US20180306182A1 - Vane pump - Google Patents
Vane pump Download PDFInfo
- Publication number
- US20180306182A1 US20180306182A1 US15/763,833 US201615763833A US2018306182A1 US 20180306182 A1 US20180306182 A1 US 20180306182A1 US 201615763833 A US201615763833 A US 201615763833A US 2018306182 A1 US2018306182 A1 US 2018306182A1
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- United States
- Prior art keywords
- vanes
- rotor
- slits
- vane pump
- pump
- 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
- 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
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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
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
-
- 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
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
-
- 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
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0881—Construction of vanes or vane holders the vanes consisting of two or more parts
-
- 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
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0023—Axial sealings for working fluid
-
- 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
- F04C2230/00—Manufacture
- F04C2230/90—Improving properties of machine parts
- F04C2230/91—Coating
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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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/70—Safety, emergency conditions or requirements
- F04C2270/701—Cold start
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2203/00—Non-metallic inorganic materials
- F05C2203/08—Ceramics; Oxides
- F05C2203/0804—Non-oxide ceramics
- F05C2203/0808—Carbon, e.g. graphite
Definitions
- the present invention relates to a vane pump.
- JP1999-230057A discloses a vane pump including a rotor that is accommodated in a housing and rotationally driven, vanes that move in a sliding manner in slits in the rotor, and a cam ring that is arranged at the outer side of the vanes and forms pump chambers with the rotor, the vanes, and so forth.
- An object of the present invention is to improve the starting performance of a vane pump.
- a vane pump 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; pump chambers defined by the rotor, the cam ring, and the pair of adjacent vanes, wherein the plurality of vanes have: a plurality of first vanes formed by applying DLC coating on a base material; and a second vane formed such that the base material is exposed, and the first vanes are respectively inserted into at least two adjacent slits of the plurality of slits.
- FIG. 1 is a front view of a vane pump according to a first embodiment of the present invention.
- FIG. 2 is a sectional view of the vane pump according to the first embodiment of the present invention.
- FIG. 3 is a front view of the vane pump according to a second embodiment of the present invention.
- FIG. 4 is a front view of the vane pump according to a third embodiment of the present invention.
- FIGS. 1 and 2 An overall configuration of a vane pump 100 according to a first embodiment of the present invention will be described with reference to FIGS. 1 and 2 .
- 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 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 pump body 10 having an accommodating concave portion 10 a for accommodating the cam ring 4 , and a pump cover 11 that is fastened to the pump body 10 to seal the accommodating concave portion 10 a.
- the driving shaft 1 is rotatably supported by the pump body 10 .
- 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 .
- the adjacent back pressure chambers 8 are communicated with each other by a back pressure groove 8 a formed in the pump cover 11 (see FIG. 2 ).
- vanes 3 are provided in the vane pump 100 .
- the vanes 3 are pushed in the directions in which the vanes 3 are drawn out from the slits 7 by the pressure of the working oil guided into the back pressure chambers 8 , 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 6 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 configuration of the vanes 3 will be described in detail later.
- 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 volumes of the pump chambers 6 , which are defined between respective vanes 3 that slide on the cam face 4 a by the rotation of the rotor 2 , are increased and discharge regions 4 c in which volumes of the pump chambers 6 are decreased.
- respective pump chambers 6 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 pump cover 11 is arranged so as to be in contact with the one side surface of each of the rotor 2 and the cam ring 4 (upper side surface in FIG. 2 ), and a side plate 5 is arranged so as to be in contact with the other side surface of each of the rotor 2 and the cam ring 4 (lower side surface in FIG. 2 ).
- the pump cover 11 and the side plate 5 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 6 are sealed.
- the two arc-shaped suction ports are formed so as to respectively open to the two suction regions 4 b of the cam ring 4 (see FIG. 1 ) in a corresponding manner and to guide the working oil to the pump chambers 6 .
- a suction passage (not shown) through which a tank (not shown) is communicated with the suction ports and that guides the working oil in the tank into the pump chambers 6 through the suction ports is formed.
- the side plate 5 has two arc-shaped discharge ports 20 that are formed so as to penetrate through the side plate 5 and open correspondingly to the discharge regions 4 c of the cam ring 4 .
- a high-pressure chamber 21 into which the working oil that has been discharged from the pump chambers 6 in the discharge regions 4 c is guided is formed.
- the working oil that has been discharged from the pump chambers 6 is guided the high-pressure chamber 21 through the discharge ports 20 of the side plate 5 .
- the working oil guided into the high-pressure chamber 21 is supplied to an external hydraulic apparatus through a discharge passage (not shown) that is formed in the pump body 10 and is in communication with the high-pressure chamber 21 .
- two arc-shaped back pressure ports 22 that are in communication with the high-pressure chamber 21 are formed.
