US20170145997A1 - Variable displacement type swash plate compressor - Google Patents
Variable displacement type swash plate compressor Download PDFInfo
- Publication number
- US20170145997A1 US20170145997A1 US15/353,135 US201615353135A US2017145997A1 US 20170145997 A1 US20170145997 A1 US 20170145997A1 US 201615353135 A US201615353135 A US 201615353135A US 2017145997 A1 US2017145997 A1 US 2017145997A1
- Authority
- US
- United States
- Prior art keywords
- swash plate
- link pin
- arm
- movable body
- 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
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- 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
-
- 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
- F04B27/0873—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
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
-
- 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
- F04B27/10—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
- F04B27/14—Control
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
-
- 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
- F04B49/12—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 varying the length of stroke of the working members
- F04B49/123—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
- F04B49/125—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
Definitions
- the present invention relates to a variable displacement type swash plate compressor.
- the compressor further includes a partitioning body, a movable body, a control chamber, and a control mechanism.
- the partitioning body and the movable body are disposed in the swash plate chamber and mounted on the drive shaft for rotation therewith.
- the movable body is movable relative to the partitioning body in the axial direction of the drive shaft so as to change the inclination angle of the swash plate.
- the control chamber is defined between the partitioning body and the movable body and causes the movable body to be moved with its internal pressure.
- the control mechanism controls the pressure in the control chamber.
- the relative positional relation between the link pin and the first and second holes remains constant without being affected by the change of the inclination angle of the swash plate.
- a swash plate type variable displacement compressor including a housing having therein a swash plate chamber and a plurality of cylinder bores, a drive shaft rotatably supported in the housing, a swash plate mounted on the drive shaft for rotation therewith in the swash plate chamber, and a link mechanism connecting the drive shaft and the swash plate and permitting changing of an inclination angle of the swash plate with respect to a direction perpendicular to an axis of rotation of the drive shaft.
- the compressor further includes a plurality of pistons received in the respective cylinder bores so as to form respective compression chamber and reciprocally movable with the rotation of the swash plate for a length of stroke determined by the inclination angle of the swash plate, a partitioning body mounted on the drive shaft for rotation therewith in the swash plate chamber, a movable body that is mounted on the drive shaft for rotation therewith and movable relative to the partitioning body along the axis of rotation in the swash plate chamber to thereby change the inclination angle of the swash plate, a control chamber that is formed between the partitioning body and the movable body, and cause the movable body to move with a pressure in the control chamber, and a control mechanism controlling the pressure in the control chamber, and a connecting mechanism connecting the swash plate and the movable body, so that the movable body pulls the swash plate to increase the inclination angle with an increase of the pressure in the control chamber.
- the swash plate has a top dead center portion that permits one of the pistons to be located at the top dead center.
- a plane that passes through the top dead center portion and the rotation axis is defined as an imaginary plane.
- the connecting mechanism includes a first arm that extends from the movable body toward the swash plate and is disposed on one side of the imaginary plane, a second arm that extends from the movable body toward the swash plate and disposed on the other side of the imaginary plane, a traction portion that is projected from the swash plate toward the movable body between the first arm and the second arm.
- the first arm has a first guide surface facing away from the swash plate and the second arm has a second guide surface facing away from the swash plate.
- the first guide surface and the second guide surface are placed in contact with the link pin.
- the link pin is held by the traction portion so as to be rollable on the first guide surface and the second guide surface.
- a restrictor is provided on opposite sides of the link pin with respect to the imaginary plane so as to prevent the link pin from moving in a direction of an axis thereof.
- FIG. 1 is a longitudinal cross-sectional view of a compressor according to a first embodiment of the present invention, showing a state of the compressor at its maximum displacement;
- FIG. 2 is a longitudinal cross-sectional view of the compressor of FIG. 1 , showing a state of the compressor in its minimum displacement;
- FIG. 3 is a schematic diagram of a control mechanism of the compressor of FIG. 1 ;
- FIG. 4 is a fragmentary schematic side view of the compressor of FIG. 1 at its maximum displacement
- FIG. 5 is a fragmentary schematic side view of the compressor of FIG. 1 at its minimum displacement
- FIG. 6 is a fragmentary perspective view of the compressor as viewed in the direction of arrow Z in FIG. 5 ;
- FIG. 7A is a perspective view of a swash plate of the compressor of FIG. 1 ;
- FIG. 7B is a front view of the swash plate as viewed in the arrow direction of arrow Y in FIG. 7A ;
- FIG. 8 is a perspective view of a movable body of the compressor of FIG. 1 ;
- FIG. 9 is a perspective view of the movable body as viewed in the direction of arrow Z in FIG. 5 ;
- FIG. 10A is a front view of the movable body
- FIG. 10B is a side view of the movable body
- FIG. 11 is a partially enlarged view of FIG. 10B ;
- FIG. 12 is a fragmentary cross-sectional view of the movable body taken along line XII-XII in FIG. 11 ;
- FIG. 13 is a fragmentary side view of the compressor, illustrating a procedure for assembling a link mechanism, the swash plate and the movable body
- FIG. 14 is a side view of a movable body of a compressor according to a second embodiment of the present invention.
- FIG. 15 is similar to FIG. 12 , but showing a fragmentary cross-sectional view of the movable body taken along line XV-XV in FIG. 14 ;
- FIG. 16 is also similar to FIG. 12 , but showing a fragmentary cross-sectional view of a movable body of a compressor according to a third embodiment of the present invention.
- FIG. 17 is a fragmentary cross-sectional view of the movable body of FIG. 16 , showing a state in which the swash plate is misaligned with respect to rotation axis.
- variable displacement type swash plate compressor according to first, second and third embodiments of the present invention, respectively, with reference to the accompanying drawings.
- FIGS. 1 and 2 there is shown a variable displacement type swash plate compressor (hereinafter simply referred to as the compressor) according to the first embodiment.
- the compressor according to the present embodiment employs a double-headed piston.
- the compressor is mounted on a vehicle and forms a part of a refrigeration circuit of an air conditioner of the vehicle.
- FIGS. 1 and 2 the left side and right side of the drawings will be referred to as the front and rear of the compressor, respectively.
- the compressor includes a housing 1 , a drive shaft 3 having an axis of rotation O 1 extending in the longitudinal direction of the compressor, a swash plate 5 , a link mechanism 7 , a plurality of pistons 9 , and an actuator 13 . As shown in FIG. 3 , the compressor further includes a control mechanism 15 .
- the housing 1 includes a first housing member 17 , a second housing member 19 , a first cylinder block 21 , a second cylinder block 23 , a first valve-forming plate 39 and a second valve-forming plate 41 .
- the first housing member 17 is formed with a boss 17 A projecting frontward and having therein a shaft seal device 25 .
- the first housing member 17 has therein an annular first suction chamber 27 A and an annular first discharge chamber 29 A.
- the first suction chamber 27 A is located radially inward of the first housing member 17
- the first discharge chamber 29 A is located radially outward of the first suction chamber 27 A in the first housing member 17 .
- the first housing member 17 further has therein a first front passage 18 A.
- the first front passage 18 A is in communication at the front end thereof with the first discharge chamber 29 A and is opened at the rear end thereof to the rear end of the first housing member 17 .
- a part of the aforementioned control mechanism 15 is formed in the second housing member 19 .
- the second housing member 19 has therein an annular second suction chamber 27 B, an annular second discharge chamber 29 B, and a pressure control chamber 31 .
- the pressure control chamber 31 is located in the center of the second housing member 19 .
- the second suction chamber 27 B is located radially outward of the pressure control chamber 31 in the second housing member 19 .
- the second discharge chamber 29 B is located radially outward of the second suction chamber 27 B in the second housing member 19 .
- the second housing member 19 further has therein a first rear passage 20 A.
- the first rear passage 20 A is in communication at the rear end thereof with the second discharge chamber 29 B and connected at the front end thereof to the front end of the second housing member 19 .
- the first cylinder block 21 is disposed on the front side of the compressor between the first housing member 17 and the second cylinder block 23 .
- the first cylinder block 21 has therein a plurality of first cylinder bores 21 A that extends along the axis of rotation O 1 of the drive shaft 3 .
- the first cylinder bores 21 A are spaced angularly at a regular interval around the drive shaft 3 .
- a first shaft hole 21 B is formed through the first cylinder block 21 , and the drive shaft 3 is inserted through the first shaft hole 21 B.
- a first slide bearing 22 A is provided in the first shaft hole 21 B.
- the first cylinder block 21 further has at the center thereof a first recess 21 C that is formed coaxially with the first shaft hole 21 B and communicates with the first shaft hole 21 B.
- the first recess 21 C has an inner diameter that is larger than that of the first shaft hole 21 B.
- a first thrust bearing 35 A is provided in the first recess 21 C.
- the second cylinder block 23 is disposed between the first cylinder block 21 and the second housing member 19 in the rear part of the compressor.
- the second cylinder block 23 and the first cylinder block 21 are connected together thereby to form a swash plate chamber 33 therebetween.
- the swash plate chamber 33 is in communication with the first recess 21 C.
- the first recess 21 C forms a part of the swash plate chamber 33 .
- the second cylinder block 23 has therein a plurality of second cylinder bores 23 A that extends along the axis of rotation O 1 of the drive shaft 3 and has the same diameter as the first cylinder bores 21 A formed in the first cylinder block 21 .
- the second cylinder bores 23 A are spaced angularly at a regular interval around the drive shaft 3 in the second cylinder block 23 .
- Each second cylinder bore 23 A is paired with its corresponding first cylinder bore 21 A. Any number of the first and second cylinder bores 21 A, 23 A may be formed in the housing as long as the first and the second cylinder bores 21 A, 23 A are provided in pairs.
- the second cylinder block 23 has therein 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. It is to be noted that the first and second slide bearings 22 A, 22 B may be replaced with rolling bearings.
- the second cylinder block 23 has at the center thereof a second recess 23 C that is formed coaxially with the second shaft hole 23 B and communicates with the second shaft hole 23 B.
- the second recess 23 C has an inner diameter that is larger than that of the second shaft hole 23 B.
- a second thrust bearing 35 B is provided in the second recess 23 C.
- the second cylinder block 23 has a discharge port 23 D, a junction 23 J, a suction port 23 S, a third front passage 18 C, a second rear passage 20 B, and a second connecting passage 37 B.
- the discharge port 23 D and the junction 23 J communicate with each other.
- the junction 23 J is connected through the discharge port 23 D to a condenser (not shown) that forms the refrigeration circuit of the vehicle air conditioner.
- the suction port 23 S and the swash plate chamber 33 are in communication with each other.
- the swash plate chamber 33 is connected to an evaporator (not shown) that forms the refrigeration circuit of the vehicle air conditioner through the suction port 23 S.
- the third front passage 18 C is in communication at the rear end thereof with the junction 23 J and is opened at the front end thereof to the front end of the second cylinder block 23 to be in communication with the second front passage 18 B.
- the second rear passage 20 B is in communication at the front end thereof with the junction 23 J and is opened at the rear end thereof to the rear end of the second cylinder block 23 .
- the second connecting passage 37 B is opened at the front end thereof to the swash plate chamber 33 and at the rear end thereof to the rear end of the second cylinder block 23 .
- the first housing member 17 and the first cylinder block 21 are joined together with the first valve-forming plate 39 interposed therebetween.
- the second housing member 19 and the second cylinder block 23 are joined together with the second valve-forming plate 41 interposed therebetween.
- first valve plate 390 , the first suction valve plate 391 , the first discharge valve plate 392 , and the first retainer plate 393 have therethrough a first suction communication hole 390 C.
- the first valve plate 390 and the first suction valve plate 391 have therethrough a first discharge communication hole 390 D.
- the first suction valve plate 391 is provided on the rear surface of the first valve plate 390 .
- the first suction valve plate 391 has a first suction reed valve 391 A for each of the first suction holes 390 A to open and close its corresponding first suction hole 390 A by elastic deformation.
- the first discharge valve plate 392 is provided on the front surface of the first valve plate 390 .
- the first discharge valve plate 392 has a first discharge reed valve 392 A for each of the first discharge holes 390 B to open and close its corresponding first discharge hole 390 B by elastic deformation.
