US20150044068A1 - Swash plate type variable displacement compressor - Google Patents

Swash plate type variable displacement compressor Download PDF

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Publication number
US20150044068A1
US20150044068A1 US14/451,871 US201414451871A US2015044068A1 US 20150044068 A1 US20150044068 A1 US 20150044068A1 US 201414451871 A US201414451871 A US 201414451871A US 2015044068 A1 US2015044068 A1 US 2015044068A1
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US
United States
Prior art keywords
suction
chamber
swash plate
compression chamber
communication
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
US14/451,871
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English (en)
Inventor
Shinya Yamamoto
Tomoji Tarutani
Takahiro Suzuki
Kei Nishii
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
Original Assignee
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: NISHII, KEI, SUZUKI, TAKAHIRO, TARUTANI, TOMOJI, YAMAMOTO, SHINYA
Publication of US20150044068A1 publication Critical patent/US20150044068A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1881—Suction pressure

Definitions

  • the present invention relates to a swash plate type variable displacement compressor.
  • Japanese Patent Application Publication No. 1-219364 discloses a swash plate type variable displacement compressor (hereinafter referred to merely as “compressor”).
  • the compressor has a housing that includes a front housing, a cylinder block and a rear housing.
  • the front housing has therein a first suction chamber and a first discharge chamber.
  • the rear housing has therein a second suction chamber, a second discharge chamber and a pressure control chamber.
  • the cylinder block has therein an inlet port, a swash plate chamber, a plurality of first cylinder bores, a plurality of second cylinder bores, and first, second, and third suction passages.
  • the inlet port and the swash plate chamber are substantially formed at the center of the cylinder block.
  • the inlet port is in communication with the external circuit.
  • the first cylinder bores are formed on the front side of the cylinder block.
  • the second cylinder bores are formed on the rear side of the cylinder block.
  • the inner diameter of the first cylinder bores is the same as that of the second cylinder bores.
  • the first and second suction passages are formed in the cylinder block at positions adjacent to the first cylinder bore.
  • the first suction passage is in communication with the inlet port and the first suction chamber.
  • the second suction passage is in communication with the first suction chamber and the swash plate chamber.
  • the third suction passage is formed in the cylinder block at a position adjacent to the second cylinder bore and in communication with the swash plate chamber and the second suction chamber.
  • each piston has a first head reciprocally slidable in the first cylinder bore and a second head reciprocally slidable in the second cylinder bore. Since the inner diameter of the first cylinder bore is the same as that of the second cylinder bore, the outer diameter of the first head of the piston is the same as that of the second head.
  • a first compression chamber is formed by the first cylinder bore and the first head and a second compression chamber is formed by the second cylinder bore and the second head.
  • the first compression chamber is communicable with the first suction chamber and the first discharge chamber.
  • the second compression chamber is communicable with the second suction chamber and the second discharge chamber.
  • Each piton has an opening and closing member that reciprocates with its corresponding piston. The reciprocating movement of the opening and closing member permits the inlet port to communicate with or be shut off from the swash plate chamber.
  • a drive shaft is inserted in the housing and rotatably supported by the cylinder block.
  • a swash plate is mounted on the drive shaft for rotation therewith in the swash plate chamber.
  • the swash plate is connected to each piston via a conversion mechanism.
  • the conversion mechanism converts rotation of the swash plate into reciprocating movement of each piston in its corresponding cylinder bore for a stroke length that is determined by the inclination angle of the swash plate.
  • a link mechanism is provided between the drive shaft and the swash plate for changing the inclination angle of the swash plate.
  • the inclination angle is an angle that the swash plate makes with respect to the direction perpendicular to the axis of the drive shaft.
  • the inclination angle is changed by an actuator that is controlled by a control mechanism.
  • the actuator is arranged in the swash plate chamber at a position on the second cylinder bore side of the swash plate.
  • the actuator includes an actuator body and has a control pressure chamber.
  • the actuator body has a support member and a spool.
  • the support member is slidably mounted on the rear end of the drive shaft.
  • the spool is provided between the cylinder block and the rear housing with the rear end of the spool disposed in the pressure control chamber.
  • the spool is slidably supported by the cylinder block and the rear housing so as to slide back and forth in the cylinder block.
  • a thrust bearing and a radial bearing are provided between the support member and the spool.
  • the link mechanism is so constructed that the top dead center position of the first head of the piston moves for a larger distance than that of the second head position with a change of the inclination angle of the swash plate.
  • the link mechanism has a spherical support member, a concave spherical surface and a lug arm.
  • the spherical support member is formed in the front end of the support member.
  • the concave spherical surface is formed in the swash plate and encloses the spherical support member.
  • the lug arm has a slit formed in the front surface of the swash plate and a plate part formed on the drive shaft.
  • the plate part has therein an elongated hole extending in the plane perpendicular to the axis of the drive shaft and toward the axis of the drive shaft from the outer periphery of the compressor.
  • the slit is swingably supported in the plate part via a pin inserted through the elongated hole.
  • the swash plate is supported swingably with respect to the drive shaft.
  • the control mechanism when the control mechanism makes communication between the second discharge chamber and the pressure control chamber, the pressure in the control chamber is higher than that in the swash plate chamber, so that the spool and the support member are moved forward. Therefore, the inclination angle of the swash plate is increased and the stroke length of the piston is increased, with the result that the compression capacity per rotation of the compressor is increased.
  • the stroke length of the piston is increased, the inlet port is made to be in communication with the swash plate chamber by the opening and closing member.
  • the manner of sucking refrigerant gas into the first compression chamber is different from that into the second compression chamber.
  • the stroke length of the piston is changed depending on the manner of sucking refrigerant gas. That is, flow rate of refrigerant gas sucked in the second compression chamber is varied according to the stroke length of the piston or according to the inclination angle of the swash plate.
  • the present invention is directed to providing a swash plate type variable displacement compressor that is advantageous in terms of silence in operation.
  • a swash plate type variable displacement compressor forms a housing having therein a suction chamber into which refrigerant is drawn through an inlet port, a discharge chamber, a swash plate chamber and a cylinder bore, a drive shaft rotatably supported by the housing, a swash plate which is rotatable by the rotation of the drive shaft, a link mechanism provided between the drive shaft and the swash plate and allowing the swash plate to change the inclination angle of the swash plate to the direction perpendicular to the rotating axis of the drive shaft, a piston received to reciprocate in the cylinder bore, a conversion mechanism reciprocating the piston in the cylinder bore according to the inclination angle of the swash plate, an actuator allowing the swash plate to change the inclination angle of the swash plate and a control mechanism controlling the actuator.
  • the cylinder bore includes a first cylinder bore provided in one surface side on the swash plate and a second cylinder bore provided in the other surface side on the swash plate.
  • the piston includes a first head part that reciprocates in the first cylinder bore and forms a first compression chamber in the first cylinder bore and a second head part that reciprocates in the second cylinder bore and forms a second compression chamber in the second cylinder bore.
  • the link mechanism is disposed so that the top dead center position of the first head part moves largely according to the change of the inclination angle of the swash plate as compared to the top dead center position of the second head part.
  • the actuator includes an actuator body that is connected to the swash plate and movable in the direction of the rotating axis of the drive shaft and a pressure control chamber that moves the actuator body by changing the pressure of the pressure control chamber by the control mechanism.
  • the swash plate type variable displacement compressor further includes a first suction flow passage through which the refrigerant is drawn through the inlet port into the first compression chamber, a second suction flow passage through which the refrigerant is drawn through the inlet port into the second compression chamber, a first suction valve mechanism provided in the first suction flow passage and a second suction valve mechanism provided in the second suction flow passage.
