US20160222953A1 - Variable displacement swash plate type compressor - Google Patents

Variable displacement swash plate type compressor Download PDF

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Publication number
US20160222953A1
US20160222953A1 US14/917,820 US201414917820A US2016222953A1 US 20160222953 A1 US20160222953 A1 US 20160222953A1 US 201414917820 A US201414917820 A US 201414917820A US 2016222953 A1 US2016222953 A1 US 2016222953A1
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US
United States
Prior art keywords
swash plate
chamber
inclination angle
compressor
drive shaft
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
Application number
US14/917,820
Other languages
English (en)
Inventor
Shinya Yamamoto
Yusuke Yamazaki
Takahiro Suzuki
Kazunari Honda
Masaki Ota
Hiroyuki Nakaima
Hideharu Yamashita
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
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Toyota Industries Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI reassignment KABUSHIKI KAISHA TOYOTA JIDOSHOKKI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OTA, MASAKI, HONDA, KAZUNARI, SUZUKI, TAKAHIRO, YAMASHITA, HIDEHARU, YAMAZAKI, YUSUKE, NAKAIMA, HIROYUKI, YAMAMOTO, SHINYA
Publication of US20160222953A1 publication Critical patent/US20160222953A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—Distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening

Definitions

  • the present invention relates to a variable displacement swash plate type compressor.
  • Patent Literature 1 discloses a conventional variable displacement swash plate type compressor (hereinafter referred to as a compressor). This compressor comprises a housing, a drive shaft, a swash plate, a link mechanism, a plurality of pistons, a conversion mechanism, and a capacity control mechanism.
  • a suction chamber, a discharge chamber, a swash plate chamber and a plurality of cylinder bores are formed.
  • the drive shaft is rotatably supported by the housing.
  • the swash plate is rotatable in the swash plate chamber by rotation of the drive shaft.
  • the link mechanism is provided between the drive shaft and the swash plate and permits change of an inclination angle of the swash plate with respect to a direction perpendicular to a driving axis of the drive shaft.
  • the link mechanism has a lug member and a transmission member. The lug member is fixed to the drive shaft in the swash plate chamber.
  • the transmission member is provided integrally with the swash plate in the swash plate chamber, and transmits rotation of the lug member to the swash plate.
  • the pistons are reciprocally accommodated in respective cylinder bores.
  • the conversion mechanism reciprocates the pistons in the cylinder bores at a stroke corresponding to the inclination angle by rotation of the swash plate.
  • the capacity control mechanism has a supply passage, a bleed passage and a control valve.
  • the supply passage provides communication between the discharge chamber and the swash plate chamber.
  • the bleed passage provides communication between the swash plate chamber and the suction chamber.
  • the control valve is capable of changing the pressure in the swash plate chamber by regulating an opening degree of the supply passage.
  • This compressor includes an actuator that is capable of changing an inclination angle, and a control mechanism that controls the actuator.
  • the actuator has a lug member, a movable body that engages with a swash plate so as to be rotatable integrally therewith and is movable in the direction of a driving axis to change the inclination angle, and a control pressure chamber that is defined by the lug member and the movable body and moves the movable body by its internal pressure.
  • the control mechanism has a control passage and a control valve.
  • the control passage has a variable pressure passage that communicates with the control pressure chamber, a low pressure passage that communicates with a suction chamber and a swash plate chamber, and a high pressure passage that communicates with a discharge chamber.
  • a part of the variable pressure passage is formed in a drive shaft.
  • the control valve regulates an opening degree of the variable pressure passage, the low pressure passage and the high pressure passage. In other words, the control valve allows the variable pressure passage to communicate with the low pressure passage or the high pressure passage.
  • this compressor is configured to change the pressure in the control pressure chamber, which has a smaller volume than the swash plate chamber, the amount of the refrigerant required to change the inclination angle can be reduced as compared to the compressor configured to change the pressure in the swash plate chamber, and thereby downsizing can be realized.
  • this compressor is configured to change the inclination angle by changing the pressure in the control pressure chamber, the blow-by gas flowing into the swash plate chamber and the liquid accumulation in the swash plate chamber are less likely to exert an adverse effect on the change of the inclination angle.
  • Patent Literature 1 Japanese Patent Laid-Open No. 2002-213350
  • Patent Literature 2 Japanese Patent Laid-Open No. 52-131204
  • variable differential pressure a differential pressure between the swash plate chamber and the control pressure chamber (hereinafter referred to as a variable differential pressure) to thereby move the movable body by a larger thrust force. That is, in this compressor, the load exerted on the movable body increases as the inclination angle decreases. Therefore, in this compressor, the amount of change in the variable differential pressure when the inclination angle changes is large; therefore, it is difficult to quickly change the inclination angle in response to the driving conditions of a vehicle or the like, and controllability is lowered.
  • the present invention has been made in the light of the conventional circumstances described above, and an object of the invention is to provide a variable displacement swash plate type compressor capable of exhibiting high controllability and excellent mountability.
