WO2016140106A1 - 可変容量型斜板式圧縮機 - Google Patents
可変容量型斜板式圧縮機 Download PDFInfo
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- WO2016140106A1 WO2016140106A1 PCT/JP2016/055241 JP2016055241W WO2016140106A1 WO 2016140106 A1 WO2016140106 A1 WO 2016140106A1 JP 2016055241 W JP2016055241 W JP 2016055241W WO 2016140106 A1 WO2016140106 A1 WO 2016140106A1
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- WIPO (PCT)
- Prior art keywords
- chamber
- swash plate
- pressure
- cylinder block
- spacer
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
- F04B27/1072—Pivot mechanisms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/12—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 having plural sets of cylinders or pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1045—Cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/42—Pumps with cylinders or pistons
Definitions
- the present invention relates to a variable displacement swash plate compressor.
- Patent Document 1 discloses a fixed displacement swash plate compressor.
- the housing of the swash plate type compressor includes a first cylinder block and a second cylinder block coupled to each other, a front housing coupled to the first cylinder block, and a rear housing coupled to the second cylinder block.
- a rotating shaft is rotatably supported in the housing. One end of the rotation shaft is rotatably supported by the first cylinder block, and the other end is rotatably supported by the second cylinder block.
- a swash plate chamber defined by the first cylinder block and the second cylinder block is formed.
- a swash plate that rotates by obtaining a driving force from the rotation shaft is accommodated.
- the inclination angle of the swash plate with respect to the direction orthogonal to the axis of the rotation axis is constant.
- the first cylinder block has a plurality of first cylinder bores formed around the rotation axis
- the second cylinder block has a plurality of second cylinder bores formed around the rotation axis.
- the first cylinder bore and the second cylinder bore are arranged in pairs in the axial direction of the rotation axis.
- Double-headed pistons are accommodated in the first cylinder bore and the second cylinder bore, which are paired, so as to be capable of reciprocating.
- Each double-ended piston is anchored to the outer periphery of the swash plate via a pair of shoes. The rotational movement of the swash plate accompanying the rotation of the rotational shaft is converted to the reciprocating linear movement of the double-ended piston via the shoe.
- Thrust bearings are respectively disposed between the rotating shaft and the first cylinder block and between the rotating shaft and the second cylinder block.
- Each thrust bearing has an axial fastening force by a housing bolt that co-clamps the first cylinder block, the second cylinder block, the front housing and the rear housing, and between the rotation shaft and the first cylinder block and the rotation shaft It is held between the second cylinder block. Therefore, the rotary shaft is held in the axial direction of the rotary shaft by both thrust bearings, and the position of the rotary shaft in the axial direction is determined.
- Such a compressor may include an actuator in the swash plate chamber to change the tilt angle of the swash plate.
- the actuator has a partition provided on the rotary shaft, a movable body moving along the axis of the rotary shaft in the swash plate chamber, and a control pressure chamber partitioned by the partition and the mobile member.
- the movable body can move along the axis of the rotation axis by changing the pressure of the control pressure chamber. Also, as the movable body moves along the axis of the rotation axis, the inclination angle of the swash plate is changed.
- An object of the present invention is to provide a variable displacement swash plate type compressor capable of suppressing rattling of a rotating shaft due to a thrust force acting on the rotating shaft while reducing power loss.
- a housing having a discharge chamber and a cylinder block in which a plurality of cylinder bores are formed, a rotary shaft rotatably supported by the housing, and a rotary shaft.
- a thrust bearing provided between the cylinder block and the rotary shaft arranged along the axis of the shaft and supporting a thrust force acting in the axial direction of the rotary shaft, and a slant formed in the housing and taking in the refrigerant from the outside
- a variable displacement swash plate type compressor provided with an actuator disposed in a swash plate chamber and capable of changing the inclination angle of the swash plate.
- the actuator is a control chamber defined by a partition provided on the rotary shaft, a movable body provided in the swash plate chamber and movable along the axis of the rotary shaft, and partitioned by the partition and the mobile member, the control chamber And a control pressure chamber for moving the movable body according to the pressure inside.
- variable displacement swash plate type compressor between the cylinder block arranged along the axis of the rotation axis and the rotation axis, the cylinder block is non-rotatably supported with respect to the rotation axis and along the axis of the rotation axis
- a movable spacer is provided, and a pressure acting chamber in communication with the discharge chamber is defined by the cylinder block and the spacer, and a seal for sealing the pressure acting chamber and the swash plate chamber between the spacer and the cylinder block
- a member is provided.
- the spacer since the spacer can not rotate with respect to the rotating shaft, the durability of the seal member can be improved as compared with the case where the spacer rotates integrally with the rotating shaft, and the pressure acting chamber and the swash plate chamber The sealability between them can be made good.
- the rotary shaft is provided with a spacer that can rotate integrally with the rotary shaft, and the cylinder block and the spacer define a pressure acting chamber communicating with the discharge chamber.
- a seal member is disposed between the pressure application chamber and the swash plate chamber to seal the space.
- the spacer preferably has an abutment portion in contact with the cylinder block in the vicinity of the cylinder block located in the axial direction of the rotation shaft.
- variable displacement swash plate type compressor even if the operation of the variable displacement swash plate type compressor is stopped and a load based on the differential pressure between the pressure of the discharge chamber and the pressure of the swash plate chamber is not applied to the rotation shaft
- the axial positioning of the shaft can be secured. Therefore, for example, even if the vehicle on which the variable displacement swash plate type compressor is mounted vibrates and the variable displacement swash plate type compressor vibrates, rattling in the axial direction of the rotation shaft can be suppressed.
- the housing has a pair of cylinder blocks, and in each of the pair of cylinder blocks, a pair of cylinder bores is formed, and each of the pair of cylinder bores is a piston
- a double-headed piston is accommodated so as to be able to reciprocate, and the double-headed piston defines a first compression chamber in one of the paired cylinder bores, a second compression chamber in the other of the paired cylinder bores, and a rotary shaft and a swash plate
- Between the two pistons is provided with a link mechanism that allows the change of the inclination angle of the swash plate with respect to the direction orthogonal to the axis of the rotation shaft, and the link mechanism is adapted to change the inclination angle of the swash plate.
- the top dead center position is arranged to be displaced more than the top dead center position of the double-ended piston in the first compression chamber, and the double-headed piston in the first compression chamber is moved from the swash plate Orientation of the compression reaction force is preferably the same as the direction of the load applied to the rotary shaft based on the differential pressure between the pressure of the pressure and oblique discharge chamber plate chamber.
- the discharge stroke in the second compression chamber by the double-headed piston is not performed. Then, the compression reaction force acting on the swash plate from the double-ended piston in the first compression chamber becomes larger than the compression reaction force acting on the swash plate from the double-ended piston in the second compression chamber. At this time, the direction of the compression reaction force acting on the swash plate from the double-ended piston in the first compression chamber is the same as the direction of the load applied to the rotating shaft based on the differential pressure between the pressure of the discharge chamber and the pressure of the swash plate chamber.