  • the inner diameter of the first cylinder bore is smaller than that of the second cylinder bore.
  • the compressor has at least either a structure in which the first suction flow passage is different from the second suction flow passage or a structure in which the first suction valve mechanism is different from the second suction valve mechanism so that the refrigerant is easily drawn through the inlet port into the first compression chamber as compared to the case in that the refrigerant is drawn through the inlet port into the second compression chamber.
  • FIG. 1 is a longitudinal sectional view of a compressor in maximum capacity according to a first embodiment of the present invention
  • FIG. 2 is a schematic diagram showing a control mechanism of the compressor of FIG. 1 ;
  • FIG. 3 is a longitudinal sectional view of the compressor of FIG. 1 in minimum capacity
  • FIG. 4 is a graph showing the relation between the rotation of a drive shaft and the intake pulsation in the case that the first suction passage and the second suction passage of the compressor of FIG. 1 are the same;
  • FIG. 5 is a graph showing the relation between the rotation of the drive shaft and the intake pulsation in the case that the first suction passage and the second suction passage of the compressor of FIG. 1 are different;
  • FIG. 6 is a longitudinal sectional view of a compressor in maximum capacity according to a second embodiment of the present invention.
  • FIG. 7 is an enlarged fragmentary view of the compressor of FIG. 6 ;
  • FIG. 8 is an enlarged fragmentary view of a compressor according to a third embodiment of the present invention.
  • FIG. 9 is an enlarged fragmentary view of a compressor according to a fourth embodiment of the present invention.
  • FIG. 10 is a longitudinal sectional view of a compressor in maximum capacity according to a fifth embodiment of the present invention.
  • FIG. 11 is a longitudinal sectional view of a compressor in maximum capacity according to a sixth embodiment of the present invention.
  • FIG. 12 is a longitudinal sectional view of a compressor in maximum capacity according to a seventh embodiment of the present invention.
  • Compressors according to the embodiments 1 through 7 of the present invention are swash plate type variable displacement compressors.
  • the compressor is mounted on a vehicle and composes a part of cooling circuit for an air conditioner.
  • the compressor according to the first embodiment of the present invention includes a housing 1 , a drive shaft 3 , a swash plate 5 , a link mechanism 7 , a plurality of pistons 9 , plural pairs of shoes 11 A, 11 B, an actuator 13 and a control mechanism 15 .
  • the aforementioned control mechanism 15 is provided in the rear housing 17 . Furthermore, the rear housing 17 has therein a pressure control chamber 25 , a first suction chamber 27 A, a first discharge chamber 29 A, an inlet port 170 and a first suction passage 171 .
  • the pressure control chamber 25 is positioned in the center part of the rear housing 17 .
  • the first discharge chamber 29 A is formed in the rear housing 17 at a position adjacent to the outer periphery of the rear housing 17 .
  • the first suction chamber 27 A is formed between the pressure control chamber 25 and the first discharge chamber 29 A in the rear housing 17 . Specifically, the first suction chamber 27 A is formed at a position that is radially outward of the pressure control chamber 25 and radially inward of the first discharge chamber 29 A.
  • a part of the first suction chamber 27 A is formed extending rearward of the rear housing 17 .
  • the inlet port 170 is formed in the top of the rear housing 17 .
  • the first suction passage 171 and the first suction chamber 27 A are integrally formed.
  • the first suction passage 171 extends upwards and is in communication with the inlet port 170 .
  • the inlet port 170 is directly connected to the first suction chamber 27 A and provides communication between an evaporator (not shown in the drawing) composing a part of the refrigerant gas circuit and the first suction chamber 27 A.
  • the front housing 19 has at the front end thereof a boss 19 A projecting forward.
  • the boss 19 A has therein a shaft seal device 31 disposed between the boss 19 A and the drive shaft 3 .
  • the front housing 19 has therein a second suction chamber 27 B and a second discharge chamber 29 B.
  • the second suction chamber 27 B is formed in the front housing 19 adjacent to the center of the front housing 19 .
  • the second discharge chamber 29 B is formed in the front housing 19 adjacent to the outer periphery of the front housing 19 .
  • the second discharge chamber 29 B and the above-described first discharge chamber 29 A are connected via a discharge passage (not shown in the drawing).
  • the discharge passage has an outlet port (not shown in the drawing) that is in communication with the external circuit of the compressor.
  • the first cylinder block 21 and the second cylinder block 23 are adjoined each other between the rear housing 17 and the front housing 19 .
  • the first cylinder block 21 and the second cylinder block 23 are of substantially the same outer diameter.
  • the first cylinder block 21 is positioned in a rear part of the compressor adjacently to the rear housing 17 .
  • the second cylinder block 23 is positioned in a front part of the compressor adjacently to the front housing 19 .
  • a swash plate chamber 33 is formed by and between the first cylinder block 21 and the second cylinder block 23 substantially in the longitudinal center of the compressor.
  • the first cylinder block 21 has therethrough a plurality of first cylinder bores 21 A that are arranged at a regular angular interval and extending axially parallel to each other.
  • the first cylinder block 21 also has therethrough a first shaft hole 21 B through which the drive shaft 3 extends and that is in communication with the pressure control chamber 25 .
  • a first slide bearing 22 A is provided in the first shaft hole 21 B.
  • the first cylinder block 21 has therein a first accommodation chamber forming part forming a first accommodating chamber 21 C that is in communication with and coaxial with the first shaft hole 21 B.
  • the first accommodating chamber 21 C is enclosed by a wall forming a part of the first cylinder block 21 and separated from each first cylinder bore 21 A.
  • the first accommodating chamber 21 C is in communication with the swash plate chamber 33 .
  • the first accommodating chamber 21 C is of a stepped configuration having a larger inner diameter on the front side of the first accommodating chamber 21 C and a smaller inner diameter on the rear side.
  • the first accommodating chamber 21 C has in the rear end thereof a first thrust bearing 35 A.
  • the first cylinder block 21 has therethrough a first communication passage 37 A through which the first suction chamber 27 A is in communication with the swash plate chamber 33 .
  • the first cylinder block 21 has therein a first retainer groove 21 E that adjustably determines the deflection of each first suction reed valve 391 A which will be described later. That is, the first retainer groove 21 E is provided in the first accommodation chamber forming part.
  • the second cylinder block 23 has therethrough a plurality of second cylinder bores 23 A the number of which is the same as that of the above-described first cylinder bores 21 A.
  • the first cylinder bores 21 A and the second cylinder bores 23 A are coaxially formed.
  • the inner diameter of the first cylinder bores 21 A is smaller than that of the second cylinder bores 23 A.
  • the second cylinder block 23 has therethrough a second shaft hole 23 B through which the drive shaft 3 is inserted.
  • a second slide bearing 22 B is provided in the second shaft hole 23 B.
  • the second cylinder block 23 has therein a second accommodation chamber forming part forming a second accommodation chamber 23 C that is in communication with and coaxial with the second shaft hole 238 .
  • the second accommodating chamber 23 C is surrounded by a wall surface that is a part of the second cylinder block 23 and separated from each second cylinder bore 23 A.
  • the second accommodating chamber 23 C is also in communication with the swash plate chamber 33 .
  • the second accommodating chamber 23 C is of a stepped configuration having a smaller inner diameter on the front side of the second accommodating chamber 23 C and a larger inner diameter on the rear side.
  • a second thrust bearing 35 B is provided in the front end of the second accommodating chamber 23 C.
  • the second cylinder block 23 has therein a second retainer groove 23 E that is recessed in the second cylinder block 23 and adjustably determines the deflection of the second suction reed valve 411 A which will be described later. That is, the second retainer groove 23 E is provided in the second accommodation chamber forming part.
