US20120073430A1 - Variable Displacement Compressor - Google Patents

Variable Displacement Compressor Download PDF

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Publication number
US20120073430A1
US20120073430A1 US13/376,346 US201013376346A US2012073430A1 US 20120073430 A1 US20120073430 A1 US 20120073430A1 US 201013376346 A US201013376346 A US 201013376346A US 2012073430 A1 US2012073430 A1 US 2012073430A1
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United States
Prior art keywords
chamber
swash plate
intermediate pressure
suction
variable displacement
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Abandoned
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US13/376,346
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English (en)
Inventor
Iwao Uchikado
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Sanden Corp
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Individual
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Publication of US20120073430A1 publication Critical patent/US20120073430A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—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
    • 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
    • F04B27/14—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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/185—Discharge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a variable displacement compressor, and specifically, to a variable displacement compressor in which reduction of pulsation and improvement of durability and resistance to pressure can be performed and a tilt angle of a swash plate can be controlled more smoothly and precisely via an axial movement member.
  • a variable displacement compressor which is provided with a cylinder head in which a suction chamber and a discharge chamber are formed, a cylinder block having a cylinder bore into which a piston is inserted at a condition capable of being reciprocated, a crank chamber formed by the cylinder block and a front housing, a swash plate which is disposed in the crank chamber and which is rotated with a main shaft and is supported so that a tilt angle thereof can be changed relative to the main shaft, and a movement conversion mechanism for converting rotational movement of the swash plate to reciprocating movement of the piston.
  • a wabble plate type variable displacement compressor wherein the above-described movement conversion mechanism has a wabble plate in which a rotational movement of the swash plate is converted into a wabble movement of the wabble plate, and which transmits the wabble movement to the pistons to reciprocate the pistons, and a rotation preventing mechanism of the wabble plate, and the rotation preventing mechanism of the wabble plate comprises (a) an inner ring provided in a housing movably in an axial direction while being prevented with rotation and having a plurality of guide grooves for guiding a plurality of balls provided for power transmission, (b) an outer ring having a plurality of guide grooves for guiding the balls at positions opposing respective guide grooves of the inner ring, connected with the wabble plate on an outer circumference of the outer ring and supported at a condition capable of being wabbled together with the wabble plate, and (c) a plurality of balls held by the guide
  • FIG. 11 shows a state achieving the maximum displacement (maximum cam angle [maximum swash plate angle]) and FIG. 12 shows a state achieving the minimum displacement (minimum cam angle [minimum swash plate angle]), respectively.
  • a swash plate 206 is provided at a condition capable of changing its tilt angle and being rotated integrally with main shaft 204 via a hinge mechanism 205 .
  • a rotation preventing mechanism 210 of wabble plate 207 comprises (i) an inner ring 213 provided movably in an axial direction although the rotation is prevented through a spline engagement mechanism 211 , provided free to be rotated relatively to main shaft 204 , and having a plurality of guide grooves for guiding a plurality of balls 212 provided for power transmission, (ii) a sleeve 214 functioning as a wabble central member of the wabble movement of wabble plate 207 , provided at a condition capable of rotating and moving in an axial direction relatively to main shaft 204 , and engaged with inner ring 213 movably in an axial direction together with inner ring 213 , (iii) an outer ring 214 having a plurality of guide groove
  • a suction chamber 217 and a discharge chamber 218 are formed in a cylinder head 216 .
  • the intake gas to the compressor is taken into suction chamber 217 from a suction port 219 through a suction throttle valve 220 in the example shown in the figures, the gas compressed in a cylinder bore 221 by piston 209 is discharged into discharge chamber 218 , and in the example shown in the figures, therefrom the gas is sent to an external circuit through a discharge interruption valve 222 and a discharge port 223 .
  • variable displacement compressors including the aforementioned conventional general variable displacement compressor and the above-described wabble plate type variable displacement compressor previously proposed by the applicant of the present application, as exemplified also in FIG. 11 , usually, a communication path 225 for introducing the discharge gas controlled from the pressure Pd in discharge chamber 218 by a control valve 224 or a throttle into crank chamber 203 and a communication path 227 for returning the crank chamber gas to suction chamber 217 side (pressure: Ps) through a control valve or a throttle 226 are provided, and by changing the opening degree of control valve 224 , the gas pressure Pc in crank chamber 203 is controlled.
  • a communication path 225 for introducing the discharge gas controlled from the pressure Pd in discharge chamber 218 by a control valve 224 or a throttle into crank chamber 203 and a communication path 227 for returning the crank chamber gas to suction chamber 217 side (pressure: Ps) through a control valve or a throttle 226 are provided, and by changing the opening degree of control valve 224 , the gas pressure
  • a couple moment generated by the rotation of rotational parts including swash plate 206 system parts (in case having wabble plate 207 , a structure including the wabble plate 207 ), and a couple moment generated by the reciprocal movement of reciprocal movement system parts including piston 209 system parts, are generated as a couple moment acting in a direction for changing a cam angle by the operation of the compressor, in accordance with the cam angle, for example, as shown in FIG. 13 , and the total couple moment due to the rotational and reciprocal movements of those parts becomes, for example, as shown in FIG.
  • the total couple moment acts in a direction for increasing the displacement (cam angle) at every cam angle). Then, separately from the couple moment due to the rotational and reciprocal movements of these parts, because distributions of gas pressure are generated in respective spaces in the compressor by the compression operation of the compressor and the pressure control operation of control valves, by these distributions of gas pressure, for example, as shown in FIG. 14 , a couple moment in a direction for increasing or decreasing the cam angle is generated.