- the load required to press the rotary shaft against the thrust bearing that is, the load applied to the rotary shaft based on the differential pressure between the pressure of the discharge chamber and the pressure of the swash plate chamber can be reduced. Therefore, rattling of the rotating shaft resulting from the thrust force acting on the rotating shaft can be efficiently suppressed.
- the outer diameter of the head of the double-headed piston housed in one of the paired cylinder bores is greater than the outer diameter of the head of the double-headed piston housed in the other of the paired cylinder bores. It is preferable to be large.
- the outer diameter of the head of the double-headed piston housed in one of the paired cylinder bores is the same as or the same as the outer diameter of the head of the double-headed piston housed in the other of the paired cylinder bores
- the compression reaction force acting on the swash plate from the double-ended piston in the first compression chamber is larger than in the case where it is too small. Therefore, the load required to press the rotating shaft against the thrust bearing, that is, the load applied to the rotating shaft based on the differential pressure between the pressure of the discharge chamber and the pressure of the swash plate chamber can be further reduced. Therefore, rattling of the rotary shaft due to the thrust force acting on the rotary shaft can be suppressed more efficiently.
- a housing having a discharge chamber and a cylinder block in which a plurality of cylinder bores are formed, a rotary shaft rotatably supported by the housing, and a rotary shaft.
- a thrust bearing provided between the cylinder block and the rotary shaft arranged along the axis of the shaft and supporting a thrust force acting in the axial direction of the rotary shaft, and a slant formed in the housing and taking in the refrigerant from the outside
- a plate chamber a swash plate housed in the swash plate chamber, capable of rotating with the drive force from the rotary shaft and capable of tilting in a direction perpendicular to the axis of the rotary shaft, and a piston housed reciprocally in the cylinder bore
- a variable displacement swash plate compressor including an actuator disposed in the swash plate chamber and capable of changing the tilt angle of the swash plate.
- the actuator is a control chamber defined by a partition provided on the rotary shaft, a movable body provided in the swash plate chamber and movable along the axis of the rotary shaft, and partitioned by the partition and the mobile member, the control chamber And a control pressure chamber for moving the movable body according to the pressure inside.
- the inclination angle of the swash plate increases as the pressure in the control pressure chamber increases, and the inclination angle of the swash plate decreases as the pressure in the control pressure chamber decreases.
- the inclination angle of the piston is changed, and the piston reciprocates in a stroke corresponding to the inclination angle of the swash plate.
- a load based on a differential pressure between the pressure of the control pressure chamber and the pressure of the swash plate chamber is applied to the thrust bearing on the rotating shaft.
- variable displacement swash plate type compressor between the cylinder block arranged along the axis of the rotation axis and the rotation axis, the cylinder block is non-rotatably supported with respect to the rotation axis and along the axis of the rotation axis
- a movable spacer is provided, and the cylinder block and the spacer define a pressure acting chamber in communication with the control pressure chamber, and between the spacer and the cylinder block, the space between the pressure acting chamber and the swash plate chamber is sealed.
- a sealing member is provided.
- the spacer since the spacer can not rotate with respect to the rotating shaft, the durability of the seal member can be improved as compared with the case where the spacer rotates integrally with the rotating shaft, and the pressure acting chamber and the swash plate chamber The sealability between them can be made good.
- the rotary shaft is provided with a spacer that can rotate integrally with the rotary shaft, and the cylinder block and the spacer define a pressure acting chamber communicating with the control pressure chamber.
- a seal member for sealing between the pressure application chamber and the swash plate chamber is disposed between the block and the block.
- the spacer preferably has an abutment portion in contact with the cylinder block in the vicinity of the cylinder block located in the axial direction of the rotation shaft.
- the housing has a pair of cylinder blocks, and in each of the pair of cylinder blocks, a pair of cylinder bores is formed, and each of the pair of cylinder bores is a piston
- a double-headed piston is accommodated so as to be able to reciprocate, and the double-headed piston defines a first compression chamber in one of the paired cylinder bores, a second compression chamber in the other of the paired cylinder bores, and a rotary shaft and a swash plate
- Between the two pistons is provided with a link mechanism that allows the change of the inclination angle of the swash plate with respect to the direction orthogonal to the axis of the rotation shaft, and the link mechanism is adapted to change the inclination angle of the swash plate.
- the top dead center position is arranged to be displaced more than the top dead center position of the double-ended piston in the first compression chamber, and the double-headed piston in the first compression chamber is moved from the swash plate Orientation of the compression reaction force is preferably the same as the direction of the load applied to the rotating shaft on the basis of the differential pressure between the pressure of the pressure and the swash plate chamber of the control pressure chamber.
- the direction of the compression reaction force acting on the swash plate from the double-ended piston in the first compression chamber is the direction of the load applied to the rotating shaft based on the differential pressure between the pressure of the control pressure chamber and the pressure of the swash plate chamber Since it is the same, the load required to press the rotary shaft against the thrust bearing, that is, the load applied to the rotary shaft based on the differential pressure between the pressure of the control pressure chamber and the pressure of the swash plate chamber can be reduced. . Therefore, rattling of the rotating shaft resulting from the thrust force acting on the rotating shaft can be efficiently suppressed.
- the outer diameter of the head of the double-headed piston housed in one of the paired cylinder bores is greater than the outer diameter of the head of the double-headed piston housed in the other of the paired cylinder bores. It is preferable to be large.
- the outer diameter of the head of the double-headed piston housed in one of the paired cylinder bores is the same as or the same as the outer diameter of the head of the double-headed piston housed in the other of the paired cylinder bores
- the compression reaction force acting on the swash plate from the double-ended piston in the first compression chamber is larger than in the case where it is too small. Therefore, the load required to press the rotating shaft against the thrust bearing, that is, the load applied to the rotating shaft based on the differential pressure between the pressure of the control pressure chamber and the pressure of the swash plate chamber can be further reduced. Therefore, rattling of the rotary shaft due to the thrust force acting on the rotary shaft can be suppressed more efficiently.
- FIG. 2 is a side sectional view showing a variable displacement swash plate compressor when the inclination angle of the swash plate is a minimum inclination angle.
- FIG. 7 is a side cross sectional view showing a variable displacement swash plate compressor according to another embodiment.
- variable displacement swash plate type compressor of the present invention is embodied will be described according to FIGS. 1 to 4.
- the variable displacement swash plate type compressor is simply referred to as a compressor.
- This compressor is used for a vehicle air conditioner.
- the left side of FIG. 1 is defined as the front side, and the right side is defined as the rear side.
- the housing 11 of the compressor 10 includes a first cylinder block 12 and a second cylinder block 13 as a pair of cylinder blocks connected to each other, and a front housing 14 connected to the first cylinder block 12. And a rear housing 15 connected to the second cylinder block 13.
- a first valve / port assembly 16 is interposed between the front housing 14 and the first cylinder block 12.
- a second valve / port assembly 17 is interposed between the rear housing 15 and the second cylinder block 13.
- a suction chamber 14 a and a discharge chamber 14 b are defined between the front housing 14 and the first valve / port assembly 16.
- the discharge chamber 14 b is disposed radially outside the suction chamber 14 a.
- a suction chamber 15a and a discharge chamber 15b are divided between the rear housing 15 and the second valve / port assembly 17.