  • a variable displacement swash plate type compressor of the present invention comprises: a housing in which a swash plate chamber and a cylinder bore are formed; a drive shaft that is rotatably supported by the housing; a swash plate that is rotatable in the swash plate chamber by rotation of the drive shaft; a link mechanism that is provided between the drive shaft and the swash plate and permits change of an inclination angle of the swash plate with respect to a direction perpendicular to a driving axis of the drive shaft; a piston that is reciprocally accommodated in the cylinder bore; a conversion mechanism that reciprocates the piston in the cylinder bore at a stroke corresponding to the inclination angle by rotation of the swash plate; an actuator capable of changing the inclination angle; and a control mechanism that controls the actuator,
  • the link mechanism has a lug member that is fixed to the drive shaft in the swash plate chamber and a transmission member that transmits rotation of the lug member to the swash plate,
  • the actuator has the lug member, a movable body that is rotatable integrally with the swash plate and is capable of changing the inclination angle by moving in the direction of the driving axis, and a control pressure chamber that is defined by the lug member and the movable body and moves the movable body by changing its internal pressure by the control mechanism,
  • an acting portion that is capable of pressing the swash plate by the pressure in the control pressure chamber is formed at the movable body
  • the acting portion abuts on the acted portion at an operative position
  • a top-dead-center corresponding portion for positioning the piston at its top dead center is defined in the swash plate
  • the operative position when the inclination angle is maximum is closer to the top-dead-center corresponding portion as compared to the operative position when the inclination angle is minimum.
  • the transmission member of the link mechanism transmits rotation of the lug member to the swash plate.
  • the operative position at which the acting portion of the movable body abuts on the acted portion of the swash plate moves in accordance with the change of the inclination angle of the swash plate. Specifically, the operative position when the inclination angle is maximum is closer to the top-dead-center corresponding portion of the swash plate as compared to the operative position when the inclination angle is minimum.
  • this compressor as compared with the case where the operative position has a constant distance from the driving axis even when the inclination angle of the swash plate changes, it is possible to move the movable body without increasing the variable differential pressure at the time of decreasing the inclination angle so as to provide a large thrust force. That is, in this compressor, it is possible to reduce the load exerted on the movable body at the time of decreasing the inclination angle. Consequently, in this compressor, the amount of change in the variable differential pressure when the inclination angle changes is small; therefore, it is easy to quickly change the inclination angle in response to the driving conditions of a vehicle or the like, and high controllability can be exhibited.
  • the compressor of the present invention is capable of exhibiting high controllability and excellent mountability.
  • the control mechanism may have a control passage and a control valve.
  • the control passage may have a variable pressure passage that communicates with the control pressure chamber, a low pressure passage that communicates with a suction chamber or a swash plate chamber, and a high pressure passage that communicates with a discharge chamber.
  • the drive shaft is inserted through the movable body, and the movable body is capable of being fitted to the lug member.
  • a space for allowing the movable body to move in the direction of the driving axis can be suitably provided between the lug member and the swash plate.
  • the movable body may have a movable cylindrical portion that is formed into a cylindrical shape and coaxial with the driving axis.
  • the lug member has a fixed cylindrical portion that is formed into a cylindrical shape and is coaxial with the driving axis at an outer circumferential side of the movable cylindrical portion to thereby provide the control pressure chamber in the movable cylindrical portion.
  • the control pressure chamber is provided in the movable cylindrical portion by the fixed cylindrical portion, the control pressure chamber can be suitably formed between the lug member and the movable body.
  • a first seal member that seals the control pressure chamber may be provided between the movable cylindrical portion and the drive shaft.
  • a second seal member that seals the control pressure chamber is provided between the movable cylindrical portion and the fixed cylindrical portion.
  • a thrust bearing that receives a thrust force which acts on the piston may be provided between the housing and the lug member.
  • the movable cylindrical portion is smaller in diameter than the thrust bearing and capable of advancing to an inner side of the thrust bearing.
  • the thrust bearing it is possible for the thrust bearing to suitably receive a suction reaction force which acts on the piston during a suction phase and a compression reaction force which acts on the piston during a compression phase. Furthermore, by allowing the movable cylindrical portion to advance to the inner side of the thrust bearing, even if the axial length of the compressor is short, the space for allowing the movable body to move in the direction of the driving axis can be sufficiently ensured.
  • the acting portion and the acted portion come into point-contact or line-contact with each other at the operative position.
  • the contact area between the acting portion and the acted portion can be made small.
  • the straight line on which the operative position and the acted portion are brought into line-contact is perpendicular to the first imaginary plane determined by the top-dead-center corresponding portion of the swash plate and the driving axis.
  • the acting portion when bringing the acting portion into point-contact or line-contact with the acted portion at the operative position, it is preferable that either one of a portion in the acting portion where it abuts on the acted portion and a portion in the acted portion where it abuts on the acting portion is formed into a curved shape.
  • the position in the movable body where the acting portion is formed and the position in the swash plate where the acted portion is formed can be designed as appropriate.
  • the acting portion and the acted portion may be located eccentrically toward the top-dead-center corresponding portion from the driving axis. It is preferable that the operative position moves toward the driving axis when the inclination angle decreases.
  • the acting portion may have an acting surface that extends in the direction perpendicular to the driving axis. It is preferable that the acted portion has a protrusion that protrudes from the swash plate and abuts on the acting surface. In this case, the acting portion and the acted portion can be suitably brought into point-contact or line-contact with each other.
  • the acting portion protrudes from the movable cylindrical portion toward the top-dead-center corresponding portion. In this case, the acting portion easily abuts on the acted portion.
  • the swash plate has a swash plate main body that is formed with an insertion hole, through which the drive shaft is inserted, and the acted portion that is integrally formed with the swash plate main body. In this case, it is possible to reduce the number of components in the compressor, facilitate manufacturing, and reduce manufacturing cost.