  • the cam angle is adjusted so as to become an arbitrary predetermined angle and the displacement of the compressor is controlled at a desired displacement.
  • Pc crank chamber pressure (gas pressure to be controlled)
  • Ps suction pressure
  • Pd discharge pressure
  • Ap area of piston (cylinder bore)
  • L 1 distance from momentary rotation center of cam angle change to line of action of pressure applied to piston in compression stroke
  • L 2 distance from momentary rotation center of cam angle change to line of action of pressure applied to piston in suction stroke
  • M 1 moment in a direction for increasing cam angle
  • M 2 moment in a direction for decreasing cam angle
  • L 1 is set to be small so that a load due to the discharge pressure does not influence the control of the swash plate cam angle. Therefore, if a differential pressure between the crank chamber pressure and the suction pressure is adjusted, the cam angle can be controlled so as to be balanced with the couple moment due to the rotational and reciprocal movements of the respective parts shown in FIG. 13 . Further, with respect to M 1 and M 2 shown in FIG. 14 , actually M 1 and M 2 are calculated for all pistons.
  • variable displacement compressor having such a conventional structure, because a control gas with relatively high temperature and high pressure, which is reduced in pressure from the discharge pressure, is introduced into the crank chamber, the durability for rotational and drive parts and for a seal portion is disadvantageous. Further, in order to solve or reduce a noise problem originating from pulsation of suction or discharge, etc., there is a case where a pulsation reducing element such as a throttle valve or a muffler is incorporated into a cylinder head, but if do so, the design freedom on layout in relation to a control valve or a refrigerant interruption valve required for a clutchless type becomes low.
  • control of the displacement is performed basically by controlling the gas pressure of the crank chamber by adjusting the pressure difference between the crank chamber pressure and the discharge chamber pressure or between the crank chamber pressure and the suction chamber pressure by changing the opening degree of the control valve, namely, because the control of the displacement (swash plate tilt angle) is performed only by control of gas pressure, there is a limit in control accuracy as compared with the control in the present invention described later which utilizes one to one mechanical correspondence between the axial position of an axial movement member and the tilt angle of the swash plate.
  • a structure of a compressor wherein, in order to aim cooling and lubrication of respective sliding portions and reduction of pulsation of suction and in order to suppress elevation of discharge temperature, a suction hole for refrigerant gas connected to an external circuit is opened to a crank chamber, and suction gas is introduced from the crank chamber into a suction chamber formed in a cylinder head through a communication path formed in a cylinder block (for example, Patent documents 2 and 3).
  • an object of the present invention is to provide a variable displacement compressor excellent in performance and property which can achieve to improve the performance of the compressor such as reduction of pulsation and improvement of durability and resistance to pressure and which can control the tilt angle of a swash plate at a target tilt angle more smoothly and precisely via an axial movement member.
  • a variable displacement compressor has a cylinder head in which a suction chamber and a discharge chamber are formed, a cylinder block having a cylinder bore into which a piston is inserted at a condition capable of being reciprocated, a crank chamber formed by the cylinder block and a front housing, a swash plate which is disposed in the crank chamber and which is rotated with a main shaft and is supported so that a tilt angle thereof can be changed relative to the main shaft, and a movement conversion mechanism for converting rotational movement of the swash plate to reciprocating movement of the piston, and is characterized in that a suction path for intake of a suction gas into the compressor is formed so as to open into the crank chamber, a communication path for communicating the crank chamber and the suction chamber is provided in the cylinder block, an axial movement member, which can move in a direction along an axis of the main shaft in an essentially one to one correspondence with the tilt angle of the swash plate, is provided around the main shaft, the
  • the suction path for intake of suction gas into the compressor from outside is not directly opened into the suction chamber formed in the cylinder head, but first it is opened into the crank chamber, and the suction gas introduced into the crank chamber is introduced into the suction chamber through the communication path provided in the cylinder block. Therefore, because the crank chamber great in capacity becomes a suction chamber relative to an external circuit, noise originating from pulsation of suction can be prevented or reduced. Further, by this structure, since it becomes possible to reduce the capacity of the suction chamber formed in the cylinder head, by an amount of the reduction, the capacity of the discharge chamber can be increased, noise originating from pulsation of discharge can also be prevented or reduced.
  • crank chamber becomes a suction gas atmosphere and the temperature and the pressure are reduced, the durability of a seal member or a drive part for the main shaft can be improved, and the pressure resistance of a housing part forming the crank chamber can be relatively improved. If the pressure resistance of a housing part, particularly, a front housing, is improved, lightening in weight due to thinning and the like becomes possible.
  • the pressure in the crank chamber and the intermediate pressure controlled by the intermediate pressure control mechanism are applied to the respective ends of the axial movement member which can move in a direction along the axis of the main shaft in an essentially one to one correspondence with the tilt angle of the swash plate, by this the axial position of the axial movement member is controlled precisely, and via the positional control, the tilt angle of the swash plate and the displacement of the compressor are controlled precisely.
  • This positional control in an axial direction of the axial movement member is performed in accordance with a pressure difference between the gas pressure of the crank chamber side (suction gas pressure) applied to one end of the axial movement member and an intermediate pressure between the discharge gas pressure and the suction gas pressure applied to the other end, and because this intermediate pressure cannot be made lower than the suction gas pressure applied to the opposite side, only by the gas pressures applied to both ends of this axial movement member, the axial movement member can be controlled only in a direction for increasing the cam angle (tilt angle of the swash plate).