- a pressure adjustment chamber 15 c is formed in the rear housing 15.
- the pressure adjustment chamber 15c is located at the central portion of the rear housing 15, and the suction chamber 15a is disposed radially outside the pressure adjustment chamber 15c.
- the discharge chamber 15b is disposed radially outside the suction chamber 15a.
- the discharge chambers 14 b and 15 b are connected to each other via the discharge passage 18.
- the discharge passage 18 is connected to an external refrigerant circuit (not shown).
- Each discharge chamber 14b, 15b is a discharge pressure area.
- the first valve / port assembly 16 is formed with a suction port 16a communicating with the suction chamber 14a and a discharge port 16b communicating with the discharge chamber 14b.
- the second valve / port assembly 17 is provided with a suction port 17a communicating with the suction chamber 15a and a discharge port 17b communicating with the discharge chamber 15b.
- a rotating shaft 20 having an axis L is rotatably supported in the housing 11.
- a cylindrical first support member 21 is press-fitted to the outer peripheral surface of the front end portion of the rotating shaft 20.
- a cylindrical second support member 22 is press-fitted to the outer peripheral surface of the rear end portion of the rotating shaft 20.
- the first support member 21 and the second support member 22 constitute a part of the rotation shaft 20.
- a first support member 21 constituting a front end portion of the rotation shaft 20 is inserted into an axial hole 12 h formed in the first cylinder block 12.
- a second support member 22 constituting a rear end portion of the rotary shaft 20 is inserted into an axial hole 13 h formed in the second cylinder block 13.
- the rear end portion of the second support member 22, that is, the rear end portion of the rotary shaft 20 is located in the pressure adjustment chamber 15c.
- a first sliding bearing 21a is disposed between the first support member 21 and the shaft hole 12h.
- a second sliding bearing 22a is disposed between the second support member 22 and the shaft hole 13h.
- the first support member 21 is rotatably supported by the first cylinder block 12 via the first slide bearing 21a, and the second support member 22 is connected to the second cylinder block 13 via the second slide bearing 22a. It is rotatably supported.
- a lip seal type shaft seal device 20 s is interposed between the front housing 14 and the rotary shaft 20.
- an engine of a vehicle as an external drive source is operatively connected via a power transmission mechanism (not shown).
- the power transmission mechanism is a constant transmission clutchless mechanism, and is, for example, a combination of a belt and a pulley.
- a swash plate chamber 24 partitioned by the first cylinder block 12 and the second cylinder block 13 is formed.
- the swash plate chamber 24 accommodates a swash plate 23 which is rotated by obtaining driving force from the rotation shaft 20 and which can be tilted in the axial direction with respect to the rotation shaft 20.
- the swash plate 23 is formed with an insertion hole 23 a through which the rotation shaft 20 is inserted.
- the swash plate 23 is attached to the rotary shaft 20 by inserting the rotary shaft 20 into the insertion hole 23 a.
- FIG. 1 shows only one first cylinder bore 12a.
- Each first cylinder bore 12a communicates with the suction chamber 14a through the suction port 16a and communicates with the discharge chamber 14b through the discharge port 16b.
- a plurality of second cylinder bores 13 a penetrating the second cylinder block 13 in the axial direction are arranged around the rotation shaft 20.
- FIG. 1 shows only one second cylinder bore 13a.
- Each second cylinder bore 13a communicates with the suction chamber 15a via the suction port 17a and communicates with the discharge chamber 15b via the discharge port 17b.
- the inner diameter of the first cylinder bore 12a is larger than the inner diameter of the second cylinder bore 13a.
- the first cylinder bores 12a and the second cylinder bores 13a are arranged in pairs at the front and back.
- a double-ended piston 25 as a piston is accommodated in the first cylinder bore 12a and the second cylinder bore 13a as a pair so as to be capable of reciprocating in the front-rear direction.
- the first head 25a of the double-ended piston 25 is accommodated in the first cylinder bore 12a
- the second head 25b of the double-ended piston 25 is accommodated in the second cylinder bore 13a.
- the outer diameter R1 of the first head 25a is larger than the outer diameter R2 of the second head 25b.
- the compressor 10 of the present embodiment is a double-headed piston type swash plate type compressor.
- Each double-ended piston 25 is anchored to the outer peripheral portion of the swash plate 23 via a pair of shoes 26.
- the rotational movement of the swash plate 23 accompanying the rotation of the rotational shaft 20 is converted to the reciprocating linear movement of the double-ended piston 25 via the shoe 26.
- the pair of shoes 26 is a conversion mechanism that causes the double-headed piston 25 to reciprocate within the first cylinder bore 12 a and the second cylinder bore 13 a by the rotation of the swash plate 23.
- a first compression chamber 19a is defined by the double-ended piston 25 and the first valve / port assembly 16 in each first cylinder bore 12a.
- a second compression chamber 19 b is defined by the double-ended piston 25 and the second valve / port assembly 17.
- the first cylinder block 12 is formed with a first small diameter hole 121b which is continuous with the shaft hole 12h and has a diameter larger than that of the shaft hole 12h. Further, the first cylinder block 12 is formed with a first large diameter hole 122b which is continuous with the first small diameter hole 121b and has a diameter larger than that of the first small diameter hole 121b. The first large diameter hole 122 b communicates with the swash plate chamber 24 and forms a part of the swash plate chamber 24. The swash plate chamber 24 and the suction chamber 14 a are in communication with each other by a suction passage 12 c which passes through the first cylinder block 12 and the first valve / port assembly 16.
- the second cylinder block 13 is formed with a second small diameter hole 131b which is continuous with the shaft hole 13h and has a diameter larger than that of the shaft hole 13h. Further, the second cylinder block 13 is formed with a second large diameter hole 132b continuous with the second small diameter hole 131b and larger in diameter than the second small diameter hole 131b.
- the second large diameter hole 132 b communicates with the swash plate chamber 24 and forms a part of the swash plate chamber 24.
- the swash plate chamber 24 and the suction chamber 15a are in communication with each other by a suction passage 13c which penetrates the second cylinder block 13 and the second valve / port assembly 17.
- a suction port 13 s is formed in a peripheral wall of the second cylinder block 13.
- the suction port 13s is connected to an external refrigerant circuit.
- the refrigerant gas taken into the swash plate chamber 24 from the external refrigerant circuit through the suction port 13s is sucked into the suction chambers 14a, 15a through the suction passages 12c, 13c. Therefore, the suction chambers 14a and 15a and the swash plate chamber 24 are in the suction pressure area, and the pressures are substantially equal.
- An annular first flange 21 f disposed in the first large diameter hole 122 b is provided on the outer peripheral surface of the first support member 21 so as to project therefrom.
- a first thrust bearing 27 a and a spacer 50 are disposed between the first flange 21 f and the first cylinder block 12.
- the first thrust bearing 27 a and the spacer 50 are disposed with their axes directed in the axial direction of the rotating shaft 20.
- the first thrust bearing 27 a is closer to the first flange 21 f than the spacer 50.
- An annular second flange 22 f disposed in the second large diameter hole 132 b is provided on the outer peripheral surface of the second support member 22 in a protruding manner.