- the first retainer plate 393 is provided on the front surface of the first discharge valve plate 392 and restricts the opening of the first discharge reed valve 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 .
- the second valve plate 410 and the second suction valve plate 411 extend radially to the outer peripheries of the second housing member 19 and the second cylinder block 23 .
- the second valve plate 410 , the second discharge valve plate 412 , and the second retainer plate 413 have therethrough a second suction hole 410 A for each of the second cylinder bores 23 A.
- the second valve plate 410 and the second suction valve plate 411 have therethrough a second discharge hole 410 B for each of the second cylinder bores 23 A.
- the second valve plate 410 , the second suction valve plate 411 , the second discharge valve plate 412 , and the second retainer plate 413 have therethrough a second suction communication hole 410 C.
- the second valve plate 410 and the second suction valve plate 411 have therethrough a second discharge communication hole 410 D.
- Each second cylinder bore 23 A is communicable with the second suction chamber 27 B through the second suction hole 410 A and is communicable also with the second discharge chamber 29 B through the second discharge hole 410 B.
- the second suction chamber 27 B and the second connecting passage 37 B are in communication with each other through the second suction communication hole 410 C.
- the first rear passage 20 A and the second rear passage 20 B are in communication with each other through the second discharge communication hole 410 D.
- the second suction valve plate 411 is provided on the front surface of the second valve plate 410 .
- the second suction valve plate 411 has a second suction reed valve 411 A for each of the second suction holes 410 A to open and close its corresponding second suction hole 410 A by elastic deformation.
- the second discharge valve plate 412 is provided on the rear surface of the second valve plate 410 .
- the second discharge valve plate 412 has a second discharge reed valve 412 A for each of the second discharge holes 410 B to open and close its corresponding second discharge hole 410 B by elastic deformation.
- the second retainer plate 413 is provided on the rear surface of the second discharge valve plate 412 and restricts the opening of the second discharge reed valve 412 A.
- the first front passage 18 A, the first discharge communication hole 390 D, the second front passage 18 B, and the third front passage 18 C cooperate to form a first discharge passage 18 .
- the first rear passage 20 A, the second discharge communication hole 410 D and the second rear passage 20 B cooperate to form a second discharge passage 20 .
- the first suction chamber 27 A is in communication with the swash plate chamber 33 through the first connecting passage 37 A and the first suction communication hole 390 C
- the second suction chamber 27 B is in communication with the swash plate chamber 33 via the second connecting passage 37 B and the second suction communication hole 410 C, so that the pressures in the first and second suction chambers 27 A, 27 B are substantially the same as those in the swash plate chamber 33 .
- the drive shaft 3 includes a drive shaft body 30 , a first support member 43 A and a second support member 43 B.
- the drive shaft body 30 extends along the axis of rotation O 1 in the housing 1 .
- the drive shaft body 30 has at the front end thereof a first small diameter portion 30 A and at the rear end thereof a second small diameter portion 30 B.
- the drive shaft body 30 is inserted through the shaft seal device 25 , the first and second slide bearings 22 A, 22 B in the housing 1 , so that the drive shaft body 30 and hence the drive shaft 3 is supported rotatably about the axis of rotation O 1 in the housing 1 .
- the front end of the drive shaft body 30 of the drive shaft 3 is inserted through the shaft seal device 25 in the boss 17 A and the rear end of the drive shaft body 30 of the drive shaft 3 extends into the pressure control chamber 31 .
- the drive shaft body 30 has mounted thereon the swash plate 5 , the link mechanism 7 , and the actuator 13 that are disposed in the swash plate chamber 33 .
- the first support member 43 A has a substantially cylindrical shape extending along the axis of rotation O 1 .
- the first support member 43 A is press-fitted on the first small diameter portion 30 A of the drive shaft body 30 to be integrated therewith.
- the first support member 43 A is supported by the first slide bearing 22 A in the first shaft hole 21 B.
- the first support member 43 A has at the rear end thereof a first flange 43 F and a mount portion 43 D through which a second pin 47 B, which will be described later, is inserted.
- the second support member 43 B has a substantially cylindrical shape extending along the axis of rotation O 1 .
- the second support member 43 B is press-fitted on the second small diameter portion 30 B of the drive shaft body 30 to be integrated therewith.
- the second support member 43 B is supported by the second slide bearing 22 B in the second shaft hole 23 B.
- the second support member 43 B has at the front end thereof a second flange 43 G.
- the second thrust bearing 35 B is held between the second flange 43 G and the bottom surface of the second recess 23 C in the axial direction of the drive shaft 3 with a predetermined preload applied to the second thrust bearing 35 B. With this arrangement, a thrust force acting on the drive shaft body 30 during the operation of the compressor is supported by the second thrust bearing 35 B.
- the swash plate 5 has a substantially disk shape having a front surface 5 A and a rear surface 5 B.
- the swash plate 5 is disposed in the swash plate chamber 33 with the front surface 5 A and the rear surfaces 5 B thereof facing frontward and rearward of the compressor, respectively.
- the swash plate 5 is tiltable with respect to a direction perpendicular to the axis of rotation O 1 .
- symbol T designates a top dead center portion which is a point or portion in the swash plate 5 where the swash plate 5 positions a first head portion 9 A of the piston 9 at the top dead center thereof, as shown in FIG. 1
- symbol U designates a bottom dead center portion which is a point or portion of the swash plate 5 where the swash plate 5 positions the first head portion 9 A of the piston 9 at the bottom dead center thereof, respectively.
- the compressor of the present embodiment is of a double-headed piston type
- the swash plate 5 positions the second head portion 9 B of the piston 9 at the bottom dead center thereof when the second head portion 9 B is positioned at the top dead center.
- Symbol D in FIG. 7B designates an imaginary plane that passes through the point T of the swash plate 5 and the axis of rotation O 1 of the drive shaft 3 .
- the swash plate 5 has a ring plate 45 having an annular shape. As shown in FIG. 7A , the part of the swash plate 5 that is radially inward of the ring plate 45 is partially projected or recessed in a direction of the axis of rotation O 1 so as to adjust the weight balance of the swash plate 5 and to avoid the interference with a first arm 110 and a second arm 120 , which will be described later.
- an insertion hole 45 A is formed through the swash plate 5 in the axial direction of the axis of rotation O 1 .
- the insertion hole 45 A has a substantially rectangular shape formed so as to have therein the axis of rotation O 1 and extending toward the top dead center portion T.
- the swash plate 5 is mounted on the drive shaft 3 in the swash plate chamber 33 with the drive shaft body 30 inserted through the insertion hole 45 A of the ring plate 45 of the swash plate 5 .
- the swash plate 5 has a traction portion 150 and a link pin 155 that form a connecting mechanism 100 .
- the connecting mechanism 100 connects the swash plate 5 to a movable body 13 A, which will be described later.
- the traction portion 150 is formed at a position in the swash plate 5 radially inward of the ring plate 45 and is closer to the bottom dead center portion U than the insertion hole 45 A is, and projects rearward from the rear surface 5 B of the swash plate 5 .
- a pin hole 150 H having the axis R 1 extending perpendicular to the imaginary plane D is formed through the traction portion 150 .
- the link pin 155 is inserted through the pin hole 150 H.
- the link pin 155 is supported rotatable about the axis R 1 by the traction portion 150 .
- the link pin 155 has a shape of circular column extending radially from the axis R 1 .
- the link pin 155 is made of a metal such as steel and aluminum alloy, but any suitable material may be used for the link pin 155 .
- the outer diameter of the link pin 155 is formed just smaller than the inner diameter of the pin hole 150 H to such an extent that lubricant oil included in a refrigerant gas forms an oil film between the outer peripheral surface of the link pin 155 and the inner peripheral surface of the pin hole 150 H, which significantly reduces the friction between the link pin 155 and the pin hole 150 H during the rolling of the link pin 155 about the axis R 1 .
- the link pin 155 has at one end thereof a first shaft portion 151 and at the other end thereof a second shaft portion 152 .
- Part of the first shaft portion 151 extends out from the pin hole 150 H of the traction portion 150 on one side of the imaginary plane D and part of the second shaft portion 152 extends out from the pin hole 150 H on the other side of the imaginary plane D.
- the swash plate 5 has a pair of connecting portions 5 G that connect the swash plate 5 and a lug arm 49 , which will be described later.
- the connecting portions 5 G are formed at positions in the swash plate 5 that are radially outward of the insertion hole 45 A of the ring plate 45 of the swash plate 5 and adjacent to the top dead center portion T.
- the connecting portions 5 G project frontward from the front surface 5 A of the swash plate 5 and are disposed on opposite sides of the insertion hole 45 A across the imaginary plane D, projecting frontward from the front surface 5 A of the swash plate 5 .
- Each connecting portion 5 G has therethrough a first pin hole 5 H extending perpendicularly to the imaginary plane D.
- a return spring (not shown) is provided between the first flange 43 F and the ring plate 45 .
- the return spring is mounted with the front end thereof set in contact with the first flange 43 F and at the rear end thereof set in contact with the ring plate 45 .
- the return spring urges the first flange 43 F and the ring plate 45 away from each other.
- the link mechanism 7 includes the aforementioned lug arm 49 , a first pin 47 A, and the aforementioned second pin 47 B.
- the lug arm 49 is disposed frontward of the swash plate 5 in the swash plate chamber 33 and positioned between the swash plate 5 and the first support member 43 A.
- the lug arm 49 has a substantially L-shape and has at the rear end thereof a weight 49 A.
- the first pin 47 A is inserted through the rear end of the lug arm 49 with the opposite ends of the first pin 47 A fixedly fitted in the first pin holes 5 H in the respective connecting portions 5 G, thus connecting the rear end of the lug arm 49 and the swash plate 5 .
- the lug arm 49 is supported swingably about a first axis M 1 that extends perpendicularly to the imaginary plane D and corresponds to the axis of the first pin 47 A.
- the front end of the lug arm 49 is connected to the first support member 43 A by the second pin 47 B.
- the lug arm 49 is supported swingably about a second axis M 2 that extends parallel to the first axis M 1 and corresponds to the axis of the second pin 47 B and relative to the first support member 43 A or the drive shaft 3 .
- the weight 49 A is provided forming a rear part of the lug arm 49 . Specifically, the weight 49 A is located on the side of the first axis M 1 that is opposite from the second axis M 2 . With the lug arm 49 connected to the swash plate 5 by the first pin 47 A, the weight 49 A is positioned in the insertion hole 45 A of the swash plate 5 . The centrifugal force caused by the rotation of the swash plate 5 about the axis of rotation O 1 acts on the weight 49 A.
- the swash plate 5 is connected to the drive shaft 3 through the link mechanism 7 , so that the swash plate 5 is rotatable with the drive shaft 3 .
- the swash plate 5 is mounted on the drive shaft 3 for rotation therewith in the swash plate chamber 33 .
- the link mechanism 7 connects the drive shaft 3 and the swash plate 5 and permits changing of the inclination angle of the swash plate 5 relative to the imaginary plane extending perpendicularly to the axis of rotation O 1 of the drive shaft 3 .
- Each second head portion 9 B is reciprocally movably received in the corresponding second cylinder bore 23 A and a second compression chamber 53 B is defined by the second head portion 9 B and the second valve-forming plate 41 in each second cylinder bore 23 A.
- the second head portions 9 B of the pistons 9 are received in the respective second cylinder bores 23 A.
- the positions of the top dead center of the first head portion 9 A and the second head portion 9 B are variable with the change of the stroke length that is caused by the change of the inclination angle of the swash plate 5 .
- the top dead center of the second head portion 9 B moves a longer distance than the first head portion 9 A does as the inclination angle of the swash plate 5 is reduced.
- the actuator 13 is disposed rearward of the swash plate 5 in the swash plate chamber 33 and movable into and out of the second recess 23 C.
- the actuator 13 includes a partitioning body 130 and the aforementioned movable body 13 A and a control chamber 13 B that is formed between the partitioning body 13 C and the movable body 13 A.
- the partitioning body 13 C and the movable body 13 A are made of a metal such as a steel and an aluminum alloy. It is to be noted that the partitioning body 13 C and the movable body 13 A need not be made of a metal, but any suitable material may be used for the partitioning body 13 C and the movable body 13 A.