  • the cam angle tilt angle of the swash plate
  • the cam angle is decided by the total balance of the couple moment generated by the gas pressures in the respective spaces in the compressor which act in the cam angle increasing/decreasing direction and the couple moment generated by the rotational and reciprocal movements of the respective parts in the compressor, for example, by setting the cam profile so that an adequate couple moment in a direction for decreasing the cam angle is generated by the operation of discharge gas to the piston, by setting so that the total balance of couple moments generated by the rotational and reciprocal movements of the respective parts in the compressor becomes one in a direction for decreasing the cam angle (a direction for decreasing the tilt angle of the swash plate, namely, a direction for decreasing the displacement) at every cam angle (tilt angle of the swash plate), or by employing both of these, the positional control in the axial direction becomes possible only by the control of the above-described intermediate pressure, via this control a precise and smooth displacement control becomes possible, and the starting shock particularly at a high-speed condition can be relieved,
  • the total balance of the couple moments generated by the rotational and reciprocal movements of the respective parts in the compressor acts in a direction for decreasing the cam angle in every region for changing the cam angle, for example, in case of a clutchless type drive force transmission system, maintenance of compressor operation off mode (namely, a mode for keeping the tilt angle of the swash plate at a minimum angle) becomes possible without performing to increase the pressure in the crank chamber, etc., the circulation amount of refrigerant in the compressor at the time of compressor operation off mode decreases, and by the amount of the decrease, it becomes possible to reduce the consumption power.
  • compressor operation off mode namely, a mode for keeping the tilt angle of the swash plate at a minimum angle
  • variable displacement compressor as the route of the above-described suction path formed so as to open into the crank chamber, various embodiments can be employed as follows.
  • a structure can be employed wherein the suction path is formed in the front housing, and the suction gas is taken directly into the crank chamber from an external circuit.
  • a structure can also be employed wherein the suction path is formed from the cylinder block to the front housing, and the suction gas from an external circuit is once taken into a cylinder block portion and therefrom taken into the crank chamber through a front housing portion.
  • a structure can also be employed wherein the suction path is formed from the cylinder head to the front housing through the cylinder block (by positioning the cylinder block therebetween), and the suction gas from an external circuit is once taken into a cylinder head portion (a portion different from the suction chamber formed in the cylinder head) and therefrom taken into the crank chamber through a cylinder block portion and a front housing portion.
  • the intermediate pressure control mechanism has a communication path (A) between the discharge chamber and the intermediate pressure chamber, a control valve provided in the communication path (A) and capable of controlling pressure reduction from a pressure in the discharge chamber to a predetermined intermediate pressure, a communication path (B) between the intermediate pressure chamber and the suction chamber, and a throttle provided in the communication path (B).
  • the intermediate pressure control mechanism has a communication path between the discharge chamber and the intermediate pressure chamber, a communication path between the intermediate pressure chamber and the suction chamber, and a control valve which is provided in both communication paths and which can control pressure reduction from a pressure in the discharge chamber to a predetermined intermediate pressure and can control a degree of throttling for a gas flow from the intermediate pressure chamber to the suction chamber.
  • the intermediate pressure control mechanism has a communication path (A) between the discharge chamber and the intermediate pressure chamber, a throttle provided in the communication path (A), a communication path (B) between the intermediate pressure chamber and the suction chamber, and a control valve provided in the communication path (B) and capable of controlling pressure reduction to a predetermined intermediate pressure in the intermediate pressure chamber.
  • the seal member provided at the other end side of the axial movement member may be a seal member allowing a leakage from the intermediate pressure chamber to the crank chamber corresponding to the amount of gas flow passing through the throttle present between the intermediate pressure chamber and the suction chamber, and in this case, it is possible to omit the communication path from the intermediate pressure chamber to the suction chamber and the throttle in the communication path.
  • the above-described movement conversion mechanism can employ various embodiments as follows.
  • a structure can be employed wherein the movement conversion mechanism has a wabble plate in which the rotational movement of the swash plate is converted into a wabble movement of the wabble plate and which transmits the wabble movement to the piston via a connecting rod and makes the piston reciprocate, and a rotation preventing mechanism of the wabble plate.
  • the movement conversion mechanism is structured as a so-called wabble plate type variable displacement compressor.
  • the structure described in Patent document 1 that is a previous application by the applicant of the present application can be employed.
  • a structure can be employed wherein the above-described rotation preventing mechanism of the wabble plate comprises (a) an inner ring provided in a housing movably in an axial direction although rotation is prevented, and having a plurality of guide grooves for guiding a plurality of balls provided for power transmission, (b) an outer ring having a plurality of guide grooves for guiding the balls at positions opposing respective guide grooves of the inner ring, connected with the wabble plate at an outer circumference and supported at a condition capable of wabbling together with the wabble plate, and (c) a plurality of balls held by the guide grooves formed in the inner ring and the outer ring at a condition of opposing each other and performing power transmission by being compressed between the guide grooves, and in this case, the inner ring may be formed as the above-described axial movement member.
  • the above-described rotation preventing mechanism of the wabble plate further comprises (d) a sleeve functioning as a wabble central member of the wabble movement of the wabble plate, provided on the main shaft to rotate relatively to the main shaft and to move in an axial direction, and engaged with the inner ring movably in an axial direction together with the inner ring, and the outer ring is supported on the sleeve wabblingly.