- a second thrust bearing 27 b as a thrust bearing is disposed between the second flange 22 f and the second cylinder block 13.
- the second thrust bearing 27 b is disposed with its axis directed in the axial direction of the rotary shaft 20.
- the second thrust bearing 27b is fitted in the second small diameter hole 131b.
- the first thrust bearing 27 a and the second thrust bearing 27 b support a thrust force that acts on the rotation shaft 20 in the axial direction of the rotation shaft 20.
- the spacer 50 is annular and is supported non-rotatably with respect to the rotation shaft 20.
- the spacer 50 is fitted so as to be movable in the axial direction of the rotation shaft 20 in the first small diameter hole 121b.
- An annular contact portion 51 that contacts the first cylinder block 12 protrudes from the spacer 50.
- the contact portion 51 is provided on an end surface 50 a in the vicinity of the first cylinder block 12 among the end surfaces of the spacer 50 located in the axial direction of the rotary shaft 20.
- the contact portion 51 is provided in the vicinity of the inner peripheral edge of the spacer 50.
- the spacer 50 is disposed in the first small diameter hole 121 b in a state where the contact portion 51 is in contact with the first cylinder block 12 and the end surface 50 a of the spacer 50 is separated from the first cylinder block 12.
- An annular seal member 52a for sealing between the end surface 50a and the first cylinder block 12 is disposed radially outside the contact portion 51 of the end surface 50a of the spacer 50.
- a seal member 52b is provided which seals between the outer peripheral surface of the spacer 50 and the inner peripheral surface of the first small diameter hole 121b.
- a seal member 52c for sealing between the inner peripheral surface of the spacer 50 and the outer peripheral surface of the first support member 21 is disposed.
- a pressure application chamber 55 is defined by the first cylinder block 12 and the spacer 50. Specifically, the pressure application chamber 55 is a space defined by the first cylinder block 12, the spacer 50, and the seal members 52a and 52b.
- the pressure application chamber 55 is in communication with the discharge chamber 14b via the supply passage 55a. Therefore, the refrigerant gas of the discharge chamber 14 b is supplied to the pressure action chamber 55 via the supply passage 55 a.
- the seal members 52 a, 52 b and 52 c seal between the pressure application chamber 55 and the swash plate chamber 24. Accordingly, leakage of the refrigerant gas supplied to the pressure acting chamber 55 into the swash plate chamber 24 is prevented by the seal members 52a, 52b and 52c.
- an actuator 30 capable of changing the inclination angle of the swash plate 23 with respect to the first direction orthogonal to the axis L of the rotating shaft 20, ie, the vertical direction in FIG. ing.
- the actuator 30 is provided between the second flange 22 f and the swash plate 23.
- the actuator 30 has an annular partition 31 which is integrally rotatable with the rotation shaft 20.
- the partition body 31 is formed with an insertion hole 31 h through which the rotation shaft 20 is inserted.
- the partition body 31 is integrated with the rotation shaft 20 by press-fitting and fixing the rotation shaft 20 in the insertion hole 31 h.
- the actuator 30 also has a bottomed cylindrical moving body 32 disposed between the second flange 22 f and the partition 31 and movable in the axial direction of the rotary shaft 20 in the swash plate chamber 24.
- the moving body 32 is disposed to be able to enter inside the second large diameter hole 132b.
- the movable body 32 includes an annular bottom 32a having a through hole 32e through which the rotation shaft 20 is inserted, and a cylindrical portion 32b extending along the axis L of the rotation shaft 20 from the outer peripheral edge of the bottom 32a.
- the moving body 32 can rotate integrally with the rotation shaft 20.
- a seal member 33 seals between the inner peripheral surface of the cylindrical portion 32 b and the outer peripheral surface of the partition 31, and a seal member 34 seals between the through hole 32 e and the rotary shaft 20.
- the actuator 30 has a control pressure chamber 35 partitioned by the partition 31 and the moving body 32.
- a return spring 28 a is fixed to the first support member 21.
- the return spring 28 a extends from the first support member 21 toward the swash plate chamber 24.
- an inclination angle reduction spring 28 b is interposed between the partition body 31 and the swash plate 23.
- the rear end of the inclination angle reducing spring 28 b is fixed to the partition 31 and the front end is fixed to the swash plate 23.
- the tilt angle reducing spring 28 b biases the swash plate 23 in the direction in which the tilt angle of the swash plate 23 is reduced.
- the in-shaft passage 29 communicating the control pressure chamber 35 and the pressure adjustment chamber 15 c is formed in the rotary shaft 20.
- the in-shaft passage 29 includes a first in-shaft passage 29 a extending along the axis L of the rotating shaft 20 and a second in-axial passage 29 b communicating with the first in-shaft passage 29 a and radially extending in the rotating shaft 20. It is formed.
- the rear end of the first in-shaft passage 29a is in communication with the pressure adjustment chamber 15c.
- the lower end of the second in-shaft passage 29 b communicates with the front end of the first in-shaft passage 29 a, and the upper end is open in the control pressure chamber 35.
- the control pressure chamber 35 and the pressure adjustment chamber 15c communicate with each other through the first in-shaft passage 29a and the second in-shaft passage 29b.
- the pressure control chamber 15 c and the suction chamber 15 a communicate with each other through the bleed passage 36.
- the bleed passage 36 is provided with an electromagnetic control valve 36s as a control mechanism.
- the control valve 36s can adjust the opening degree of the bleed passage 36 based on the pressure of the suction chamber 15a.
- the flow rate of the refrigerant gas flowing through the bleed passage 36 is adjusted by the control valve 36s, and the pressure of the pressure adjustment chamber 15c is controlled.
- the pressure adjustment chamber 15 c and the discharge chamber 15 b communicate with each other through the air supply passage 37.
- An orifice 37a is provided in the air supply passage 37, and the flow rate of the refrigerant gas flowing through the air supply passage 37 is restricted by the orifice 37a.
- the movable body 32 moves along the axis L of the rotation shaft 20 with respect to the partition 31. Therefore, the refrigerant gas introduced into the control pressure chamber 35 is a control gas used to control the movement of the movable body 32.
- a lug arm 40 which is a link mechanism that allows change of the inclination angle of the swash plate 23, is disposed.
- the lug arm 40 is formed in a substantially L-shape.
- a weight portion 40w is provided at the rear end of the lug arm 40. The weight portion 40 w passes through the groove portion 23 b of the swash plate 23 and is positioned rearward of the swash plate 23.
- the rear portion of the lug arm 40 is connected to the upper end of the swash plate 23 by a cylindrical first pin 41 traversing the inside of the groove 23 b.
- the front end of the lug arm 40 is connected to a connecting portion (not shown) of the first support member 21 by a cylindrical second pin 42.
- the front end of the lug arm 40 is swingably supported on the first support member 21 with the axis of the second pin 42 as the second swing center M2.
- a connecting portion 32 c that protrudes toward the swash plate 23 is provided.
- a cylindrical connecting pin 43 is fixed to the connecting portion 32c.
- an insertion hole 23 h through which the connection pin 43 is inserted is formed in the swash plate 23.