- the peripheral wall 131 of the movable body 13 A has a cylindrical shape extending frontward from the outer periphery of the bottom wall 130 .
- the inner diameter of the peripheral wall 131 is formed slightly larger than the outer diameter of the partitioning body 13 C.
- the drive shaft body 30 is inserted through the insertion hole 130 A of the movable body 13 A.
- the movable body 13 A is mounted on the drive shaft body 30 for rotation therewith and movable relative to the partitioning body 13 C along the axis of rotation O 1 .
- the first arm 110 , the second arm 120 , the traction portion 150 and the link pin 155 cooperate to form the connecting mechanism 100 that connects the swash plate 5 and the movable body 13 A.
- the first and second arms 110 , 120 extend frontward from the movable body 13 A toward the swash plate 5 .
- the first arm 110 is disposed on one side of the imaginary plane D that is adjacent to the first shaft portion 151 of the link pin 155
- the second arm 120 is disposed on the other side of the imaginary plane D that is adjacent to the second shaft portion 152 of the link pin 155 .
- the traction portion 150 extends rearward from the swash plate 5 toward the movable body 13 A and between the first arm 110 and the second arm 120 .
- the first arm 110 includes a first facing portion 111 and a first engaging portion 116 .
- the second arm 120 includes a second facing portion 121 and the second engaging portion 126 .
- the front ends of the first and second arms 110 , 120 are bent thereby to form the first and second engaging portions 116 , 126 extending toward the imaginary plane D, respectively.
- the first engaging portion 116 is formed extending from the front end of the first facing portion 111 and the second engaging portion 126 extending from the front end of the second facing portion 121 toward the imaginary plane D.
- the first engaging portion 116 and the second engaging portion 126 are disposed in facing relation to each other across the imaginary plane D.
- the first engaging portion 116 of the first arm 110 has a flat first guide surface 115 facing away from the swash plate 5 .
- the second engaging portion 126 of the second arm 120 has a flat second guide surface 125 facing away from the swash plate 5 .
- the first and second guide surfaces 115 , 125 are tilted so that distances from the first and second guide surfaces 115 , 125 to the axis of rotation O 1 increase toward the rear of the compressor.
- the first guide surface 115 of the first arm 110 is in contact with the first shaft portion 151 of the link pin 155
- the second guide surface 125 of the second arm 120 is in contact with the second shaft portion 152 of the link pin 155 , respectively
- the link pin 155 With the link pin 155 held by the traction portion 150 rotatably about the axis R 1 , the link pin 155 is rollable on the first and second guide surfaces 115 , 125 .
- the first facing portion 111 of the first arm 110 faces an end surface 151 E of the first shaft portion 151 of the link pin 155 on one side of the imaginary plane D
- the second facing portion 121 of the second arm 120 faces an end surface 152 E of the second shaft portion 152 of the link pin 155 on the other side of the imaginary plane D, respectively.
- Peripheries of the end surfaces 151 E, 152 E of the respective first and second shaft portions 151 , 152 are chamfered.
- the first and second facing portions 111 , 122 are disposed facing the first and second shaft portions 151 , 152 of the link pin 155 , respectively, so that the movement of the link pin 155 in axial direction of the axis R 1 is restricted.
- the first and second facing portions 111 , 112 correspond to the restrictor of the present invention.
- the first and second shaft portions 151 , 152 of the link pin 155 are movable in a reciprocating manner while rolling on the first guide surface 115 of the first arm 110 and the second guide surface 125 of the second arm 120 , respectively.
- D 1 designates a direction in which the link pin 155 moves on the first and second guide surfaces 115 , 125 with an increase of the inclination angle of the swash plate 5 is increased.
- the moving direction D 1 is directed frontward and inclined toward the axis of rotation O 1 .
- the first and second arms 110 , 120 are opened on the side thereof that is upstream with respect to the moving direction D 1 through which the first and second shaft portions 151 , 152 may be passed to be inserted into the corresponding first and second arms 110 , 120 .
- the second small diameter portion 30 B of the drive shaft body 30 before being press-fitted into the second support member 43 B is inserted through the insertion hole 45 A of the swash plate 5 .
- the swash plate 5 thus having the drive shaft 3 inserted through the insertion hole 45 A thereof is brought close to the lug arm 49 and the weight 49 A of the lug arm 49 is inserted through the insertion hole 45 A of the swash plate 5 .
- the traction portion 150 of the swash plate 5 is located radially outward of and eccentric to the axis of rotation O 1 of the drive shaft 3 .
- the partitioning body 13 C and the movable body 13 A of the actuator 13 are assembled on the drive shaft body 30 from the second small diameter portion 30 B side, and the movable body 13 A is moved frontward toward the swash plate 5 .
- the link pin 155 is inserted through the pin hole 150 H of the traction portion 150 .
- the position of the swash plate 5 is adjusted so that the first and second shaft portions 151 , 152 of the link pin 155 are located radially outward of the first and second guide surfaces 115 , 125 , respectively.
- the swash plate 5 is moved in the moving direction D 1 so that the first and second shaft portions 151 , 152 of the link pin 155 held by the traction portion 150 are placed in contact with the corresponding first and second guide surfaces 115 , 125 of the first and second arms 110 , 120 , respectively.
- the first pin 47 A is inserted through the rear end of the lug arm 49 , the opposite ends of the first pin 47 A are fixedly fitted to the first pin holes 5 H of the connecting portions 5 G, respectively. Accordingly, the swash plate 5 and the movable body 13 A are connected together via the connecting mechanism 100 .
- the first and second facing portions 111 , 121 prevent the link pin 155 from being displaced in the axial direction of the axis R 1 .
- control chamber 13 B that is defined by the bottom wall 130 and the peripheral wall 131 of the movable body 13 A and the partitioning body 13 C is formed in the swash plate chamber 33 .
- the second small diameter portion 30 B of the drive shaft body 30 has therein an axial passage 3 A that extends frontward from the rear end of the drive shaft body 30 along the axis of rotation O and a radial passage 3 B that extends radially from the front end of the axial passage 3 A and is opened at the outer peripheral surface of the drive shaft body 30 .
- the axial passage 3 A is in communication through the rear end thereof with the pressure control chamber 31 and the radial passage 3 B is in communication with the control chamber 13 B.
- the control chamber 13 B and the pressure control chamber 31 communicate with each other through the radial passage 3 B and the axial passage 3 A.
- the control mechanism 15 includes a low-pressure passage 15 A, a high-pressure passage 15 B, a control valve 15 C, an orifice 15 D, the axial passage 3 A and the radial passage 3 B.
- the control mechanism 15 controls the pressure in the control chamber 13 B.
- the control valve 15 C is provided in the low-pressure passage 15 A.
- the control valve 15 C controls the opening of the low-pressure passage 15 A according to the internal pressure of the second suction chamber 27 B.
- the compressor of the present embodiment is connected with the aforementioned evaporator (not shown) through a pipe (not shown) connected to the suction port 23 S.
- the compressor is also connected to the aforementioned condenser (not shown) by a pipe (not shown) through the discharge port 23 D.
- the condenser is connected to the evaporator through the pipe and an expansion valve (neither shown).
- the compressor, the evaporator, the expansion valve and the condenser cooperate to form a refrigeration circuit of the vehicle air conditioner.
- the evaporator, the expansion valve, the condenser and the pipes are omitted from the illustration in the drawings.
- the refrigerant gas discharged into the first discharge chamber 29 A is flowed through the first discharge passage 18 to the junction 23 J.
- the refrigerant gas discharged into the second discharge chamber 29 B is flowed through the second discharge passage 20 to the junction 23 J.
- the refrigerant gas flowed to the junction 23 J is discharged through the discharge port 23 D to the condenser through the pipe.
- the inclination angle of the swash plate 5 relative to the imaginary plane extending perpendicularly to the axis of rotation O 1 of the drive shaft 3 is changed by the actuator 13 , which increases or decreases the stroke length of the piston 9 and hence changes the displacement of the compressor.
- the first and second shaft portions 151 , 152 of the link pin 155 move away from the axis of rotation O 1 while rolling on the first and second guide surfaces 115 , 125 of the first and second arms 110 , 120 , as shown in FIG. 11 .
- the swash plate 5 is swung clockwise about the axis M 1 .
- the lug arm 49 is swung counterclockwise about the second axis M 2 , thus moving the front end of the lug arm 49 close to the first flange 43 F of the first support member 43 A, with the result that the inclination angle of the swash plate 5 is reduced.
- the stroke length of the piston 9 is decreased and the discharge volume per rotation of the drive shaft 3 is decreased accordingly.
- the stroke length of the piston 9 is minimum and the discharge volume per rotation of the drive shaft 3 becomes minimum accordingly.
- the movable body 13 A of the actuator 13 is movable along the axis of rotation O 1 so as to change the inclination angle of the swash plate 5 and in response to a change of pressure in the control chamber 136 of the actuator 13 .
- the link pin 155 is held rotatable about the axis R 1 by the traction portion 150 , as shown in FIGS. 7B, 11 and 12 , with the film of lubrication oil which is contained in the refrigerant gas formed between the outer peripheral surface of the link pin 155 and the inner peripheral surface of the pin hole 150 H.
- the first shaft portion 151 of the link pin 155 is in contact with the first guide surface 115 on the side thereof that is opposite from the swash plate 5 and the second shaft portion 152 of the link pin 155 is in contact with the second guide surface 125 on the side thereof that is opposite from the swash plate 5 .
- the first and second facing portions 111 , 121 functioning as the restrictors face the corresponding end surfaces 151 E, 152 E of the link pin 155 so as to prevent the displacement of the link pin 155 in axial direction of the axis R 1 .
- the first and second shaft portions 151 , 152 are movable in a reciprocating manner and rollable on the first and second guide surfaces 115 , 125 , respectively.
- the end surfaces 151 E, 152 E of the first and second shaft portions 151 , 152 are chamfered.
- the end surfaces 151 E, 152 E of the first and second shaft portions 151 , 152 permits smooth sliding contact of the first and second shaft portions 151 , 152 with the first and second facing portions 111 , 121 , which allows the first and second shaft portions 151 , 152 to rotate smoothly on the first and second guide surfaces 115 , 125 .
- the compressor of the first embodiment permits smooth changing of the inclination angle of the swash plate 5 .
- the compressor provides the improved durability because the first and second shaft portions 151 , 152 and the first and second guide surfaces 115 , 125 are protected against friction wear.
- the first and second facing portions 111 , 121 of the first and second arms 110 , 120 that prevent the displacement of the link pin 155 in the axial direction of the axis R 1 , so that the production cost may be reduced because no additional parts needs to be used.
- the second embodiment differs from the first embodiment in that the movable body 13 A includes a first arm 210 and a second arm 220 , which are shown in FIGS. 14 and 15 , in place of the first and second arms 110 , 120 of the first embodiment.
- a pair of circlips 159 functioning as the restrictor is mounted on the first and second shaft portions 151 , 152 of the link pin 155 .
- the circlips 159 are disposed adjacently to the opposite side surfaces of the traction portion 150 .
- the rest of the configuration of the compressor according to the second embodiment is substantially the same as the first embodiment and, therefore, further detailed description of the second embodiment will be omitted.
- like reference numerals will be used to designate like parts or elements of the first embodiment.
- the first and second arms 220 extend frontward toward the swash plate 5 from the movable body 13 A.
- the first arm 210 is disposed on the side of the movable body 13 A opposite from the imaginary plane D.
- elongated holes 210 H, 220 H are formed through the ends of the first and second arms 210 , 220 , respectively, extending perpendicularly to the imaginary plane D. As shown in FIG. 14 , the elongated holes 210 H and 220 H are elongated in the moving direction D 1 .
- the first and second arms 210 , 220 have flat first and second guide surfaces 215 , 225 on the inner surface of the elongated holes 210 H, 220 H, respectively, facing away from the swash plate 5 and extending in the moving direction D 1 .
- the first guide surface 215 of the first arm 210 is in contact with the first shaft portion 151 of the link pin 155 and the second guide surface 225 of the second arm 220 is in contact with the second shaft portion 152 of the link pin 155 .