  • the shape and depth of the first retainer groove 21 E formed in the first cylinder block 21 are the same as those of the second retainer groove 23 E formed in the second cylinder block 23 .
  • a first valve forming plate 39 is provided between the rear housing 17 and the first cylinder block 21 .
  • a second valve forming plate 41 is provided between the front housing 19 and the second cylinder block 23 .
  • the first valve forming plate 39 includes a first valve plate 390 , a first suction valve plate 391 , a first discharge valve plate 392 and a first retainer plate 393 .
  • a first suction hole 390 A is formed through the first valve plate 390 , the first discharge valve plate 392 and the first retainer plate 393 for each first cylinder bore 21 A.
  • a first discharge hole 390 B is formed through the first valve plate 390 and the first suction valve plate 391 for each first cylinder bore 21 A.
  • a first communication hole 390 C is formed through the first valve plate 390 , the first suction valve plate 391 , the first discharge valve plate 392 and the first retainer plate 393 .
  • Each first cylinder bore 21 A is communicable with the first suction chamber 27 A through the first suction hole 390 A.
  • Each first cylinder bore 21 A is communicable with the first discharge chamber 29 A through the first discharge hole 390 B.
  • the first suction chamber 27 A is in communication with the first communication passage 37 A through the first communication hole 390 C.
  • the first suction valve plate 391 is provided on the front surface of the first valve plate 390 .
  • the first suction valve plate 391 has a plurality of first suction reed valves 391 A that open and close the respective first suction holes 390 A by elastic deformation.
  • the first discharge valve plate 392 is provided on the rear surface of the first valve plate 390 .
  • the first discharge valve plate 392 has a plurality of first discharge reed valves 392 A that open and close the respective first discharge holes 390 B by elastic deformation.
  • the first retainer plate 393 is provided on the rear surface of the first discharge valve plate 392 and regulates the lift of the first discharge reed valves 392 A.
  • the second valve forming plate 41 includes a second valve plate 410 , a second suction valve plate 411 , a second discharge valve plate 412 and a second retainer plate 413 .
  • a second suction hole 410 A is formed through the second valve plate 410 , the second discharge valve plate 412 and the second retainer plate 413 for each second cylinder bore 23 A.
  • a second discharge hole 410 B is formed through the second valve plate 410 and the second suction valve plate 411 for each second cylinder bore 23 A.
  • a second communication hole 410 C is formed through the second valve plate 410 , the second suction valve plate 411 , the second discharge valve plate 412 and the second retainer plate 413 .
  • the second suction valve plate 411 is provided on the rear surface of the second valve plate 410 .
  • the second suction valve plate 411 has a plurality of second suction reed valves 411 A that open and close the respective second suction holes 410 A by elastic deformation.
  • the second discharge valve plate 412 is provided on the front surface of the second valve plate 410 .
  • the second discharge valve plate 412 has a plurality of second discharge reed valves 412 A that open and close the respective second discharge holes 410 B by elastic deformation.
  • the second retainer plate 413 is provided on the front surface of the second discharge valve plate 412 and regulates the lift of the second discharge reed valves 412 A.
  • the first suction hole 390 A and the second suction hole 410 A are formed to have the same opening area.
  • the first discharge hole 390 B and the second discharge hole 410 B are formed to have the same opening area.
  • the first communication hole 390 C and the second communication hole 410 C are formed to have the same opening area.
  • the first suction valve plate 391 and the second suction valve plate 411 are formed to have the same thickness. Therefore, the thickness of the first suction reed valve 391 A is the same as that of the second suction reed valve 411 A.
  • the first discharge valve plate 392 and the second discharge valve plate 412 are formed to have the same thickness. Therefore, the thickness of the first discharge reed valve 392 A is also the same as that of the second discharge reed valve 412 A.
  • the first retainer plate 393 and the second retainer plate 413 are formed symmetrically so that the lift of the first discharge reed valve 392 A determined by the first retainer plate 393 is the same as that of the second discharge reed valve 412 A determined by the second retainer plate 413 .
  • each first cylinder bore 21 A is communicable with the first suction chamber 27 A through the corresponding first suction hole 390 A.
  • the first suction chamber 27 A is in communication with the inlet port 170 through the first suction passage 171 .
  • the first suction passage 171 , the first suction chamber 27 A and the corresponding first suction hole 390 A cooperate to form a first suction flow passage 2 .
  • the second suction chamber 27 B is in communication with the inlet port 170 through the first and second communication passages 37 A, 37 B, the swash plate chamber 33 , the first suction chamber 27 A and the first suction passage 171 .
  • the first suction passage 171 , the first suction chamber 27 A, the swash plate chamber 33 , the first and second communication holes 390 C, 410 C, the first and second communication passages 37 A, 37 B, the second suction chamber 27 B and the second suction hole 410 A cooperate to form a second suction flow passage 4 .
  • the first and second suction chambers 27 A and 27 B are in communication with the swash plate chamber 33 through the first and second communication passages 37 A, 37 B and the first and second communication holes 390 C, 410 C, so that the pressure in the first and second suction chambers 27 A and 27 B is substantially the same as that in the swash plate chamber 33 .
  • the pressures in the swash plate chamber 33 and in the first and second suction chambers 27 A and 27 B are lower than those in the first and second discharge chambers 29 A, 29 B because refrigerant gas flowed through an evaporator is flowed into the swash plate chamber 33 through the inlet port 170 , the first suction passage 171 , the first suction chamber 27 A and the first communication passage 37 A.
  • the drive shaft 3 includes a shaft body 30 and first and second support members 43 A, 43 B.
  • the shaft body 30 extends rearward from the boss 19 A and is inserted through the first and second slide bearings 22 A, 22 B.
  • the shaft body 30 and hence the drive shaft 3 is supported rotatably around the axis of rotation O.
  • the front and rear ends of the shaft body 30 are located in the boss 19 A and in the pressure control chamber 25 , respectively.
  • the swash plate 5 and the actuator 13 are mounted on the shaft body 30 and arranged in the swash plate chamber 33 .
  • the first support member 43 A is press-fitted on the shaft body 30 adjacent to the front end of the shaft body 30 to be in sliding contact with the second slide bearing 22 B.
  • the first support member 43 A is formed with a flange 431 that is in contact with the second thrust bearing 35 B and a mounting portion (not shown) in which a second pin 47 B described later is inserted.
  • a first return spring 44 A is fixed at the front end thereof to the first support member 43 A.
  • the first return spring 44 A extends in the direction of the axis of rotation O from the first support member 43 A toward the swash plate chamber 33 .
  • the second support member 43 B is press-fitted on the shaft body 30 at a position adjacent to the rear end of the shaft body 30 so as to be in sliding contact with the first slide bearing 22 A.
  • the second support member 43 B is formed with a flange 432 that is located in the first accommodating chamber 21 C between the first thrust bearing 35 A and the actuator 13 .
  • the shaft body 30 has therein an axial passage 3 B extending in the direction of the axis of rotation O from the rear end toward the front end of the shaft body 30 and a radial passage 3 C that extends radially outward from the front end of the axial passage 3 B and opens at the outer periphery of the shaft body 30 .
  • the rear end of the axial passage 3 B is opened to the pressure control chamber 25 and the radially outer end of the radial passage 3 C is opened to a pressure control chamber 13 C described later.
  • the drive shaft 3 has a threaded front end 3 D and is connected to a pulley or an electromagnetic clutch (not shown in the drawing) through this threaded front end 3 D.
  • a belt (not shown in the drawing) driven by an engine is wound around the pulley or the pulley of the electromagnetic clutch.