- the insertion hole 23 h is formed radially outward of the insertion hole 23 a of the swash plate 23. That is, the connecting portion 32 c is connected to the lower end of the swash plate 23 via the connecting pin 43.
- the double-headed piston 25 is accommodated so as to be capable of reciprocating in the first cylinder bore 12a and the second cylinder bore 13a which are paired.
- a dead volume corresponding to the clearance between the double-ended piston 25 at the top dead center position and the second valve / port assembly 17 in the second compression chamber 19b. Will increase.
- the discharge stroke is performed without a significant increase in dead volume corresponding to the clearance between the double-headed piston 25 at the top dead center position and the first valve / port assembly 16. It will be.
- the lag arm 40 displaces the top dead center position of the double-headed piston 25 in the second compression chamber 19b more than the top dead center position of the double-headed piston 25 in the first compression chamber 19a. It is arranged as.
- the refrigerant gas is not discharged from the second compression chamber 19b. Therefore, as the inclination angle of the swash plate 23 decreases from the predetermined inclination angle to the minimum inclination angle, the pressure of the second compression chamber 19 b does not reach the discharge pressure. Therefore, the discharge and suction of the refrigerant gas are not performed, and the compression and expansion of the refrigerant gas are only repeated.
- the swash plate 23 swings in the direction opposite to the swinging direction when the inclination angle of the swash plate 23 decreases around the first swinging center M1.
- the lug arm 40 swings around the second swinging center M2 in the opposite direction to the time when the inclination angle of the swash plate 23 decreases, and the lug arm 40 separates from the first flange 21f.
- the inclination angle of the swash plate 23 is increased, the stroke of the double-headed piston 25 is increased, and the displacement is increased.
- the rotating shaft 20 is sandwiched in the axial direction of the rotating shaft 20 by the first thrust bearing 27 a and the second thrust bearing 27 b.
- the axial position of the rotating shaft 20 is determined.
- the displacement increases, the compression reaction force acting on the swash plate 23 from the double-headed piston 25 increases, and the thrust force transmitted from the swash plate 23 to the rotation shaft 20 increases. Since the position of the direction is determined, rattling of the rotating shaft 20 due to the thrust force acting on the rotating shaft 20 is suppressed.
- the dead volume of the second compression chamber 19b When the inclination angle of the swash plate 23 decreases, the dead volume increases in the second compression chamber 19b.
- the dead volume of the second compression chamber 19 b reaches a predetermined size, the discharge stroke in the second compression chamber 19 b by the double-ended piston 25 is not performed. Then, the compression reaction force acting on the swash plate 23 from the double-headed piston 25 in the first compression chamber 19a becomes larger than the compression reaction force acting on the swash plate 23 from the double-headed piston 25 in the second compression chamber 19b.
- the direction of the compression reaction force acting on the swash plate 23 from the double-headed piston 25 in the first compression chamber 19a is applied to the rotating shaft 20 based on the differential pressure between the pressure of the pressure application chamber 55 and the pressure of the swash plate chamber 24. Same as the direction of the load. Therefore, the load required to press the rotating shaft 20 against the second thrust bearing 27b, that is, the load applied to the rotating shaft 20 based on the differential pressure between the pressure of the pressure acting chamber 55 and the pressure of the swash plate chamber 24 is It becomes possible to make it small.
- a load based on a differential pressure between the pressure of the pressure acting chamber 55 and the pressure of the swash plate chamber 24 is applied to the second thrust bearing 27 b on the rotating shaft 20.
- the differential pressure between the pressure in the pressure application chamber 55 and the pressure in the swash plate chamber 24 is increased.
- the load applied to the rotating shaft 20 increases toward the second thrust bearing 27b.
- the rotary shaft 20 is pressed against the second thrust bearing 27 b, and the axial position of the rotary shaft 20 is fixed.
- the spacer 50 is supported non-rotatably with respect to the rotating shaft 20 and is movable in the axial direction of the rotating shaft 20. According to this configuration, the durability of the seal members 52a and 52b can be improved as compared with the case where the spacer 50 is integrally rotated with the rotary shaft 20, and the sealability between the pressure application chamber 55 and the swash plate chamber 24 Can be made good.
- the load required to press the rotating shaft 20 against the second thrust bearing 27b that is, the load applied to the rotating shaft 20 based on the differential pressure between the pressure of the pressure acting chamber 55 and the pressure of the swash plate chamber 24 is It can be made smaller.
- rattling of the rotary shaft 20 due to the thrust force acting on the rotary shaft 20 can be efficiently suppressed.
- the outer diameter R1 of the first head 25a is larger than the outer diameter R2 of the second head 25b.
- the outer diameter R1 of the first head 25a is the same as the outer diameter R2 of the second head 25b, or the outer diameter R1 of the first head 25a is the outer diameter of the second head 25b.
- the compression reaction force acting on the swash plate 23 from the double-ended piston 25 in the first compression chamber 19a is larger than that in the case where the diameter R2 is smaller. Therefore, the load required to press the rotating shaft 20 against the second thrust bearing 27b, that is, the load applied to the rotating shaft 20 based on the differential pressure between the pressure of the pressure acting chamber 55 and the pressure of the swash plate chamber 24 It can be made smaller. Therefore, rattling of the rotary shaft 20 due to the thrust force acting on the rotary shaft 20 can be suppressed more efficiently.
- the direction of the compression reaction force acting on the swash plate 23 from the double-headed piston 25 in the first compression chamber 19a is the rotational shaft 20 based on the differential pressure between the pressure of the pressure application chamber 55 and the pressure of the swash plate chamber 24.
- the direction of the load applied to is opposite to that of.
- the above load is set in the first compression chamber 19a.
- the compression reaction force acting on the swash plate 23 from the double-ended piston 25 needs to be greater. Therefore, it is necessary to increase the pressure receiving area of the pressure application chamber 55.
- the direction of the compression reaction force acting on the swash plate 23 from the double-headed piston 25 in the first compression chamber 19a is rotated based on the pressure difference between the pressure of the pressure acting chamber 55 and the pressure of the swash plate chamber 24.
- the direction of the load applied to the shaft 20 is the same. According to this, the pressure receiving area of the pressure application chamber 55 can be reduced. Therefore, the spacer 50 can be miniaturized, and the compressor 10 can be miniaturized.
- the spacer 60 may be integrally rotatable with the rotation shaft 20.
- the spacer 60 has an annular shape and is press-fitted to the rotating shaft 20.
- a seal member 61 is disposed on the outer peripheral surface of the spacer 60 to seal between the outer peripheral surface of the spacer 60 and the inner peripheral surface of the first small diameter hole 121b.
- the spacer 60 is disposed in the first small diameter hole 121 b in a state where the end face in the vicinity of the first cylinder block 12 is separated from the first cylinder block 12. Further, the pressure acting chamber 55 is divided by the first cylinder block 12 and the spacer 50.
- a seal member 62 for sealing between the shaft hole 12 h and the outer peripheral surface of the first support member 21 is disposed on the outer peripheral surface of the first support member 21. According to this, since the spacer 60 can be integrally rotated with the rotating shaft 20, there is no need to dispose a thrust bearing between the spacer 60 and the rotating shaft 20, and the number of parts can be reduced. Thus, the weight of the compressor 10 can be reduced.