- the first and second shaft portions 151 , 152 are reciprocally movable while rolling on the first and second guide surfaces 215 , 216 , respectively.
- the compressor of the second embodiment permits smooth changing the inclination angle of the swash plate 5 , similarly to the compressor of the first embodiment.
- the compressor of the second embodiment achieves improved durability because the first and second shaft portions 151 , 152 and the first and second guide surfaces 215 , 225 are protected against friction wear.
- the pin hole 350 H has a generally hourglass shape with a diameter that is increased axially outward from the middle toward the opposite ends, as shown in FIGS. 16 and 17 .
- Lubrication oil contained in the refrigerant gas forms an oil film between the outer peripheral surface of the link pin 155 and the inner peripheral surface of the pin hole 350 H at the middle portion thereof.
- the link pin 155 is rotatably supported in the pin hole 350 H.
- the pin hole 350 H corresponds to the support hole of the present invention.
- the traction portion 150 of the swash plate 5 supports the link pin 155 rotatably about the axis R 1 while permitting the link pin 155 to be tilted with respect to the direction extending perpendicularly to the imaginary plane D, as indicated by two dashed-dotted lines in FIG. 17 .
- the first and second shaft portions 151 , 152 are reciprocally movable while rolling on the first and second guide surfaces 115 , 125 , respectively. Though shown in FIG. 17 in an exaggerated manner, when the swash plate 5 is disposed in twisted state, or misaligned with respect to the to the axis of rotation O 1 , the relative position between the first and second arms 110 , 120 and the traction portion 150 fails to be maintained.
- the first and second shaft portions 151 , 152 of the link pin 155 and the first and second guide surfaces 115 , 125 are kept in contact by causing the axis R 1 of the link pin 155 to be inclined with respect to the direction perpendicular to the imaginary plane D, so that the pulling force is applied generally evenly to the first and second arms 110 , 120 .
- the end surfaces 151 E, 152 E of the first and second shaft portions 151 , 152 may slide smoothly in contact with the first and second facing portions 111 , 121 , which allows the first and second shaft portions 151 , 152 to roll smoothly on the first and second guide surfaces 115 , 125 .
- the compressor of the third embodiment permits smooth changing of the inclination angle of the swash plate 5 .
- the compressor of the third embodiment achieves improved durability because the first and second shaft portions 151 , 152 and the first and second guide surfaces 115 , 125 are protected against friction wear.
- the present invention is not limited to the above described first, second and third embodiments, but it may be modified in various manners within the scope of the invention, as exemplified below.
- the restrictor is not limited to the first and second facing portions 111 , 121 of the first and second arms 110 , 120 of the first embodiment and the two circlips 159 of the second embodiment, but any restrictor may be used as long as the displacement of the link pin 155 in axial direction thereof is prevented.
- the end surfaces 151 E, 152 E of the first and second shaft portions 151 , 152 in the first embodiment are chamfered and the end surfaces 151 E, 152 E of the first and second shaft portions 151 , 152 in the third embodiment have a hemispherical shape, the end surfaces of the link pin may have a rounded edge.
- the actuator 13 may be disposed on the first cylinder block 21 side in the swash plate chamber 33 with respect to the swash plate 5 .
- the present invention is applicable to an air conditioner or the like.
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Abstract
A variable displacement type swash plate compressor includes a housing having therein a swash plate chamber and a plurality of cylinder bores, a drive shaft, a swash plate, and a link mechanism and a plurality of pistons. The compressor further includes a partitioning body, a movable body, a control chamber, a control mechanism and a connecting mechanism. The connecting mechanism includes first and second arms, a traction portion, and a link pin. The first and second arms have first and second guide surfaces that are placed in contact with the link pin. The link pin is held by the traction portion so as to be rollable on the first and second guide surfaces, respectively. A restrictor is provided on the ling pin or in the first and second arms so as to prevent the link pin from moving in a direction of an axis thereof.
Description
- The present invention relates to a variable displacement type swash plate compressor.
- Japanese Unexamined Patent Application Publication No. 2014-190265 discloses a conventional variable displacement type swash plate compressor (hereinafter simply referred to as compressor). The compressor includes a housing, a drive shaft, a swash plate, a link mechanism and a plurality of pistons. The housing has therein a swash plate chamber and a plurality of cylinder bores. The drive shaft is rotatably supported in the housing. The swash plate is mounted on the drive shaft for rotation therewith in the swash plate chamber. The link mechanism is provided between the drive shaft and the swash plate and permits changing of an inclination angle of the swash plate relative to an imaginary plane extending perpendicularly to the axis of rotation of the drive shaft. Each piston is received in its corresponding cylinder bore and reciprocally movable in the cylinder bore with a stroke length that is determined by the inclination angle of the swash plate thereby to form a compression chamber in the cylinder bore.
- The compressor further includes a partitioning body, a movable body, a control chamber, and a control mechanism. The partitioning body and the movable body are disposed in the swash plate chamber and mounted on the drive shaft for rotation therewith. The movable body is movable relative to the partitioning body in the axial direction of the drive shaft so as to change the inclination angle of the swash plate. The control chamber is defined between the partitioning body and the movable body and causes the movable body to be moved with its internal pressure. The control mechanism controls the pressure in the control chamber.
- The movable body is connected to the swash plate through the link mechanism. Specifically, the link mechanism includes a first arm and a second arm that are provided in the movable body, and a traction portion that is formed in the swash plate. The first and second arms extend toward the swash plate, and the traction portion projects toward the movable body in a space between the first and second arms.
- The first arm has therethrough a circular first hole and the second arm has a circular second hole, respectively. The traction portion includes a pin having one end thereof inserted through the first hole and the other end thereof through the second hole, respectively.
- The movement of the movable body away from the swash plate in the axial direction of the drive shaft by an increased pressure in the control chamber is transmitted through the first and second holes of the first and second arms and the link pin held by the traction portion. As a result, the movable body pulls the swash plate thereby to increase the inclination angle of the swash plate.
- According to the compressor disclosed in the Publication, the relative positional relation between the link pin and the first and second holes remains constant without being affected by the change of the inclination angle of the swash plate. In order to enhance the freedom of setting the pattern of changing of the inclination angle of the swash plate, it may be contemplated, for example, to form the first and second holes into elongated holes and to form a first guide surface that is contactable with the link pin on a side thereof opposite to the swash plate and a second guide surface that is contactable with the link pin on the side thereof opposite to the swash plate so that the link pin is disposed slidably and reciprocally on the first and second guide surfaces with the change of the inclination angle of the swash plate.
- In the compressor having such configuration, however, there is a fear that changing the inclination angle of the swash plate may not take place smoothly because of the friction occurring between the link pin, which is fixed to the traction portion so as to prevent the link pin from falling off from the traction portion, and the first and second guide surface on which the link pin slides.
- The present invention, which has been made in light of the above described problems, is directed to providing a variable displacement type swash plate compressor that permits smooth changing of the inclination angle of the swash plate.
- In accordance with an aspect of the present invention, there is provided a swash plate type variable displacement compressor including a housing having therein a swash plate chamber and a plurality of cylinder bores, a drive shaft rotatably supported in the housing, a swash plate mounted on the drive shaft for rotation therewith in the swash plate chamber, and a link mechanism connecting the drive shaft and the swash plate and permitting changing of an inclination angle of the swash plate with respect to a direction perpendicular to an axis of rotation of the drive shaft. The compressor further includes a plurality of pistons received in the respective cylinder bores so as to form respective compression chamber and reciprocally movable with the rotation of the swash plate for a length of stroke determined by the inclination angle of the swash plate, a partitioning body mounted on the drive shaft for rotation therewith in the swash plate chamber, a movable body that is mounted on the drive shaft for rotation therewith and movable relative to the partitioning body along the axis of rotation in the swash plate chamber to thereby change the inclination angle of the swash plate, a control chamber that is formed between the partitioning body and the movable body, and cause the movable body to move with a pressure in the control chamber, and a control mechanism controlling the pressure in the control chamber, and a connecting mechanism connecting the swash plate and the movable body, so that the movable body pulls the swash plate to increase the inclination angle with an increase of the pressure in the control chamber. The swash plate has a top dead center portion that permits one of the pistons to be located at the top dead center. A plane that passes through the top dead center portion and the rotation axis is defined as an imaginary plane. The connecting mechanism includes a first arm that extends from the movable body toward the swash plate and is disposed on one side of the imaginary plane, a second arm that extends from the movable body toward the swash plate and disposed on the other side of the imaginary plane, a traction portion that is projected from the swash plate toward the movable body between the first arm and the second arm. The first arm has a first guide surface facing away from the swash plate and the second arm has a second guide surface facing away from the swash plate. The first guide surface and the second guide surface are placed in contact with the link pin. The link pin is held by the traction portion so as to be rollable on the first guide surface and the second guide surface. A restrictor is provided on opposite sides of the link pin with respect to the imaginary plane so as to prevent the link pin from moving in a direction of an axis thereof.
- Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
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FIG. 1 is a longitudinal cross-sectional view of a compressor according to a first embodiment of the present invention, showing a state of the compressor at its maximum displacement; -
FIG. 2 is a longitudinal cross-sectional view of the compressor ofFIG. 1 , showing a state of the compressor in its minimum displacement; -
FIG. 3 is a schematic diagram of a control mechanism of the compressor ofFIG. 1 ; -
FIG. 4 is a fragmentary schematic side view of the compressor ofFIG. 1 at its maximum displacement; -
FIG. 5 is a fragmentary schematic side view of the compressor ofFIG. 1 at its minimum displacement; -
FIG. 6 is a fragmentary perspective view of the compressor as viewed in the direction of arrow Z inFIG. 5 ; -
FIG. 7A is a perspective view of a swash plate of the compressor ofFIG. 1 ; -
FIG. 7B is a front view of the swash plate as viewed in the arrow direction of arrow Y inFIG. 7A ; -
FIG. 8 is a perspective view of a movable body of the compressor ofFIG. 1 ; -
FIG. 9 is a perspective view of the movable body as viewed in the direction of arrow Z inFIG. 5 ; -
FIG. 10A is a front view of the movable body; -
FIG. 10B is a side view of the movable body; -
FIG. 11 is a partially enlarged view ofFIG. 10B ; -
FIG. 12 is a fragmentary cross-sectional view of the movable body taken along line XII-XII inFIG. 11 ; -
FIG. 13 is a fragmentary side view of the compressor, illustrating a procedure for assembling a link mechanism, the swash plate and the movable body -
FIG. 14 is a side view of a movable body of a compressor according to a second embodiment of the present invention; -
FIG. 15 is similar toFIG. 12 , but showing a fragmentary cross-sectional view of the movable body taken along line XV-XV inFIG. 14 ; -
FIG. 16 is also similar toFIG. 12 , but showing a fragmentary cross-sectional view of a movable body of a compressor according to a third embodiment of the present invention; and -
FIG. 17 is a fragmentary cross-sectional view of the movable body ofFIG. 16 , showing a state in which the swash plate is misaligned with respect to rotation axis. - The following will describe a variable displacement type swash plate compressor according to first, second and third embodiments of the present invention, respectively, with reference to the accompanying drawings.