  • the swash plate has a swash plate main body that is formed with an insertion hole, through which the drive shaft is inserted, and the acted portion that is fixed to the swash plate main body. In this case, it is possible to improve the flexibility of design with respect to the swash plate main body and the acted portion.
  • a suction chamber and a discharge chamber may be formed in the housing. It is preferable that the suction chamber and the swash plate chamber communicate with each other. In this case, the pressure in the swash plate chamber can be made low as well as the suction chamber.
  • control mechanism may have a control passage that provides communication between the control pressure chamber and the suction chamber and/or the discharge chamber, and a control valve that is capable of regulating an opening degree of the control passage. It is preferable that at least a part of the control passage is formed in the drive shaft. In this case, it is possible to suitably change the pressure in the control pressure chamber and suitably move the movable body while downsizing the control mechanism.
  • a pressure regulation chamber that communicates with the control pressure chamber through the control passage and allows a pressure therein to be changed by the control valve may be formed between the housing and one end of the drive shaft. It is preferable that a third seal member that seals the pressure regulation chamber is provided between the housing and the drive shaft.
  • the control pressure chamber moves the movable body.
  • the third seal member hermeticity of the pressure regulation chamber can be suitably ensured.
  • various seals can be employed besides O-rings etc. as in the case of the first and second seal members described above.
  • the third seal member may be of the same kind as or a different kind from the first and second seal members.
  • the compressor of the present invention is capable of exhibiting high controllability and excellent mountability.
  • FIG. 1 is a sectional view of a compressor according to Embodiment 1 at the time of maximum displacement.
  • FIG. 2 is a schematic diagram showing a control mechanism of the compressor according to Embodiment 1.
  • FIG. 3 is an enlarged sectional view of an essential part of the compressor according to Embodiment 1, showing a rear end portion of a drive shaft.
  • FIG. 4 is an enlarged sectional view of an essential part of the compressor according to Embodiment 1, showing an actuator.
  • FIG. 5 is a front perspective view showing a swash plate of the compressor according to Embodiment 1.
  • FIG. 6 is a sectional view of the compressor according to Embodiment 1 at the time of minimum displacement.
  • FIG. 7A is an enlarged sectional view of an essential part of the compressor according to Embodiment 1, showing an operative position where an acting portion abuts on an acted portion when an inclination angle of the swash plate is maximum.
  • FIG. 7B is an enlarged sectional view of an essential part of the compressor according to Embodiment 1, showing the operative position when the inclination angle is minimum.
  • FIG. 8 is a graph showing a relation between the inclination angle and a variable differential pressure.
  • FIG. 9 is a schematic view of the compressor according to Embodiment 1 and a compressor of a comparative example, showing a difference in strokes of movable bodies.
  • FIG. 10 is a sectional view of a compressor according to Embodiment 2 at the time of maximum displacement.
  • Embodiments 1 and 2 which embody the present invention, will be described with reference to the drawings.
  • the compressors of Embodiments 1 and 2 are variable displacement single-head swash plate type compressors. These compressors are both mounted on vehicles and constitute refrigeration circuits of vehicle air-conditioning apparatus.
  • the compressor of Embodiment 1 includes a housing 1 , a drive shaft 3 , a swash plate 5 , a link mechanism 7 , a plurality of pistons 9 , a plurality of pairs of shoes 11 a and 11 b , an actuator 13 , and a control mechanism 15 which is shown in FIG. 2 .
  • the illustration of the swash plate 5 is partially simplified for ease of explanation. The same applies to FIGS. 6 and 10 , which will be described later.
  • the housing 1 has a front housing 17 that is located at a front side in the compressor, a rear housing 19 that is located at a rear side in the compressor, a cylinder block 21 that is located between the front housing 17 and the rear housing 19 , and a valve unit 23 .
  • the front housing 17 has a front wall 17 a that extends in the up-down direction of the compressor at the front side, and a circumferential wall 17 b that is integrated with the front wall 17 a and extends rearward from the front side of the compressor.
  • the front housing 17 is formed into a substantially cylindrical shape with a bottom.
  • a swash plate chamber 25 is formed in the front housing 17 .
  • a boss 17 c that protrudes frontward is formed on the front wall 17 a .
  • a shaft seal device 27 is provided in the boss 17 c .
  • a first shaft hole 17 d that extends in the front-rear direction of the compressor is formed in the boss 17 c .
  • a first sliding bearing 29 a is provided in the first shaft hole 17 d.
  • An inlet port 250 that communicates with the swash plate chamber 25 is formed through the circumferential wall 17 b . Through the inlet port 250 , the swash plate chamber 25 is connected to an evaporator, which is not illustrated.
  • a part of the control mechanism 15 is provided in the rear housing 19 .
  • a first pressure regulation chamber 31 a is disposed at the center of the rear housing 19 .
  • the discharge chamber 35 is disposed annularly at an outer circumferential side in the rear housing 19 .
  • the suction chamber 33 is formed annularly between the first pressure regulation chamber 31 a and the discharge chamber 35 in the rear housing 19 .
  • the discharge chamber 35 is connected to an outlet port which is not illustrated.
  • Cylinder bores 21 a are formed in the cylinder block 21 at equiangular intervals in a circumferential direction. Front end sides of the respective cylinder bores 21 a communicate with the swash plate chamber 25 . Furthermore, a retainer groove 21 b that restricts a lift amount of suction reed valves 41 a , which will be described later, is formed in the cylinder block 21 .
  • a second shaft hole 21 c that extends in the front-rear direction of the compressor and communicates with the swash plate chamber 25 is formed through the cylinder block 21 .