- the spacer 60 may be integrally formed on the rotating shaft 20.
- the contact portion 51 may be omitted from the spacer 50.
- an annular flange 50 f is provided in the vicinity of the first large diameter hole 122 b on the outer peripheral surface of the spacer 50.
- the flange 50 f is in contact with the end face 123 b of the boundary portion between the first small diameter hole 121 b and the first large diameter hole 122 b in the first cylinder block 12.
- the spacer 50 is disposed in the first small diameter hole 121b in a state where the end surface 50a of the spacer 50 is separated from the first cylinder block 12 by bringing the flange 50f into contact with the end surface 123b.
- the pressure application chamber 65 may be in communication with the control pressure chamber 35, and the pressure of the pressure application chamber 65 may be the same as the pressure of the control pressure chamber 35.
- a load based on a differential pressure between the pressure of the control pressure chamber 35 and the pressure of the swash plate chamber 24 may be applied to the rotation shaft 20 toward the second thrust bearing 27 b.
- the lug arm 40, the spacer 50, and the like are arranged so as to be reversed in the axial direction of the rotation shaft 20.
- FIG. 1 the embodiment shown in FIG.
- the first cylinder block 12 is formed with a supply passage 65a communicating the pressure application chamber 65 with the pressure adjustment chamber 15c.
- the refrigerant gas of the pressure adjustment chamber 15c is supplied to the pressure application chamber 65 via the supply passage 65a.
- the pressure of the pressure adjustment chamber 15 c is the same as the pressure of the control pressure chamber 35.
- the direction of the compression reaction force acting on the swash plate 23 from the double-headed piston 25 in the first compression chamber 19a is the load applied to the rotating shaft 20 based on the differential pressure between the pressure of the pressure application chamber 65 and the pressure of the swash plate chamber 24. The same as the direction of
- the rotational shaft 20 is sandwiched in the axial direction of the rotational shaft 20 by the first thrust bearing 27a and the second thrust bearing 27b, and the axial position of the rotational shaft 20 is determined.
- the displacement increases, the compression reaction force acting on the swash plate 23 from the double-headed piston 25 increases, and the thrust force transmitted from the swash plate 23 to the rotation shaft 20 increases. Since the position of the direction is determined, rattling of the rotating shaft 20 due to the thrust force acting on the rotating shaft 20 is suppressed.
- the pressure of the control pressure chamber 35 approaches the pressure of the discharge chamber 15b as the discharge capacity increases, and the pressure of the control pressure chamber 35 approaches the pressure of the suction chamber 15a as the discharge capacity decreases.
- the load based on the differential pressure between the pressure in the pressure application chamber 65 and the pressure in the swash plate chamber 24 approaches the load based on the differential pressure between the pressure in the discharge chamber 15 b and the pressure in the swash plate chamber 24.
- the load based on the differential pressure between the pressure in the pressure application chamber 65 and the pressure in the swash plate chamber 24 approaches the load based on the differential pressure between the pressure in the suction chamber 15a and the pressure in the swash plate chamber 24. Therefore, as the displacement decreases, the load applied to the rotary shaft 20 toward the second thrust bearing 27b decreases to approach the load based on the differential pressure between the pressure in the suction chamber 15a and the pressure in the swash plate chamber 24. Do. Therefore, when the displacement is changed, the load applied to the rotary shaft 20 toward the second thrust bearing 27b is smaller than the load based on the differential pressure between the pressure of the discharge chamber 15b and the pressure of the swash plate chamber 24. can do. Therefore, the sliding resistance between the second thrust bearing 27b and the rotary shaft 20 is reduced, and the power loss is reduced.
- the embodiment shown in FIG. 7 is the same as the embodiment shown in FIG. 1 except that a load based on the differential pressure between the pressure of the control pressure chamber 35 and the pressure of the swash plate chamber 24 is applied to the second thrust bearing 27b.
- the configuration is basically the same as that of the embodiment shown in FIG. Therefore, the same effects as the effects (2) to (6) of the embodiment shown in FIGS. 1 to 4 can be obtained.
- a spacer that can rotate integrally with the rotary shaft 20 may be provided. According to this, since the spacer can be integrally rotated with the rotating shaft 20, it is not necessary to dispose a thrust bearing between the spacer and the rotating shaft 20, and the number of parts can be reduced.
- the direction of the compression reaction force acting on the swash plate 23 from the double-headed piston 25 in the first compression chamber 19a is the load applied to the rotating shaft 20 based on the differential pressure between the pressure of the pressure application chamber 55 and the pressure of the swash plate chamber 24. It may be opposite to the direction of.
- the outer diameter R1 of the first head 25a may be the same as the outer diameter R2 of the second head 25b.
- the outer diameter R1 of the first head 25a may be smaller than the outer diameter R2 of the second head 25b.
- the discharge chamber 15 b may be in communication with the pressure application chamber 55.
- the moving body 32 moves so that the inclination angle of the swash plate 23 becomes large by the pressure of the control pressure chamber 35 becoming almost equal to the pressure of the suction chamber 15a, and the pressure of the control pressure chamber 35 becomes approximately the pressure of the discharge chamber 15b
- the actuator 30 may be configured to move the moving body 32 so that the inclination angle of the swash plate 23 is reduced by equalizing. That is, the actuator 30 may be configured to increase the discharge capacity by reducing the pressure of the control pressure chamber 35.
- An electromagnetic control valve may be provided on the air supply passage 37 communicating the pressure adjustment chamber 15c and the discharge chamber 15b, and an orifice may be provided on the bleed passage communicating the pressure adjustment chamber 15c and the suction chamber 15a.
- the compressor 10 may be a single-headed piston type swash plate compressor employing a single-headed piston.
- the compressor 10 may obtain drive power from an external drive source via a clutch.
- variable displacement swash plate type compressor 11: housing, 12: first cylinder block as cylinder block, 12a: first cylinder bore as cylinder bore, 13: second cylinder block as cylinder block, 13a: as cylinder bore Second cylinder bore, 14b, 15b: Discharge chamber, 19a: First compression chamber as one compression chamber, 19b: Second compression chamber as the other compression chamber, 20: Rotary shaft, 23: Swash plate, 24: Oblique Plate chamber 25 double-ended piston as piston 25a first head as one head 25b second head as the other head 27b second thrust bearing as thrust bearing 30 as an actuator , 31: compartment body, 32: moving body, 35: control pressure chamber, 40: link mechanism, lug arm, 50, 60: spacer, 51: corresponding Parts, 52a, 52 b, 52c ... sealing member, 55 and 65 ... pressure action chamber.