  • the swash plate 5 is of an annular plate shape and has a rear surface 5 A and a front surface 5 B.
  • the rear surface 5 A faces the first cylinder bore 21 A or faces rearward.
  • the rear surface 5 A side of the swash plate 5 corresponds to one side of the swash plate of the present invention.
  • the front surface 5 B faces the second cylinder bore 23 A or faces frontward.
  • the front surface 5 B side of the swash plate 5 corresponds to the other side of the swash plate of the present invention.
  • the swash plate 5 is fixed on a ring plate 45 which is of an annular plate shape and has at the center thereof a hole 45 A.
  • the swash plate 5 is mounted on the drive shaft 3 in the swash plate chamber 33 with the shaft body 30 of the drive shaft 3 inserted through the hole 45 A.
  • the aforementioned link mechanism 7 has a lug arm 49 .
  • the lug arm 49 is disposed in the swash plate chamber 33 frontward of the swash plate 5 and located between the swash plate 5 and the first support member 43 .
  • the lug arm 49 is formed to have a substantially L shape shown in FIG. 1 .
  • the lug arm 49 is in contact with the flange 431 of the first support member 43 A.
  • the lug arm 49 keeps the swash plate 5 at its minimum inclination angle.
  • the lug arm 49 has in the rear end thereof a weight member 49 A that extends over an approximate semicircle in the peripheral direction of the actuator 13 . The shape of the weight member 49 A may be changed.
  • the rear end of the lug arm 49 is connected to one end of the ring plate 45 by a first pin 47 A so that the lug arm 49 is pivotally supported at the rear end thereof by one end of the ring plate 45 of the swash plate 5 and swingable around a first axis M 1 that corresponds to the axis of the first pin 47 A.
  • the first axis M 1 extends in the direction perpendicular to the axis of rotation O of the drive shaft 3 .
  • the front end of the lug arm 49 is connected to the first support member 43 A by the second pin 47 B so that the lug arm 49 is pivotally supported at the front end thereof by the first support member 43 A of the drive shaft 3 and swingable around a second axis M 2 that corresponds to the axis of the second pin 47 B.
  • the second axis M 2 extends parallel to the first axis M 1 .
  • the lug arm 49 and the first and second pins 47 A, 47 B correspond to the link mechanism of the present invention.
  • the weight member 49 A is provided extending on the rear side of the first axis M 1 opposite from the second axis M 2 .
  • the lug arm 49 is supported by the ring plate 45 through the first pin 47 A.
  • the weight member 49 A is inserted in a groove 45 B of the ring plate 45 and disposed in the rear surface of the ring plate 45 , namely in the rear surface 5 A side of the swash plate 5 .
  • Centrifugal force developed during rotation of the swash plate 5 around the axis of rotation O acts on the weight member 49 A in the rear surface 5 A side of the swash plate 5 .
  • the swash plate 5 is connected to the drive shaft 3 by the link mechanism 7 , so that the swash plate 5 and the drive shaft 3 rotate together.
  • the link mechanism 7 is so arranged that the swash plate 5 is placed at a position adjacent to the second cylinder bore 23 A when the inclination angle of the swash plate 5 becomes minimum.
  • the front part and the rear end of the lug arm 49 are swung around the first axis M 1 and the second axis M 2 , respectively and the swash plate 5 changes the inclination angle thereof, accordingly.
  • Each piston 9 has a first head 9 A at the rear end thereof, a second head 9 B at the front end thereof and a recessed part 9 C at the center thereof.
  • the first head 9 A is received in the first cylinder bore 21 A so as to slide therein reciprocally.
  • a first compression chamber 21 D is formed in each first cylinder bore 21 A by the first head 9 A and the first valve forming plate 39 .
  • the second head 9 B is received in the second cylinder bore 23 A so as to slide therein reciprocally.
  • a second compression chamber 23 D is formed in each second cylinder bore 23 A by the second head 9 B and the second valve forming plate 41 .
  • the inner diameter of the first cylinder bore 21 A is smaller than that of the second cylinder bore 23 A, so that the outer diameter of the first head 9 A is smaller than that of the second head 9 B.
  • the first cylinder bore 21 A and the second cylinder bore 23 A are formed coaxially, so that the first head 9 A and the second head 9 B are also disposed coaxially.
  • the length of the first head 9 A in the stroke direction of the piston 9 is the same as that of the second head 9 B, so that the length from the center of the recessed part 9 C of each piston 9 to the top of the first head 9 A is the same as that of the second head 98 .
  • a pair of hemispherical shoes 11 A, 11 B is provided in the recessed part 9 C of each piston 9 in such a manner that the rotation of the swash plate 5 is converted to reciprocating movement of the piston 9 in its associated first and second cylinder bores 21 A, 23 A.
  • the shoes 11 A, 11 B correspond to the conversion mechanism of the present invention.
  • the first and second heads 9 A, 9 B can reciprocate in the first and second cylinder bores 21 A, 23 A, respectively, with the stroke length that is determined according to the inclination angle of the swash plate 5 .
  • the swash plate 5 when the inclination angle of the swash plate 5 becomes minimum, the swash plate 5 is located in the swash plate chamber 33 closer to the second cylinder bore 23 A than to the first cylinder bore 21 A.
  • the stroke length of the piston 9 becomes maximum, accordingly, the top dead center position of the first head 9 A is closest to the first valve forming plate 39 and the top dead center position of the second head 9 B is closest to the second valve forming plate 41 .
  • the inclination angle of the swash plate 5 becomes minimum, as shown in FIG.
  • the top dead center position of the first head 9 A is located farthest from the first valve forming plate 39 .
  • the top dead center position of the second head 9 B is similar to the position when the stroke length of the piston 9 is maximum and keeps located at a position close to the second valve forming plate 41 .
  • the actuator 13 is disposed in the swash plate chamber 33 at a position adjacent to the first cylinder bore 21 A.
  • the actuator 13 is movable in such a way that a part of the actuator 13 enters the first accommodating chamber 21 C and is accommodated in the first accommodating chamber 21 C.
  • the actuator 13 has a movable member 13 A, a fixed member 13 B and a pressure control chamber 13 C.
  • the actuator body of the present invention is formed by the movable member 13 A and the fixed member 13 B.
  • the pressure control chamber 13 C is formed between the movable member 13 A and the fixed member 13 B.
  • the movable member 13 A has a body portion 130 and a peripheral wall 131 .
  • the body portion 130 is formed in the rear part of the movable member 13 A and extends radially from the axis of rotation O.
  • the peripheral wall 131 extends frontward from the outer periphery of the body portion 130 .
  • the peripheral wall 131 has at the front end thereof a connecting part 132 .
  • the movable member 13 A is formed by the body portion 130 , the peripheral wall 131 and the connecting part 132 and has a bottomed cylindrical shape.
  • the fixed member 13 B is formed in a disk shape having an inner diameter that is substantially the same as that of the movable member 13 A.
  • a second return spring 44 B is provided between the fixed member 138 and the ring plate 45 . Specifically, the second return spring 44 B is fixed at the rear end thereof to the fixed member 13 B and at the front end thereof to the other end side of the ring plate 45 .
  • the shaft body 30 is inserted through the movable member 13 A and the fixed member 13 B, so that the movable member 13 A positioned in the first accommodating chamber 21 C is disposed on the opposite side of the swash plate 5 from the link mechanism 7 .
  • the fixed member 138 is disposed rearward of the swash plate 5 and in the movable member 13 A and surrounded by the peripheral wall 131 .
  • the pressure control chamber 13 C is formed between the movable member 13 A and the fixed member 13 B.