  • variable displacement compressor except employing the structure of the above-described wabble plate type variable displacement compressor, for example, an embodiment may be employed wherein the above-described movement conversion mechanism is formed as a mechanism for conversion into reciprocal movement of the piston via a pair of shoes slid on both surfaces of an outer circumference of the swash plate.
  • variable displacement compressor in order to be able to control the tilt angle of the swash plate at a target tilt angle efficiently, precisely and quickly, it is preferred to add a device to a cam mechanism for changing the tilt angle of the swash plate.
  • the tilt angle of the swash plate can be changed through a cam mechanism interposed between the main shaft and the swash plate, and a cam profile of the cam mechanism is set so that a momentary rotation center of the swash plate is given at a position at which a load due to a compression reactive force of at least one piston among a plurality of pistons present in a compression stroke operates as a couple moment acting in a direction for decreasing displacement relatively to the swash plate.
  • a concrete example of this mechanism will be explained in detail in the embodiment of the present invention described later.
  • such a mechanism can be realized as follows.
  • the above-described cam mechanism comprises a sliding engagement mechanism formed by a slot formed on one of an arm extending from main shaft side and an arm extending from swash plate side and a pin provided on the other, and the above-described cam profile is set by forming a shape of the slot as an S-shape.
  • respective parts are set so that a total balance of a couple moment generated in a tilt angle changing plane of the swash plate by at least rotational and reciprocal movement of the respective parts becomes one in a direction for decreasing tilt angle in every tilt angle of the swash plate.
  • the total balance of the couple moment of the swash plate due to the rotational and reciprocal movements of respective parts always acts in a direction for decreasing the tilt angle of the swash plate, namely, since it always acts in desired one direction, as long as the aforementioned intermediate pressure applied to the other end of the axial movement member is controlled, it becomes possible to control the tilt angle of the swash plate at a target tilt angle easily and precisely.
  • the axial movement member can be operated only in a direction for increasing the cam angle (the tilt angle of the swash plate).
  • the cam angle the tilt angle of the swash plate
  • a couple moment for decreasing the tilt angle always acts to the swash plate, for example, in case where the compressor operation off mode is required to be kept, etc., only by driving and rotating the compressor the swash plate is naturally changed in angle in a direction of a minimum tilt angle, and after changed to the minimum tilt angle, the swash plate is maintained at the minimum tilt angle.
  • this embodiment is effective for a case where the swash plate to be changed in tilt angle is required to be always pushed in a direction for decreasing the tilt angle regardless of change of the tilt angle, etc.
  • variable displacement compressor by the structure where the suction gas is taken into the crank chamber through the suction path opening into the crank chamber, noise originating from pulsation of suction can be prevented or reduced by functioning the crank chamber with a great capacity as a suction chamber. Further, because a suction throttle valve is omitted, the design freedom on layout of cylinder head can be increased. Further, by the structure where the suction gas is introduced into the suction chamber formed in the cylinder head from the crank chamber through the communication path, because it becomes possible to reduce the capacity of the suction chamber, and by the amount of the reduction, the capacity of the discharge chamber can be increased, noise originating from pulsation of discharge can also be prevented or reduced.
  • the temperature and pressure in the crank chamber can be reduced, the durability of the respective drive parts and the pressure resistance of a housing part can be improved, and it becomes possible to thin the housing part and make the whole of the compressor small and light in weight.
  • the pressure in the crank chamber and the intermediate pressure controlled by the intermediate pressure control mechanism are applied to the respective ends of the axial movement member and the axial position of the axial movement member is controlled precisely, through the position control, it becomes possible to control the tilt angle of the swash plate and the displacement of the compressor stably and precisely.
  • FIG. 1 is a vertical sectional view of a variable displacement compressor according to a first embodiment of the present invention showing a state at the time of a maximum tilt angle of a swash plate.
  • FIG. 2 is an enlarged partial sectional view of the variable displacement compressor depicted in FIG. 1 .
  • FIG. 3 is a vertical sectional view of the variable displacement compressor depicted in FIG. 1 showing a state at the time of a minimum tilt angle of the swash plate.
  • FIG. 4 is an enlarged partial sectional view of the variable displacement compressor depicted in FIG. 3 .
  • FIG. 5 is a diagram indicating a relationship between a cam angle and a couple moment, showing a balance of the couple moments due to rotational and reciprocal movements of respective parts of the variable displacement compressor depicted in FIG. 1 .
  • FIG. 6 is an explanation diagram showing a balance of a couple moment due to gas pressures of the variable displacement compressor depicted in FIG. 1 .
  • FIG. 7 is a partial vertical sectional view of a variable displacement compressor according to a second embodiment of the present invention.
  • FIG. 8 is a vertical sectional view of a variable displacement compressor according to a third embodiment of the present invention.
  • FIG. 9 is a vertical sectional view of a variable displacement compressor according to a fourth embodiment of the present invention.
  • FIG. 10 is a vertical sectional view of a variable displacement compressor according to a fifth embodiment of the present invention.
  • FIG. 11 is a vertical sectional view of a conventional variable displacement compressor at the time of a maximum tilt angle of a swash plate.
  • FIG. 12 is a vertical sectional view of the variable displacement compressor depicted in FIG. 11 at the time of a minimum tilt angle of the swash plate.
  • FIG. 13 is a diagram indicating a relationship between a cam angle and a couple moment, showing a balance of the couple moments due to rotational and reciprocal movements of respective parts of the variable displacement compressor depicted in FIG. 11 .