Abstract
Description
この構成によれば、ハウジングを組み付けた際、ハウジングに対し回転軸の軸方向に作用する締結力によって、シリンダブロックから当接部を介してスペーサには、スラスト軸受に向けて荷重が付与される。その結果、回転軸がスラスト軸受に押し付けられて、回転軸の軸方向の位置を決めることができる。したがって、例えば、可変容量型斜板式圧縮機の運転が停止されており、吐出室の圧力と斜板室の圧力との差圧に基づく荷重が回転軸に付与されていない場合であっても、回転軸の軸方向の位置決めを確保することができる。よって、例えば、可変容量型斜板式圧縮機が搭載された車両が振動し、可変容量型斜板式圧縮機が振動しても、回転軸の軸方向に生じるがたつきを抑制することができる。
この構成によれば、ハウジングを組み付けた際、ハウジングに対し回転軸の軸方向に作用する締結力によって、シリンダブロックから当接部を介してスペーサには、スラスト軸受に向けて荷重が付与される。その結果、回転軸がスラスト軸受に押し付けられて、回転軸の軸方向の位置を決めることができる。したがって、例えば、可変容量型斜板式圧縮機の運転が停止されており、制御圧室の圧力と斜板室の圧力との差圧に基づく荷重が回転軸に付与されていない場合であっても、回転軸の軸方向の位置決めを確保することができる。よって、例えば、可変容量型斜板式圧縮機が搭載された車両が振動し、可変容量型斜板式圧縮機が振動しても、回転軸の軸方向に生じるがたつきを抑制することができる。
吐出容量が増大して、吐出室14bの圧力が高くなると、圧力作用室55の圧力と斜板室24の圧力との差圧が増大する。すると、スペーサ50が第1スラスト軸受27aに向けて移動する。これにより、スペーサ50が第1スラスト軸受27aを押圧し、第1スラスト軸受27aがスペーサ50によって第1フランジ21fに押し付けられて、第1スラスト軸受27aがスペーサ50と第1フランジ21fとの間で挟持される。また、第1スラスト軸受27aが第1フランジ21fに押し付けられることで、回転軸20が第2スラスト軸受27bに向けて押圧される。その結果、第2フランジ22fが第2スラスト軸受27bに押し付けられ、第2スラスト軸受27bが第2フランジ22fと第2シリンダブロック13との間で挟持される。したがって、回転軸20には、圧力作用室55の圧力と斜板室24の圧力との差圧に基づく荷重が、第2スラスト軸受27bに向けて付与される。
(1)回転軸20には、圧力作用室55の圧力と斜板室24の圧力との差圧に基づく荷重が、第2スラスト軸受27bに向けて付与されている。この構成によれば、吐出容量が増大して、吐出室14bの圧力が高くなると、圧力作用室55の圧力と斜板室24の圧力との差圧が増大する。この場合、第2スラスト軸受27bに向けて回転軸20に付与される荷重が増大する。これにより、回転軸20が第2スラスト軸受27bに押し付けられて、回転軸20の軸方向の位置が固定される。よって、吐出容量が増大して、両頭ピストン25から斜板23に作用する圧縮反力が増大し、斜板23から回転軸20に伝達されるスラスト力が増大しても、回転軸20の軸方向の位置が固定されているため、回転軸20に作用するスラスト力に起因した回転軸20のがたつきが抑制される。
図5に示すように、スペーサ60が、回転軸20と一体回転可能であってもよい。スペーサ60は円環状であるとともに、回転軸20に圧入されている。スペーサ60の外周面には、スペーサ60の外周面と第1小径孔121bの内周面との間をシールするシール部材61が配設されている。スペーサ60は、第1シリンダブロック12近傍の端面を第1シリンダブロック12から離した状態で、第1小径孔121b内に配置されている。また、第1シリンダブロック12とスペーサ50とによって、圧力作用室55が区画されている。第1支持部材21の外周面には、軸孔12hと第1支持部材21の外周面との間をシールするシール部材62が配設されている。これによれば、スペーサ60が回転軸20と一体回転可能であるため、スペーサ60と回転軸20との間にスラスト軸受を配設する必要が無く、部品点数を削減することができる。よって、圧縮機10の軽量化を図ることができる。
図6に示すように、スペーサ50から当接部51を省略してもよい。この場合、スペーサ50の外周面における第1大径孔122b近傍には、環状のフランジ50fが突設されている。フランジ50fは、第1シリンダブロック12における第1小径孔121bと第1大径孔122bとの境界部の端面123bに当接している。スペーサ50は、フランジ50fを端面123bに当接させることで、スペーサ50の端面50aを第1シリンダブロック12から離した状態で、第1小径孔121b内に配置されている。
第1頭部25aの外径R1は、第2頭部25bの外径R2より小さくてもよい。
吐出室15bを、圧力作用室55に連通させてもよい。
圧縮機10は、片頭ピストンを採用した片頭ピストン型斜板式圧縮機であってもよい。
Claims (12)
- 可変容量型斜板式圧縮機であって、
吐出室、及び複数のシリンダボアが形成されたシリンダブロックを有するハウジングと、
前記ハウジングにより回転可能に支持される回転軸と、
前記回転軸の軸線に沿って配列された前記シリンダブロックと前記回転軸との間に設けられるとともに前記回転軸の軸方向へ作用するスラスト力を支持するスラスト軸受と、
前記ハウジング内に形成されるとともに外部から冷媒を取り込む斜板室と、
前記斜板室に収容され、前記回転軸から駆動力を得て回転し、前記回転軸の軸線に直交する方向に対して傾動可能な斜板と、
前記シリンダボアに往復動可能に収納されるピストンと、
前記斜板室内に配置されるとともに前記斜板の傾角を変更可能なアクチュエータとを備え、
前記アクチュエータは、
前記回転軸に設けられる区画体と、
前記斜板室内に設けられると共に前記回転軸の軸線に沿って移動可能な移動体と、
前記区画体と前記移動体とによって区画される制御室であって、前記制御室の内部の圧力によって前記移動体を移動させる制御圧室とを備え、
前記回転軸の軸線に沿った前記移動体の移動に伴い、前記斜板の傾角が変更されて、前記ピストンが前記斜板の傾角に応じたストロークで往復動し、
前記回転軸には、前記吐出室の圧力と前記斜板室の圧力との差圧に基づく荷重が前記スラスト軸受に向けて付与されている、可変容量型斜板式圧縮機。 - 前記回転軸の軸線に沿って配列された前記シリンダブロックと前記回転軸との間には、前記回転軸に対して回転不能に支持されるとともに前記回転軸の軸線に沿って移動可能なスペーサが設けられ、
前記シリンダブロックと前記スペーサとによって、前記吐出室に連通する圧力作用室が区画され、
前記スペーサと前記シリンダブロックとの間には、前記圧力作用室と前記斜板室との間をシールするシール部材が配設されている、請求項1に記載の可変容量型斜板式圧縮機。 - 前記回転軸には、前記回転軸と一体回転可能なスペーサが設けられ、
前記シリンダブロックと前記スペーサとによって、前記吐出室に連通する圧力作用室が区画され、
前記スペーサと前記シリンダブロックとの間には、前記圧力作用室と前記斜板室との間をシールするシール部材が配設されている、請求項1に記載の可変容量型斜板式圧縮機。 - 前記スペーサは、前記回転軸の軸方向に位置する前記シリンダブロック近傍に、前記シリンダブロックと当接する当接部を有している、請求項2又は請求項3に記載の可変容量型斜板式圧縮機。
- 前記ハウジングは、一対のシリンダブロックを有し、
前記一対のシリンダブロックのそれぞれには、対となるシリンダボアが形成され、
前記対となるシリンダボアのそれぞれには、前記ピストンとしての両頭ピストンが往復動可能に収納され、
前記両頭ピストンによって、前記対となるシリンダボアの一方に第1圧縮室が区画され、前記対となるシリンダボアの他方に第2圧縮室が区画され、
前記回転軸と前記斜板との間には、前記回転軸の軸線に直交する方向に対する前記斜板の傾角の変更を許容するリンク機構が設けられ、