  • the pressure control chamber 13 C is separated from the swash plate chamber 33 by the body portion 130 and the peripheral wall 131 of the movable member 13 A and the fixed member 13 B.
  • the radial passage 3 C is opened to the pressure control chamber 13 C.
  • the pressure control chamber 13 C is in communication with the pressure control chamber 25 through the radial passage 3 C and the axial passage 3 B.
  • the movable member 13 A is mounted on the shaft body 30 such that the movable member 13 A is rotatable together with the drive shaft 3 and slidable in the direction of the axis of rotation O of the drive shaft 3 .
  • the fixed member 13 B is fixedly mounted on the shaft body 30 for rotation therewith, but immovable in the axial direction of the drive shaft 3 . Therefore, the movable member 13 A slides axially relative to the fixed member 13 B in moving in the axial direction of the drive shaft 3 .
  • the other end of the ring plate 45 is connected to the connecting part 132 of the movable member 13 A by a third pin 47 C, so that the other end of the ring plate 45 and hence the swash plate 5 is supported swingably around the axis M 3 that is the axis of the third pin 47 C by the movable member 13 A.
  • the axis M 3 extends parallel to the first and second axes M 1 , M 2 .
  • the movable member 13 A is connected to the swash plate 5 .
  • the movable member 13 A is brought into contact with the flange 432 .
  • control mechanism 15 has a bleed passage 15 A, a supply passage 15 B, a control valve 15 C and an orifice 15 D.
  • the bleed passage 15 A is connected at one end thereof to the pressure control chamber 25 and at the other end thereof to the first suction chamber 27 A, so that the pressure control chamber 13 C, the pressure control chamber 25 and the first suction chamber 27 A are in communication with each other through the bleed passage 15 A, the axial passage 3 B and the radial passage 3 C.
  • the supply passage 15 B is connected at one end thereof to the pressure control chamber 25 and at the other end thereof to the first discharge chamber 29 A.
  • the pressure control chamber 13 C, the pressure control chamber 25 and the first discharge chamber 29 A are in communication with each other through the supply passage 15 B, the axial passage 3 B and the radial passage 3 C.
  • the orifice 15 D is provided in the supply passage 15 B and regulates the flow rate of the refrigerant gas flowing through the supply passage 15 B.
  • the control valve 15 C is provided in the bleed passage 15 A for controlling the opening of the bleed passage 15 A and hence the flow rate of the refrigerant gas flowing through the bleed passage 15 A according to the pressure in the first suction chamber 27 A.
  • the inlet port 170 of the compressor in FIG. 1 is connected through a tube to an evaporator (not shown) of the refrigerant gas circuit and the aforementioned outlet port (not shown in the drawing) is connected through a tube to a condenser (not shown) of the refrigerant gas circuit.
  • the condenser is connected to the evaporator through tubes and an expansion valve.
  • the refrigerant gas circuit is composed of the compressor, the evaporator, the expansion valve, the condenser and the like. Illustration of the evaporator, the expansion valve, the condenser and tubes is omitted.
  • the drive shaft 3 rotates the swash plate 5 , which causes the pistons 9 to reciprocate in the first and second cylinder bores 21 A, 23 A.
  • the volumes of the first and second compression chambers 21 D, 23 D and hence the displacement or the capacity of the compressor changes according to the stroke length of the pistons 9 .
  • the suction process in which refrigerant gas is drawn into the first and second compression chambers 21 D, 23 D, the compression process in which the refrigerant gas is compressed in the first and second compression chambers 21 D, 23 D and the discharge process in which the compressed refrigerant gas is discharged from the first and second compression chambers 21 D, 23 D are repeated in this order.
  • the first suction reed valve 391 A opens the first suction hole 390 A by the pressure difference created between the first compression chamber 21 D and the first suction chamber 27 A, so that refrigerant gas in the first suction chamber 27 A is drawn into the first compression chamber 21 D.
  • the second suction reed valve 411 A opens the second suction hole 410 A by the pressure difference between the second compression chamber 23 D and the second suction chamber 27 B, so that refrigerant gas in the second suction chamber 27 B is flowed into the second compression chamber 23 D.
  • the first discharge reed valve 392 A opens the first discharge hole 390 B by the pressure difference between the first compression chamber 21 D and the first discharge chamber 29 A, so that the refrigerant gas compressed in the first compression chamber 21 D is discharged out into the first discharge chamber 29 A.
  • the second discharge reed valve 412 A opens the second discharge hole 410 B by the pressure difference between the second compression chamber 23 D and the second discharge chamber 29 B, so that refrigerant gas compressed in the second compression chamber 23 D is discharged out into the second discharge chamber 29 B.
  • piston compression reaction force acts on the rotating parts including the swash plate 5 , the ring plate 45 , the lug arm 49 and the first pin 47 A in the direction that reduces the inclination angle of the swash plate 5 .
  • Changing the inclination angle of the swash plate 5 changes the stroke length of the piston 9 and hence performs the displacement control.
  • the actuator 13 is moved by piston compression reaction force acting on the swash plate 5 , so that the movable member 13 A is moved toward the swash plate 5 and to a position close to the lug arm 49 , as shown in FIG. 3 .
  • the other end of the ring plate 45 that is, the other end of the swash plate 5 is swung clockwise around the first axis M 3 as seen in FIG. 3 while overcoming the urging force of the second return spring 44 B.
  • the rear end of the lug arm 49 is swung counterclockwise around the first axis M 1 , while the front part of the lug arm 49 swings counterclockwise around the second axis M 2 , so that the lug arm 49 approaches the flange 431 of the first support member 43 A.
  • the swash plate 5 swings with the axis M 3 as the point of load, around the first axis M 1 as the fulcrum point and the inclination angle of the swash plate 5 approaches zero with respect to the direction perpendicular to the axis of rotation O of the drive shaft 3 , so that the stroke length of the piston 9 decreases. Therefore, the volumes of refrigerant gas to be drawn and delivered per revolution of the compressor decrease.
  • the inclination angle of the swash plate 5 shown in FIG. 3 is the minimum inclination angle in the compressor according to the present embodiment.
  • Centrifugal force developed by the weight member 49 A is also applied to the swash plate 5 in such a way that tends to cause the swash plate 5 to incline so as to decrease its inclination angle.
  • the aforementioned movement of the movable member 13 A toward the swash plate chamber 33 causes the front end of the movable member 13 A to be located inside the weight member 49 A.
  • the inclination angle of the swash plate 5 decreases, approximately half of the movable member 13 A on the front side thereof is covered by the weight member 49 A.
  • the top dead center position of the first head 9 A is located farther from the first valve forming plate 39 .
  • compression of refrigerant gas is performed slightly in the second compression chamber 23 D, while no compression of refrigerant gas is performed in the first compression chamber 21 D.
  • the movable member 13 A pulls the other end side of the swash plate 5 rearward at the axis M 3 through the connecting part 132 , thus causing the other end side of the swash plate 5 to swing counterclockwise around the axis M 3 . Then, the rear end of the lug arm 49 is swung clockwise around the first axis M 1 , while the front part of the lug arm 49 is swung clockwise around the second axis M 2 . The lug arm 49 is then moved away from the flange 431 of the first support member 43 A.
  • the swash plate 5 is swung around the first axis M 1 with the axis M 3 as the point of load in the direction that increases the inclination angle of the swash plate 5 , with the result that the stroke length of the piston 9 is increased and the suction capacity and the displacement per revolution increase.
  • the inclination angle of the swash plate 5 shown in FIG. 1 is the maximum inclination angle in the compressor according to the present embodiment.
  • the inner diameter of the first cylinder bore 21 A is smaller than that of the second cylinder bore 23 A, so that the outer diameter of the second head 9 B is larger than that of the first head 9 A.