- Each of the back pressure ports 22 communicates with the back pressure chambers 8 .
- the working oil in the high-pressure chamber 21 is guided into the back pressure chambers 8 through the back pressure ports 22 .
- the vane pump 100 As the rotor 2 is rotated, the working oil is sucked from the tank to each of the pump chambers 6 in the suction regions 4 b of the cam ring 4 through the suction ports and the suction passage, and the working oil is discharged to the outside from each of the pump chambers 6 in the discharge regions 4 c of the cam ring 4 through the discharge ports 20 and the discharge passage. As described above, in the vane pump 100 , the working oil is supplied/discharged by expansion/contraction of the respective pump chambers 6 caused by the rotation of the rotor 2 .
- the plurality of vanes 3 have first vanes 3 a that are formed by coating DLC (Diamond Like Carbon) on a base material and second vanes 3 b that are formed such that the base material is exposed.
- a state in which the base material is exposed means a state in which the DLC coating is not applied over the entirety of the vane 3 and the surface of the base material remains exposed as the surface of the vane 3 .
- the plurality of vanes 3 have two first vanes 3 a that are respectively inserted into the slits 7 , which are adjacent to each other. Because the first vanes 3 a on which the DLC coating is applied have a superior slidability, the viscous resistance of the working oil has less effect on the first vanes 3 a. Thus, even in the low-temperature situation in which the viscosity and the viscous resistance of the working oil are high, the first vanes 3 a project out from the slits 7 easily by the rotation of the rotor 2 . Thereby, one pump chamber (hereinafter referred to as “an initial pump chamber 6 a ”) is defined by the adjacent first vanes 3 a, and the starting performance of the vane pump 100 in the low-temperature situation is improved.
- an initial pump chamber 6 a one pump chamber
- the initial pump chamber 6 a is defined by the two adjacent first vanes 3 a
- a part of the working oil discharged from the initial pump chamber 6 a is guided into the back pressure chambers 8 through the high-pressure chamber 21 and the back pressure ports 22 .
- the second vanes 3 b on which the DLC coating is not applied are also pushed into the directions in which the second vanes 3 b are drawn out from the slits 7 by the pressure in the back pressure chambers 8 , and thereby, the second vanes 3 b project out from the slits 7 and define the pump chambers 6 .
- the initial pump chamber 6 a is defined by the two first vanes 3 a, it is possible to facilitate projection of other vanes 3 (the second vanes 3 b ) from the slits 7 , and so, it is possible to further improve the starting performance in the low-temperature situation.
- the first vanes 3 a have the superior slidability, because the DLC coating is applied on the base material, the cost required for the manufacture is high. Thus, if all of the plurality of vanes 3 are formed as the first vanes 3 a in order to improve the starting performance of the vane pump 100 , the manufacturing cost of the vane pump 100 is increased.
- the wear resistance of the first vanes 3 a is also improved.
- the durability of the vane pump 100 is also improved.
- the vane pump 100 has the two suction regions 4 b and two discharge regions 4 c.
- the vane pump 100 may have one or at least three suction regions 4 b and one or at least three discharge regions 4 c.
- the vane pump 100 because the sliding resistance of the first vanes 3 a on which the DLC coating is applied is small, even in the low-temperature situation, the first vanes 3 a project out from the slits 7 easily by the centrifugal force caused by the rotation of the rotor 2 . Thus, at the starting time of the vane pump 100 , the initial pump chamber 6 a is formed easily by the adjacent first vanes 3 a. Therefore, it is possible to improve the starting performance of the vane pump 100 .
- the initial pump chamber 6 a is defined by the two adjacent first vanes 3 a
- the working oil is guided into the back pressure chambers 8 through the high-pressure chamber 21 and the back pressure ports 22 , and so, the second vanes 3 b also project out from the slits 7 and define the pump chambers 6 .
- the initial pump chamber 6 a is defined by the two first vanes 3 a, it is possible to facilitate projection of the second vanes 3 b from the slits 7 , and so, it is possible to further improve the starting performance in the low-temperature situation.
- the vane pump 100 even there are only two adjacent first vanes 3 a, because the initial pump chamber 6 a is defined by the first vanes 3 a at the starting time and the working oil is guided into the respective back pressure chambers 8 , the projection of the second vanes 3 b from the slits 7 is facilitated. Therefore, by forming only two adjacent vanes 3 of twelve vanes 3 as the first vanes 3 a, it is possible to improve the starting performance of the vane pump 100 in the low-temperature situation, and at the same time, it is possible to suppress the increase in the manufacturing cost of the vane pump 100 .
- a vane pump 200 according to a second embodiment of the present invention will be described with reference to FIG. 3 .
- differences from the above-mentioned first embodiment will be mainly described, and components that are the same as those in the vane pump 100 in the above-mentioned first embodiment are assigned the same reference numerals and descriptions thereof will be omitted.