前記リンク機構は、前記斜板の傾角の変更に伴い、前記第2圧縮室における前記両頭ピストンの上死点位置が前記第1圧縮室における前記両頭ピストンの上死点位置よりも大きく変位するように配置され、
前記第1圧縮室での前記両頭ピストンから前記斜板に作用する圧縮反力の向きが、前記吐出室の圧力と前記斜板室の圧力との差圧に基づき前記回転軸に付与される荷重の向きと同じである、請求項1~請求項4のいずれか一項に記載の可変容量型斜板式圧縮機。 - 前記対となるシリンダボアの一方に収納される前記両頭ピストンの頭部の外径は、前記対となるシリンダボアの他方に収納される前記両頭ピストンの頭部の外径よりも大きい、請求項5に記載の可変容量型斜板式圧縮機。
- 可変容量型斜板式圧縮機であって、
吐出室、及び複数のシリンダボアが形成されたシリンダブロックを有するハウジングと、
前記ハウジングにより回転可能に支持される回転軸と、
前記回転軸の軸線に沿って配列された前記シリンダブロックと前記回転軸との間に設けられるとともに前記回転軸の軸方向へ作用するスラスト力を支持するスラスト軸受と、
前記ハウジング内に形成されるとともに外部から冷媒を取り込む斜板室と、
前記斜板室に収容され、前記回転軸からの駆動力を得て回転し、前記回転軸の軸線に直交する方向に対して傾動可能な斜板と、
前記シリンダボアに往復動可能に収納されるピストンと、
前記斜板室内に配置されるとともに前記斜板の傾角を変更可能なアクチュエータとを備え、
前記アクチュエータは、
前記回転軸に設けられる区画体と、
前記斜板室内に設けられると共に前記回転軸の軸線に沿って移動可能な移動体と、
前記区画体と前記移動体とによって区画される制御室であって、前記制御室の内部の圧力によって前記移動体を移動させる制御圧室とを備え、
前記回転軸の軸線に沿った前記移動体の移動に伴い、前記制御圧室の圧力が高くなると前記斜板の傾角が大きくなり、前記制御圧室の圧力が低くなると前記斜板の傾角が小さくなるように、前記斜板の傾角が変更されて、前記ピストンが前記斜板の傾角に応じたストロークで往復動し、
前記回転軸には、前記制御圧室の圧力と前記斜板室の圧力との差圧に基づく荷重が前記スラスト軸受に向けて付与されている、可変容量型斜板式圧縮機。 - 前記回転軸の軸線に沿って配列された前記シリンダブロックと前記回転軸との間には、前記回転軸に対して回転不能に支持されるとともに前記回転軸の軸線に沿って移動可能なスペーサが設けられ、
前記シリンダブロックと前記スペーサとによって、前記制御圧室に連通する圧力作用室が区画され、
前記スペーサと前記シリンダブロックとの間には、前記圧力作用室と前記斜板室との間をシールするシール部材が配設されている、請求項7に記載の可変容量型斜板式圧縮機。 - 前記回転軸には、前記回転軸と一体回転可能なスペーサが設けられ、
前記シリンダブロックと前記スペーサとによって、前記制御圧室に連通する圧力作用室が区画され、
前記スペーサと前記シリンダブロックとの間には、前記圧力作用室と前記斜板室との間をシールするシール部材が配設されている、請求項7に記載の可変容量型斜板式圧縮機。 - 前記スペーサは、前記回転軸の軸方向に位置する前記シリンダブロック近傍に、前記シリンダブロックと当接する当接部を有している、請求項8又は請求項9に記載の可変容量型斜板式圧縮機。
- 前記ハウジングは、一対のシリンダブロックを有し、
前記一対のシリンダブロックのそれぞれには、対となるシリンダボアが形成され、
前記対となるシリンダボアのそれぞれには、前記ピストンとしての両頭ピストンが往復動可能に収納され、
前記両頭ピストンによって、前記対となるシリンダボアの一方に第1圧縮室が区画され、前記対となるシリンダボアの他方に第2圧縮室が区画され、
前記回転軸と前記斜板との間には、前記回転軸の軸線に直交する方向に対する前記斜板の傾角の変更を許容するリンク機構が設けられ、
前記リンク機構は、前記斜板の傾角の変更に伴い、前記第2圧縮室における前記両頭ピストンの上死点位置が前記第1圧縮室における前記両頭ピストンの上死点位置よりも大きく変位するように配置され、
前記第1圧縮室での前記両頭ピストンから前記斜板に作用する圧縮反力の向きが、前記制御圧室の圧力と前記斜板室の圧力との差圧に基づき前記回転軸に付与される荷重の向きと同じである、請求項7~請求項10のいずれか一項に記載の可変容量型斜板式圧縮機。 - 前記対となるシリンダボアの一方に収納される前記両頭ピストンの頭部の外径は、前記対となるシリンダボアの他方に収納される前記両頭ピストンの頭部の外径よりも大きい、請求項11に記載の可変容量型斜板式圧縮機。
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Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH07279839A (ja) * | 1994-04-08 | 1995-10-27 | Toyota Autom Loom Works Ltd | 斜板式圧縮機における振動防止構造 |
JPH09151847A (ja) * | 1995-12-04 | 1997-06-10 | Nippon Soken Inc | 斜板型圧縮機 |
WO2014157209A1 (ja) * | 2013-03-29 | 2014-10-02 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
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US4277972A (en) * | 1979-12-06 | 1981-07-14 | Modular Data Systems, Inc. | Engine dynamometer |
JPH028565A (ja) * | 1988-01-11 | 1990-01-12 | Taiho Kogyo Co Ltd | リップシール装置 |
JP3066879B2 (ja) * | 1991-07-16 | 2000-07-17 | 株式会社デンソー | 可変容量式斜板型圧縮機 |
KR100215157B1 (ko) * | 1996-06-19 | 1999-08-16 | 이소가이 지세이 | 가변용량 압축기 및 그 부착방법 |
DE19939131A1 (de) * | 1999-08-18 | 2001-03-08 | Zexel Gmbh | Axialkolbentriebwerk mit einem stufenlos verstellbaren Kolbenhub |
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2016
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- 2016-02-23 WO PCT/JP2016/055241 patent/WO2016140106A1/ja active Application Filing
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JPH07279839A (ja) * | 1994-04-08 | 1995-10-27 | Toyota Autom Loom Works Ltd | 斜板式圧縮機における振動防止構造 |
JPH09151847A (ja) * | 1995-12-04 | 1997-06-10 | Nippon Soken Inc | 斜板型圧縮機 |
WO2014157209A1 (ja) * | 2013-03-29 | 2014-10-02 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
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