shaft 81) in the vicinity immediately below the vane of thehollow shaft 81, and the portion (input shaft spline portion) in which the spline of theinput shaft 103 is formed is indicated byreference character 103A. - On the other hand, in the
hollow shaft 81, there arelarge diameter portions pump body portion 8 side: right end side inFIG. 10 ) and on a rear end side (thecover portion 7 side, the left end side inFIG. 10 ), respectively. And in theinput shaft 103, on regions in the axial direction corresponding to thelarge diameter portions hollow shaft 81 is not formed, there areregions - The
large diameter portions hollow shaft 81 and thenon-spline portions input shaft 103 construct a lubricant-oil filling space (large diameter portion) in which the lubricant oil (grease oil, for example) is filled. - In
FIG. 10 , the square ring 82 (made of resin or oil-resistant rubber, for example), which is a ring having a square sectional shape, is provided as a sealing member for the lubricant oil on thelarge diameter portion 81B on the distal end side (the side separated from the cover portion 7: right end side inFIG. 10 ). The inner diameter of thesquare ring 82 is substantially equal to the outer diameter of theinput shaft 103. - After the grease oil is filled in the
large diameter portions FIG. 10 ) of thehollow shaft 81, by attaching thevane pump 80 to thetransmission device 101, the space of thelarge diameter portion 81C on the rear end side (the left end side inFIG. 10 ) is closed by a housing of thetransmission device 101, and the grease oil can be sealed. On the other hand, the space of thelarge diameter portion 81B on the distal end side (right end side inFIG. 10 ) is sealed by providing thesquare ring 82 on the outer peripheral surface of thenon-spline portion 103B on which no spline is engraved in theinput shaft 103, and the grease-filled state can be maintained. - In a case that the vane pump is to be driven by the internal combustion engine, the torque fluctuation specific to the internal combustion engine operates to the splines through the input shaft, the teeth of the male and female splines collide against each other (teeth are hit by each other), and there, surfaces of the teeth of the splines are damaged.
- On the other hand, in the sixth embodiment shown in
FIG. 10 , by interposing the grease oil which is the lubricant oil, collision of teeth of the spline against each other, which collision would damage the tooth surface, can be reduced by the grease oil operating as a cushion. - The other constructions and operative effects of the sixth embodiment shown in
FIG. 10 are similar to those in each of the embodiments shown inFIGS. 1 to 6 ,FIG. 7 ,FIG. 8 , andFIG. 9 . - Here, a variation of the sixth embodiment will be described with reference to
FIG. 11 . - In the sixth embodiment shown in
FIG. 10 , since the spline is not engraved in thelarge diameter portion 81A on the distal end side (right end side inFIG. 10 ) of thehollow shaft 81, thesquare ring 82 can be installed as it is. However, as shown inFIG. 11(A) , in a case that the spline is formed on the whole region in the axial direction of thehollow shaft 91 of thevane pump 90, in order to provide thesquare ring 82 for sealing as shown inFIG. 10 , it is necessary to cut off the spline (on the inner peripheral surface of the hollow shaft) on (the distal end side (right end side inFIG. 11 ) of the hollow shaft 91) the region in which thesquare ring 82 should be installed by machining so as to form a cylindrical surface, and to install thesquare ring 82 at the spot after the machining. - On the other hand, in the variation of the sixth embodiment, as shown in
FIG. 11(B) , the spline seal 92 (made of resin) is used as a sealing member for the lubricant oil, and then, on the outer periphery surface of thespline seal 92, there are plurality of projection-and-recess which corresponds to the female spline on the inner peripheral surface of thehollow shaft 91. - When the input shaft 103 (rotation driving shaft,
FIG. 1 ), not shown, and thehollow shaft 91 are connected, thespline seal 92 is assembled from the distal end side (right end side inFIG. 11 ) of thehollow shaft 91, the outer peripheral surface of theinput shaft 103 is inserted into the space on the inner side in the radial direction of thespline seal 92, and then, the male spline of theinput shaft 103 and the female spline on the inner peripheral surface of thehollow shaft 91 are engaged. Since thespline seal 92 has the projection-and-recess surface formed on the outer periphery corresponding to the female spline of thehollow shaft 91, the male spline of theinput shaft 103 and the female spline of thehollow shaft 91 can be sealed. Therefore, it is not necessary to cut off the spline (on the inner peripheral surface of the hollow shaft 91) by machining in order to form the cylindrical surface, at the spot where thespline seal 92 should be installed. And while the female spline is formed over the entire length of thehollow shaft 91, the lubricant oil can be sealed therein without increasing a machining cost. - The other constructions and operative effects of the variation shown in
FIG. 11 are similar to those in the sixth embodiment shown inFIG. 10 . - The embodiments shown in drawings are merely exemplifications and it should be noted that the descriptions of the embodiments are not intended to limit the technical scope of the present invention.
