US20180258931A1 - Vane pump - Google Patents
Vane pump Download PDFInfo
- Publication number
- US20180258931A1 US20180258931A1 US15/759,990 US201615759990A US2018258931A1 US 20180258931 A1 US20180258931 A1 US 20180258931A1 US 201615759990 A US201615759990 A US 201615759990A US 2018258931 A1 US2018258931 A1 US 2018258931A1
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- US
- United States
- Prior art keywords
- pump
- side plate
- cam ring
- pressure chamber
- pins
- 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
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
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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
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
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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
-
- 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
- F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—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
- F04C2/32—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
- F04C2/324—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the inner member and reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
Definitions
- the present invention relates to a vane pump.
- JP2002-21742A discloses a vane pump that includes a pump unit, a body, and a cover having a concave portion for accommodating the pump unit.
- a pump housing is formed by the body and the cover.
- the pump unit has a cam ring, a rotor, vanes, a first side plate that covers a side surface of each of the cam ring and the rotor on the body side, a second side plate that covers a side surface of each of the cam ring and the rotor on the cover side, and alignment pins for aligning positions of the cam ring and the both side plates in the circumferential direction by penetrating through insertion holes of the cam ring and by being press-fitted into first press-fitting holes of the first side plate and second press-fitting holes of the second side plate.
- tip-end portions of the alignment pins serve as projected portions projected from the first side plate, and the pump unit is aligned with respect to the cover by press-fitting the projected portions into the press-fitting holes of the cover.
- the pump unit is aligned by press-fitting the alignment pins penetrating through the cam ring into the press-fitting holes of the pump cover.
- the press-fitting holes need to be formed by avoiding the inner side of the cam ring in which the rotor is arranged, there is a restriction on the positions of the press-fitting holes.
- the positions of the press-fitting holes are restricted as described above, there is also a restriction on a shape of a passage of working fluid formed in the pump cover.
- An object of the present invention is to improve a degree of freedom for designing a passage of working fluid in a vane pump.
- a vane pump includes: a pump body having a concave portion; a pump cover attached to the pump body, the pump cover being configured to seal the concave portion; and a pump cartridge accommodated in an accommodating space defined by the concave portion and the pump cover.
- the pump cartridge includes: a rotor linked to a driving shaft; a plurality of slits formed in the rotor in a radiating pattern to open in an outer circumference of the rotor; a plurality of vanes respectively inserted into the plurality of slits in a slidable manner; a cam ring having an inner circumferential surface on which tip-ends of the vanes slide by rotation of the rotor; a side plate provided between a bottom portion of the concave portion in the pump body and the cam ring; a first pin provided so as to extend from the cam ring to the side plate; and a second pin provided so as to extend from the side plate to the pump body.
- FIG. 1 is a sectional view of a vane pump according to an embodiment of the present invention.
- FIG. 2 is a plan view showing a pump cartridge of the vane pump according to the embodiment of the present invention.
- FIG. 3 is a plan view showing a bottom portion of a pump body of the vane pump according to the embodiment of the present invention.
- FIG. 4 is a sectional view taken along a line A-A in FIG. 3 .
- FIG. 5 is a plan view showing a first modification of the vane pump according to the embodiment of the present invention.
- FIG. 6 is a plan view showing a second modification of the vane pump according to the embodiment of the present invention.
- a configuration of a vane pump 100 according to an embodiment of the present invention will be described below with reference to FIGS. 1 to 4 .
- the vane pump 100 is used as a fluid pressure source for a fluid pressure apparatus mounted on a vehicle, such as, for example, a power steering apparatus, a continuously variable transmission, or the like.
- a fluid pressure apparatus mounted on a vehicle
- the fixed displacement vane pump 100 using working oil as working fluid will be described.
- the vane pump 100 may also be a variable displacement vane pump.
- the vane pump 100 has a pump body 30 that has a concave portion 30 a, a pump cover 31 that is attached to the pump body 30 and seals the concave portion 30 a, and a pump cartridge 10 that is accommodated in an accommodating space defined by the concave portion 30 a and the pump cover 31 and discharges the working oil.
- the pump cartridge 10 includes a plurality of vanes 3 that are provided so as to be able to reciprocate in the radial direction relative to the rotor 2 , a cam ring 4 that accommodates the rotor 2 and has a cam face 4 a serving as an inner circumferential surface on which tip-ends of the vanes 3 slide by rotation of the rotor 2 , a first side plate 5 serving as a side plate that is arranged between the cam ring 4 and the bottom portion of the concave portion 30 a of the pump body 30 so as to be in contact with the one side surface of the cam ring 4 (lower side surface in FIG.
- FIG. 2 is a plan view showing the pump cartridge 10 in a state in which the second side plate is removed.
- slits 7 having openings in an outer circumferential surface of the rotor 2 are formed in a radiating pattern with predetermined gaps.
- the vanes 3 are respectively inserted into the slits 7 in a reciprocatable manner.
- back pressure chambers 8 into which discharge pressure is guided are defined by base-end portions of the vanes 3 .
- vanes 3 are pushed by the pressure of the working oil guided to the back pressure chambers 8 in the directions in which the vanes 3 are drawn out from the slits 7 , and tip-end portions of the vanes 3 are brought into contact with the cam face 4 a of the cam ring 4 .
- a plurality of pump chambers 9 are defined in the cam ring 4 by the outer circumferential surface of the rotor 2 , the cam face 4 a of the cam ring 4 , and the adjacent vanes 3 .
- the cam ring 4 is an annular member in which the cam face 4 a on the inner circumference has a substantially oval shape.
- the cam ring 4 has suction regions 4 b in which volume of each pump chamber 9 , which is defined between respective vanes 3 that slide on the cam face 4 a by the rotation of the rotor 2 , is increased and discharge regions 4 c in which volume of each pump chamber 9 is decreased.