- the vane pump 200 differs from that in the above-mentioned first embodiment in that three first vanes 3 a are provided.
- the vane pump 200 has three first vanes 3 a and nine second vanes 3 b.
- the three first vanes 3 a are arranged side by side in a consecutive manner, and two initial pump chambers 6 a are respectively defined between the first vanes 3 a.
- the vane pump 200 similarly to the vane pump 100 , because the sliding resistance of the first vanes 3 a on which the DLC coating is applied is small, even in the low-temperature situation, the first vanes 3 a project out from the slits 7 easily by the centrifugal force caused by the rotation of the rotor 2 . Thus, at the starting time of the vane pump 200 , the initial pump chambers 6 a are formed easily by the consecutive three first vanes 3 a. Therefore, it is possible to improve the starting performance of the vane pump 200 .
- the vane pump 200 similarly to the vane pump 100 , because the initial pump chambers 6 a are each defined by the two adjacent first vanes 3 a, the working oil is guided into the back pressure chambers 8 through the high-pressure chamber 21 and the back pressure ports 22 , and thereby, the second vanes 3 b also project out from the slits 7 and form the pump chambers. As described above, because two initial pump chambers 6 a are defined by the three first vanes 3 a, it is possible to facilitate projection of the second vanes 3 b from the slits 7 , and so, it is possible to further improve the starting performance in the low-temperature situation.
- the first vanes 3 a project out from the slits 7 easily, and the projected first vanes 3 a are pushed back into the slits 7 as they enter the discharge regions 4 c.
- the working oil in the back pressure chambers 8 defined by these first vanes 3 a is guided into the back pressure chambers 8 in the adjacent suction regions 4 b through the back pressure groove 8 a.
- the vane pump 200 because two initial pump chambers 6 a are defined, it is possible to increase the flowing amount of the working oil guided into the back pressure chambers 8 at the starting time. Thus, it is possible to allow the second vanes 3 b to project out from the slits 7 with high reliability, and it is possible to further improve the starting performance of the vane pump 200 .
- a vane pump 300 according to a third embodiment of the present invention will be described with reference to FIG. 4 .
- differences from the above-mentioned second embodiment will be mainly described, and components that are the same as those in the vane pump 200 in the above-mentioned second embodiment are assigned the same reference numerals and descriptions thereof will be omitted.
- two initial pump chambers 6 a are defined by the consecutive three first vanes 3 a arranged side by side.
- the vane pump 300 differs from that in the above-mentioned second embodiment in that the two initial pump chambers 6 a are defined by four first vanes 3 a.
- the vanes 3 have four first vanes 3 a and eight second vanes 3 b.
- the four first vanes 3 a are arranged such that pairs of the adjacent first vanes 3 a face against each other with the center of the rotor 2 located therebetween.
- one initial pump chamber 6 a is defined by two adjacent first vanes 3 a
- two initial pump chambers 6 a that face against each other with the center of the rotor 2 located therebetween are defined by the four first vanes 3 a.
- a state in which a part of the vanes 3 are moved downward in the vertical direction due to the gravitational force and are brought into contact with the cam face 4 a (a state in which the vanes 3 are projected out from the slits 7 ) may be maintained even when the operation is stopped.
- the vane pump 300 because the two initial pump chambers 6 a that face against each other with the center of the rotor 2 located therebetween are defined, when the operation is stopped, as compared with the case in the vane pumps 100 and 200 according to the first and second embodiments, the first vanes 3 a are more likely to be located at the position where a state in which the first vanes 3 a are projected out from the slits 7 is achieved (in particular, at the lower portion in the vertical direction). Therefore, in the vane pump 300 , even when the operation is stopped, the initial pump chamber 6 a is likely to be defined, and it is possible to further improve the starting performance.
- the vane pumps 100 , 200 , and 300 include: the rotor 2 that is linked to the driving shaft 1 ; the plurality of slits 7 that are formed in the rotor 2 in a radiating pattern and have opening in the outer circumference of the rotor 2 ; 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 ; and the pump chambers 6 that are defined by the rotor 2 , the cam ring 4 , and a pair of adjacent vanes 3 .
- the plurality of vanes 3 have the plurality of first vanes 3 a that are formed by applying the DLC coating on the base material and the second vanes 3 b that are formed such that the base material is exposed, and the first vanes 3 a are respectively inserted into at least two adjacent slits 7 of the plurality of slits 7 .
- the vane pumps 100 , 200 , and 300 further include the back pressure chambers 8 that are defined in the slits 7 by the base-end portions of the vanes 3 and into which the working oil discharged from the pump chambers 6 is guided.