  • FIG. 14 is an explanation diagram showing a balance of a couple moment due to gas pressures of the variable displacement compressor depicted in FIG. 11 .
  • FIGS. 1 to 6 show a variable displacement compressor according to a first embodiment of the present invention.
  • FIG. 1 shows a state at the time of a maximum displacement (a maximum cam angle [a maximum swash plate angle]) of a variable displacement compressor 1
  • FIG. 3 shows a state at the time of a minimum displacement (a minimum cam angle [a minimum swash plate angle]).
  • a main shaft 5 is inserted into a crank chamber 4 formed by a front housing 2 and a cylinder block 3 , relatively to main shaft 5 , provided is a rotor 6 which is fixed to main shaft 5 and rotated integrally with main shaft 5 , and disposed is a swash plate 7 which can be changed in its tilt angle relative to main shaft 5 and which can be rotated integrally with main shaft 5 .
  • a hinge mechanism 12 forming a sliding mechanism wherein an arm 8 extending from rotor 6 side (main shaft 5 side) and an arm 9 extending from swash plate 7 side are provided, a slot 10 is provided on arm 9 side and a pin 11 engaging slot 10 is provided on arm 8 side, and via the hinge mechanism 12 , swash plate 7 is provided at a condition capable of being changed in tilt angle and being rotated integrally with main shaft 5 .
  • a counter weight 13 is embedded or attached in order to achieve a rotational balance between swash plate 7 and the rotation mechanism including hinge mechanism 12 .
  • slot 10 is formed as an S shape in order to set the cam profile of the cam mechanism due to hinge mechanism 12 , as described later in detail using FIG. 5 , so that a momentary rotation center of swash plate 7 is given at a position at which a load due to a compression reactive force of at least one piston among a plurality of pistons present in a compression stroke operates as a couple moment acting in a direction for decreasing displacement relatively to swash plate 7 .
  • a suction port 14 is provided directly on front housing 2 , and a suction path 15 for taking suction gas from outside into crank chamber 4 is formed only on front housing 2 .
  • a wabble plate type variable displacement compressor 1 in which provided is a wabble plate 18 which is free to rotate relatively to swash plate 7 via bearings 16 , 17 and whose wabble movement is only allowed at a condition prevented with its rotation.
  • the rotational movement of swash plate 7 is converted into the wabble movement of wabble plate 18
  • the wabble movement is the reciprocal movement of a piston 21 which is inserted into a cylinder bore 20 at a condition free to be reciprocated, through a connecting rod 19 .
  • Rotation preventing mechanism 22 of wabble plate 18 is formed as a mechanism comprising (i) an inner ring 27 provided movably in an axial direction although the rotation is prevented through a spline engagement mechanism 24 formed between it and a center hole 23 of cylinder block 3 , provided free to be rotated relatively to main shaft 5 via a bearing 48 , and having a plurality of guide grooves 26 for guiding a plurality of balls 25 provided for power transmission, (ii) a sleeve 28 functioning as a wabble central member of the wabble movement of wabble plate 18 , provided at a condition capable of rotating and moving in an axial direction relatively to main shaft 5 , and engaged with inner ring 27 movably in an axial direction together with inner ring 27 , (iii) an outer ring 30 having a plurality of guide grooves 29 for guiding balls 25 at positions opposing respective guide grooves 26 of inner ring 27 , supported on sleeve 28 wabblingly, and supporting wabble plate 18 fixedly on its outer circum
  • Inner ring 27 in this rotation preventing mechanism 22 of wabble plate 18 forms an axial movement member according to the present invention, which can move in a direction along an axis of main shaft 5 in an essentially one to one correspondence with the tilt angle of swash plate 7 .
  • a suction chamber 32 is formed at the radially outside position and a discharge chamber 33 is formed at the radially inside position, respectively.
  • the suction gas into the compressor is, first, taken into crank chamber 4 from suction port 14 through suction path 15 , from crank chamber 4 , it is introduced into suction chamber 32 through a communication path 34 formed in cylinder block 3 , and therefrom, it is taken into cylinder bore 20 to be served to the compression stroke due to piston 21 .
  • the gas compressed by piston 21 in cylinder bore 20 is discharged into discharge chamber 33 , and in the embodiment shown in the figure, therefrom, it is sent to an external circuit through a discharge interruption valve 35 and a discharge port 36 .
  • the gas pressure (Ps) of crank chamber 4 side is applied to one end of the above-described inner ring 27 as the axial movement member, and to the other end, an intermediate pressure (Pm) between the pressure (Pd) in discharge chamber 33 and the pressure (Ps) in suction chamber 32 .
  • an intermediate pressure chamber 38 sealed by seal members 37 and 45 relatively to crank chamber 4 side, and the pressure in intermediate pressure chamber 38 is controlled at the above-described predetermined intermediate pressure (Pm) by an intermediate pressure control mechanism 39 .
  • This intermediate pressure control mechanism 39 is formed as follows in this embodiment.
  • a communication path 40 is provided between discharge chamber 33 and intermediate pressure chamber 38 , in the communication path 40 disposed is a control valve 41 capable of controlling pressure reduction from the pressure (Pd) in discharge chamber 33 to a predetermined intermediate pressure (Pm), a communication path 42 is provided between intermediate pressure chamber 38 and suction chamber 32 , and in the communication path 42 , formed is an throttle 43 (orifice) capable of reducing the pressure from intermediate pressure (Pm) to the pressure (Ps) in suction chamber 32 .