- respective pump chambers 9 are expanded/contracted by the rotation of the rotor 2 .
- the cam ring 4 has two suction regions 4 b and two discharge regions 4 c.
- the first side plate 5 and the second side plate 6 are arranged in such a manner that both side surfaces of each of the rotor 2 and the cam ring 4 are sandwiched, and thereby, the pump chambers 9 are sealed.
- two arc-shaped discharge ports 20 a and 20 b which open correspondingly to the discharge regions 4 c of the cam ring 4 , are formed so as to penetrate through the first side plate 5 .
- the two discharge ports 20 a and 20 b are provided so as to face each other with the angular intervals of 180°.
- an arc-shaped high-pressure chamber 21 is formed in the bottom portion of the concave portion 30 a of the pump body 30 .
- the working oil that has been discharged from the pump chambers 9 in the discharge regions 4 c is guided into the high-pressure chamber 21 through the discharge ports 20 a and 20 b of the first side plate 5 .
- the pump body 30 is formed with a discharge passage 22 that is in communication with the high-pressure chamber 21 through a high-pressure port 22 a opening to the high-pressure chamber 21 and that supplies the working oil in the high-pressure chamber 21 to an external hydraulic apparatus.
- the high-pressure port 22 a opens to the high-pressure chamber 21 at the position deviated from that of each of the two discharge ports 20 a and 20 b in the circumferential direction. In FIG. 1 , illustrations of the high-pressure port 22 a and the discharge passage 22 are omitted.
- the high-pressure chamber 21 is formed to have an arc-shaped such that both ends of the high-pressure chamber 21 are separated by a raised portion 35 that is raised from the pump body 30 towards the first side plate 5 so as to become higher than the bottom portion of the high-pressure chamber 21 .
- the raised portion 35 is provided in the circumferential direction region R 2 that differs from the circumferential direction region R 1 where the high-pressure port 22 a is provided.
- each of the flows of the working oil guided from the discharge ports 20 a and 20 b to the high-pressure chamber 21 tends to flow in one direction (the directions of the arrows in FIG. 3 ) towards the high-pressure port 22 a directly without being directed towards the raised portion 35 .
- the raised portion 35 may be brought into contact with the first side plate 5 , or as shown in FIG. 4 , the raised portion 35 may be provided such that a communication gap 36 is formed between the raised portion 35 and the first side plate 5 .
- the high-pressure chamber 21 may not be completely divided by the raised portion 35 , and the raised portion 35 may connect the both ends of the high-pressure chamber 21 through the communication gap 36 formed between the raised portion 35 and the first side plate 5 .
- the communication gap 36 having the cross-sectional area that is smaller than that of the high-pressure chamber 21 imparts resistance to the flow of the working oil
- the working oil guided from the discharge ports 20 a and 20 b to the high-pressure chamber 21 is less likely to flow towards the raised portion 35 and tends to directly flow into the high-pressure chamber 21 towards the high-pressure port 22 a.
- the phrase “the raised portion 35 that separates the both ends of the high-pressure chamber 21 ” is not restricted to that completely divides the high-pressure chamber 21 , and the phrase also includes the raised portion 35 that allows communication between the both ends of the high-pressure chamber 21 but makes the working oil to flow in one direction towards the high-pressure port 22 a more easily.
- two arc-shaped back pressure ports 23 that are in communication with the high-pressure chamber 21 are formed (see FIG. 1 ).
- the back pressure ports 23 respectively communicate with the back pressure chambers 8 . With such a configuration, the working oil in the high-pressure chamber 21 is guided into the back pressure chambers 8 through the back pressure ports 23 .
- two arc-shaped suction ports (not shown) that correspondingly open to the two suction regions 4 b of the cam ring 4 (see FIG. 2 ) and that guide the working oil to the pump chambers 9 are formed.
- a suction passage (not shown) through which the tank (not shown) is communicated with the suction ports and that guides the working oil in the tank to the pump chambers 9 through the suction ports is formed.
- the working oil is sucked from the tank through the suction ports and the suction passage to the respective pump chambers 9 in the suction regions 4 b of the cam ring 4 , and the working oil is discharged to the outside from the respective pump chambers 9 in the discharge regions 4 c of the cam ring 4 through the discharge ports 20 a and 20 b and the discharge passage 22 .
- the working oil is supplied/discharged by expansion/contraction of the respective pump chambers 9 caused by the rotation of the rotor 2 .
- the pump cartridge 10 further has two first pins 11 that are provided so as to extend from the first side plate 5 to the second side plate 6 through the cam ring 4 (see FIG. 1 ) and two second pins 12 that are provided so as to extend from the first side plate 5 to the pump body 30 (see FIG. 4 ).
- the first pins 11 penetrate through the cam ring 4 , and both ends thereof are respectively press-fitted into upper-side first press-fitting holes 11 a formed in the second side plate 6 and lower-side first press-fitting holes 11 b formed in the first side plate 5 .
- the two first pins 11 are symmetrically arranged with respect to the center of the cam ring 4 (see FIG. 2 ).
- the two first pins 11 do not respectively penetrate through the first and second side plates 5 and 6 . In other words, the both ends of the first pins 11 do not project out from end surfaces of the first and second side plates 5 and 6 .
- both ends of the second pins 12 are respectively press-fitted into upper-side second press-fitting holes 12 a formed in the first side plate 5 and lower-side second press-fitting holes 12 b formed in the raised portion 35 .
- the second pins 12 are provided so as to avoid and so as not to penetrate a part of the high-pressure chamber 21 formed between the two discharge ports 20 a and 20 b and the high-pressure port 22 a .