- the initial pump chamber 6 a is defined by the two adjacent first vanes 3 a
- the working oil is guided into the back pressure chambers 8
- the second vanes 3 b also project out from the slits 7 by the pressure of the working oil in the back pressure chambers 8 and define the pump chambers 6 .
- the initial pump chamber 6 a is defined by the two first vanes 3 a, it is possible to facilitate projection of the second vanes 3 b from the slits 7 , and so, it is possible to further improve the starting performance in the low-temperature situation.
- the plurality of vanes 3 have two first vanes 3 a.
- the vane pump 200 has three first vanes 3 a, and the three first vanes 3 a are arranged side by side in a consecutive manner.
- the vane pump 300 has four first vanes 3 a, and the four first vanes 3 a are arranged such that the pairs of the adjacent first vanes 3 a face against each other with the center of the rotor 2 located therebetween.
Abstract
A vane pump includes a rotor; a plurality of slits that are formed in the rotor, the plurality of vanes being respectively inserted into the plurality of slits in a slidable manner; a cam ring that has a cam face on which tip-ends of the vanes slide by the rotation of the rotor; and pump chambers that are defined by the rotor, the cam ring, and an adjacent pair of the vanes. The plurality of vanes have a plurality of first vanes that are formed by applying a DLC coating on a base material and second vanes that are formed such that the base material is exposed, the first vanes being respectively inserted into at least two adjacent slits of the plurality of slits.
Description
- The present invention relates to a vane pump.
- JP1999-230057A discloses a vane pump including a rotor that is accommodated in a housing and rotationally driven, vanes that move in a sliding manner in slits in the rotor, and a cam ring that is arranged at the outer side of the vanes and forms pump chambers with the rotor, the vanes, and so forth.
- Because working oil has high viscosity and high viscous resistance in a low-temperature situation, in the vane pump in the low-temperature situation, the vanes are prevented from sliding due to the viscous resistance of the working oil. Therefore, at a starting time of the vane pump in the low-temperature situation, the pump chambers are not easily defined by the vanes. As described above, in the low-temperature situation, the starting performance of the vane pump is deteriorated.
- An object of the present invention is to improve the starting performance of a vane pump.
- According to one aspect of the present invention, a vane pump 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; pump chambers defined by the rotor, the cam ring, and the pair of adjacent vanes, wherein the plurality of vanes have: a plurality of first vanes formed by applying DLC coating on a base material; and a second vane formed such that the base material is exposed, and the first vanes are respectively inserted into at least two adjacent slits of the plurality of slits.
-
FIG. 1 is a front view of a vane pump according to a first embodiment of the present invention. -
FIG. 2 is a sectional view of the vane pump according to the first embodiment of the present invention. -
FIG. 3 is a front view of the vane pump according to a second embodiment of the present invention. -
FIG. 4 is a front view of the vane pump according to a third embodiment of the present invention. - An overall configuration of a
vane pump 100 according to a first embodiment of the present invention will be described with reference toFIGS. 1 and 2. - 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. - 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. 1 . - As shown in
FIGS. 1 and 2 , thevane pump 100 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, apump body 10 having an accommodatingconcave portion 10 a for accommodating thecam ring 4, and apump cover 11 that is fastened to thepump body 10 to seal the accommodatingconcave portion 10 a. As shown inFIG. 2 , thedriving shaft 1 is rotatably supported by thepump body 10. - As shown in
FIG. 1 , 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. In addition, the adjacentback pressure chambers 8 are communicated with each other by aback pressure groove 8 a formed in the pump cover 11 (seeFIG. 2 ). - In the
vane pump 100, twelvevanes 3 are provided. Thevanes 3 are pushed in the directions in which thevanes 3 are drawn out from theslits 7 by the pressure of the working oil guided into theback pressure chambers 8, 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 6 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 configuration of thevanes 3 will be described in detail later. - 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 volumes of thepump chambers 6, which are defined betweenrespective vanes 3 that slide on thecam face 4 a by the rotation of therotor 2, are increased anddischarge regions 4 c in which volumes of thepump chambers 6 are decreased. As described above,respective pump chambers 6 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. 2 , thepump cover 11 is arranged so as to be in contact with the one side surface of each of therotor 2 and the cam ring 4 (upper side surface inFIG. 2 ), and aside plate 5 is arranged so as to be in contact with the other side surface of each of therotor 2 and the cam ring 4 (lower side surface inFIG. 2 ). Thepump cover 11 and theside plate 5 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 6 are sealed. - On an