  • the above-described intermediate pressure chamber 38 is formed between the rear end portion (the other end portion) of inner ring 27 and a valve plate 44 at the rear end portion of main shaft 5 , and this intermediate pressure chamber 38 becomes a condition shown in FIG. 2 in correspondence with the condition shown in FIG. 1 , and is interposed between main shaft 5 and inner ring 27 , both members are supported at a condition free to be relatively rotated and inner ring 27 is supported movably in an axial direction relatively to main shaft 5 . It is sealed in pressure relatively to crank chamber 4 side by the aforementioned seal members 37 and 45 . As shown in FIG.
  • an axial load is generated by a pressure difference between the intermediate pressure Pm applied to an annular pressure receiving surface 46 surrounded by seal members 37 , 45 and the pressure of crank chamber 4 side applied to the opposite side.
  • Intermediate pressure chamber 38 becomes a condition shown in FIG. 4 in correspondence with the condition shown in FIG. 3 , seal members 37 , 45 are sealed slidably in an axial direction, and at the time of minimum cam angle (minimum tilt angle of swash plate), accompanying with the slide movement of inner ring 27 , the capacity of intermediate pressure chamber 38 is decreased.
  • a clutchless type compressor in which a rotational drive force from a power source (not shown in the figure) is transmitted directly to main shaft 5 via a pulley 47 , is exemplified in the above-described embodiment, it is possible to form it as a clutch type compressor in which therebetween a clutch (in particular, an electromagnetic clutch) (not shown in the figure) capable of switching between the power transmission interrupted condition and the power transmission condition is interposed.
  • a clutch in particular, an electromagnetic clutch
  • variable displacement compressor 1 In variable displacement compressor 1 thus constructed, suction path 15 taking the suction gas from outside into compressor 1 is formed only in front housing 2 , the suction gas taken through suction path 15 is first sucked into crank chamber 4 , and therefrom, introduced into suction chamber 32 through communication path 34 . Therefore, because crank chamber 4 having a large capacity becomes a suction chamber relative to an external circuit, noise originating from suction pulsation is prevented or reduced. Further, because a suction throttle valve can be omitted, the design freedom on layout of cylinder head 31 can be increased.
  • crank chamber 4 becomes a suction gas atmosphere and the temperature and pressure thereof can be reduced as compared with those in a conventional structure, the durability of respective drive parts including rotor 6 , bearings supporting it, hinge mechanism 12 , etc. can be improved, and further, the pressure resistance of housing parts (in particular, front housing 2 ) forming crank chamber 4 may be improved relatively. In particular, if the pressure resistance of front housing 2 is improved, it can be made thinner, and can be made small-sized and light in weight.
  • the tilt angle of swash plate 7 and the displacement of compressor 1 can be controlled via the positional control of the axial movement member (inner ring 27 ) movable in a direction along the axis of main shaft 5 in an essentially one to one correspondence with the tilt angle of swash plate 7 , it becomes possible to depend the control of the tilt angle of swash plate 7 on the mechanical accuracy, and it becomes possible to improve the control precision greatly.
  • FIG. 5 shows a balance of couple moments due to rotational and reciprocal movements of respective parts in compressor 1
  • FIG. 6 shows a balance of a couple moment due to gas pressures applied to respective parts in compressor 1 . Meanings of respective symbols in FIG. 6 are as follows.
  • M ⁇ ⁇ 1 Ps ⁇ Ap ⁇ L ⁇ ⁇ 1 + Pm ⁇ As ⁇ L ⁇ ⁇ 3 + Ps ⁇ Ap ⁇ L ⁇ ⁇ 2
  • M 1 and M 2 shown in FIG. 6 actually M 1 and M 2 are calculated for all pistons. Further, it is preferred that Ap and As, and L 1 and L 3 , are set so as to become adequate relationships, respectively.
  • the moment of piston 21 in suction stroke is cancelled because the pressures at it front and rear sides are same pressure (Ps).
  • the cam angle of the swash plate can be controlled optimum by controlling the pressure difference between Pm and Ps at a condition where the position of momentary rotation center (C) is set at an adequate position (namely, the cam profile in the cam mechanism is set adequately) and the pressure receiving area of inner ring 27 is set at an adequate size. More accurately, by the pressure difference between Pm and Ps, the moment of the system including inner ring 27 is decided, and the balance of respective moments is taken.
  • the balance of the couple moments due to the rotational and reciprocal movements in the above-described compressor 1 is preferably set so as to become the property shown in FIG. 5 .
  • the balance of the couple moment due to the gas pressures in the above-described compressor 1 becomes a moment for urging in a direction for increasing the cam angle when the intermediate pressure Pm is increased, as the balance of the couple moments due to the rotational and reciprocal movements of respective parts, as shown in FIG. 5 , it is preferably set so as to be urged in a direction for decreasing the cam angle at every cam angle.
  • FIG. 5 even at a minimum cam angle, it is set so that the total couple moment always acts in a direction for decreasing the cam angle.
  • counter weight 13 also can contribute this desirable setting.
  • FIG. 7 shows a main portion of a variable displacement compressor 51 according to a second embodiment of the present invention.
  • the intermediate pressure (Pm) is introduced into intermediate pressure chamber 38 after the discharge gas is controlled by a control valve 52 disposed in communication path 40 from discharge chamber 33 in cylinder head 31 to intermediate pressure chamber 38 , and returned from intermediate pressure chamber 38 into suction chamber 32 again through control valve 52 in a communication path 53 from intermediate pressure chamber 38 to suction chamber 32 .