  • the first suction flow passage 2 and the second suction flow passage 4 have the same structure so that refrigerant gas drawn in the inlet port 170 is flowed for substantially the same distance into each of the first compression chambers 21 D and each of the second compression chamber 23 D.
  • the amplitude of the intake pulsation occurring in the first compression chamber 21 D which is indicated by dashed-dotted line in FIG. 4 is smaller than that in the second compression chamber 23 D which is indicated by dashed line in FIG. 4 .
  • the intake pulsation that remains in such compressor results from combining the above intake pulsations and is indicated by solid line in FIG. 4 .
  • the first suction flow passage 2 and the second suction flow passage 4 have different structures.
  • refrigerant gas is directly supplied from the inlet port 170 into the first suction chamber 27 A through the first suction passage 171 .
  • the first suction reed valve 391 A is bent and opens the first suction hole 390 A thereby to allow the refrigerant gas drawn from the inlet port 170 into the first suction chamber 27 A to be introduced into the first compression chamber 21 D.
  • the intake resistance acting on the refrigerant gas drawn into the first compression chamber 21 D in suction process (hereinafter referred to as “the first intake resistance”) is smaller than the intake resistance acting on the refrigerant gas drawn into the second compression chamber 23 D in suction process (hereinafter referred to as “the second intake resistance”), so that in the first suction flow passage 2 in which the first intake resistance is small, refrigerant gas is flowed easily into the first compression chamber 21 D and the amplitude of intake pulsation occurring in the first compression chamber 21 D becomes large.
  • the second suction flow passage 4 in which the second intake resistance is large refrigerant gas is flowed less easily into the second compression chamber 23 D and the amplitude of the intake pulsation occurring in the second compression chamber 23 D is small.
  • the amplitude of the intake pulsation occurring in the second compression chamber 23 D is lower due to the relatively large second intake resistance as compared to the case of FIG. 4 .
  • the amplitude of the intake pulsation in first compression chamber 21 D which is indicated by dashed-dotted line in FIG. 5 , is higher as compared to the case of FIG. 4 .
  • the difference of the amplitude of the intake pulsation between the first compression chamber 21 D and the second compression chamber 23 D occurs.
  • the difference of the intake pulsation amplitude can be suitably reduced. That is, the intake pulsation combined by the intake pulsation in the first compression chamber 21 D and the intake pulsation in the second compression chamber 23 D can be reduced as shown in FIG. 5 with a solid line in the compressor. As a result, the intake pulsation is reduced over the entire range of displacements of the compressor and noise can be reduced.
  • the compressor according to the first embodiment is advantageous in terms of silence in operation.
  • the movable member 13 A moves frontward in the swash plate chamber 33 to a position close to the fixed member 13 B as shown in FIG. 3 thereby to reduce the volume of the pressure control chamber 13 C.
  • the swash plate 5 reduces its inclination angle with a decrease of the volume of the pressure control chamber 13 C. Allowing the movable member 13 A to move frontward in the swash plate chamber 33 , the first accommodating chamber 21 C also serves as part of the swash plate chamber 33 .
  • the movable member 13 A moves rearward in the swash plate chamber 33 away from the fixed member 138 to a position shown in FIG. 1 thereby to increase the volume of the pressure control chamber 13 C.
  • the swash plate 5 increases its inclination angle with an increase of the volume of the pressure control chamber 13 C.
  • the inclination angle of the swash plate 5 becomes larger, while the volume of the swash plate chamber 33 gradually becomes smaller.
  • the volume of the swash plate chamber 33 becomes minimum. Therefore, the muffler effect of the swash plate chamber 33 is suppressed with an increasing inclination angle of the swash plate 5 and the reduction effect of the intake pulsation in the second compression chamber 23 D is suppressed. That is, the intake pulsation amplitude in the second compression chamber 23 D may be increased to a level that is close to that in the first compression chamber 21 D.
  • the difference of the intake pulsation between the first compression chamber 21 D and the second compression chamber 23 D can be suitably reduced according a change of the displacement of the compressor.
  • no inlet port and no first suction passage such as 170 and 171 of the first embodiment shown in FIGS. 1 and 3 is formed in the rear housing 17 , so that the first suction chamber 27 A is smaller than that of the first embodiment.
  • the first cylinder block 21 of the compressor according to the second embodiment has therein a first communication passage 38 A and an inlet port 330 .
  • the second cylinder block 23 of the compressor according to the second embodiment has therein a second communication passage 38 B.
  • the inner diameter of the first communication passage 38 A is the same as that of the second communication passage 38 B.
  • the first communication passage 38 A is communication with the swash plate chamber 33 .
  • the first suction chamber 27 A is in communication with the first communication passage 38 A through the first communication hole 390 C.
  • the inlet port 330 is in communication with the first suction chamber 27 A through the first communication passage 38 A.
  • the second communication passage 38 B is in communication with the swash plate chamber 33 .
  • the second suction chamber 27 B is in communication with the second communication passage 38 B through the second communication hole 410 C.
  • the inlet port 330 is in communication with the second suction chamber 27 B through the second communication passage 38 B.
  • the inlet port 330 is formed through the first cylinder block 21 at a position that is adjacent to the front end of the first cylinder block 21 and located approximately at the longitudinal center of the housing 1 .
  • the swash plate chamber 33 is connected through the inlet port 330 to an evaporator (not shown in the drawing) forming a part of the refrigerant gas circuit in which the present compressor is connected. Because the inlet port 330 is located approximately at the longitudinal center of the housing 1 , the distance from the first communication passage 38 A to the inlet port 330 is substantially the same as that from the second communication passage 38 B to the inlet port 330 .
  • the first suction valve plate 391 is thinner than the second suction valve plate 411 , so that the first suction reed valve 391 A is thinner than the second suction reed valve 411 A.
  • the first suction hole 390 A, the second suction hole 410 A, the first discharge holes 390 B and the second discharge holes 410 B are formed substantially in the same size, or the opening as those of the compressor according to the first embodiment.
  • the first retainer plate 393 and the second retainer plate 413 are formed to have substantially the same shape as those of the compressor according to the first embodiment.
  • refrigerant gas drawn from an evaporator into the swash plate chamber 33 through the inlet port 330 is flowed through the first communication passage 38 A into the first suction chamber 27 A and introduced through the first suction hole 390 A into the first compression chamber 21 D.
  • the first suction flow passage 2 A is formed by the first communication passage 38 A, the first suction chamber 27 A and each of the first suction hole 390 A.
  • the first suction reed valves 391 A is thinner than the second suction reed valves 411 A, so that in suction process, the first suction reed valve 391 A opens the first suction hole 390 A more easily than the second suction reed valve 411 A opens the second suction hole 410 A.
  • the first intake resistance is smaller than the second intake resistance and, therefore, in the suction process, refrigerant gas can be drawn into the first compression chamber 21 D more easily than refrigerant gas drawn into the second compression chamber 23 D. That is, as shown in FIG.
  • the increased second intake resistance reduces the amplitude of the intake pulsation in the second compression chamber 23 D with a dashed line compared to the case shown in FIG. 4 .
  • the decreased first suction resistance increases the amplitude of the intake pulsation in the first compression chamber 21 D shown in FIG. 5 with a dashed-dotted line compared to the case shown in FIG. 4
  • the difference of the intake pulsation between the first compression chamber 21 D and the second compression chamber 23 D can be suitably reduced.
  • the other effects of the compressor according to the second embodiment are the same as those of the compressor according to the first embodiment.