- Referring to
FIGS. 1 and 2 , there is shown a variable displacement type swash plate compressor (hereinafter simply referred to as the compressor) according to the first embodiment. The compressor according to the present embodiment employs a double-headed piston. The compressor is mounted on a vehicle and forms a part of a refrigeration circuit of an air conditioner of the vehicle. InFIGS. 1 and 2 , the left side and right side of the drawings will be referred to as the front and rear of the compressor, respectively. - The compressor includes a housing 1, a
drive shaft 3 having an axis of rotation O1 extending in the longitudinal direction of the compressor, aswash plate 5, alink mechanism 7, a plurality ofpistons 9, and anactuator 13. As shown inFIG. 3 , the compressor further includes acontrol mechanism 15. - Referring to
FIGS. 1 and 2 , the housing 1 includes afirst housing member 17, asecond housing member 19, afirst cylinder block 21, asecond cylinder block 23, a first valve-formingplate 39 and a second valve-formingplate 41. - The
first housing member 17 is formed with aboss 17A projecting frontward and having therein ashaft seal device 25. Thefirst housing member 17 has therein an annularfirst suction chamber 27A and an annularfirst discharge chamber 29A. Thefirst suction chamber 27A is located radially inward of thefirst housing member 17, and thefirst discharge chamber 29A is located radially outward of thefirst suction chamber 27A in thefirst housing member 17. - The
first housing member 17 further has therein a firstfront passage 18A. The firstfront passage 18A is in communication at the front end thereof with thefirst discharge chamber 29A and is opened at the rear end thereof to the rear end of thefirst housing member 17. - A part of the
aforementioned control mechanism 15 is formed in thesecond housing member 19. Thesecond housing member 19 has therein an annularsecond suction chamber 27B, an annularsecond discharge chamber 29B, and apressure control chamber 31. Thepressure control chamber 31 is located in the center of thesecond housing member 19. Thesecond suction chamber 27B is located radially outward of thepressure control chamber 31 in thesecond housing member 19. Thesecond discharge chamber 29B is located radially outward of thesecond suction chamber 27B in thesecond housing member 19. - The
second housing member 19 further has therein a firstrear passage 20A. The firstrear passage 20A is in communication at the rear end thereof with thesecond discharge chamber 29B and connected at the front end thereof to the front end of thesecond housing member 19. - The
first cylinder block 21 is disposed on the front side of the compressor between thefirst housing member 17 and thesecond cylinder block 23. Thefirst cylinder block 21 has therein a plurality of first cylinder bores 21A that extends along the axis of rotation O1 of thedrive shaft 3. The first cylinder bores 21A are spaced angularly at a regular interval around thedrive shaft 3. Afirst shaft hole 21B is formed through thefirst cylinder block 21, and thedrive shaft 3 is inserted through thefirst shaft hole 21B. A first slide bearing 22A is provided in thefirst shaft hole 21B. - The
first cylinder block 21 further has at the center thereof afirst recess 21C that is formed coaxially with thefirst shaft hole 21B and communicates with thefirst shaft hole 21B. Thefirst recess 21C has an inner diameter that is larger than that of thefirst shaft hole 21B. A first thrust bearing 35A is provided in thefirst recess 21C. - The
first cylinder block 21 has therein a first connectingpassage 37A and asecond front passage 18B. The front ends of the first connectingpassage 37A and thesecond front passage 18B are opened to the front end of thefirst cylinder block 21 and the rear ends of the first connectingpassage 37A and thesecond front passage 18B are opened to the rear end of thefirst cylinder block 21. - The
second cylinder block 23 is disposed between thefirst cylinder block 21 and thesecond housing member 19 in the rear part of the compressor. Thesecond cylinder block 23 and thefirst cylinder block 21 are connected together thereby to form aswash plate chamber 33 therebetween. Theswash plate chamber 33 is in communication with thefirst recess 21C. Thus, thefirst recess 21C forms a part of theswash plate chamber 33. - The
second cylinder block 23 has therein a plurality of second cylinder bores 23A that extends along the axis of rotation O1 of thedrive shaft 3 and has the same diameter as the first cylinder bores 21A formed in thefirst cylinder block 21. As with case of the first cylinder bores 21A, the second cylinder bores 23A are spaced angularly at a regular interval around thedrive shaft 3 in thesecond cylinder block 23. Each second cylinder bore 23A is paired with its correspondingfirst cylinder bore 21A. Any number of the first and second cylinder bores 21A, 23A may be formed in the housing as long as the first and the second cylinder bores 21A, 23A are provided in pairs. - The
second cylinder block 23 has therein asecond shaft hole 23B through which thedrive shaft 3 is inserted. A second slide bearing 22B is provided in thesecond shaft hole 23B. It is to be noted that the first andsecond slide bearings - In addition, the
second cylinder block 23 has at the center thereof asecond recess 23C that is formed coaxially with thesecond shaft hole 23B and communicates with thesecond shaft hole 23B. Thesecond recess 23C has an inner diameter that is larger than that of thesecond shaft hole 23B. A second thrust bearing 35B is provided in thesecond recess 23C. - The
second cylinder block 23 has adischarge port 23D, ajunction 23J, asuction port 23S, a thirdfront passage 18C, a secondrear passage 20B, and a second connectingpassage 37B. Thedischarge port 23D and thejunction 23J communicate with each other. Thejunction 23J is connected through thedischarge port 23D to a condenser (not shown) that forms the refrigeration circuit of the vehicle air conditioner. Thesuction port 23S and theswash plate chamber 33 are in communication with each other. Theswash plate chamber 33 is connected to an evaporator (not shown) that forms the refrigeration circuit of the vehicle air conditioner through thesuction port 23S. - The third
front passage 18C is in communication at the rear end thereof with thejunction 23J and is opened at the front end thereof to the front end of thesecond cylinder block 23 to be in communication with thesecond front passage 18B. The secondrear passage 20B is in communication at the front end thereof with thejunction 23J and is opened at the rear end thereof to the rear end of thesecond cylinder block 23. The second connectingpassage 37B is opened at the front end thereof to theswash plate chamber 33 and at the rear end thereof to the rear end of thesecond cylinder block 23. - The
first housing member 17 and thefirst cylinder block 21 are joined together with the first valve-formingplate 39 interposed therebetween. Thesecond housing member 19 and thesecond cylinder block 23 are joined together with the second valve-formingplate 41 interposed therebetween. - The first valve-forming
plate 39 includes afirst valve plate 390, a firstsuction valve plate 391, a firstdischarge valve plate 392, and afirst retainer plate 393. Thefirst valve plate 390 and the firstsuction valve plate 391 extend radially to the outer peripheries of thefirst housing member 17 and thefirst cylinder block 21. Thefirst valve plate 390, the firstdischarge valve plate 392, and thefirst retainer plate 393 have therethrough afirst suction hole 390A for each of the first cylinder bores 21A. Thefirst valve plate 390 and the firstsuction valve plate 391 have therethrough afirst discharge hole 390B for each of the first cylinder bores 21A. In addition, thefirst valve plate 390, the firstsuction valve plate 391, the firstdischarge valve plate 392, and thefirst retainer plate 393 have therethrough a firstsuction communication hole 390C. Thefirst valve plate 390 and the firstsuction valve plate 391 have therethrough a firstdischarge communication hole 390D. - Each
first cylinder bore 21A is communicable with thefirst suction chamber 27A through thefirst suction hole 390A and is communicable also with thefirst discharge chamber 29A through thefirst discharge hole 390B. Thefirst suction chamber 27A and the first connectingpassage 37A are in communication with each other through the firstsuction communication hole 390C. The firstfront passage 18A and thesecond front passage 18B are in communication with each other through the firstdischarge communication hole 390D. - The first
suction valve plate 391 is provided on the rear surface of thefirst valve plate 390. The firstsuction valve plate 391 has a firstsuction reed valve 391A for each of thefirst suction holes 390A to open and close its correspondingfirst suction hole 390A by elastic deformation. The firstdischarge valve plate 392 is provided on the front surface of thefirst valve plate 390. The firstdischarge valve plate 392 has a firstdischarge reed valve 392A for each of the first discharge holes 390B to open and close its correspondingfirst discharge hole 390B by elastic deformation. Thefirst retainer plate 393 is provided on the front surface of the firstdischarge valve plate 392 and restricts the opening of the firstdischarge reed valve 392A. - The second valve-forming
plate 41 includes asecond valve plate 410, a secondsuction valve plate 411, a seconddischarge valve plate 412, and asecond retainer plate 413. Thesecond valve plate 410 and the secondsuction valve plate 411 extend radially to the outer peripheries of thesecond housing member 19 and thesecond cylinder block 23. Thesecond valve plate 410, the seconddischarge valve plate 412, and thesecond retainer plate 413 have therethrough asecond suction hole 410A for each of the second cylinder bores 23A. Thesecond valve plate 410 and the secondsuction valve plate 411 have therethrough asecond discharge hole 410B for each of the second cylinder bores 23A. In addition, thesecond valve plate 410, the secondsuction valve plate 411, the seconddischarge valve plate 412, and thesecond retainer plate 413 have therethrough a secondsuction communication hole 410C. Thesecond valve plate 410 and the secondsuction valve plate 411 have therethrough a seconddischarge communication hole 410D. - Each second cylinder bore 23A is communicable with the
second suction chamber 27B through thesecond suction hole 410A and is communicable also with thesecond discharge chamber 29B through thesecond discharge hole 410B. Thesecond suction chamber 27B and the second connectingpassage 37B are in communication with each other through the secondsuction communication hole 410C. The firstrear passage 20A and the secondrear passage 20B are in communication with each other through the seconddischarge communication hole 410D. - The second
suction valve plate 411 is provided on the front surface of thesecond valve plate 410. The secondsuction valve plate 411 has a secondsuction reed valve 411A for each of the second suction holes 410A to open and close its correspondingsecond suction hole 410A by elastic deformation. The seconddischarge valve plate 412 is provided on the rear surface of thesecond valve plate 410. The seconddischarge valve plate 412 has a seconddischarge reed valve 412A for each of the second discharge holes 410B to open and close its correspondingsecond discharge hole 410B by elastic deformation. Thesecond retainer plate 413 is provided on the rear surface of the seconddischarge valve plate 412 and restricts the opening of the seconddischarge reed valve 412A. - In the compressor, the first
front passage 18A, the firstdischarge communication hole 390D, thesecond front passage 18B, and the thirdfront passage 18C cooperate to form afirst discharge passage 18. The firstrear passage 20A, the seconddischarge communication hole 410D and the secondrear passage 20B cooperate to form asecond discharge passage 20. - The
first suction chamber 27A is in communication with theswash plate chamber 33 through the first connectingpassage 37A and the firstsuction communication hole 390C, and thesecond suction chamber 27B is in communication with theswash plate chamber 33 via the second connectingpassage 37B and the secondsuction communication hole 410C, so that the pressures in the first andsecond suction chambers swash plate chamber 33. - The
drive shaft 3 includes adrive shaft body 30, afirst support member 43A and asecond support member 43B. - The
drive shaft body 30 extends along the axis of rotation O1 in the housing 1. Thedrive shaft body 30 has at the front end thereof a firstsmall diameter portion 30A and at the rear end thereof a secondsmall diameter portion 30B. - The
drive shaft body 30 is inserted through theshaft seal device 25, the first andsecond slide bearings drive shaft body 30 and hence thedrive shaft 3 is supported rotatably about the axis of rotation O1 in the housing 1. The front end of thedrive shaft body 30 of thedrive shaft 3 is inserted through theshaft seal device 25 in theboss 17A and the rear end of thedrive shaft body 30 of thedrive shaft 3 extends into thepressure control chamber 31. - The
drive shaft body 30 has mounted thereon theswash plate 5, thelink mechanism 7, and theactuator 13 that are disposed in theswash plate chamber 33. - The
drive shaft body 30 has at the front end thereof a threadedportion 3E. Thedrive shaft 3 is connected to a pulley or an electromagnetic clutch (neither shown) through the threadedportion 3E. - The
first support member 43A has a substantially cylindrical shape extending along the axis of rotation O1. Thefirst support member 43A is press-fitted on the firstsmall diameter portion 30A of thedrive shaft body 30 to be integrated therewith. Thefirst support member 43A is supported by the first slide bearing 22A in thefirst shaft hole 21B. Thefirst support member 43A has at the rear end thereof afirst flange 43F and amount portion 43D through which asecond pin 47B, which will be described later, is inserted. - The first thrust bearing 35A is held between the