  • a second sliding bearing 29 b is provided in the second shaft hole 21 c .
  • a spring chamber 21 d is formed in the cylinder block 21 .
  • the spring chamber 21 d is located between the swash plate chamber 25 and the second shaft hole 21 c .
  • a return spring 37 is disposed in the spring chamber 21 d .
  • the return spring 37 urges the swash plate 5 frontward in the swash plate chamber 25 when the inclination angle becomes minimum.
  • a suction passage 39 that communicates with the swash plate chamber 25 is formed in the cylinder block 21 .
  • the valve unit 23 is provided between the rear housing 19 and the cylinder block 21 .
  • the valve unit 23 includes a valve plate 40 , a suction valve plate 41 , a discharge valve plate 43 and a retainer plate 45 .
  • Suction ports 40 a are formed in the valve plate 40 , the discharge valve plate 43 and the retainer plate 45 .
  • discharge ports 40 b are formed in the valve plate 40 and the suction valve plate 41 .
  • the respective cylinder bores 21 a communicate with the suction chamber 33 through the respective suction ports 40 a , and communicate with the discharge chamber 35 through the respective discharge ports 40 b .
  • a first communication hole 40 c and a second communication hole 40 d are formed in the valve plate 40 , the suction valve plate 41 , the discharge valve plate 43 and the retainer plate 45 . Through the first communication hole 40 c , the suction chamber 33 and the suction passage 39 communicate with each other.
  • the suction valve plate 41 is provided on the front surface of the valve plate 40 .
  • a plurality of suction reed valves 41 a that are capable of opening and closing the respective suction ports 40 a by elastic deformation are formed in the suction valve plate 41 .
  • the discharge valve plate 43 is provided on the rear surface of the valve plate 40 .
  • a plurality of discharge reed valves 43 a that are capable of opening and closing the respective discharge ports 40 b by elastic deformation are formed in the discharge valve plate 43 .
  • the retainer plate 45 is provided on the rear surface of the discharge valve plate 43 . The retainer plate 45 restricts a lift amount of the discharge reed valves 43 a.
  • the drive shaft 3 is inserted from a boss 17 c to the rear side of the housing 1 .
  • the front end side of the drive shaft 3 is supported by the shaft seal device 27 in the boss 17 c and supported by the first sliding bearing 29 a in the first shaft hole 17 d .
  • the rear end side of the drive shaft 3 is supported by the second sliding bearing 29 b in the second shaft hole 21 c .
  • the drive shaft 3 is rotatably supported around a driving axis O with respect to the housing 1 .
  • a second pressure regulation chamber 31 b is defined by the rear end of the drive shaft 3 in the second shaft hole 21 c .
  • the second pressure regulation chamber 31 b communicates with the first pressure regulation chamber 31 a through the second communication hole 40 d .
  • a pressure regulation chamber 31 is formed by the first and the second pressure regulation chambers 31 a and 31 b.
  • ring grooves 3 c and 3 d are formed at the rear end of the drive shaft 3 .
  • O-rings 49 a and 49 b are provided in the ring grooves 3 c and 3 d , respectively.
  • the pressure regulation chamber 31 is sealed with the O-rings 49 a and 49 b , whereby the swash plate chamber 25 does not communicate with the pressure regulation chamber 31 .
  • the O-rings 49 a and 49 b correspond to the third seal member in the present invention.
  • the link mechanism 7 includes a lug plate 51 , a pair of lug arms 53 that are formed at the lug plate 51 , and a pair of swash plate arms 5 e and 5 f .
  • the lug plate 51 corresponds to the lug member in the present invention.
  • the swash plate arms 5 e and 5 f correspond to the transmission member in the present invention.
  • the lug plate 51 is formed into a substantially annular shape.
  • the lug plate 51 is press-fitted to the drive shaft 3 and rotatable integrally with the drive shaft 3 .
  • the lug plate 51 is located at the front end side in the swash plate chamber 25 and disposed in front of the swash plate 5 . Furthermore, a thrust bearing 55 is provided between the lug plate 51 and the front wall 17 a.
  • a fixed cylindrical portion 51 a that is formed into a cylindrical shape and extends in the front-rear direction of the lug plate 51 is provided in a recessed manner in the lug plate 51 .
  • the fixed cylindrical portion 51 a extends from the rear end surface of the lug plate 51 to a position on an inner side of the thrust bearing 55 in the lug plate 51 .
  • the lug arms 53 extend rearward from the lug plate 51 . Furthermore, a cam surface 51 b is formed at the lug plate 51 at a position between the lug arms 53 . In FIG. 1 etc., only one of the lug arms 53 is illustrated for ease of explanation.
  • the swash plate 5 has a swash plate main body 50 , the swash plate arms 5 e and 5 f , and a protrusion 5 g .
  • the protrusion 5 g corresponds to the acted portion in the present invention.
  • the swash plate main body 50 is formed into an annular flat-plate shape and has a front surface 5 a and a rear surface 5 b ; in addition, a top-dead-center corresponding portion T for positioning the respective pistons 9 at their top dead center is defined therein.
  • a restriction portion 5 c that protrudes frontward from the swash plate 5 is formed on the front surface 5 a . As shown in FIG. 1 , the restriction portion 5 c abuts on the lug plate 51 when the inclination angle of the swash plate 5 becomes maximum.
  • the swash plate main body 50 is formed with an insertion hole 5 d . The drive shaft 3 is inserted through the insertion hole 5 d.