- the raised portion 35 is provided, the working oil guided from the discharge ports 20 a and 20 b scarcely flows towards the raised portion 35 and mainly flows directly towards the high-pressure port 22 a through a part of the high-pressure chamber 21 formed between the discharge ports 20 a and 20 b and the high-pressure port 22 a. Therefore, if the second pins 12 are provided so as to penetrate through a part of the high-pressure chamber 21 formed between the discharge ports 20 a and 20 b and the high-pressure port 22 a, the flow-passage cross-sectional area is reduced and the flow of the working oil discharged from the pump chambers 9 is disturbed.
- the pump cartridge 10 may be rotated about the second pins 12 by an angle corresponding to a gap formed between the pump cartridge 10 and the concave portion 30 a of the pump body 30 in the radial direction.
- the vane pump 100 because two second pins 12 are provided, the rotation of the pump cartridge 10 about the second pins 12 is reliably prevented.
- the single second pin 12 may be provided.
- three or more second pins 12 may be provided.
- the pump cartridge 10 has the second side plate 6 that is provided between the pump cover 31 and the cam ring 4 .
- the pump cartridge 10 may not have the second side plate 6 , and the pump cover 31 may be brought into direct contact with the cam ring 4 .
- the first pins 11 are provided so as to extend from the cam ring 4 to the first side plate 5 , and the both ends thereof are respectively press-fitted into the cam ring 4 and the first side plate 5 .
- the first pins 11 may be provided such that one end of the first pins 11 , which is press-fitted into the cam ring 4 , does not penetrate through the cam ring 4 and does not project out from the cam ring 4 towards the pump cover 31 .
- the high-pressure port 22 a opens to the high-pressure chamber 21 at the position deviated from that of each of the two discharge ports 20 a and 20 b in the circumferential direction.
- the high-pressure port 22 a may open to the high-pressure chamber 21 at the position facing against the one discharge port 20 a. Even in this case, the working oil guided from the other discharge port 20 b passes through the high-pressure chamber 21 extending between the discharge port 20 b and the high-pressure port 22 a in the circumferential direction region R 1 .
- the second pins 12 are provided at the positions where the raised portion 35 is formed.
- the second pins 12 may be provided at any positions as long as the flow of the working oil flowing from the discharge ports 20 a and 20 b to the high-pressure port 22 a is not disturbed.
- the second pins 12 may be provided at the positions where the second pins 12 do not penetrates through the high-pressure chamber 21 extending between each of the two discharge ports 20 a and 20 b and the high-pressure port 22 a.
- the second pins 12 may be provided at any positions in the circumferential direction region R 2 , where the raised portion 35 is provided, at the opposite side of the circumferential direction region R 1 , where the high-pressure port 22 a is provided. Even in this case, because the flows of the working oil flowing from the discharge ports 20 a and 20 b to the high-pressure port 22 a are not disturbed by the second pins 12 , the similar effects as those of the above-mentioned embodiment are afforded.
- the vane pump is the so-called balanced vane pump 100 in which the cam ring has the two discharge regions and the two suction regions.
- the vane pump may be a so-called unbalanced vane pump 200 in which the cam ring has one discharge region and one suction region.
- the first side plate is formed with a single suction port (not shown) that opens correspondingly to the suction region.
- the second side plate is formed with a single discharge port 20 c that opens correspondingly to the discharge region.
- an arc-shaped high-pressure chamber 121 is formed at the position corresponding to the discharge port 20 c.
- the second pins 12 are provided at positions where the second pins 12 avoid and do not penetrate through a part of the high-pressure chamber 121 extending in the circumferential direction between the discharge port 20 c and the high-pressure port 22 a.
- the pump cartridge 10 integration of which is achieved with the first pins 11 is aligned with respect to the pump body 30 by the second pins 12 that are provided so as to extend from the first side plate 5 to the pump body 30 .
- the shape of the passage of the working oil formed in the pump cover 31 is not restricted by the alignment hole. Therefore, the degree of freedom for designing the passage of the working oil formed in the pump cover 31 is improved.
- the degree of freedom for designing the passage is improved, it is possible to optimize layout of the suction passage and to increase the cross-sectional area of the suction passage, and thereby, the sucking property thereof can be improved. Therefore, it is possible to suppress occurrence of vibration and cavitation of the vane pump 100 .
- the vane pump 100 because the second pins 12 are provided in the raised portion 35 , the flow of the working oil discharged from the pump chambers 9 is not disturbed by the second pins 12 . Thus, it is possible to align the pump cartridge 10 without affecting the flow of the working oil discharged from the pump chambers 9 .
- the vane pumps 100 and 200 include: the pump body 30 that has the concave portion 30 a; the pump cover 31 that is attached to the pump body 30 and seals the concave portion 30 a; and the pump cartridge 10 that is accommodated in an accommodating space defined by the concave portion 30 a and the pump cover 31 .
- the pump cartridge 10 includes: the rotor 2 that is linked to the driving shaft; the plurality of slits 7 that have opening in the outer circumference of the rotor 2 and are formed in a radiating pattern; the plurality of vanes 3 that are respectively inserted into the plurality of slits 7 in a slidable manner; the cam ring 4 that has the cam face 4 a on which the tip-ends of the vanes 3 slide by the rotation of the rotor 2 ; the first side plate 5 that is provided between the bottom portion of the concave portion 30 a in the pump body 30 and the cam ring 4 ; the first pins 11 that are provided so as to extend from the cam ring 4 to the first side plate 5 ; and the second pins 12 that are provided so as to extend from the first side plate 5 to the pump body 30 .
- the pump cartridge 10 integration of which is achieved by the first pins 11 is aligned with respect to the pump body 30 by the second pins 12 that are provided so as to extend from the first side plate 5 to the pump body 30 .
- the shape of the passage of the working oil formed in the pump cover 31 is not restricted by the alignment hole. Therefore, the degree of freedom for designing the passage of the working oil in the vane pumps 100 and 200 is improved.
- the pump cartridge 10 includes two or more second pins 12 .