end surface 11 a of thepump cover 11 on which therotor 2 slides, the two arc-shaped suction ports (not shown) are formed so as to respectively open to the twosuction regions 4 b of the cam ring 4 (seeFIG. 1 ) in a corresponding manner and to guide the working oil to thepump chambers 6. In addition, in thepump cover 11, a suction passage (not shown) through which a tank (not shown) is communicated with the suction ports and that guides the working oil in the tank into thepump chambers 6 through the suction ports is formed. - The
side plate 5 has two arc-shaped discharge ports 20 that are formed so as to penetrate through theside plate 5 and open correspondingly to thedischarge regions 4 c of thecam ring 4. - In the
pump body 10, a high-pressure chamber 21 into which the working oil that has been discharged from thepump chambers 6 in thedischarge regions 4 c is guided is formed. The working oil that has been discharged from thepump chambers 6 is guided the high-pressure chamber 21 through thedischarge ports 20 of theside plate 5. The working oil guided into the high-pressure chamber 21 is supplied to an external hydraulic apparatus through a discharge passage (not shown) that is formed in thepump body 10 and is in communication with the high-pressure chamber 21. - In the
side plate 5, two arc-shapedback pressure ports 22 that are in communication with the high-pressure chamber 21 are formed. Each of theback pressure ports 22 communicates 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 22. - With the
vane pump 100, as therotor 2 is rotated, the working oil is sucked from the tank to each of thepump chambers 6 in thesuction regions 4 b of thecam ring 4 through the suction ports and the suction passage, and the working oil is discharged to the outside from each of thepump chambers 6 in thedischarge regions 4 c of thecam ring 4 through thedischarge ports 20 and the discharge passage. As described above, in thevane pump 100, the working oil is supplied/discharged by expansion/contraction of therespective pump chambers 6 caused by the rotation of therotor 2. - Next, the configurations of the
vanes 3 will be specifically described. - As shown in
FIG. 1 , the plurality ofvanes 3 havefirst vanes 3 a that are formed by coating DLC (Diamond Like Carbon) on a base material andsecond vanes 3 b that are formed such that the base material is exposed. A state in which the base material is exposed means a state in which the DLC coating is not applied over the entirety of thevane 3 and the surface of the base material remains exposed as the surface of thevane 3. - The plurality of
vanes 3 have twofirst vanes 3 a that are respectively inserted into theslits 7, which are adjacent to each other. Because thefirst vanes 3 a on which the DLC coating is applied have a superior slidability, the viscous resistance of the working oil has less effect on thefirst vanes 3 a. Thus, even in the low-temperature situation in which the viscosity and the viscous resistance of the working oil are high, the first vanes 3 a project out from theslits 7 easily by the rotation of therotor 2. Thereby, one pump chamber (hereinafter referred to as “aninitial pump chamber 6 a”) is defined by the adjacentfirst vanes 3 a, and the starting performance of thevane pump 100 in the low-temperature situation is improved. - In addition, because the
initial pump chamber 6 a is defined by the two adjacentfirst vanes 3 a, a part of the working oil discharged from theinitial pump chamber 6 a is guided into theback pressure chambers 8 through the high-pressure chamber 21 and theback pressure ports 22. Thus, thesecond vanes 3 b on which the DLC coating is not applied are also pushed into the directions in which thesecond vanes 3 b are drawn out from theslits 7 by the pressure in theback pressure chambers 8, and thereby, thesecond vanes 3 b project out from theslits 7 and define thepump chambers 6. As described above, because theinitial pump chamber 6 a is defined by the twofirst vanes 3 a, it is possible to facilitate projection of other vanes 3 (thesecond vanes 3 b) from theslits 7, and so, it is possible to further improve the starting performance in the low-temperature situation. - Although the
first vanes 3 a have the superior slidability, because the DLC coating is applied on the base material, the cost required for the manufacture is high. Thus, if all of the plurality ofvanes 3 are formed as thefirst vanes 3 a in order to improve the starting performance of thevane pump 100, the manufacturing cost of thevane pump 100 is increased. - In contrast, in the
vane pump 100, other tenvanes 3 than the twofirst vanes 3 a are all formed as thesecond vanes 3 b. Even there are only two adjacentfirst vanes 3 a, because theinitial pump chamber 6 a is defined by thefirst vanes 3 a at the starting time, the working oil discharged from theinitial pump chamber 6 a is guided into respectiveback pressure chambers 8, and the projection of thesecond vanes 3 b from theslits 7 is facilitated. Thereby, the starting performance of thevane pump 100 is improved sufficiently. Therefore, by forming only twoadjacent vanes 3 of twelvevanes 3 as thefirst vanes 3 a, it is possible to improve the starting performance of thevane pump 100 in the low-temperature situation, and at the same time, it is possible to suppress the increase in the manufacturing cost of thevane pump 100. - In addition, by applying the DLC coating, the wear resistance of the
first vanes 3 a is also improved. Thus, the durability of thevane pump 100 is also improved. - Next, a modification of the above-mentioned first embodiment will be described.
- In the above-mentioned first embodiment, the
vane pump 100 has the twosuction regions 4 b and twodischarge regions 4 c. Instead of this configuration, thevane pump 100 may have one or at least threesuction regions 4 b and one or at least threedischarge regions 4 c. - According to the first embodiment mentioned above, the advantages described below are afforded.