  • the swash plate arms 5 e and 5 f are formed on the front surface 5 a of the swash plate main body 50 at positions eccentric toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O.
  • the swash plate arms 5 e and 5 f extend frontward from the front surface 5 a.
  • the protrusion 5 g protrudes frontward from the front surface 5 a and is integrated with the swash plate main body 50 .
  • the protrusion 5 g is formed into a substantially hemispherical shape, and located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O so as to be disposed between the swash plate arm 5 e and the swash plate arm 5 f.
  • the lug plate 51 is connected to the swash plate 5 .
  • the swash plate 5 is rotatable along with the lug plate 51 in the swash plate chamber 25 .
  • the tip ends of the swash plate arms 5 e and 5 f abut on the cam surface 51 b.
  • the swash plate arms 5 e and 5 f and the protrusion 5 g are located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O.
  • the swash plate arms 5 e and 5 f slide on the cam surface 51 b , whereby the swash plate 5 is able to change its inclination angle with respect to the direction perpendicular to the driving axis O from the maximum inclination angle shown in FIG. 1 to the minimum inclination angle shown in FIG. 6 while substantially maintaining the position of the top-dead-center corresponding portion T.
  • the actuator 13 includes the lug plate 51 , a movable body 13 a and a control pressure chamber 13 b.
  • the movable body 13 a through which the drive shaft 3 is inserted, is slidable in contact with the drive shaft 3 to move in the direction of the driving axis O.
  • the movable body 13 a is formed into a cylindrical shape and coaxial with the drive shaft 3 , and the diameter thereof is smaller than that of the thrust bearing 55 shown in FIG. 1 .
  • the movable body 13 a has a first movable cylindrical portion 131 , a second movable cylindrical portion 132 and a third movable cylindrical portion 133 .
  • the first movable cylindrical portion 131 is located at a rear end side in the movable body 13 a and has the smallest diameter in the movable body 13 a .
  • the second movable cylindrical portion 132 continues from the front end of the first movable cylindrical portion 131 and is formed such that its diameter increases gradually toward the front side of the movable body 13 a .
  • the third movable cylindrical portion 133 continues from the front end of the second movable cylindrical portion 132 and extends toward the front side of the movable body 13 a .
  • the third movable cylindrical portion 133 has the largest diameter in the movable body 13 a.
  • an acting portion 134 is integrally formed at the rear end of the first movable cylindrical portion 131 .
  • the acting portion 134 extends vertically from a position near the driving axis O toward the top-dead-center corresponding portion T of the swash plate 5 , and is located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O.
  • the acting portion 134 has an acting surface 134 a which is formed into a flat shape. As shown in FIG. 7 , the acting surface 134 a comes into point-contact with the protrusion 5 g at an operative position F.
  • the movable body 13 a is rotatable integrally with the lug plate 51 and the swash plate 5 .
  • the protrusion 5 g and the acting portion 134 are located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O
  • the operative position F is also located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O as shown in FIG. 1 .
  • the movable body 13 a is capable of being fitted to the lug plate 51 by allowing the second movable cylindrical portion 132 and the third movable cylindrical portion 133 shown in FIG. 4 to advance into the fixed cylindrical portion 51 a (see FIG. 1 ).
  • the third movable cylindrical portion 133 reaches a position on an inner side of the thrust bearing 55 in the fixed cylindrical portion 51 a.
  • the control pressure chamber 13 b is formed by the second movable cylindrical portion 132 , the third movable cylindrical portion 133 , the fixed cylindrical portion 51 a and the drive shaft 3 . Furthermore, a ring groove 131 a is formed in the inner circumferential surface of the first movable cylindrical portion 131 , and a ring groove 133 a is formed in the outer circumferential surface of the third movable cylindrical portion 133 . O-rings 49 c and 49 d are provided in the ring grooves 131 a and 133 a , respectively. The O-ring 49 c corresponds to the first seal member in the present invention, and the O-ring 49 d corresponds to the second seal member in the present invention. The control pressure chamber 13 b is sealed with the O-rings 49 c and 49 d , whereby the hermeticity of the control pressure chamber 13 b is ensured.
  • an axial path 3 a that extends in the direction of the driving axis O from the rear end of the drive shaft 3 toward the front end thereof and a radial path 3 b that extends radially from the front end of the axial path 3 a and opens at the outer circumferential surface of the drive shaft 3 are formed in the drive shaft 3 .
  • the rear end of the axial path 3 a opens to the pressure regulation chamber 31 .
  • the radial path 3 b opens to the control pressure chamber 13 b .
  • the pressure regulation chamber 31 and the control pressure chamber 13 b communicate with each other.
  • the drive shaft 3 is connected to a pulley or an electromagnetic clutch, which are not illustrated, via a screw portion 3 e which is formed at the tip end thereof.
  • the pistons 9 are respectively accommodated in the respective cylinder bores 21 a and capable of reciprocating in the respective cylinder bores 21 a .
  • Compression chambers 57 are defined in the respective cylinder bores 21 a by the respective pistons 9 and the valve unit 23 .
  • an engaging portion 9 a is formed in a recessed manner in each of the pistons 9 .
  • the shoes 11 a and 11 b formed into a hemispherical shape are provided in the respective engaging portions 9 a .
  • the shoes 11 a and 11 b convert the rotation of the swash plate 5 into reciprocal movement of the pistons 9 .