  • the intermediate pressure (Pm) is controlled by the control of control valve 52 for adjusting the introduction amount into intermediate pressure chamber 38 and the relief amount from intermediate pressure chamber 38 .
  • the other structures are formed correspondingly to the first embodiment shown in FIG. 1 . Also in such a structure, operation and advantage similar to those in the aforementioned first embodiment can be obtained, and further, simplification of the intermediate pressure control mechanism becomes possible.
  • FIG. 8 shows a variable displacement compressor 61 according to a third embodiment of the present invention.
  • a suction path 62 is formed from a suction port 64 provided in a cylinder head 63 up to cylinder block 65 and front housing 66 .
  • a communication path 68 from a crank chamber 67 to suction chamber 32 in cylinder head 63 is formed by utilizing an insertion hole of a fastening bolt 69 for front housing 66 , cylinder block 65 and cylinder head 63 .
  • intermediate pressure (Pm) is introduced into intermediate pressure chamber 38 as a pressure reduced from the pressure (Pd) in discharge chamber 33 by a throttle 70 , and returned into suction chamber 32 through a control valve 72 disposed in a communication path 71 from intermediate pressure chamber 38 to suction chamber 32 .
  • the other structures are formed correspondingly to the first embodiment shown in FIG. 1 . Also in such a structure, operation and advantage similar to those in the aforementioned first embodiment can be obtained.
  • FIG. 9 shows a variable displacement compressor 81 according to a fourth embodiment of the present invention.
  • a suction chamber 83 is formed at the radially inner side and a discharge chamber 84 is formed at the radially outer side.
  • a suction path 86 of the suction gas to a crank chamber 85 is formed up to a front housing 90 through a suction port 88 and a suction muffler chamber 89 provided in a cylinder block 87 .
  • a communication path 91 from crank chamber 85 to suction chamber 83 in cylinder head 82 is disposed straightly at the radially inner side between cylinder bores 20 in cylinder block 87 .
  • the intermediate pressure (Pm) is introduced into intermediate pressure chamber 38 after being controlled a control valve 93 disposed in a communication path 92 from discharge chamber 84 to intermediate pressure chamber 38 , and from intermediate pressure chamber 38 , returned to suction chamber 32 after being reduced by a throttle 94 .
  • the other structures are formed correspondingly to the first embodiment shown in FIG. 1 . Also in such a structure, operation and advantage similar to those in the aforementioned first embodiment can be obtained, and further, formation of communication path 91 in cylinder block 87 can be facilitated. Further, since the pulsation of suction damped at suction muffler chamber 89 is further damped at crank chamber 85 , the pulsation of suction can be damped more surely. Further, also with respect to the discharge gas, if it may be discharged via a discharge muffler chamber 95 through a discharge interruption valve 96 and a discharge port 97 , the pulsation of discharge can also be damped.
  • FIG. 10 shows a variable displacement compressor 101 according to a fifth embodiment of the present invention.
  • Wabble plate 18 as shown in the above-described first to fourth embodiments is not provided, and it is structured as a so-called single sided swash plate type variable displacement compressor 101 .
  • the movement conversion mechanism from the rotational movement of a swash plate 102 to the reciprocal movement of a piston 103 is formed as a mechanism for conversion into the reciprocal movement of piston 103 via a pair of shoes 104 slid on both surfaces of the outer circumference of swash plate 102 .
  • a sleeve 106 is provided around a main shaft 105 movably on main shaft 105 in an axial direction at a condition prevented in rotation by spline mechanism 24 .
  • a thrust bearing 107 is provided at the front side of sleeve 106 , and it is structured so that the central portion of swash plate 102 can move in an axial direction integrally with sleeve 106 together with the thrust bearing 107 and a collar 108 free to move in an axial direction.
  • a reducing spring 109 is provided for urging swash plate 102 in a direction for decreasing the tilt angle (namely, in a direction for decreasing the cam angle of the cam mechanism formed by hinge mechanism 12 ), thereby always urging swash plate 102 in a direction of minimum tilt angle.
  • collar 108 and reducing spring 109 rotate integrally with main shaft 105 together with swash plate 102 , the swash plate 102 is supported on collar 108 at a condition capable of changing the tilt angle within the tilt angle changing plane.
  • intermediate pressure chamber 38 At the other end side of sleeve 106 , formed is intermediate pressure chamber 38 similarly to in the first embodiment, and in the intermediate pressure chamber 38 , provided is a return spring 110 for urging swash plate 102 , which has been changed in angle to the minimum tilt angle side, in a direction for increasing the tilt angle.
  • the other structures are formed correspondingly to the first embodiment shown in FIG. 1 , and therefore, the explanation is omitted by labeling the same symbols used in FIG. 1 . Even in such a single sided swash plate type variable displacement compressor, operation and advantage similar to those in the first embodiment can be obtained.