- In the embodiments shown in drawings, the
input shaft 103 of thetransmission device 101 is inserted into the hollow portion of thehollow shafts output shaft 105 of the motor 102 (driving source) such as a motor can be inserted into the hollow portion of thehollow shafts -
- 1, 21, 51, 61, 71, 81, 91 hollow shaft
- 1A shaft-side recess portion
- 2, 22 rotor
- 2A rotor-side stepped portion
- 3, 23 wire ring
- 4 (4A, 4B), 24 (24A, 24B) mechanical seal
- 5, 25 relief circuit for protection
- 6, 26 cam ring
- 7, 27 cover portion
- 8, 28 body portion
- 9, 29, 55 relief circuit for mechanical seal
- 10, 20, 50, 60, 70, 80, 90 vane pump
- 11, 31 vane
- 11G vane groove
- 12 pressure-oil storage portion for vane
- 13, 33 intake circuit
- 14, 34 intake port
- 15, 35 (35-1, 35-2) ejection circuit
- 16, 36 (36-1, 36-2) ejection port
- 17, 37 circuit for pressure loading
- 18, 38 pressure plate
- 19, 39, 54 bearing bush
- 40 intermediate plate
- 52 key
- 53 keyway
- 61B engagement groove
- 62 spring pin
- 71B accommodating portion
- 72 engagement ball
- 73 pressing bolt
- 82 square ring (sealing member for lubricant oil)
- 92 spline seal (sealing member for lubricant oil)
- 101 transmission device
- 102 driving source
- 103 input shaft
- 105 output shaft
- B joining bolt
- H bolt hole
- α pump chamber
Claims (13)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016-219546 | 2016-11-10 | ||
JP2016219546 | 2016-11-10 | ||
PCT/JP2017/037677 WO2018088148A1 (en) | 2016-11-10 | 2017-10-18 | Vane pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US20200011326A1 true US20200011326A1 (en) | 2020-01-09 |
Family
ID=62109869
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/347,586 Abandoned US20200011326A1 (en) | 2016-11-10 | 2017-10-18 | Vane pump |
Country Status (5)
Country | Link |
---|---|
US (1) | US20200011326A1 (en) |
EP (1) | EP3540226A4 (en) |
JP (1) | JP6932312B2 (en) |
CN (1) | CN110121595A (en) |
WO (1) | WO2018088148A1 (en) |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1012112A (en) * | ||||
US2387629A (en) * | 1941-11-12 | 1945-10-23 | Waseige Charles Raymond | Rotary vane pump |
GB573860A (en) * | 1942-11-18 | 1945-12-10 | Bendix Aviat Corp | Improvements in rotary pumps |
JPS5259310A (en) * | 1975-11-11 | 1977-05-16 | Matsushita Electric Ind Co Ltd | Open type rotary compressor |
JPS5630716Y2 (en) * | 1977-04-19 | 1981-07-21 | ||
JPS59215980A (en) * | 1983-05-20 | 1984-12-05 | Nippon Piston Ring Co Ltd | Production method for rotor of rotary compressor |
JPH03266724A (en) * | 1990-03-15 | 1991-11-27 | Koyo Seiko Co Ltd | Driving linking device for four-wheel drive |
DE29501158U1 (en) * | 1995-01-25 | 1995-03-30 | Electrolux Corporate Patents & | Locking device for a drive shaft |
WO2000053926A1 (en) * | 1999-03-05 | 2000-09-14 | Honda Giken Kogyo Kabushiki Kaisha | Rotary fluid machinery, vane fluid machinery, and waste heat recovery device of internal combustion engine |
JP2002130235A (en) * | 2000-10-30 | 2002-05-09 | Unisia Jecs Corp | Device for holding ring |
DE10118720A1 (en) * | 2001-04-12 | 2002-10-17 | Luk Fahrzeug Hydraulik | pump |
KR101452510B1 (en) * | 2008-07-22 | 2014-10-23 | 엘지전자 주식회사 | Compressor |
JP2012163040A (en) | 2011-02-07 | 2012-08-30 | Hitachi Automotive Systems Ltd | Vane pump |
JP5958261B2 (en) * | 2011-10-19 | 2016-07-27 | 株式会社ジェイテクト | Driving force transmission device |
JP6218653B2 (en) * | 2014-03-13 | 2017-10-25 | Kyb株式会社 | Vane pump and manufacturing method thereof |
-
2017
- 2017-10-18 JP JP2018550097A patent/JP6932312B2/en active Active
- 2017-10-18 CN CN201780069206.1A patent/CN110121595A/en active Pending
- 2017-10-18 WO PCT/JP2017/037677 patent/WO2018088148A1/en unknown
- 2017-10-18 US US16/347,586 patent/US20200011326A1/en not_active Abandoned
- 2017-10-18 EP EP17868938.6A patent/EP3540226A4/en not_active Withdrawn
Also Published As
Publication number | Publication date |
---|---|
JPWO2018088148A1 (en) | 2019-11-07 |
CN110121595A (en) | 2019-08-13 |
JP6932312B2 (en) | 2021-09-08 |
WO2018088148A1 (en) | 2018-05-17 |
EP3540226A1 (en) | 2019-09-18 |
EP3540226A4 (en) | 2020-06-24 |
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