  • the shoes 11 a and 11 b correspond to the conversion mechanism in the present invention. In this manner, the pistons 9 are able to reciprocate in the cylinder bores 21 a at a stroke corresponding to the inclination angle of the swash plate 5 .
  • a wobble type conversion mechanism in which a wobble plate is supported at the side of the rear surface 5 b of the swash plate main body 50 via a thrust bearing and the wobble plate is connected to the respective pistons 9 via connecting rods.
  • the control mechanism 15 has a low pressure passage 15 a , a high pressure passage 15 b , a control valve 15 c , an orifice 15 d , the axial path 3 a and the radial path 3 b .
  • a control passage in the present invention is formed by the low pressure passage 15 a , the high pressure passage 15 b , the axial path 3 a and the radial path 3 b .
  • the axial path 3 a and the radial path 3 b serve as variable pressure passages.
  • the low pressure passage 15 a is connected to the pressure regulation chamber 31 and the suction chamber 33 .
  • the control pressure chamber 13 b , the pressure regulation chamber 31 and the suction chamber 33 communicate with one another through the low pressure passage 15 a , the axial path 3 a and the radial path 3 b .
  • the high pressure passage 15 b is connected to the pressure regulation chamber 31 and the discharge chamber 35 .
  • the control pressure chamber 13 b , the pressure regulation chamber 31 and the discharge chamber 35 communicate with one another through the high pressure passage 15 b , the axial path 3 a and the radial path 3 b .
  • the high pressure passage 15 b is provided with the orifice 15 d , whereby the flow rate of the refrigerant flowing through the high pressure passage 15 b is reduced.
  • the control valve 15 c is provided at the low pressure passage 15 a .
  • the control valve 15 c is capable of regulating the flow rate of the refrigerant flowing through the low pressure passage 15 a based on the pressure in the suction chamber 33 .
  • a pipe that leads to the evaporator is connected to the inlet port 250 shown in FIG. 1
  • a pipe that leads to a condenser is connected to the outlet port.
  • the condenser is connected to the evaporator via pipes and an expansion valve.
  • the refrigeration circuit of vehicle air-conditioning apparatus is constituted by the compressor, the evaporator, the expansion valve, the condenser and the like. Illustration of the evaporator, the expansion valve, the condenser and the pipes is omitted.
  • the swash plate 5 rotates and the pistons 9 reciprocate in the respective cylinder bores 21 a .
  • the volume of the compression chambers 57 thus changes in response to the stroke of the pistons 9 .
  • the refrigerant introduced from the evaporator into the swash plate chamber 25 through the inlet port 250 thus passes the suction chamber 33 through the suction passage 39 and then is compressed in the compression chambers 57 . Subsequently, the refrigerant compressed in the compression chambers 57 is discharged to the discharge chamber 35 and then discharged to the condenser from the outlet port.
  • control mechanism 15 when the control valve 15 c shown in FIG. 2 increases the flow rate of the refrigerant flowing through the low pressure passage 15 a , the refrigerant in the discharge chamber 35 is less likely to pass the high pressure passage 15 b and the orifice 15 d and be stored in the pressure regulation chamber 31 . Therefore, the pressure in the control pressure chamber 13 b becomes substantially equal to that in the suction chamber 33 . As a result, as shown in FIG.
  • the volume of the control pressure chamber 13 b decreases and the movable body 13 a moves from the side of the swash plate 5 toward the lug plate 51 in the direction of the driving axis O. Then, in the movable body 13 a , the second movable cylindrical portion 132 and the third movable cylindrical portion 133 advance into the fixed cylindrical portion 51 a.
  • the inclination angle of the swash plate 5 shown in FIG. 1 is the maximum inclination angle in this compressor.
  • the swash plate arms 5 e and 5 f abut on the cam surface 51 b at a first position P 1 .
  • the acting surface 134 a of the acting portion 134 operates in such a manner as to press the protrusion 5 g rearward in the swash plate chamber 25 at the operative position F. Therefore, the swash plate arms 5 e and 5 f slide on the cam surface 51 b so as to approach the driving axis O, and the bottom dead center side of the swash plate 5 pivots in a counterclockwise direction while substantially maintaining the position of the top-dead-center corresponding portion T. In this manner, in this compressor, the inclination angle of the swash plate 5 with respect to the direction perpendicular to the driving axis O of the drive shaft 3 decreases.
  • the stroke of the pistons 9 decreases and the discharge capacity per rotation of the drive shaft 3 becomes small. Furthermore, when the inclination angle decreases, the swash plate 5 abuts on the return spring 37 .
  • the inclination angle of the swash plate 5 shown in FIG. 6 is the minimum inclination angle in this compressor.
  • the swash plate arms 5 e and 5 f abut on the cam surface 51 b at a second position P 2 .
  • this compressor employs the actuator 13 so as to change the inclination angle of the swash plate 5 by changing the pressure in the control pressure chamber 13 b , which has a smaller volume than the swash plate chamber 25 . Therefore, in this compressor, the amount of the refrigerant required to change the inclination angle can be reduced as compared to the compressor configured to change the inclination angle by changing the pressure in the swash plate chamber 25 . As a result, this compressor is capable of suppressing enlargement of the swash plate chamber 25 and the housing 1 .
  • the swash plate arms 5 e and 5 f of the link mechanism 7 transmit the rotation of the lug plate 51 to the swash plate 5 and permit change of the inclination angle while substantially maintaining the position of the top-dead-center corresponding portion T of the swash plate 5 .