- the first side plate 5 has the discharge ports 20 a, 20 b, and 20 c that guide the working fluid discharged from the pump chambers 9 in the pump cartridge 10 , which are defined by the rotor 2 , the cam ring 4 , and the adjacent vanes 3 ;
- the pump body 30 has the arc-shaped high-pressure chambers 21 and 121 into which the working oil that has been discharged from the pump chambers 9 is guided through the discharge ports 20 a, 20 b, and 20 c and has the discharge passage 22 that is in communication with the high-pressure chamber 21 through the high-pressure port 22 a opening to the high-pressure chambers 21 and 121 ; and the second pins 12 are provided at the positions where the second pins 12 do not penetrate through a part of the high-pressure chamber 21 extending in the circumferential direction between each of the discharge ports 20 a and 20 b and the high-pressure port 22 a.
- the pump body 30 is formed with the raised portion 35 that separates the both ends of the high-pressure chamber 21 , and the second pins 12 are provided so as to extend from the first side plate 5 to the raised portion 35 .
- the second pins 12 do not penetrate through a part of the high-pressure chamber 21 extending in the circumferential direction between the discharge ports 20 a, 20 b, and 20 c and the high-pressure port 22 a, the flow of the working oil guided from the discharge ports 20 a, 20 b, and 20 c to the high-pressure port 22 a is not disturbed by the second pins 12 . Therefore, it is possible to align the pump cartridge 10 without affecting the flow of the working oil.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
A vane pump includes a pump cartridge that is accommodated in an accommodating space defined by the concave portion and the pump cover. The pump cartridge includes a first side plate that is provided between the bottom portion of the concave portion in the pump body and a cam ring; first pins that are provided so as to extend from the cam ring to the first side plate; and second pins that are provided so as to extend from the first side plate to the pump body.
Description
- TECHNICAL FIELD
- The present invention relates to a vane pump.
- JP2002-21742A discloses a vane pump that includes a pump unit, a body, and a cover having a concave portion for accommodating the pump unit. In this vane pump, a pump housing is formed by the body and the cover.
- In the vane pump disclosed in JP2002-21742A, the pump unit has a cam ring, a rotor, vanes, a first side plate that covers a side surface of each of the cam ring and the rotor on the body side, a second side plate that covers a side surface of each of the cam ring and the rotor on the cover side, and alignment pins for aligning positions of the cam ring and the both side plates in the circumferential direction by penetrating through insertion holes of the cam ring and by being press-fitted into first press-fitting holes of the first side plate and second press-fitting holes of the second side plate. In the vane pump, tip-end portions of the alignment pins serve as projected portions projected from the first side plate, and the pump unit is aligned with respect to the cover by press-fitting the projected portions into the press-fitting holes of the cover.
- With the vane pump disclosed in JP2002-21742A, the pump unit is aligned by press-fitting the alignment pins penetrating through the cam ring into the press-fitting holes of the pump cover. However, because the press-fitting holes need to be formed by avoiding the inner side of the cam ring in which the rotor is arranged, there is a restriction on the positions of the press-fitting holes. As the positions of the press-fitting holes are restricted as described above, there is also a restriction on a shape of a passage of working fluid formed in the pump cover.
- An object of the present invention is to improve a degree of freedom for designing a passage of working fluid in a vane pump.
- According to one aspect of the present invention, a vane pump includes: a pump body having a concave portion; a pump cover attached to the pump body, the pump cover being configured to seal the concave portion; and a pump cartridge accommodated in an accommodating space defined by the concave portion and the pump cover. The pump cartridge includes: a rotor linked to a driving shaft; a plurality of slits formed in the rotor in a radiating pattern to open in an outer circumference of the rotor; a plurality of vanes respectively inserted into the plurality of slits in a slidable manner; a cam ring having an inner circumferential surface on which tip-ends of the vanes slide by rotation of the rotor; a side plate provided between a bottom portion of the concave portion in the pump body and the cam ring; a first pin provided so as to extend from the cam ring to the side plate; and a second pin provided so as to extend from the side plate to the pump body.
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FIG. 1 is a sectional view of a vane pump according to an embodiment of the present invention. -
FIG. 2 is a plan view showing a pump cartridge of the vane pump according to the embodiment of the present invention. -
FIG. 3 is a plan view showing a bottom portion of a pump body of the vane pump according to the embodiment of the present invention. -
FIG. 4 is a sectional view taken along a line A-A inFIG. 3 . -
FIG. 5 is a plan view showing a first modification of the vane pump according to the embodiment of the present invention. -
FIG. 6 is a plan view showing a second modification of the vane pump according to the embodiment of the present invention. - A configuration of a
vane pump 100 according to an embodiment of the present invention will be described below with reference toFIGS. 1 to 4 . - The
vane pump 100 is used as a fluid pressure source for a fluid pressure apparatus mounted on a vehicle, such as, for example, a power steering apparatus, a continuously variable transmission, or the like. In this embodiment, the fixeddisplacement vane pump 100 using working oil as working fluid will be described. Thevane pump 100 may also be a variable displacement vane pump. - As shown in
FIG. 1 , thevane pump 100 has apump body 30 that has aconcave portion 30 a, apump cover 31 that is attached to thepump body 30 and seals theconcave portion 30 a, and apump cartridge 10 that is accommodated in an accommodating space defined by theconcave portion 30 a and thepump cover 31 and discharges the working oil. - In the
vane pump 100, motive force from an engine (not shown) is transmitted to an end portion of adriving shaft 1, and arotor 2 linked to thedriving shaft 1 is rotated. Therotor 2 is rotated in the clockwise direction inFIG. 2 . - As shown in
FIGS. 1 and 2 , thepump cartridge 10 includes a plurality ofvanes 3 that are provided so as to be able to reciprocate in the radial direction relative to therotor 2, acam ring 4 that accommodates therotor 2 and has acam face 4 a serving as an inner circumferential surface on which tip-ends of thevanes 3 slide by rotation of therotor 2, afirst side plate 5 serving as a side plate that is arranged between thecam ring 4 and the bottom portion of theconcave portion 30 a of thepump body 30 so as to be in contact with the one side surface of the cam ring 4 (lower side surface inFIG. 1 ), and asecond side plate 6 that is arranged between thecam ring 4 and thepump cover 31 so as to be in contact with the other side surface of the cam ring 4 (upper side surface inFIG. 1 ). Here,FIG. 2 is a plan view showing thepump cartridge 10 in a state in which the second side plate is removed. - As shown in