- In the
vane pump 100, because the sliding resistance of thefirst vanes 3 a on which the DLC coating is applied is small, even in the low-temperature situation, thefirst vanes 3 a project out from theslits 7 easily by the centrifugal force caused by the rotation of therotor 2. Thus, at the starting time of thevane pump 100, theinitial pump chamber 6 a is formed easily by the adjacentfirst vanes 3 a. Therefore, it is possible to improve the starting performance of thevane pump 100. - In addition, in the
vane pump 100, because theinitial pump chamber 6 a is defined by the two adjacentfirst vanes 3 a, the working oil is guided into theback pressure chambers 8 through the high-pressure chamber 21 and theback pressure ports 22, and so, thesecond vanes 3 b also project out from theslits 7 and define thepump chambers 6. As described above, because theinitial pump chamber 6 a is defined by the twofirst vanes 3 a, it is possible to facilitate projection of thesecond vanes 3 b from theslits 7, and so, it is possible to further improve the starting performance in the low-temperature situation. - In addition, in the
vane pump 100, even there are only two adjacentfirst vanes 3 a, because theinitial pump chamber 6 a is defined by thefirst vanes 3 a at the starting time and the working oil is guided into the respectiveback pressure chambers 8, the projection of thesecond vanes 3 b from theslits 7 is facilitated. Therefore, by forming only twoadjacent vanes 3 of twelvevanes 3 as thefirst vanes 3 a, it is possible to improve the starting performance of thevane pump 100 in the low-temperature situation, and at the same time, it is possible to suppress the increase in the manufacturing cost of thevane pump 100. - Next, a
vane pump 200 according to a second embodiment of the present invention will be described with reference toFIG. 3 . In the following, differences from the above-mentioned first embodiment will be mainly described, and components that are the same as those in thevane pump 100 in the above-mentioned first embodiment are assigned the same reference numerals and descriptions thereof will be omitted. - In the above-mentioned first embodiment, the two adjacent
first vanes 3 a are provided, and all thevanes 3 other than thefirst vanes 3 a are formed as thesecond vanes 3 b. Instead of employing this configuration, thevane pump 200 differs from that in the above-mentioned first embodiment in that threefirst vanes 3 a are provided. - As shown in
FIG. 3 , thevane pump 200 has threefirst vanes 3 a and ninesecond vanes 3 b. - The three
first vanes 3 a are arranged side by side in a consecutive manner, and twoinitial pump chambers 6 a are respectively defined between thefirst vanes 3 a. - According to the second embodiment mentioned above, the advantages described below are afforded.
- In the
vane pump 200, similarly to thevane pump 100, because the sliding resistance of thefirst vanes 3 a on which the DLC coating is applied is small, even in the low-temperature situation, thefirst vanes 3 a project out from theslits 7 easily by the centrifugal force caused by the rotation of therotor 2. Thus, at the starting time of thevane pump 200, theinitial pump chambers 6 a are formed easily by the consecutive threefirst vanes 3 a. Therefore, it is possible to improve the starting performance of thevane pump 200. - In addition, in the
vane pump 200, similarly to thevane pump 100, because theinitial pump chambers 6 a are each defined by the two adjacentfirst vanes 3 a, the working oil is guided into theback pressure chambers 8 through the high-pressure chamber 21 and theback pressure ports 22, and thereby, thesecond vanes 3 b also project out from theslits 7 and form the pump chambers. As described above, because twoinitial pump chambers 6 a are defined by the threefirst vanes 3 a, it is possible to facilitate projection of thesecond vanes 3 b from theslits 7, and so, it is possible to further improve the starting performance in the low-temperature situation. - In addition, in the
vane pump 200, even at the starting time, thefirst vanes 3 a project out from theslits 7 easily, and the projectedfirst vanes 3 a are pushed back into theslits 7 as they enter thedischarge regions 4 c. By thefirst vanes 3 a that are pushed back into theslits 7, the working oil in theback pressure chambers 8 defined by thesefirst vanes 3 a is guided into theback pressure chambers 8 in theadjacent suction regions 4 b through theback pressure groove 8 a. Thereby, it is possible to further facilitate projection of thevanes 3 in thesuction regions 4 b. - In addition, in the
vane pump 200, because twoinitial pump chambers 6 a are defined, it is possible to increase the flowing amount of the working oil guided into theback pressure chambers 8 at the starting time. Thus, it is possible to allow thesecond vanes 3 b to project out from theslits 7 with high reliability, and it is possible to further improve the starting performance of thevane pump 200. - Next, a
vane pump 300 according to a third embodiment of the present invention will be described with reference toFIG. 4 . In the following, differences from the above-mentioned second embodiment will be mainly described, and components that are the same as those in thevane pump 200 in the above-mentioned second embodiment are assigned the same reference numerals and descriptions thereof will be omitted. - In the above-mentioned second embodiment, two
initial pump chambers 6 a are defined by the consecutive threefirst vanes 3 a arranged side by side. Instead of employing this configuration, thevane pump 300 differs from that in the above-mentioned second embodiment in that the twoinitial pump chambers 6 a are defined by fourfirst vanes 3 a. - As shown in
FIG. 4 , in thevane pump 300, thevanes 3 have fourfirst vanes 3 a and eightsecond vanes 3 b. - In the
vane pump 300, the fourfirst vanes 3 a are arranged such that pairs of the adjacentfirst vanes 3 a face against each other with the center of therotor 2 located therebetween. In other words, oneinitial pump chamber 6 a is defined by two adjacentfirst vanes 3 a, and twoinitial pump chambers 6 a that face against each other with the center of therotor 2 located therebetween are defined by the fourfirst vanes 3 a. - According to the above-mentioned third embodiment, in addition to the advantages similar to those offered by the above-mentioned second embodiment, the advantages described below are afforded.