  • the acting portion 134 of the movable body 13 a and the protrusion 5 g of the swash plate 5 are located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O.
  • the acting surface 134 a of the acting portion 134 comes into point-contact with the protrusion 5 g at the operative position F, and in order to decrease the inclination angle of the swash plate 5 , the acting surface 134 a presses the protrusion 5 g .
  • the operative position F moves in accordance with the change of the inclination angle.
  • the operative position F when the inclination angle is maximum, the operative position F is located at a position near the top-dead-center corresponding portion T of the swash plate 5 . Then, as the inclination angle decreases, the position where the swash plate arms 5 e and 5 f abuts on the cam surface 51 b moves toward the second position P 2 . Thereby, in this compressor, as shown by the white arrow in FIG. 7B , the operative position F moves toward the driving axis O as the inclination angle of the swash plate 5 decreases.
  • the operative position F when the inclination angle is maximum is closer to the top-dead-center corresponding portion T of the swash plate 5 as compared to the operative position F when the inclination angle is minimum.
  • the operative position F does not move to the opposite side of the top-dead-center corresponding portion T across the driving axis O.
  • this compressor as compared with the case where the operative position F has a constant distance from the driving axis O, it is possible to move the movable body 13 a without increasing the variable differential pressure at the time of decreasing the inclination angle so as to provide a large thrust force. That is, in this compressor, the load exerted on the movable body 13 a at the time of decreasing the inclination angle can be reduced. Consequently, in this compressor, the amount of change in the variable differential pressure when the inclination angle changes is small; therefore, it is easy to change the inclination angle quickly in response to the driving conditions of the vehicle on which the compressor is mounted, and high controllability can be exhibited.
  • the compressor of the comparative example is configured by partially changing the compressor of Embodiment 1 such that the protrusion 5 g and the acting portion 134 are not provided in the swash plate 5 and the movable body 13 a .
  • the rear end of the first movable cylindrical portion 131 of the movable body 13 a abuts on the front surface 5 a at a position around the insertion hole 5 d . Therefore, in the compressor of the comparative example, the movable body 13 a abuts on the swash plate 5 at a position almost on the driving axis O.
  • the graph in FIG. 8 shows, in the compressor of the comparative example, it is necessary to increase the variable differential pressure when the inclination angle decreases so as to move the movable body 13 a by a larger thrust force.
  • the compressor of Embodiment 1 it is possible to move the movable body 13 a without increasing the variable differential pressure to thereby provide a large thrust force as described above. Consequently, in the compressor of Embodiment 1, the variable differential pressure required at the time of changing the inclination angle can be made small and almost uniform as a whole.
  • the movable body 13 a in order to displace the swash plate 5 at the maximum inclination angle in this drawing (see the double-dashed chain line) until it reaches the minimum inclination angle, the movable body 13 a needs to move by a distance S 2 in the direction of the driving axis O.
  • the movable body 13 a moves by a distance S 1 in the direction of the driving axis O in order to displace the swash plate 5 at the maximum inclination angle until it reaches the minimum inclination angle. That is, in the compressor of Embodiment 1, the stroke of the movable body 13 a in the direction of the driving axis O is shorter than that of the compressor in the comparative example.
  • the compressor of Embodiment 1 is capable of exhibiting high controllability and excellent mountability.
  • the movable body 13 a in order to change the inclination angle of the swash plate 5 , the movable body 13 a merely abuts directly on and presses the swash plate 5 , and the acting portion 134 is not connected to the protrusion 5 g with a connection pin or the like. Consequently, in this compressor, there is no risk that the configuration of a connecting portion changes the posture of the movable body 13 a , and thus, the posture of the movable body 13 a is less likely to change at the time of changing the inclination angle. Furthermore, in this compressor, it is possible to suppress complication of the configuration and realize reduction in manufacturing cost.
  • the drive shaft 3 is inserted through the movable body 13 a , and the movable body 13 a is capable of being fitted to the lug plate 51 by accommodating the movable body 13 a in the fixed cylindrical portion 51 a .
  • the third movable cylindrical portion 133 of the movable body 13 a advances to the position on the inner side of the thrust bearing 55 in the fixed cylindrical portion 51 a . Therefore, in this compressor, the space for allowing the movable body 13 a to move in the direction of the driving axis O can be suitably provided between the lug plate 51 and the swash plate 5 while making the axial length short.
  • the thrust bearing 55 provided in the compressor can suitably receive the suction reaction force and the compression reaction force which act on the pistons 9 .
  • control pressure chamber 13 b can be suitably formed between the lug plate 51 and the movable body 13 a by the fixed cylindrical portion 51 a .
  • the hermeticity of the control pressure chamber 13 b is suitably ensured by the O-rings 49 c and 49 d which are provided at the first and the third movable cylindrical portions 131 and 133 respectively.
  • the acting portion 134 and the protrusion 5 g are located eccentrically toward the top-dead-center corresponding portion T from the driving axis O, and the operative position F moves toward the driving axis O as described above as the inclination angle of the swash plate 5 decreases. Therefore, in this compressor, the space for allowing the movable body 13 a to move in the direction of the driving axis O is easily provided between the lug plate 51 and the swash plate without disrupting the change of the inclination angle. Therefore, in this compressor, it is possible to increase the diameter of the actuator 13 to quickly move the movable body 13 a by a sufficient thrust force. Also in this aspect, this compressor is capable of quickly changing the inclination angle in response to the driving conditions of a vehicle.