first flange 43F and the bottom surface of thefirst recess 21C in the axial direction of thedrive shaft 3, with a predetermined preload applied to the first thrust bearing 35A. With this arrangement, a thrust force acting on thedrive shaft 3 during the operation of the compressor is supported by the first thrust bearing 35A. - The
second support member 43B has a substantially cylindrical shape extending along the axis of rotation O1. Thesecond support member 43B is press-fitted on the secondsmall diameter portion 30B of thedrive shaft body 30 to be integrated therewith. Thesecond support member 43B is supported by the second slide bearing 22B in thesecond shaft hole 23B. Thesecond support member 43B has at the front end thereof asecond flange 43G. - The second thrust bearing 35B is held between the
second flange 43G and the bottom surface of thesecond recess 23C in the axial direction of thedrive shaft 3 with a predetermined preload applied to the second thrust bearing 35B. With this arrangement, a thrust force acting on thedrive shaft body 30 during the operation of the compressor is supported by the second thrust bearing 35B. - As shown in
FIGS. 1, 2, 4 through 7A and 7B , theswash plate 5 has a substantially disk shape having afront surface 5A and arear surface 5B. Theswash plate 5 is disposed in theswash plate chamber 33 with thefront surface 5A and therear surfaces 5B thereof facing frontward and rearward of the compressor, respectively. As shown inFIGS. 1 and 2 showing theswash plate 5 in its minimum and maximum positions, respectively, theswash plate 5 is tiltable with respect to a direction perpendicular to the axis of rotation O1. - Referring to
FIG. 7B , symbol T designates a top dead center portion which is a point or portion in theswash plate 5 where theswash plate 5 positions afirst head portion 9A of thepiston 9 at the top dead center thereof, as shown inFIG. 1 , and symbol U designates a bottom dead center portion which is a point or portion of theswash plate 5 where theswash plate 5 positions thefirst head portion 9A of thepiston 9 at the bottom dead center thereof, respectively. Since the compressor of the present embodiment is of a double-headed piston type, theswash plate 5 positions thesecond head portion 9B of thepiston 9 at the bottom dead center thereof when thesecond head portion 9B is positioned at the top dead center. Symbol D inFIG. 7B designates an imaginary plane that passes through the point T of theswash plate 5 and the axis of rotation O1 of thedrive shaft 3. - As shown in
FIGS. 1, 2, 6, 7A and 7B , theswash plate 5 has aring plate 45 having an annular shape. As shown inFIG. 7A , the part of theswash plate 5 that is radially inward of thering plate 45 is partially projected or recessed in a direction of the axis of rotation O1 so as to adjust the weight balance of theswash plate 5 and to avoid the interference with afirst arm 110 and asecond arm 120, which will be described later. - As shown in
FIGS. 7A and 7B , aninsertion hole 45A is formed through theswash plate 5 in the axial direction of the axis of rotation O1. Theinsertion hole 45A has a substantially rectangular shape formed so as to have therein the axis of rotation O1 and extending toward the top dead center portion T. As shown inFIGS. 1 and 2 , theswash plate 5 is mounted on thedrive shaft 3 in theswash plate chamber 33 with thedrive shaft body 30 inserted through theinsertion hole 45A of thering plate 45 of theswash plate 5. - As shown in
FIGS. 1, 2, and 4 to 7B , theswash plate 5 has atraction portion 150 and alink pin 155 that form a connectingmechanism 100. The connectingmechanism 100 connects theswash plate 5 to amovable body 13A, which will be described later. As shown inFIGS. 7A and 7B , thetraction portion 150 is formed at a position in theswash plate 5 radially inward of thering plate 45 and is closer to the bottom dead center portion U than theinsertion hole 45A is, and projects rearward from therear surface 5B of theswash plate 5. Apin hole 150H having the axis R1 extending perpendicular to the imaginary plane D is formed through thetraction portion 150. Thelink pin 155 is inserted through thepin hole 150H. - As shown in
FIGS. 6 and 7B , thelink pin 155 is supported rotatable about the axis R1 by thetraction portion 150. Thelink pin 155 has a shape of circular column extending radially from the axis R1. According to the present embodiment, thelink pin 155 is made of a metal such as steel and aluminum alloy, but any suitable material may be used for thelink pin 155. The outer diameter of thelink pin 155 is formed just smaller than the inner diameter of thepin hole 150H to such an extent that lubricant oil included in a refrigerant gas forms an oil film between the outer peripheral surface of thelink pin 155 and the inner peripheral surface of thepin hole 150H, which significantly reduces the friction between thelink pin 155 and thepin hole 150H during the rolling of thelink pin 155 about the axis R1. - The
link pin 155 has at one end thereof afirst shaft portion 151 and at the other end thereof asecond shaft portion 152. Part of thefirst shaft portion 151 extends out from thepin hole 150H of thetraction portion 150 on one side of the imaginary plane D and part of thesecond shaft portion 152 extends out from thepin hole 150H on the other side of the imaginary plane D. - As shown in
FIGS. 4, 5, 7A and 7B , theswash plate 5 has a pair of connectingportions 5G that connect theswash plate 5 and alug arm 49, which will be described later. As shown inFIGS. 7A and 7B , the connectingportions 5G are formed at positions in theswash plate 5 that are radially outward of theinsertion hole 45A of thering plate 45 of theswash plate 5 and adjacent to the top dead center portion T. The connectingportions 5G project frontward from thefront surface 5A of theswash plate 5 and are disposed on opposite sides of theinsertion hole 45A across the imaginary plane D, projecting frontward from thefront surface 5A of theswash plate 5. Each connectingportion 5G has therethrough afirst pin hole 5H extending perpendicularly to the imaginary plane D. - Referring to
FIGS. 1 and 2 , a return spring (not shown) is provided between thefirst flange 43F and thering plate 45. Specifically, the return spring is mounted with the front end thereof set in contact with thefirst flange 43F and at the rear end thereof set in contact with thering plate 45. The return spring urges thefirst flange 43F and thering plate 45 away from each other. - As shown in
FIGS. 1, 2, 4 and 5 , thelink mechanism 7 includes theaforementioned lug arm 49, afirst pin 47A, and the aforementionedsecond pin 47B. - Referring to
FIGS. 1 and 2 , thelug arm 49 is disposed frontward of theswash plate 5 in theswash plate chamber 33 and positioned between theswash plate 5 and thefirst support member 43A. Thelug arm 49 has a substantially L-shape and has at the rear end thereof aweight 49A. - The
first pin 47A is inserted through the rear end of thelug arm 49 with the opposite ends of thefirst pin 47A fixedly fitted in thefirst pin holes 5H in the respective connectingportions 5G, thus connecting the rear end of thelug arm 49 and theswash plate 5. Thelug arm 49 is supported swingably about a first axis M1 that extends perpendicularly to the imaginary plane D and corresponds to the axis of thefirst pin 47A. - The front end of the
lug arm 49 is connected to thefirst support member 43A by thesecond pin 47B. Thus, thelug arm 49 is supported swingably about a second axis M2 that extends parallel to the first axis M1 and corresponds to the axis of thesecond pin 47B and relative to thefirst support member 43A or thedrive shaft 3. - The
weight 49A is provided forming a rear part of thelug arm 49. Specifically, theweight 49A is located on the side of the first axis M1 that is opposite from the second axis M2. With thelug arm 49 connected to theswash plate 5 by thefirst pin 47A, theweight 49A is positioned in theinsertion hole 45A of theswash plate 5. The centrifugal force caused by the rotation of theswash plate 5 about the axis of rotation O1 acts on theweight 49A. - In the compressor of the present embodiment, the
swash plate 5 is connected to thedrive shaft 3 through thelink mechanism 7, so that theswash plate 5 is rotatable with thedrive shaft 3. In other words, theswash plate 5 is mounted on thedrive shaft 3 for rotation therewith in theswash plate chamber 33. With the swinging movement of the opposite ends of thelug arm 49 about the first axis M1 and the second axis M2, respectively, the inclination angle of theswash plate 5 with respect to an imaginary plane extending perpendicularly to the axis O1 is variable between the maximum inclination angle shown inFIGS. 1 and 4 and the minimum inclination angle shown inFIGS. 2, 5 and 6 . In other words, thelink mechanism 7 connects thedrive shaft 3 and theswash plate 5 and permits changing of the inclination angle of theswash plate 5 relative to the imaginary plane extending perpendicularly to the axis of rotation O1 of thedrive shaft 3. - As shown in
FIGS. 1 and 2 , thepistons 9 are double-headed pistons each having at the front end thereof thefirst head portion 9A and at the rear end thereof thesecond head portion 9B. Eachfirst head portion 9A is reciprocally movably received in the correspondingfirst cylinder bore 21A and afirst compression chamber 53A is defined by thefirst head portion 9A and the first valve-formingplate 39 in eachfirst cylinder bore 21A. In other words, thefirst head portions 9A of thepistons 9 are received in the respective first cylinder bores 21A so as to form thefirst compression chambers 53A. Eachsecond head portion 9B is reciprocally movably received in the correspondingsecond cylinder bore 23A and asecond compression chamber 53B is defined by thesecond head portion 9B and the second valve-formingplate 41 in each second cylinder bore 23A. In other words, thesecond head portions 9B of thepistons 9 are received in the respective second cylinder bores 23A. - Each
piston 9 has at the center thereof an engagingportion 9C to receive therein a pair ofhemispherical shoes shoe 11A and theshoe 11B slide on thefront surface 5A and therear surface 5B of theswash plate 5, respectively. The rotation of theswash plate 5 is converted into the reciprocal motion of thepiston 9 by way of theshoes first head portion 9A and thesecond head portion 9B of thepiston 9 are reciprocally movable by the rotation of theswash plate 5 in their corresponding first cylinder bore 21A and the second cylinder bore 23A, respectively, for a stroke length that is determined by the inclination angle of theswash plate 5. - In this compressor, the positions of the top dead center of the
first head portion 9A and thesecond head portion 9B are variable with the change of the stroke length that is caused by the change of the inclination angle of theswash plate 5. Specifically, the top dead center of thesecond head portion 9B moves a longer distance than thefirst head portion 9A does as the inclination angle of theswash plate 5 is reduced. - The
actuator 13 is disposed rearward of theswash plate 5 in theswash plate chamber 33 and movable into and out of thesecond recess 23C. Theactuator 13 includes apartitioning body 130 and the aforementionedmovable body 13A and acontrol chamber 13B that is formed between thepartitioning body 13C and themovable body 13A. In the present embodiment, thepartitioning body 13C and themovable body 13A are made of a metal such as a steel and an aluminum alloy. It is to be noted that thepartitioning body 13C and themovable body 13A need not be made of a metal, but any suitable material may be used for thepartitioning body 13C and themovable body 13A. - The
partitioning body 13C has a substantially annular disk shape extending radially outwardly from the axis of rotation O1 and has at the center thereof aninsertion hole 133. An O-ring 139B is provided in the outer periphery of thepartitioning body 13C. Thedrive shaft body 30 is press-fitted into theinsertion hole 133 of thepartitioning body 13C, so that thedrive shaft body 30 is rotatable with thepartitioning body 13C facing theswash plate 5 from behind thereof. It is to be noted that thepartitioning body 13C may be mounted on thedrive shaft body 30 so as to be movable along the axis of rotation O1. - A spring (not shown) is provided between the
partitioning body 13C and thering plate 45, acting so as to reduce the inclination angle of theswash plate 5. Specifically, the spring is mounted with the rear end thereof set in contact with thepartitioning body 13C and the front end thereof set in contact with thering plate 45. The spring urges thepartitioning body 13C and thering plate 45 away from each other. - As shown in
FIGS. 1, 2, 4 to 6, and 8 to 12 , themovable body 13A includes abottom wall 130, aperipheral wall 131, thefirst arm 110, and thesecond arm 120. Although thefirst arm 110 is not shown inFIGS. 1, 2, and 10B , thefirst arm 110 is disposed on the side of the imaginary plane D that is opposite to thesecond arm 120. - As shown in
FIGS. 1, 2, 6 and 9 , thebottom wall 130 forms the rear part of themovable body 13A and has a substantially disk shape extending radially outwardly. Thebottom wall 130 has aninsertion hole 130A through which the secondsmall diameter portion 30B of thedrive shaft body 30 is inserted. As shown inFIGS. 1 and 2 , an O-ring 139A is provided in the inner periphery of thebottom wall 130. - As shown in
FIGS. 1, 2, 8 and 9 , theperipheral wall 131 of themovable body 13A has a cylindrical shape extending frontward from the outer periphery of thebottom wall 130. The inner diameter of theperipheral wall 131 is formed slightly larger than the outer diameter of thepartitioning body 13C. - As shown in
FIGS. 1, 2 and 6 , thedrive shaft body 30 is inserted through theinsertion hole 130A of themovable body 13A. Thus, themovable body 13A is mounted on thedrive shaft body 30 for rotation therewith and movable relative to thepartitioning body 13C along the axis of rotation O1. - As shown in