FIG. 2 , in therotor 2,slits 7 having openings in an outer circumferential surface of therotor 2 are formed in a radiating pattern with predetermined gaps. Thevanes 3 are respectively inserted into theslits 7 in a reciprocatable manner. In theslits 7,back pressure chambers 8 into which discharge pressure is guided are defined by base-end portions of thevanes 3. - The
vanes 3 are pushed by the pressure of the working oil guided to theback pressure chambers 8 in the directions in which thevanes 3 are drawn out from theslits 7, and tip-end portions of thevanes 3 are brought into contact with thecam face 4 a of thecam ring 4. With such a configuration, a plurality ofpump chambers 9 are defined in thecam ring 4 by the outer circumferential surface of therotor 2, thecam face 4 a of thecam ring 4, and theadjacent vanes 3. - The
cam ring 4 is an annular member in which thecam face 4 a on the inner circumference has a substantially oval shape. Thecam ring 4 hassuction regions 4 b in which volume of eachpump chamber 9, which is defined betweenrespective vanes 3 that slide on thecam face 4 a by the rotation of therotor 2, is increased anddischarge regions 4 c in which volume of eachpump chamber 9 is decreased. As described above,respective pump chambers 9 are expanded/contracted by the rotation of therotor 2. In this embodiment, thecam ring 4 has twosuction regions 4 b and twodischarge regions 4 c. - As shown in
FIG. 1 , thefirst side plate 5 and thesecond side plate 6 are arranged in such a manner that both side surfaces of each of therotor 2 and thecam ring 4 are sandwiched, and thereby, thepump chambers 9 are sealed. - As shown in
FIG. 2 , in thefirst side plate 5, two arc-shaped discharge ports discharge regions 4 c of thecam ring 4, are formed so as to penetrate through thefirst side plate 5. The twodischarge ports - As shown in
FIG. 3 , an arc-shaped high-pressure chamber 21 is formed in the bottom portion of theconcave portion 30 a of thepump body 30. The working oil that has been discharged from thepump chambers 9 in thedischarge regions 4 c is guided into the high-pressure chamber 21 through thedischarge ports first side plate 5. - The
pump body 30 is formed with adischarge passage 22 that is in communication with the high-pressure chamber 21 through a high-pressure port 22 a opening to the high-pressure chamber 21 and that supplies the working oil in the high-pressure chamber 21 to an external hydraulic apparatus. The high-pressure port 22 a opens to the high-pressure chamber 21 at the position deviated from that of each of the twodischarge ports FIG. 1 , illustrations of the high-pressure port 22 a and thedischarge passage 22 are omitted. - The high-
pressure chamber 21 is formed to have an arc-shaped such that both ends of the high-pressure chamber 21 are separated by a raisedportion 35 that is raised from thepump body 30 towards thefirst side plate 5 so as to become higher than the bottom portion of the high-pressure chamber 21. Of two circumferential direction regions R1 and R2 between the twodischarge ports portion 35 is provided in the circumferential direction region R2 that differs from the circumferential direction region R1 where the high-pressure port 22 a is provided. As the raisedportion 35 is provided, flows of the working oil flowing in the directions (the directions approaching the raised portion 35) opposite from the directions approaching the high-pressure port 22 a fromrespective discharge ports FIG. 3 ) are prevented. Therefore, each of the flows of the working oil guided from thedischarge ports pressure chamber 21 tends to flow in one direction (the directions of the arrows inFIG. 3 ) towards the high-pressure port 22 a directly without being directed towards the raisedportion 35. - The raised
portion 35 may be brought into contact with thefirst side plate 5, or as shown inFIG. 4 , the raisedportion 35 may be provided such that acommunication gap 36 is formed between the raisedportion 35 and thefirst side plate 5. In other words, the high-pressure chamber 21 may not be completely divided by the raisedportion 35, and the raisedportion 35 may connect the both ends of the high-pressure chamber 21 through thecommunication gap 36 formed between the raisedportion 35 and thefirst side plate 5. Even in this case, because thecommunication gap 36 having the cross-sectional area that is smaller than that of the high-pressure chamber 21 imparts resistance to the flow of the working oil, the working oil guided from thedischarge ports pressure chamber 21 is less likely to flow towards the raisedportion 35 and tends to directly flow into the high-pressure chamber 21 towards the high-pressure port 22 a. As described above, as used herein, the phrase “the raisedportion 35 that separates the both ends of the high-pressure chamber 21” is not restricted to that completely divides the high-pressure chamber 21, and the phrase also includes the raisedportion 35 that allows communication between the both ends of the high-pressure chamber 21 but makes the working oil to flow in one direction towards the high-pressure port 22 a more easily. - In addition, in the
first side plate 5, two arc-shapedback pressure ports 23 that are in communication with the high-pressure chamber 21 are formed (seeFIG. 1 ). Theback pressure ports 23 respectively communicate with theback pressure chambers 8. With such a configuration, the working oil in the high-pressure chamber 21 is guided into theback pressure chambers 8 through theback pressure ports 23. - In the
second side plate 6, two arc-shaped suction ports (not shown) that correspondingly open to the twosuction regions 4 b of the cam ring 4 (seeFIG. 2 ) and that guide the working oil to thepump chambers 9 are formed. In addition, in thepump cover 31, a suction passage (not shown) through which the tank (not shown) is communicated with the suction ports and that guides the working oil in the tank to thepump chambers 9 through the suction ports is formed. - In the
vane pump 100, by the rotation of therotor 2, the working oil is sucked from the tank through the suction ports and the suction passage to therespective pump chambers 9 in thesuction regions 4 b of thecam ring 4, and the working oil is discharged to the outside from therespective pump chambers 9 in thedischarge regions 4 c of thecam ring 4 through thedischarge ports discharge passage 22. As described above, in thevane pump 100, the working oil is supplied/discharged by expansion/contraction of therespective pump chambers 9 caused by the rotation of therotor 2. - The
pump cartridge 10 further has twofirst pins 11 that are provided so as to extend from thefirst side plate 5 to thesecond side plate 6 through the cam ring 4 (seeFIG. 1 ) and twosecond pins 12 that are provided so as to extend from thefirst side plate 5 to the pump body 30 (seeFIG. 4 ). - As shown in