  • the acting portion 134 protrudes from the first movable cylindrical portion 131 toward the top-dead-center corresponding portion T of the swash plate 5 and is integrated with the movable body 13 a . Furthermore, the acting surface 134 a is formed at the acting portion 134 . Thereby, in this compressor, the acting surface 134 a can easily abut on the protrusion 5 g at the position eccentric toward the top-dead-center corresponding portion T from the driving axis O.
  • the protrusion 5 g is formed to protrude in a substantially hemispherical manner, the acting surface 134 a can be suitably brought into point-contact with the protrusion 5 g . Consequently, in this compressor, the contact area between the acting surface 134 a and the protrusion 5 g can be made small, whereby the swash plate 5 can easily change its inclination angle.
  • the protrusion 5 g is integrally formed with the front surface 5 a of the swash plate main body 50 . Therefore, in this compressor, it is possible to reduce the number of components, facilitate manufacturing, and reduce manufacturing cost.
  • the swash plate chamber 25 and the suction chamber 33 communicate with each other through the suction passage 39 .
  • the pressure in the swash plate chamber 25 can be made low as well as the suction chamber 33 .
  • control mechanism 15 adjusts the pressure in the pressure regulation chamber 31 and thus the pressure in the control pressure chamber 13 b by regulating the opening degree of the control valve 15 c .
  • the axial path 3 a and the radial path 3 b are formed in the drive shaft 3 . Consequently, in this compressor, it is possible to suitably change the pressure in the control pressure chamber 13 b and suitably move the movable body 13 a while downsizing the control mechanism 15 .
  • the hermeticity of the pressure regulation chamber 31 is suitably ensured by the O-rings 49 a and 49 b which are provided at the rear end of the drive shaft 3 .
  • the swash plate 5 has the swash plate main body 50 , the swash plate arms 5 e and 5 f and a contact member 59 .
  • the contact member 59 also corresponds to the acted portion in the present invention.
  • the contact member 59 is formed to be a separate body from the swash plate main body 50 .
  • the contact member 59 is attached to the front surface 5 a of the swash plate main body 50 at a position between the swash plate arms 5 e and 5 f , and located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O.
  • a protrusion 59 a that protrudes frontward is formed at the contact member 59 .
  • the protrusion 59 a is formed into a substantially hemispherical shape.
  • the protrusion 59 a comes into point-contact with the acting surface 134 a of the acting portion 134 at the operative position F.
  • the acting portion 134 abuts on the contact member 59 at a position eccentric toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O.
  • the other components of this compressor are the same as those of the compressor of Embodiment 1, and, where the components are the same, same reference numerals are used and detailed explanation thereof is omitted.
  • this compressor since the swash plate 5 and the contact member 59 are separate bodies, it is possible to improve the flexibility of design with respect to the swash plate main body 50 and the contact member 59 .
  • the other operations of this compressor are the same as those of the compressor of Embodiment 1.
  • Embodiments 1 and 2 Although the present invention has been described above in line with Embodiments 1 and 2, it is needless to say that the present invention is not limited to Embodiments 1 and 2 described above and may be modified and applied as appropriate without departing from the gist of the invention.
  • the compressors of Embodiments 1 and 2 may be configured such that the operative position F moves toward the driving axis O while the inclination angle of the swash plate 5 decreases to a predetermined angle from the maximum state, and the operative position F does not move while the inclination angle of the swash plate 5 reaches its minimum inclination angle from the predetermined angle.
  • the protrusion 5 g and the protrusion 59 a may be formed into a flat-plate shape, and the acting surface 134 a of the acting portion 134 may be formed into a curved shape. This enables the protrusion 5 g and the protrusion 59 a to come into line-contact with the acting portion 134 at the operative position F.
  • control mechanism 15 may be configured such that the control valve 15 c is provided at the high pressure passage 15 b and the orifice 15 d is provided at the low pressure passage 15 a .
  • the flow rate of the high-pressure refrigerant flowing through the high pressure passage 15 b can be regulated by the control valve 15 c . Therefore, due to the high pressure in the discharge chamber 35 , the pressure in the control pressure chamber 13 b can be increased quickly and the compression capacity can be decreased quickly.
  • a three-way valve that is connected to the low pressure passage 15 a and the high pressure passage 15 b may be provided so that the flow rate of the refrigerant flowing through the low pressure passage 15 a and the high pressure passage 15 b is adjusted by regulating an opening degree of the three-way valve.
  • the present invention is applicable to air-conditioning apparatus and the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US14/917,820 2013-09-11 2014-09-10 Variable displacement swash plate type compressor Abandoned US20160222953A1 (en)

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JP2013-187967 2013-09-11
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CN105556121A (zh) 2016-05-04
JPWO2015037637A1 (ja) 2017-03-02
CN105531477A (zh) 2016-04-27
KR101796406B1 (ko) 2017-12-01
KR20160051875A (ko) 2016-05-11
KR101889628B1 (ko) 2018-08-17
KR20160052682A (ko) 2016-05-12
JP6037028B2 (ja) 2016-11-30
WO2015037637A1 (ja) 2015-03-19
JPWO2015037636A1 (ja) 2017-03-02
US20160222952A1 (en) 2016-08-04
WO2015037636A1 (ja) 2015-03-19
DE112014004156B4 (de) 2019-11-21
JP6037027B2 (ja) 2016-11-30
CN105531477B (zh) 2017-06-23
CN105556121B (zh) 2017-05-24
DE112014004173T5 (de) 2016-05-25

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