- In the
vane pump 300, in a case where, in particular, therotor 2 is provided such that the central axis thereof is inclined from the vertical direction, a state in which a part of thevanes 3 are moved downward in the vertical direction due to the gravitational force and are brought into contact with thecam face 4 a (a state in which thevanes 3 are projected out from the slits 7) may be maintained even when the operation is stopped. In thevane pump 300, because the twoinitial pump chambers 6 a that face against each other with the center of therotor 2 located therebetween are defined, when the operation is stopped, as compared with the case in the vane pumps 100 and 200 according to the first and second embodiments, thefirst vanes 3 a are more likely to be located at the position where a state in which thefirst vanes 3 a are projected out from theslits 7 is achieved (in particular, at the lower portion in the vertical direction). Therefore, in thevane pump 300, even when the operation is stopped, theinitial pump chamber 6 a is likely to be defined, and it is possible to further improve the starting performance. - The configurations, operations, and effects of the embodiment of the present invention will be collectively described below.
- The vane pumps 100, 200, and 300 include: the
rotor 2 that is linked to the drivingshaft 1; the plurality ofslits 7 that are formed in therotor 2 in a radiating pattern and have opening in the outer circumference of therotor 2; 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; and thepump chambers 6 that are defined by therotor 2, thecam ring 4, and a pair ofadjacent vanes 3. The plurality ofvanes 3 have the plurality offirst vanes 3 a that are formed by applying the DLC coating on the base material and thesecond vanes 3 b that are formed such that the base material is exposed, and thefirst vanes 3 a are respectively inserted into at least twoadjacent slits 7 of the plurality ofslits 7. - With this configuration, because the sliding resistance of the
first vanes 3 a on which the DLC coating is applied is small, even in the low-temperature situation, thefirst vanes 3 a project out from theslits 7 easily by the centrifugal force caused by the rotation of therotor 2. Thus, at the starting time of the vane pumps 100, 200, and 300, theinitial pump chamber 6 a is formed easily by the adjacentfirst vanes 3 a. Therefore, the starting performance of the vane pumps 100, 200, and 300 is improved. - In addition, the vane pumps 100, 200, and 300 further include the
back pressure chambers 8 that are defined in theslits 7 by the base-end portions of thevanes 3 and into which the working oil discharged from thepump chambers 6 is guided. - With this configuration, because the
initial pump chamber 6 a is defined by the two adjacentfirst vanes 3 a, the working oil is guided into theback pressure chambers 8, and thesecond vanes 3 b also project out from theslits 7 by the pressure of the working oil in theback pressure chambers 8 and define thepump chambers 6. As described above, because theinitial pump chamber 6 a is defined by the twofirst vanes 3 a, it is possible to facilitate projection of thesecond vanes 3 b from theslits 7, and so, it is possible to further improve the starting performance in the low-temperature situation. - In addition, in the
vane pump 100, the plurality ofvanes 3 have twofirst vanes 3 a. - With this configuration, even there are only two adjacent
first vanes 3 a, because theinitial pump chamber 6 a is defined by thefirst vanes 3 a at the starting time and the working oil is guided into the respectiveback pressure chambers 8, the projection of thesecond vanes 3 b from theslits 7 is facilitated. Therefore, by forming only twoadjacent vanes 3 of the plurality ofvanes 3 as thefirst vanes 3 a, it is possible to improve the starting performance of thevane pump 100 in the low-temperature situation, and at the same time, it is possible to suppress the increase in the manufacturing cost of thevane pump 100. - In addition, the
vane pump 200 has threefirst vanes 3 a, and the threefirst vanes 3 a are arranged side by side in a consecutive manner. - With this configuration, because two
initial pump chambers 6 a are defined, at the starting time, it is possible to increase the flowing amount of the working oil guided into theback pressure chambers 8. Thus, it is possible to allow thesecond vanes 3 b to project out from theslits 7 with high reliability, and thereby, it is possible to further improve the starting performance of the vane pumps 200 and 300. - In addition, the
vane pump 300 has fourfirst vanes 3 a, and the fourfirst vanes 3 a are arranged such that the pairs of the adjacentfirst vanes 3 a face against each other with the center of therotor 2 located therebetween. - With this configuration, because the pairs of the adjacent
first vanes 3 a are arranged so as to face against each other with the center of therotor 2 located therebetween, even when the operation of thevane pump 300 is stopped, it is likely that thefirst vanes 3 a are located at the lower portion of therotor 2 in the vertical direction and theinitial pump chamber 6 a is defined. Therefore, it is possible to further improve the starting performance of thevane pump 300. - 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.2015-191667 filed with the Japan Patent Office on Sep. 29, 2015, the entire contents of which are incorporated into this specification.