  • the compressor according to the third embodiment differs from the compressor of the second embodiment in that the first suction hole 390 A of the first valve forming plate 39 and the second suction hole 410 A of the second valve forming plate 41 are formed to have the different size with respect to the opening area thereof. Specifically, the inner diameter of the first suction hole 390 A is larger than that of the second suction hole 410 A.
  • the compressor according to the third embodiment differs from the compressor of the second embodiment also in that the first suction valve plate 391 and the second suction valve plate 411 are formed to have the same thickness as in the case of the compressor according to the first embodiment. Therefore, the thickness of the first suction reed valve 391 A is the same as that of the second suction reed valve 411 A.
  • the rest of the structure of the compressor according to the third embodiment, including the opening areas of the first discharge hole 390 B and the second discharge hole 410 B, is substantially the same as the compressor according to the second embodiment.
  • refrigerant gas drawn from an evaporator into the swash plate chamber 33 through the inlet port 330 is flowed through the first and second suction flow passages 2 A, 4 A into the first and second compression chamber 21 D, 23 D, respectively in a manner similar to the case of the compressor according to the second embodiment.
  • the first suction hole 390 A provides a larger opening than the second suction hole 410 A, so that refrigerant gas flows through first suction hole 390 A more easily than through the second suction hole 410 A. Therefore, the first intake resistance is smaller than the second intake resistance.
  • refrigerant gas is flowed into the first compression chamber 21 D more easily than in the second compression chamber 23 D.
  • the inner diameter of the first cylinder bores 21 A is smaller than that of the second cylinder bores 23 A, so that the difference of the intake pulsation between the first compression chamber 21 D and the second compression chamber 23 D can be suitably reduced.
  • the other effects of the compressor according to the third embodiment are the same as those of the compressor according to the first embodiment.
  • the compressor according to the fourth embodiment shown in FIG. 9 differs from the compressor of the second embodiment in that the first retainer groove 21 E and the second retainer groove 23 E are formed differently. Specifically, the first retainer groove 21 E is formed deeper than the second retainer groove 23 E.
  • the compressor according to the fourth embodiment also differs from the compressor of the second embodiment also in that the thicknesses of the first suction reed valve 391 A and the second suction reed valve 411 A are the same.
  • the rest of the compressor according to the fourth embodiment including the opening area of the first discharge hole 390 B and the second discharge hole 410 B is substantially the same as the compressor according to the second embodiment.
  • refrigerant gas drawn from an evaporator into the swash plate chamber 33 through the inlet port 330 is introduced through the first and second suction flow passages 2 A, 4 A into the first and second compression chamber 21 D, 23 D, respectively.
  • the first suction reed valve 391 A is bent larger than the second suction reed valve 411 A during suction process.
  • the first suction reed valve 391 A opens larger than the second suction reed valve 411 A during suction process, so that refrigerant gas through the first suction hole 390 A is flowed more easily than through the second suction hole 410 A. Therefore, the first intake resistance is also smaller than the second intake resistance, so that refrigerant gas is flowed more easily into the first compression chamber 21 D than through the second compression chamber 23 D during suction process.
  • the inner diameter of the first cylinder bores 21 A is smaller than that of the second cylinder bores 23 A, so that the difference of the amplitude of the intake pulsation between the first compression chamber 21 D and the second compression chamber 23 D can be suitably reduced.
  • the other effects of the compressor according to the fourth embodiment are the same as those of the compressor according to the first embodiment.
  • the compressor according to the fifth embodiment shown in FIG. 10 has the first and second communication passages 38 A, 38 B formed in the first and second cylinder blocks 21 , 23 , respectively.
  • the compressor of FIG. 10 differs from the compressor of the second embodiment in that the first and second communication passages 38 A, 38 B have different inner diameters.
  • the inner diameter of the first communication passage 38 A is larger than that of the second communication passage 38 B and, therefore, the diameter of the first communication hole 390 C of the first valve forming plate 39 is larger than that of the second communication hole 410 C of the second valve forming plate 41 .
  • the thickness of the first suction reed valves 391 A is substantially the same as that of the second suction reed valves 411 A as in the case of the compressor according to the first embodiment.
  • the rest of structure of the compressor according to the fifth embodiment, including the opening area of the first discharge hole 390 B and the second discharge hole 410 B, is substantially the same as that of the compressor according to the second embodiment.
  • refrigerant gas drawn from an evaporator through the inlet port 330 into the swash plate chamber 33 is flowed through the first and second suction flow passages 2 A, 4 A into the first and second compression chamber 21 D, 23 D, respectively. Because, the inner diameter of the first communication passage 38 A is larger than that of the second communication passage 38 B, the inner diameter of the first suction flow passage 2 A is larger than that of the second suction flow passage 4 A.
  • the compressor according to the sixth embodiment shown in FIG. 11 has the first communication passage 38 A and the inlet port 330 formed in the first cylinder block 21 and the second communication passage 38 B formed in the second cylinder block 23 .
  • the compressor of the present sixth embodiment differs from the compressor of the second embodiment in that the inlet port 330 is formed through the first cylinder block 21 at a position adjacent to the center of the first cylinder block 21 . That is, the inlet port 330 is formed at a position that is closer to the rear end of the housing 1 than the inlet port 330 of the second embodiment, so that the distance between the first communication passage 38 A and the inlet port 330 is different from that between the second communication passage 38 B and the inlet port 330 . Specifically, the distance between the first communication passage 38 A and the inlet port 330 is smaller than that between the second communication passage 38 B and the inlet port 330 .
  • the thickness of the first suction reed valve 391 A is the same as that of the second suction reed valve 411 A in the compressor according to the sixth embodiment.
  • the rest of the structure of the compressor according to the sixth embodiment, including the opening areas of the first discharge hole 3908 and of the second discharge holes 410 B, is substantially the same as that of the compressor according to the second embodiment.
  • refrigerant gas flowed from an evaporator through the inlet port 330 into the swash plate chamber 33 is introduced through the first and second suction flow passages 2 A, 4 A into the first and second compression chamber 21 D, 23 D, respectively.
  • the distance between the first communication passage 38 A and the inlet port 330 is smaller from that between the second communication passage 38 B and the inlet port 330 . Therefore, the overall length of the first suction flow passage 2 A is shorter than that of the second suction flow passage 4 A.
  • the compressor according to the seventh embodiment has a rear housing 18 instead of the rear housing 17 of the compressor according to the first embodiment.
  • the compressor has a first valve forming plate 51 between the rear housing 18 and the first cylinder block 21 .
  • the drive shaft 3 is formed by a shaft body 300 , the first support member 43 A and a second support member 46 .
  • the first cylinder block 21 has therethrough the first communication passage 38 A and the inlet port 330 and the second cylinder block 23 has formed therethrough the second communication passage 38 B.
  • the rear housing 18 has therein the control mechanism 15 , the first suction chamber 27 A and the first discharge chamber 29 A.
  • the rear housing 17 has further therein the pressure control chamber 250 .
  • the pressure control chamber 250 is formed smaller than the pressure control chamber 25 in the first embodiment. By forming the pressure control chamber 250 smaller, the first suction chamber 27 A in the rear housing 18 may be formed larger.
  • An O ring 251 is provided in the pressure control chamber 250 .
  • the pressure control chamber 250 is in communication with the first suction chamber 27 A and the first discharge chamber 29 A through the bleed passage 15 A and the supply passage 15 B.
  • no inlet port 170 and no first suction passage 171 is formed in the rear housing 18 .
  • a first suction passage 21 F is formed in the first cylinder block 21 , extending from the first shaft hole 21 B toward the first cylinder bore 21 A.
  • a communication hole 220 is formed in the first slide bearing 22 A in communication with the first suction passage 21 F.