FIGS. 1 and 2 , thepartitioning body 13C is disposed in themovable body 13A in such a manner that themovable body 13A is circumferentially surrounded by theperipheral wall 131 of themovable body 13A. The O-ring 139B is provided in the outer periphery of thepartitioning body 13C to seal between thepartitioning body 13C and themovable body 13A. As themovable body 13A moves along the axis of rotation O1, the inner peripheral surface of theperipheral wall 131 of themovable body 13A slides on the outer peripheral surface of thepartitioning body 13C. - As shown in
FIGS. 1, 2, 4 to 6 and 8 to 12 , thefirst arm 110, thesecond arm 120, thetraction portion 150 and thelink pin 155 cooperate to form the connectingmechanism 100 that connects theswash plate 5 and themovable body 13A. - The first and
second arms movable body 13A toward theswash plate 5. As shown inFIGS. 9, 10A and 12 , thefirst arm 110 is disposed on one side of the imaginary plane D that is adjacent to thefirst shaft portion 151 of thelink pin 155, and thesecond arm 120 is disposed on the other side of the imaginary plane D that is adjacent to thesecond shaft portion 152 of thelink pin 155. As shown inFIG. 6 , thetraction portion 150 extends rearward from theswash plate 5 toward themovable body 13A and between thefirst arm 110 and thesecond arm 120. - As, shown in
FIGS. 8 to 12 , thefirst arm 110 includes a first facingportion 111 and a firstengaging portion 116. Similarly, thesecond arm 120 includes a second facingportion 121 and the secondengaging portion 126. - The rear ends of the first and second facing
portions movable body 13A at positions that are closer to the bottom dead center portion U than to the axis of rotation O1. The distances from the front end of the first and second facingportions portions - As shown in
FIGS. 8 through 12 , the front ends of the first andsecond arms portions portion 116 is formed extending from the front end of the first facingportion 111 and the secondengaging portion 126 extending from the front end of the second facingportion 121 toward the imaginary plane D. As shown inFIGS. 9 and 12 , the first engagingportion 116 and the secondengaging portion 126 are disposed in facing relation to each other across the imaginary plane D. - As shown in
FIGS. 8 through 12 , the first engagingportion 116 of thefirst arm 110 has a flatfirst guide surface 115 facing away from theswash plate 5. The secondengaging portion 126 of thesecond arm 120 has a flatsecond guide surface 125 facing away from theswash plate 5. The first and second guide surfaces 115, 125 are tilted so that distances from the first and second guide surfaces 115, 125 to the axis of rotation O1 increase toward the rear of the compressor. - As shown in
FIGS. 1, 2, 4 through 6, 11 and 12 , thefirst guide surface 115 of thefirst arm 110 is in contact with thefirst shaft portion 151 of thelink pin 155, and thesecond guide surface 125 of thesecond arm 120 is in contact with thesecond shaft portion 152 of thelink pin 155, respectively With thelink pin 155 held by thetraction portion 150 rotatably about the axis R1, thelink pin 155 is rollable on the first and second guide surfaces 115, 125. - As shown, for example, in
FIGS. 6 and 12 , the first facingportion 111 of thefirst arm 110 faces anend surface 151E of thefirst shaft portion 151 of thelink pin 155 on one side of the imaginary plane D, and the second facingportion 121 of thesecond arm 120 faces anend surface 152E of thesecond shaft portion 152 of thelink pin 155 on the other side of the imaginary plane D, respectively. Peripheries of the end surfaces 151E, 152E of the respective first andsecond shaft portions - The first and second facing
portions 111, 122 are disposed facing the first andsecond shaft portions link pin 155, respectively, so that the movement of thelink pin 155 in axial direction of the axis R1 is restricted. The first and second facingportions 111, 112 correspond to the restrictor of the present invention. - With a change in the inclination angle of the
swash plate 5, the first andsecond shaft portions link pin 155 are movable in a reciprocating manner while rolling on thefirst guide surface 115 of thefirst arm 110 and thesecond guide surface 125 of thesecond arm 120, respectively. Referring toFIG. 11 , for example, D1 designates a direction in which thelink pin 155 moves on the first and second guide surfaces 115, 125 with an increase of the inclination angle of theswash plate 5 is increased. The moving direction D1 is directed frontward and inclined toward the axis of rotation O1. - As shown in
FIGS. 6, 8 through 11 , the first andsecond arms second shaft portions second arms - The following will describe the assembling procedure of the
swash plate 5 and themovable body 13A through the connectingmechanism 100. Firstly, thefirst support member 43A of thedrive shaft 3 and the front end of thelug arm 49 are connected together by thesecond pin 47B, as shown inFIG. 13 . - Then, the second
small diameter portion 30B of thedrive shaft body 30 before being press-fitted into thesecond support member 43B is inserted through theinsertion hole 45A of theswash plate 5. Theswash plate 5 thus having thedrive shaft 3 inserted through theinsertion hole 45A thereof is brought close to thelug arm 49 and theweight 49A of thelug arm 49 is inserted through theinsertion hole 45A of theswash plate 5. At this time, thetraction portion 150 of theswash plate 5 is located radially outward of and eccentric to the axis of rotation O1 of thedrive shaft 3. - Subsequently, the
partitioning body 13C and themovable body 13A of theactuator 13 are assembled on thedrive shaft body 30 from the secondsmall diameter portion 30B side, and themovable body 13A is moved frontward toward theswash plate 5. Then, thelink pin 155 is inserted through thepin hole 150H of thetraction portion 150. The position of theswash plate 5 is adjusted so that the first andsecond shaft portions link pin 155 are located radially outward of the first and second guide surfaces 115, 125, respectively. - The
swash plate 5 is moved in the moving direction D1 so that the first andsecond shaft portions link pin 155 held by thetraction portion 150 are placed in contact with the corresponding first and second guide surfaces 115, 125 of the first andsecond arms first pin 47A is inserted through the rear end of thelug arm 49, the opposite ends of thefirst pin 47A are fixedly fitted to thefirst pin holes 5H of the connectingportions 5G, respectively. Accordingly, theswash plate 5 and themovable body 13A are connected together via the connectingmechanism 100. The first and second facingportions link pin 155 from being displaced in the axial direction of the axis R1. - As shown in
FIGS. 1 and 2 , thecontrol chamber 13B that is defined by thebottom wall 130 and theperipheral wall 131 of themovable body 13A and thepartitioning body 13C is formed in theswash plate chamber 33. - The second
small diameter portion 30B of thedrive shaft body 30 has therein anaxial passage 3A that extends frontward from the rear end of thedrive shaft body 30 along the axis of rotation O and aradial passage 3B that extends radially from the front end of theaxial passage 3A and is opened at the outer peripheral surface of thedrive shaft body 30. Theaxial passage 3A is in communication through the rear end thereof with thepressure control chamber 31 and theradial passage 3B is in communication with thecontrol chamber 13B. Thus, thecontrol chamber 13B and thepressure control chamber 31 communicate with each other through theradial passage 3B and theaxial passage 3A. - As shown in
FIG. 3 , thecontrol mechanism 15 includes a low-pressure passage 15A, a high-pressure passage 15B, acontrol valve 15C, anorifice 15D, theaxial passage 3A and theradial passage 3B. Thecontrol mechanism 15 controls the pressure in thecontrol chamber 13B. - The low-
pressure passage 15A is connected to thepressure control chamber 31 and thesecond suction chamber 27B. Thecontrol chamber 13B, thepressure control chamber 31 and thesecond suction chamber 27B are connected through the low-pressure passage 15A, theaxial passage 3A and theradial passage 3B. The high-pressure passage 15B is connected between thepressure control chamber 31 and thesecond discharge chamber 29B. Thecontrol chamber 13B, thepressure control chamber 31 and thesecond discharge chamber 29B are connected through the high-pressure passage 15B, theaxial passage 3A and theradial passage 3B. The high-pressure passage 15B is provided with theorifice 15D. - The
control valve 15C is provided in the low-pressure passage 15A. Thecontrol valve 15C controls the opening of the low-pressure passage 15A according to the internal pressure of thesecond suction chamber 27B. - The compressor of the present embodiment is connected with the aforementioned evaporator (not shown) through a pipe (not shown) connected to the
suction port 23S. The compressor is also connected to the aforementioned condenser (not shown) by a pipe (not shown) through thedischarge port 23D. The condenser is connected to the evaporator through the pipe and an expansion valve (neither shown). The compressor, the evaporator, the expansion valve and the condenser cooperate to form a refrigeration circuit of the vehicle air conditioner. The evaporator, the expansion valve, the condenser and the pipes are omitted from the illustration in the drawings. - In the compressor having the above-described configuration, the rotation of the
swash plate 5 driven by thedrive shaft 3 causes eachpiston 9 to reciprocate in the respective first and second cylinder bores 21A, 23A. The refrigerant gas introduced into the first andsecond suction chambers second compression chambers second discharge chambers second compression chambers piston 9. - The refrigerant gas discharged into the
first discharge chamber 29A is flowed through thefirst discharge passage 18 to thejunction 23J. Similarly, the refrigerant gas discharged into thesecond discharge chamber 29B is flowed through thesecond discharge passage 20 to thejunction 23J. The refrigerant gas flowed to thejunction 23J is discharged through thedischarge port 23D to the condenser through the pipe. - The following will describe the operation of the compressor. In the compressor of the present embodiment, the inclination angle of the
swash plate 5 relative to the imaginary plane extending perpendicularly to the axis of rotation O1 of thedrive shaft 3 is changed by theactuator 13, which increases or decreases the stroke length of thepiston 9 and hence changes the displacement of the compressor. - Firstly, the operation of the compressor in increasing the inclination angle of the
swash plate 5 to its maximum position shown inFIG. 1 will be described. In thecontrol mechanism 15 shown inFIG. 3 , when the opening of the low-pressure passage 15A is reduced by thecontrol valve 15C, the pressure in thepressure control chamber 31 is increased due to the pressure of the refrigerant gas in thesecond discharge chamber 29B, and the pressure in thecontrol chamber 13B is increased accordingly. As a result, the variable pressure difference between thecontrol chamber 13B and theswash plate chamber 33 is increased. Accordingly, themovable body 13A of theactuator 13 is moved rearward from the position shown inFIG. 2 against the compression reaction force acting on theswash plate 5 through eachpiston 9 and enters into thesecond recess 23C, as shown inFIG. 1 . - This causes the
movable body 13A to pull theswash plate 5 rearward in theswash plate chamber 33 through the first and second guide surfaces 115, 125 of the first andsecond arms second shaft portions link pin 155, against the urging force of the spring (not shown) for reducing the inclination angle of theswash plate 5. In this case, the first andsecond shaft portions swash plate 5 swings counterclockwise about the first axis M1 as seen inFIGS. 1 and 2 , and the front end of thelug arm 49 swings clockwise about the second axis M2 to move away from thefirst flange 43F of thefirst support member 43A. As a result, the inclination angle of theswash plate 5 is increased thereby to increase the stroke length of thepiston 9, and the displacement of the compressor per rotation of thedrive shaft 3 is increased. When the inclination angle of theswash plate 5 is maximum, as shown inFIG. 1 , the stroke of thepistons 9 is maximum and the displacement of the compressor is maximum. - The operation of the compressor in decreasing the inclination angle of the
swash plate 5 from the maximum position (FIG. 1 ) to the minimum position (FIG. 2 ) will be described. In thecontrol mechanism 15 inFIG. 3 , when the opening of the low-pressure passage 15A is increased by thecontrol valve 15C, the pressure in thepressure control chamber 31 and hence the pressure in thecontrol chamber 13B becomes substantially the same as the pressure in thesecond suction chamber 27B, with the result that the pressure difference between thecontrol chamber 13B and theswash plate chamber 33 becomes small. - The compression reaction force acting on the
swash plate 5 through eachpiston 9 urges theswash plate 5 in the direction that reduces the inclination angle of theswash plate 5. Accordingly, themovable body 13A is pulled or moved frontward in theswash plate chamber 33 through the first and second guide surfaces 115, 125 of the first andsecond arms second shaft portions link pin 155, resisting the urging force of the return spring. During such movement of themovable body 13A, the first andsecond shaft portions link pin 155 move away from the axis of rotation O1 while rolling on the first and second guide surfaces 115, 125 of the first andsecond arms FIG. 11 . As a result, theswash plate 5 is swung clockwise about the axis M1. In addition, thelug arm 49 is swung counterclockwise about the second axis M2, thus moving the front end of thelug arm 49 close to thefirst flange 43F of thefirst support member 43A, with the result that the inclination angle of theswash plate 5 is reduced. With the reduction of the inclination angle of theswash plate 5, the stroke length of thepiston 9 is decreased and the discharge volume per rotation of thedrive shaft 3 is decreased accordingly. When the inclination angle of theswash plate 5 is minimum, the stroke length of thepiston 9 is minimum and the discharge volume per rotation of thedrive shaft 3 becomes minimum accordingly. In other words, themovable body 13A of theactuator 13 is movable along the axis of rotation O1 so as to change the inclination angle of theswash plate 5 and in response to a change of pressure in the control chamber 136 of theactuator 13. - According to the compressor of the first embodiment, the