FIG. 1 , thefirst pins 11 penetrate through thecam ring 4, and both ends thereof are respectively press-fitted into upper-side first press-fittingholes 11 a formed in thesecond side plate 6 and lower-side first press-fittingholes 11 b formed in thefirst side plate 5. Thereby, integration of thepump cartridge 10 is achieved. The twofirst pins 11 are symmetrically arranged with respect to the center of the cam ring 4 (seeFIG. 2 ). The twofirst pins 11 do not respectively penetrate through the first andsecond side plates first pins 11 do not project out from end surfaces of the first andsecond side plates - As shown in
FIG. 4 , both ends of thesecond pins 12 are respectively press-fitted into upper-side second press-fittingholes 12 a formed in thefirst side plate 5 and lower-side second press-fittingholes 12 b formed in the raisedportion 35. As shown inFIG. 3 , thesecond pins 12 are provided so as to avoid and so as not to penetrate a part of the high-pressure chamber 21 formed between the twodischarge ports pressure port 22 a. By providing the second pins 12, thepump cartridge 10 is aligned with respect to thepump body 30. - Because the raised
portion 35 is provided, the working oil guided from thedischarge ports portion 35 and mainly flows directly towards the high-pressure port 22 a through a part of the high-pressure chamber 21 formed between thedischarge ports pressure port 22 a. Therefore, if thesecond pins 12 are provided so as to penetrate through a part of the high-pressure chamber 21 formed between thedischarge ports pressure port 22 a, the flow-passage cross-sectional area is reduced and the flow of the working oil discharged from thepump chambers 9 is disturbed. - In contrast, in the
vane pump 100, as shown inFIG. 3 , because thesecond pins 12 are provided in the raisedportion 35, the flow of the working oil is disturbed by the second pins 12. Thus, by providing thesecond pins 12 in the raisedportion 35, it is possible to align thepump cartridge 10 with respect to thepump body 30 without affecting the flow of the working oil discharged from thepump chambers 9. In addition, because there is no need to form an alignment hole of thepump cartridge 10 in thepump cover 31, the passage shape of the suction passage formed in thepump cover 31 is not restricted by the alignment hole. Thus, the degree of freedom for designing the passage formed in thepump cover 31 is improved. With such a configuration, because it is possible to optimize layout of the suction passage and increase the cross-sectional area, and thereby, the sucking property thereof can be improved, it is possible to suppress occurrence of vibration and cavitation of thevane pump 100. - In addition, in a case in which a single
second pin 12 is provided, thepump cartridge 10 may be rotated about thesecond pins 12 by an angle corresponding to a gap formed between thepump cartridge 10 and theconcave portion 30 a of thepump body 30 in the radial direction. In contrast, in thevane pump 100, because twosecond pins 12 are provided, the rotation of thepump cartridge 10 about the second pins 12 is reliably prevented. In cases such as there is no risk of rotation of thepump cartridge 10 about the second pins 12, the singlesecond pin 12 may be provided. In addition, three or moresecond pins 12 may be provided. - Next, a modification of the above-mentioned embodiment will be described with reference to
FIGS. 5 and 6 . - In the above-mentioned embodiment, the
pump cartridge 10 has thesecond side plate 6 that is provided between thepump cover 31 and thecam ring 4. Instead of this configuration, thepump cartridge 10 may not have thesecond side plate 6, and thepump cover 31 may be brought into direct contact with thecam ring 4. In this case, thefirst pins 11 are provided so as to extend from thecam ring 4 to thefirst side plate 5, and the both ends thereof are respectively press-fitted into thecam ring 4 and thefirst side plate 5. In other words, thefirst pins 11 may be provided such that one end of thefirst pins 11, which is press-fitted into thecam ring 4, does not penetrate through thecam ring 4 and does not project out from thecam ring 4 towards thepump cover 31. - In addition, in the above-mentioned embodiment, the high-
pressure port 22 a opens to the high-pressure chamber 21 at the position deviated from that of each of the twodischarge ports FIG. 5 , the high-pressure port 22 a may open to the high-pressure chamber 21 at the position facing against the onedischarge port 20 a. Even in this case, the working oil guided from theother discharge port 20 b passes through the high-pressure chamber 21 extending between thedischarge port 20 b and the high-pressure port 22 a in the circumferential direction region R1. Therefore, even when thesecond pins 12 are provided at the positions where the raisedportion 35 is formed in the circumferential direction region R2 at the opposite side of the circumferential direction region R1, the flow of the working oil is not disturbed. Thus, the similar effects as those of the above-mentioned embodiment are afforded. - In addition, in the above-mentioned embodiment, the
second pins 12 are provided at the positions where the raisedportion 35 is formed. Instead of this configuration, the second pins 12 may be provided at any positions as long as the flow of the working oil flowing from thedischarge ports pressure port 22 a is not disturbed. Specifically, as shown inFIG. 5 , the second pins 12 may be provided at the positions where thesecond pins 12 do not penetrates through the high-pressure chamber 21 extending between each of the twodischarge ports pressure port 22 a. In other words, the second pins 12 may be provided at any positions in the circumferential direction region R2, where the raisedportion 35 is provided, at the opposite side of the circumferential direction region R1, where the high-pressure port 22 a is provided. Even in this case, because the flows of the working oil flowing from thedischarge ports pressure port 22 a are not disturbed by the second pins 12, the similar effects as those of the above-mentioned embodiment are afforded. - In addition, in the above-mentioned embodiment, the vane pump is the so-called
balanced vane pump 100 in which the cam ring has the two discharge regions and the two suction regions. Instead, the vane pump may be a so-calledunbalanced vane pump 200 in which the cam ring has one discharge region and one suction region. - More specifically, in the
vane pump 200, the first side plate is formed with a single suction port (not shown) that opens correspondingly to the suction region. In addition, the second side plate is formed with asingle discharge port 20 c that opens correspondingly to the discharge region. - In the
pump body 30, as shown inFIG. 6 , an arc-shaped high-pressure chamber 121 is formed at the position corresponding to thedischarge port 20 c. - The second pins 12 are provided at positions where the
second pins 12 avoid and do not penetrate through a part of the high-pressure chamber 121 extending in the circumferential direction between thedischarge port 20 c and the high-pressure port 22 a. With such a configuration, even with an unbalanced vane pump, similarly to the above-mentioned embodiment, it is possible to align thepump cartridge 10 without disturbing the flow of the working oil flowing from thedischarge port 20 c to the high-pressure port 22 a by the second pins 12. - According to the embodiment mentioned above, the advantages described below are afforded.