  • no first retainer groove such as 21 E is formed in the first cylinder block 21 .
  • the first valve forming plate 51 has a first valve plate 510 , a first discharge valve plate 511 and a first retainer plate 512 .
  • the first valve plate 510 has therein the first discharge hole 5108 for each first cylinder bore 21 A.
  • a first communication hole 510 C and an insertion hole 510 D are formed in the first valve plate 510 , the first discharge valve plate 511 and the first retainer plate 512 .
  • the first cylinder bores 21 A is communicable with the first discharge chamber 29 A through the first discharge hole 5108 .
  • the first suction chamber 27 A is in communication with the first communication passage 38 A through the first communication hole 510 C.
  • the rear end of the drive shaft 3 is inserted through the insertion hole 510 D.
  • the opening area of the first discharge hole 510 B is the same as that of the second discharge hole 410 B.
  • the opening area of the first communication hole 510 C is the same as that of the second communication hole 410 C.
  • a first discharge valve plate 511 is provided on the rear surface of the first valve plate 510 .
  • the first discharge valve plate 511 is formed with a plurality of first discharge reed valves 511 A that open and close the respective first discharge holes 510 B by elastic deformation.
  • the first retainer plate 512 is provided on the rear surface of the first discharge valve plate 511 .
  • the first retainer plate 512 regulates the lift of the first discharge reed valve 511 A.
  • the first retainer plate 512 and the second retainer plate 413 are formed symmetrically, so that the lift of the first discharge reed valve 511 A is the same as that of the second discharge reed valve 412 A.
  • the shaft body 300 is formed so that the outer diameter of the rear end thereof is smallest of the other portions thereof and smaller than the inner diameter of the insertion hole 510 D.
  • the rear end of the shaft body 300 is inserted through the insertion hole 510 D into the pressure control chamber 250 .
  • the O ring 251 is mounted on the rear end of the shaft body 300 for sealing the pressure control chamber 250 .
  • the shaft body 300 has therein the axial passage 3 B and the radial passage 3 C.
  • the pressure control chamber 250 is in communication with the pressure control chamber 13 C through the axial passage 3 B and the radial passage 3 C.
  • the first support member 43 A is press-fitted on the front end portion of the shaft body 300 and the second support member 46 is press-fitted on the rear end portion of the shaft body 300 .
  • the second support member 46 is in sliding contact with the first slide bearing 22 A.
  • the second support member 46 is formed with a flange 460 .
  • the flange 460 is formed between the first thrust bearing 35 A and the actuator 13 and located in the first accommodating chamber 21 C.
  • the diameter of the rear end portion of the shaft body 300 is small, so that a communication passage 38 C is formed between the second support member 46 and the shaft body 300 .
  • the communication passage 38 C is in communication with the first suction chamber 27 A through a space between the insertion hole 510 D and the rear end portion of the shaft body 300 .
  • a rotating passage 46 A is formed in the second support member 46 .
  • the rotating passage 46 A is in communication with the communication passage 38 C and opens on the outer peripheral surface of the second support member 46 .
  • the communication passage 38 C is brought into communication with the first compression chamber 21 D through the first suction passage 21 F when the rotating passage 46 A is made into communication with the communication hole 220 with the rotation of the drive shaft 3 .
  • the first suction chamber 27 A is in communication with the first compression chamber 21 D.
  • the first suction flow passage 2 B is formed by the first communication passage 38 A, the first suction chamber 27 A, the communication passage 38 C, the communication hole 220 and the first suction passage 21 F.
  • the rest of the structure of the compressor according to the seventh embodiment is substantially the same as the compressor according to the second embodiment.
  • refrigerant gas is drawn from the inlet port 330 through the first communication passage 38 A into the first suction chamber 27 A.
  • the first and second support members 43 A, 46 are rotated with the drive shaft 3 . Therefore, in suction process of the first compression chamber 21 D, the rotating passage 46 A is communicable with the communication hole 220 .
  • the communication passage 38 C is communicable with the first suction passage 21 F, so that the refrigerant gas is drawn through the communication passage 38 C; the rotating passage 46 A, the communication hole 220 and the first suction passage 21 F into the first compression chamber 21 D.
  • refrigerant gas is drawn through the second suction flow passage 4 A into the second compression chamber 23 D in the same manner as the compressor according to the second embodiment.
  • the communication passage 38 C is communicable with the first suction passage 21 F during suction process by the rotation of the drive shaft 3 and refrigerant gas in the first suction chamber 27 A is drawn into the first compression chamber 21 D, so that the first suction resistance is small.
  • refrigerant gas is drawn more easily into the first compression chamber 21 D than into the second compression chamber 23 D.
  • the compressor according to the seventh embodiment described above wherein the inner diameter of the first cylinder bore 21 A is smaller than that of the second cylinder bore 23 A, the difference of the amplitude of the intake pulsation between the first compression chamber 21 D and the second compression chamber 23 D can be suitably reduced.
  • the other effects of the compressor according to the seventh embodiment are the same as those of the compressor according to the first embodiment.
  • refrigerant gas is drawn through the inlet port 170 or 330 more easily into the first compression chamber 21 D than into the corresponding second compression chamber 23 D by appropriately combining the features of the compressors according the first through seventh embodiments.
  • the compressor may have a structure in which the actuator 13 is disposed in the second accommodating chamber 23 C and the lug arm 49 is disposed in the first accommodating chamber 21 C.
  • the compressor may have a structure in which the control valve 15 C is provide in the supply passage 15 B and the orifice 15 D in the bleed passage 15 A, respectively.
  • the flow rate of high pressure refrigerant gas flowing through the supply passage 15 B can be controlled by the control valve 15 C.
  • the pressure in the pressure control chamber 13 C may be increased rapidly by high pressure in the first discharge chamber 29 A, so that the compressor displacement can be rapidly reduced.
  • the present invention is applicable to an air conditioner and the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US14/451,871 2013-08-08 2014-08-05 Swash plate type variable displacement compressor Abandoned US20150044068A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013-165506 2013-08-08
JP2013165506A JP6107528B2 (ja) 2013-08-08 2013-08-08 容量可変型斜板式圧縮機

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5032060A (en) * 1989-11-02 1991-07-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Continuously variable capacity swash plate type refrigerant compressor
US5259736A (en) * 1991-12-18 1993-11-09 Sanden Corporation Swash plate type compressor with swash plate hinge coupling mechanism
US6467296B2 (en) * 2000-01-25 2002-10-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Air conditioning system for vehicle
US20140127042A1 (en) * 2012-11-05 2014-05-08 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2176300A (en) * 1937-12-06 1939-10-17 Frank J Fette Gas compressor
JPS5142112A (ja) * 1974-10-09 1976-04-09 Japan Steel Works Ltd Shabanshikimukyuyuatsushukuki
JP2641477B2 (ja) * 1988-02-29 1997-08-13 株式会社日本自動車部品総合研究所 可変容量式斜板型圧縮機
JP2807068B2 (ja) * 1990-08-10 1998-09-30 株式会社日本自動車部品総合研究所 可変容量式斜板型圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5032060A (en) * 1989-11-02 1991-07-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Continuously variable capacity swash plate type refrigerant compressor
US5259736A (en) * 1991-12-18 1993-11-09 Sanden Corporation Swash plate type compressor with swash plate hinge coupling mechanism
US6467296B2 (en) * 2000-01-25 2002-10-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Air conditioning system for vehicle
US20140127042A1 (en) * 2012-11-05 2014-05-08 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor

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JP6107528B2 (ja) 2017-04-05
DE102014215663A1 (de) 2015-02-12
DE102014215663B4 (de) 2017-04-13

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