Claims (5)
1. A vane pump comprising:
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;
pump chambers defined by the rotor, the cam ring, and the pair of adjacent vanes,
wherein the plurality of vanes have:
a plurality of first vanes formed by applying DLC coating on a base material; and
a second vane formed such that the base material is exposed, and
the first vanes are respectively inserted into at least two adjacent slits of the plurality of slits.
2. The vane pump according to claim 1 , further comprising
back pressure chambers into which working fluid discharged from the pump chamber is guided, the back pressure chambers being defined in the slits by base-end portions of the vanes.
3. The vane pump according to claim 1 , wherein
the plurality of vanes have the two first vanes.
4. The vane pump according to claim 1 , wherein
the plurality of vanes have the three first vanes, and
the three first vanes are arranged side by side in a consecutive manner.
5. The vane pump according to claim 1 , wherein
the plurality of vanes have the four first vanes, and
the four first vanes are arranged such that pairs of the adjacent first vanes face against each other with a center of the rotor located therebetween.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015-191667 | 2015-09-29 | ||
JP2015191667A JP6480841B2 (en) | 2015-09-29 | 2015-09-29 | Vane pump |
PCT/JP2016/075860 WO2017056850A1 (en) | 2015-09-29 | 2016-09-02 | Vane pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US20180306182A1 true US20180306182A1 (en) | 2018-10-25 |
Family
ID=58423246
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/763,833 Abandoned US20180306182A1 (en) | 2015-09-29 | 2016-09-02 | Vane pump |
Country Status (6)
Country | Link |
---|---|
US (1) | US20180306182A1 (en) |
EP (1) | EP3358187A1 (en) |
JP (1) | JP6480841B2 (en) |
CN (1) | CN108026921A (en) |
MX (1) | MX2018003766A (en) |
WO (1) | WO2017056850A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2020076338A (en) * | 2018-11-06 | 2020-05-21 | 株式会社ミクニ | Vane pump and rotor assembly |
KR102553909B1 (en) * | 2021-09-13 | 2023-07-07 | 현대트랜시스 주식회사 | Transmission |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04269387A (en) * | 1991-02-25 | 1992-09-25 | Toyoda Mach Works Ltd | Vane pump |
US5672054A (en) * | 1995-12-07 | 1997-09-30 | Carrier Corporation | Rotary compressor with reduced lubrication sensitivity |
JP4616140B2 (en) * | 2005-09-30 | 2011-01-19 | 三菱電機株式会社 | Hermetic compressor and water heater |
JP2007284760A (en) * | 2006-04-18 | 2007-11-01 | Toyota Motor Corp | Sliding member |
JP2014181635A (en) * | 2013-03-19 | 2014-09-29 | Jtekt Corp | Vane structure and vane device |
-
2015
- 2015-09-29 JP JP2015191667A patent/JP6480841B2/en active Active
-
2016
- 2016-09-02 MX MX2018003766A patent/MX2018003766A/en unknown
- 2016-09-02 EP EP16851026.1A patent/EP3358187A1/en not_active Withdrawn
- 2016-09-02 WO PCT/JP2016/075860 patent/WO2017056850A1/en active Application Filing
- 2016-09-02 US US15/763,833 patent/US20180306182A1/en not_active Abandoned
- 2016-09-02 CN CN201680054620.0A patent/CN108026921A/en active Pending
Also Published As
Publication number | Publication date |
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CN108026921A (en) | 2018-05-11 |
JP2017066937A (en) | 2017-04-06 |
JP6480841B2 (en) | 2019-03-13 |
EP3358187A1 (en) | 2018-08-08 |
MX2018003766A (en) | 2018-07-06 |
WO2017056850A1 (en) | 2017-04-06 |
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