- In the
vane pump 100, thepump cartridge 10 integration of which is achieved with the first pins 11 is aligned with respect to thepump body 30 by thesecond pins 12 that are provided so as to extend from thefirst side plate 5 to thepump body 30. Thus, because there is no need to form the alignment hole for thepump cartridge 10 in thepump cover 31, the shape of the passage of the working oil formed in thepump cover 31 is not restricted by the alignment hole. Therefore, the degree of freedom for designing the passage of the working oil formed in thepump cover 31 is improved. - In addition, because the degree of freedom for designing the passage is improved, it is possible to optimize layout of the suction passage and to increase the cross-sectional area of the suction passage, and thereby, the sucking property thereof can be improved. Therefore, it is possible to suppress occurrence of vibration and cavitation of the
vane pump 100. - In addition, in the
vane pump 100, because thesecond pins 12 are provided in the raisedportion 35, the flow of the working oil discharged from thepump chambers 9 is not disturbed by the second pins 12. Thus, it is possible to align thepump cartridge 10 without affecting the flow of the working oil discharged from thepump chambers 9. - In addition, in the
vane pump 100, because the twosecond pins 12 are provided, the rotation of thepump cartridge 10 relative to thepump body 30 is also prevented. - The configurations, operations, and effects of the embodiment of the present invention will be collectively described below.
- The vane pumps 100 and 200 include: the
pump body 30 that has theconcave portion 30 a; thepump cover 31 that is attached to thepump body 30 and seals theconcave portion 30 a; and thepump cartridge 10 that is accommodated in an accommodating space defined by theconcave portion 30 a and thepump cover 31. Thepump cartridge 10 includes: therotor 2 that is linked to the driving shaft; the plurality ofslits 7 that have opening in the outer circumference of therotor 2 and are formed in a radiating pattern; the plurality ofvanes 3 that are respectively inserted into the plurality ofslits 7 in a slidable manner; thecam ring 4 that has thecam face 4 a on which the tip-ends of thevanes 3 slide by the rotation of therotor 2; thefirst side plate 5 that is provided between the bottom portion of theconcave portion 30 a in thepump body 30 and thecam ring 4; thefirst pins 11 that are provided so as to extend from thecam ring 4 to thefirst side plate 5; and thesecond pins 12 that are provided so as to extend from thefirst side plate 5 to thepump body 30. - In this configuration, the
pump cartridge 10 integration of which is achieved by the first pins 11 is aligned with respect to thepump body 30 by thesecond pins 12 that are provided so as to extend from thefirst side plate 5 to thepump body 30. Thus, because there is no need to form the alignment hole for thepump cartridge 10 in thepump cover 31, the shape of the passage of the working oil formed in thepump cover 31 is not restricted by the alignment hole. Therefore, the degree of freedom for designing the passage of the working oil in the vane pumps 100 and 200 is improved. - In addition, in the vane pumps 100 and 200, the
pump cartridge 10 includes two or more second pins 12. - According to this configuration, the rotation of the
pump cartridge 10 relative to thepump body 30 can be prevented. - In addition, in the vane pumps 100 and 200, the
first side plate 5 has thedischarge ports pump chambers 9 in thepump cartridge 10, which are defined by therotor 2, thecam ring 4, and theadjacent vanes 3; thepump body 30 has the arc-shaped high-pressure chambers pump chambers 9 is guided through thedischarge ports discharge passage 22 that is in communication with the high-pressure chamber 21 through the high-pressure port 22 a opening to the high-pressure chambers second pins 12 are provided at the positions where thesecond pins 12 do not penetrate through a part of the high-pressure chamber 21 extending in the circumferential direction between each of thedischarge ports pressure port 22 a. - In addition, in the vane pumps 100 and 200, the
pump body 30 is formed with the raisedportion 35 that separates the both ends of the high-pressure chamber 21, and thesecond pins 12 are provided so as to extend from thefirst side plate 5 to the raisedportion 35. - According to these configurations, because the
second pins 12 do not penetrate through a part of the high-pressure chamber 21 extending in the circumferential direction between thedischarge ports pressure port 22 a, the flow of the working oil guided from thedischarge ports pressure port 22 a is not disturbed by the second pins 12. Therefore, it is possible to align thepump cartridge 10 without affecting the flow of the working oil. - Embodiments of this invention were described above, but the above embodiments are merely examples of applications of this invention, and the technical scope of this invention is not limited to the specific constitutions of the above embodiments.