  • variable displacement compressor according to the present invention can be applied to any variable displacement compressor having a predetermined axial movement member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US13/376,346 2009-06-05 2010-06-03 Variable Displacement Compressor Abandoned US20120073430A1 (en)

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JP2009-136544 2009-06-05
JP2009136544A JP5519193B2 (ja) 2009-06-05 2009-06-05 可変容量圧縮機
PCT/JP2010/003724 WO2010140374A1 (ja) 2009-06-05 2010-06-03 可変容量圧縮機

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US20140033911A1 (en) * 2012-08-04 2014-02-06 Robert Bosch Gmbh Hydrostatic axial piston machine
US20140377087A1 (en) * 2012-02-06 2014-12-25 Sanden Corporation Variable Displacement Compressor
US20150118073A1 (en) * 2012-04-25 2015-04-30 Sanden Corporation Variable-Capacity Comprenssor And Method For Manufacturing Same
US20150275872A1 (en) * 2014-03-27 2015-10-01 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9228577B2 (en) 2012-11-05 2016-01-05 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9228576B2 (en) 2012-11-05 2016-01-05 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9273679B2 (en) 2013-03-27 2016-03-01 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate compressor
US20160069334A1 (en) * 2013-03-29 2016-03-10 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
US9309875B2 (en) 2012-11-05 2016-04-12 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9309874B2 (en) 2012-11-05 2016-04-12 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9316217B2 (en) 2012-11-05 2016-04-19 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US20160153436A1 (en) * 2014-11-27 2016-06-02 Kabushiki Kaisha Toyota Jidoshokki Variable displacement type swash plate compressor
US20160222953A1 (en) * 2013-09-11 2016-08-04 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
US20160237994A1 (en) * 2015-02-16 2016-08-18 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash-plate compressor
US9429147B2 (en) 2013-03-27 2016-08-30 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate compressor
US9512832B2 (en) 2013-10-31 2016-12-06 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9523357B2 (en) 2013-03-29 2016-12-20 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
US9651035B2 (en) 2014-03-20 2017-05-16 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
US9752563B2 (en) 2013-11-06 2017-09-05 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9803628B2 (en) 2013-03-29 2017-10-31 Kabushiki Kaisha Toyota Jidoshokki Compressor with drive and tilt mechanisms located on the same side of a swash plate
US9816498B2 (en) 2013-03-29 2017-11-14 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash-plate compressor
DE102014118183B4 (de) * 2013-12-11 2018-02-01 Kabushiki Kaisha Toyota Jidoshokki Variabler verdrängungstaumelscheibenkompressor mit durchbrochenem ringförmigen element in der ablaufpassage zwischen steuerdruckkammer und taumelscheibenkammer
US9903352B2 (en) 2012-11-05 2018-02-27 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor

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JP5949805B2 (ja) * 2014-02-25 2016-07-13 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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JP6287483B2 (ja) * 2014-03-28 2018-03-07 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP2016102418A (ja) * 2014-11-27 2016-06-02 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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US20140377087A1 (en) * 2012-02-06 2014-12-25 Sanden Corporation Variable Displacement Compressor
US9765765B2 (en) * 2012-02-06 2017-09-19 Sanden Holdings Corporation Three-bore variable displacement compressor with a swash plate having an adjustable incline
DE112013000858B4 (de) * 2012-02-06 2017-11-30 Sanden Holdings Corporation Verdichter mit variabler Verdrängung und verbesserter Verteilung der Ölströmung
US20150118073A1 (en) * 2012-04-25 2015-04-30 Sanden Corporation Variable-Capacity Comprenssor And Method For Manufacturing Same
US10012218B2 (en) * 2012-04-25 2018-07-03 Sanden Holdings Corporation Variable displacement compressor and swash place linkage connection
US20140033911A1 (en) * 2012-08-04 2014-02-06 Robert Bosch Gmbh Hydrostatic axial piston machine
US9228577B2 (en) 2012-11-05 2016-01-05 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9309875B2 (en) 2012-11-05 2016-04-12 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9309874B2 (en) 2012-11-05 2016-04-12 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9316217B2 (en) 2012-11-05 2016-04-19 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9903352B2 (en) 2012-11-05 2018-02-27 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9228576B2 (en) 2012-11-05 2016-01-05 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9273679B2 (en) 2013-03-27 2016-03-01 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate compressor
US9429147B2 (en) 2013-03-27 2016-08-30 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate compressor
US20160069334A1 (en) * 2013-03-29 2016-03-10 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
US9816498B2 (en) 2013-03-29 2017-11-14 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash-plate compressor
US9523357B2 (en) 2013-03-29 2016-12-20 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
US9803628B2 (en) 2013-03-29 2017-10-31 Kabushiki Kaisha Toyota Jidoshokki Compressor with drive and tilt mechanisms located on the same side of a swash plate
US20160222953A1 (en) * 2013-09-11 2016-08-04 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
US9512832B2 (en) 2013-10-31 2016-12-06 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US9752563B2 (en) 2013-11-06 2017-09-05 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
DE102014118183B4 (de) * 2013-12-11 2018-02-01 Kabushiki Kaisha Toyota Jidoshokki Variabler verdrängungstaumelscheibenkompressor mit durchbrochenem ringförmigen element in der ablaufpassage zwischen steuerdruckkammer und taumelscheibenkammer
US9651035B2 (en) 2014-03-20 2017-05-16 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
US9651036B2 (en) * 2014-03-27 2017-05-16 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US20150275872A1 (en) * 2014-03-27 2015-10-01 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
US20160153436A1 (en) * 2014-11-27 2016-06-02 Kabushiki Kaisha Toyota Jidoshokki Variable displacement type swash plate compressor
US20160237994A1 (en) * 2015-02-16 2016-08-18 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash-plate compressor

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KR20120024874A (ko) 2012-03-14
JP2010281289A (ja) 2010-12-16
CN102459897A (zh) 2012-05-16
WO2010140374A1 (ja) 2010-12-09
EP2423507A1 (en) 2012-02-29
JP5519193B2 (ja) 2014-06-11
EP2423507A4 (en) 2013-08-14

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