link pin 155 is held rotatable about the axis R1 by thetraction portion 150, as shown inFIGS. 7B, 11 and 12 , with the film of lubrication oil which is contained in the refrigerant gas formed between the outer peripheral surface of thelink pin 155 and the inner peripheral surface of thepin hole 150H. Thefirst shaft portion 151 of thelink pin 155 is in contact with thefirst guide surface 115 on the side thereof that is opposite from theswash plate 5 and thesecond shaft portion 152 of thelink pin 155 is in contact with thesecond guide surface 125 on the side thereof that is opposite from theswash plate 5. The first and second facingportions link pin 155 so as to prevent the displacement of thelink pin 155 in axial direction of the axis R1. In the compressor having this configuration, the first andsecond shaft portions second shaft portions link pin 155 on the first and second guide surfaces 115, 152 reduces the friction therebetween effectively and, as compared with the case in which thelink pin 155 is fixed to thetraction portion 150 and the first andsecond shaft portions - In addition, the end surfaces 151E, 152E of the first and
second shaft portions second shaft portions second shaft portions portions second shaft portions - Therefore, the compressor of the first embodiment permits smooth changing of the inclination angle of the
swash plate 5. In addition, the compressor provides the improved durability because the first andsecond shaft portions - In the compressor of the present embodiment, the first and second facing
portions second arms link pin 155 in the axial direction of the axis R1, so that the production cost may be reduced because no additional parts needs to be used. - The following will describe a second embodiment of the present invention with reference to
FIGS. 14 and 15 . The second embodiment differs from the first embodiment in that themovable body 13A includes afirst arm 210 and asecond arm 220, which are shown inFIGS. 14 and 15 , in place of the first andsecond arms circlips 159 functioning as the restrictor is mounted on the first andsecond shaft portions link pin 155. Thecirclips 159 are disposed adjacently to the opposite side surfaces of thetraction portion 150. The rest of the configuration of the compressor according to the second embodiment is substantially the same as the first embodiment and, therefore, further detailed description of the second embodiment will be omitted. In the description below, like reference numerals will be used to designate like parts or elements of the first embodiment. - As shown in
FIG. 14 , the first andsecond arms 220 extend frontward toward theswash plate 5 from themovable body 13A. Although not shown inFIG. 14 , thefirst arm 210 is disposed on the side of themovable body 13A opposite from the imaginary plane D. - As shown in
FIG. 15 , thefirst arm 210 and thesecond arm 220 are disposed on one side and other side of the imaginary plane D, or the sides on which thefirst shaft portion 151 and thesecond shaft portion 152 of thelink pin 155 are disposed. Thetraction portion 150 extends rearward from theswash plate 5 toward themovable body 13A between the first andsecond arms - As shown in
FIGS. 14 and 15 ,elongated holes second arms FIG. 14 , theelongated holes - Referring to
FIGS. 14 and 15 , the first andsecond arms elongated holes swash plate 5 and extending in the moving direction D1. - The
first guide surface 215 of thefirst arm 210 is in contact with thefirst shaft portion 151 of thelink pin 155 and thesecond guide surface 225 of thesecond arm 220 is in contact with thesecond shaft portion 152 of thelink pin 155. - In the compressor of the second embodiment having such configuration, with the changing of the inclination angle of the
swash plate 5, the first andsecond shaft portions - Accordingly, the compressor of the second embodiment permits smooth changing the inclination angle of the
swash plate 5, similarly to the compressor of the first embodiment. In addition, the compressor of the second embodiment achieves improved durability because the first andsecond shaft portions - The following will describe a third embodiment of the present invention with reference to
FIGS. 16 and 17 . The compressor of the third embodiment has apin hole 350H in which thelink pin 155 is rotatably supported in thetraction portion 150 instead of thepin hole 150H according to the compressor of the first embodiment. In addition, the first andsecond shaft portions link pin 155 of the compressor according to the third embodiment havespherical end surfaces - In the compressor of the third embodiment, the
pin hole 350H has a generally hourglass shape with a diameter that is increased axially outward from the middle toward the opposite ends, as shown inFIGS. 16 and 17 . Lubrication oil contained in the refrigerant gas forms an oil film between the outer peripheral surface of thelink pin 155 and the inner peripheral surface of thepin hole 350H at the middle portion thereof. Thelink pin 155 is rotatably supported in thepin hole 350H. Thepin hole 350H corresponds to the support hole of the present invention. Specifically, thetraction portion 150 of theswash plate 5 supports thelink pin 155 rotatably about the axis R1 while permitting thelink pin 155 to be tilted with respect to the direction extending perpendicularly to the imaginary plane D, as indicated by two dashed-dotted lines inFIG. 17 . - In the compressor of the third embodiment having such configuration, the first and
second shaft portions FIG. 17 in an exaggerated manner, when theswash plate 5 is disposed in twisted state, or misaligned with respect to the to the axis of rotation O1, the relative position between the first andsecond arms traction portion 150 fails to be maintained. In the third embodiment, however, the first andsecond shaft portions link pin 155 and the first and second guide surfaces 115, 125 are kept in contact by causing the axis R1 of thelink pin 155 to be inclined with respect to the direction perpendicular to the imaginary plane D, so that the pulling force is applied generally evenly to the first andsecond arms - In the third embodiment in which the end surfaces 151E, 152E of the first and
second shaft portions second shaft portions portions second shaft portions - Accordingly, the compressor of the third embodiment permits smooth changing of the inclination angle of the
swash plate 5. In addition, the compressor of the third embodiment achieves improved durability because the first andsecond shaft portions - The present invention is not limited to the above described first, second and third embodiments, but it may be modified in various manners within the scope of the invention, as exemplified below.
- The restrictor is not limited to the first and second facing
portions second arms circlips 159 of the second embodiment, but any restrictor may be used as long as the displacement of thelink pin 155 in axial direction thereof is prevented. - Although the end surfaces 151E, 152E of the first and
second shaft portions second shaft portions - The
actuator 13 may be disposed on thefirst cylinder block 21 side in theswash plate chamber 33 with respect to theswash plate 5. - The present invention is applicable to an air conditioner or the like.
Claims (4)
1. A variable displacement type swash plate compressor comprising:
a housing having therein a swash plate chamber and a plurality of cylinder bores;
a drive shaft rotatably supported in the housing;
a swash plate mounted on the drive shaft for rotation therewith in the swash plate chamber;
a link mechanism connecting the drive shaft and the swash plate and permitting changing of an inclination angle of the swash plate with respect to a direction perpendicular to an axis of rotation of the drive shaft;
a plurality of pistons received in the respective cylinder bores so as to form respective compression chambers and reciprocally movable with the rotation of the swash plate for a length of stroke determined by the inclination angle of the swash plate;
a partitioning body mounted on the drive shaft for rotation therewith in the swash plate chamber;
a movable body that is mounted on the drive shaft for rotation therewith and movable relative to the partitioning body along the axis of rotation in the swash plate chamber to thereby change the inclination angle of the swash plate;
a control chamber that is formed between the partitioning body and the movable body and causes the movable body to move with a pressure in the control chamber;
a control mechanism controlling the pressure in the control chamber; and
a connecting mechanism connecting the swash plate and the movable body so that the movable body pulls the swash plate to increase the inclination angle with an increase of the pressure in the control chamber,
wherein the swash plate has a top dead center portion that permits one of the pistons to be located at the top dead center,
wherein a plane that passes through the top dead center portion and the axis of rotation is defined as an imaginary plane,
wherein the connecting mechanism includes a first arm that extends from the movable body toward the swash plate and is disposed on one side of the imaginary plane, a second arm that extends from the movable body toward the swash plate and disposed on the other side of the imaginary plane, and a traction portion that is projected from the swash plate toward the movable body between the first arm and the second arm, and a link pin that connects the first arm and the second arm of the movable body and the traction portion,
wherein the first arm has a first guide surface facing away from the swash plate and the second arm has a second guide surface facing away from the swash plate,
wherein the first guide surface and the second guide surface are placed in contact with the link pin,
wherein the link pin is held by the traction portion so as to be rollable on the first guide surface and the second guide surface, and
wherein a restrictor is provided on the link pin or in the first and second arms so as to prevent the link pin from moving in a direction of an axis thereof.
2. The variable displacement type swash plate compressor according to claim 1 , wherein the first arm includes a first facing portion that faces one end surface of the link pin and the second arm includes a second facing portion that faces the other end surface of the link pin, and wherein the first facing portion and the second facing portion cooperate to form the restrictor.
3. The variable displacement type swash plate according to claim 2 , wherein peripheries of the end surfaces of the link pin are chamfered.
4. The variable displacement type swash plate according to claim 1 , wherein the traction portion has a support hole in which the link pin is rotatably supported, wherein the support hole has a diameter that is increased axially outward from the middle toward the opposite ends of the support hole.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015228850A JP2017096163A (en) | 2015-11-24 | 2015-11-24 | Variable displacement-type swash plate compressor |
JP2015-228850 | 2015-11-24 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20170145997A1 true US20170145997A1 (en) | 2017-05-25 |
Family
ID=58693862
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/353,135 Abandoned US20170145997A1 (en) | 2015-11-24 | 2016-11-16 | Variable displacement type swash plate compressor |
Country Status (4)
Country | Link |
---|---|
US (1) | US20170145997A1 (en) |
JP (1) | JP2017096163A (en) |
KR (1) | KR20170060583A (en) |
DE (1) | DE102016122232A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160208787A1 (en) * | 2015-01-21 | 2016-07-21 | Kabushiki Kaisha Toyota Jidoshokki | Double- headed piston type swash plate compressor |
US11649811B2 (en) * | 2017-12-08 | 2023-05-16 | Estra Automotive Systems Co., Ltd. | Variable capacity swash plate type compressor |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6083291B2 (en) | 2013-03-27 | 2017-02-22 | 株式会社豊田自動織機 | Variable capacity swash plate compressor |
-
2015
- 2015-11-24 JP JP2015228850A patent/JP2017096163A/en active Pending
-
2016
- 2016-11-16 US US15/353,135 patent/US20170145997A1/en not_active Abandoned
- 2016-11-18 DE DE102016122232.1A patent/DE102016122232A1/en not_active Withdrawn
- 2016-11-18 KR KR1020160154058A patent/KR20170060583A/en not_active Application Discontinuation
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160208787A1 (en) * | 2015-01-21 | 2016-07-21 | Kabushiki Kaisha Toyota Jidoshokki | Double- headed piston type swash plate compressor |
US11649811B2 (en) * | 2017-12-08 | 2023-05-16 | Estra Automotive Systems Co., Ltd. | Variable capacity swash plate type compressor |
Also Published As
Publication number | Publication date |
---|---|
JP2017096163A (en) | 2017-06-01 |
KR20170060583A (en) | 2017-06-01 |
DE102016122232A1 (en) | 2017-05-24 |
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AS | Assignment |
Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:OGAWA, HIROMICHI;YAMAMOTO, SHINYA;SUZUKI, TAKAHIRO;AND OTHERS;REEL/FRAME:040347/0405 Effective date: 20161108 |
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STCB | Information on status: application discontinuation |
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