- This application claims priority based on Japanese Patent Application No. 2015-183260 filed with the Japan Patent Office on Sep. 16, 2015, the entire contents of which are incorporated into this specification.
Claims (4)
1. A vane pump comprising:
a pump body having a concave portion;
a pump cover attached to the pump body, the pump cover being configured to seal the concave portion; and
a pump cartridge accommodated in an accommodating space defined by the concave portion and the pump cover, wherein
the pump cartridge comprises:
a rotor linked to a driving shaft;
a plurality of slits formed in the rotor in a radiating pattern to open in an outer circumference of the rotor;
a plurality of vanes respectively inserted into the plurality of slits in a slidable manner;
a cam ring having an inner circumferential surface on which tip-ends of the vanes slide by rotation of the rotor;
a side plate provided between a bottom portion of the concave portion in the pump body and the cam ring;
a first pin provided so as to extend from the cam ring to the side plate; and
a second pin provided so as to extend from the side plate to the pump body.
2. The vane pump according to claim 1 , wherein
the pump cartridge comprises two or more second pins.
3. The vane pump according to claim 1 , wherein
the side plate has a discharge port configured to guide working fluid that has been discharged from pump chambers in the pump cartridge, the pump chambers being defined by the rotor, the cam ring, and the adjacent vanes,
the pump body has:
an arc-shaped high-pressure chamber into which the working fluid that has been discharged from the pump chambers is guided through the discharge port; and
a discharge passage configured to communicate with the high-pressure chamber through a high-pressure port opening to the high-pressure chamber, and
the second pin is provided at a position where the second pin does not penetrate through a part of the high-pressure chamber extending in a circumferential direction between the discharge port and the high-pressure port.
4. The vane pump according to claim 3 , wherein
the pump body is formed with a raised portion, the raised portion being configured to separate both ends of the high-pressure chamber, and
the second pin is provided so as to extend from the side plate to the raised portion.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015183260A JP6581450B2 (en) | 2015-09-16 | 2015-09-16 | Vane pump |
JP2015-183260 | 2015-09-16 | ||
PCT/JP2016/075170 WO2017047363A1 (en) | 2015-09-16 | 2016-08-29 | Vane pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US20180258931A1 true US20180258931A1 (en) | 2018-09-13 |
Family
ID=58289049
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/759,990 Abandoned US20180258931A1 (en) | 2015-09-16 | 2016-08-29 | Vane pump |
Country Status (5)
Country | Link |
---|---|
US (1) | US20180258931A1 (en) |
EP (1) | EP3351798A1 (en) |
JP (1) | JP6581450B2 (en) |
CN (1) | CN108026920A (en) |
WO (1) | WO2017047363A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7021866B2 (en) * | 2017-05-11 | 2022-02-17 | Kyb株式会社 | Cartridge type vane pump and pump device equipped with it |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3207077A (en) * | 1963-05-27 | 1965-09-21 | Gen Motors Corp | Pump |
US3253548A (en) * | 1958-09-19 | 1966-05-31 | Gen Motors Corp | Pump |
US4373871A (en) * | 1981-05-04 | 1983-02-15 | General Motors Corporation | Compact power steering pump |
US4419058A (en) * | 1981-06-08 | 1983-12-06 | General Motors Corporation | Hydraulic pump rotating group axial alignment structure |
US4842500A (en) * | 1986-05-20 | 1989-06-27 | Atsugi Motor Parts Company, Limited | Vane pump with positioning pins for cam ring |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3940145B2 (en) * | 2004-12-06 | 2007-07-04 | ユニシア ジェーケーシー ステアリングシステム株式会社 | Variable displacement vane pump |
JP2008163787A (en) * | 2006-12-27 | 2008-07-17 | Kayaba Ind Co Ltd | Vane pump |
JP2009052526A (en) * | 2007-08-29 | 2009-03-12 | Kayaba Ind Co Ltd | Vane pump |
JP5372582B2 (en) * | 2009-04-17 | 2013-12-18 | カヤバ工業株式会社 | Vane pump |
CN104061153A (en) * | 2014-05-27 | 2014-09-24 | 大连液压件有限公司 | Steering pump with single oil opening |
-
2015
- 2015-09-16 JP JP2015183260A patent/JP6581450B2/en active Active
-
2016
- 2016-08-29 EP EP16846234.9A patent/EP3351798A1/en not_active Withdrawn
- 2016-08-29 CN CN201680054168.8A patent/CN108026920A/en active Pending
- 2016-08-29 WO PCT/JP2016/075170 patent/WO2017047363A1/en active Application Filing
- 2016-08-29 US US15/759,990 patent/US20180258931A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3253548A (en) * | 1958-09-19 | 1966-05-31 | Gen Motors Corp | Pump |
US3207077A (en) * | 1963-05-27 | 1965-09-21 | Gen Motors Corp | Pump |
US4373871A (en) * | 1981-05-04 | 1983-02-15 | General Motors Corporation | Compact power steering pump |
US4419058A (en) * | 1981-06-08 | 1983-12-06 | General Motors Corporation | Hydraulic pump rotating group axial alignment structure |
US4842500A (en) * | 1986-05-20 | 1989-06-27 | Atsugi Motor Parts Company, Limited | Vane pump with positioning pins for cam ring |
Also Published As
Publication number | Publication date |
---|---|
EP3351798A1 (en) | 2018-07-25 |
JP6581450B2 (en) | 2019-09-25 |
WO2017047363A1 (en) | 2017-03-23 |
JP2017057793A (en) | 2017-03-23 |
CN108026920A (en) | 2018-05-11 |
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