EP2423507A1 - Compresseur à déplacement variable - Google Patents

Compresseur à déplacement variable Download PDF

Info

Publication number
EP2423507A1
EP2423507A1 EP10783162A EP10783162A EP2423507A1 EP 2423507 A1 EP2423507 A1 EP 2423507A1 EP 10783162 A EP10783162 A EP 10783162A EP 10783162 A EP10783162 A EP 10783162A EP 2423507 A1 EP2423507 A1 EP 2423507A1
Authority
EP
European Patent Office
Prior art keywords
chamber
swash plate
intermediate pressure
suction
variable displacement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP10783162A
Other languages
German (de)
English (en)
Other versions
EP2423507A4 (fr
Inventor
Iwao Uchikado
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of EP2423507A1 publication Critical patent/EP2423507A1/fr
Publication of EP2423507A4 publication Critical patent/EP2423507A4/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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
  • variable displacement compressor previously proposed by the applicant of the present application concretely has a structure, for example, as shown in Figs. 11 and 12 .
  • 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 grooves for guiding balls 212 at
  • 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 P
  • 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 cam angle is adjusted so as to become an arbitrary predetermined angle and the displacement of the compressor is controlled at a desired displacement.
  • 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.
  • 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]).
  • 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, and 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 circumference, and (iv) a plurality
  • 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.
  • 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 ia 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
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP10783162.0A 2009-06-05 2010-06-03 Compresseur à déplacement variable Withdrawn EP2423507A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009136544A JP5519193B2 (ja) 2009-06-05 2009-06-05 可変容量圧縮機
PCT/JP2010/003724 WO2010140374A1 (fr) 2009-06-05 2010-06-03 Compresseur à déplacement variable

Publications (2)

Publication Number Publication Date
EP2423507A1 true EP2423507A1 (fr) 2012-02-29
EP2423507A4 EP2423507A4 (fr) 2013-08-14

Family

ID=43297517

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10783162.0A Withdrawn EP2423507A4 (fr) 2009-06-05 2010-06-03 Compresseur à déplacement variable

Country Status (6)

Country Link
US (1) US20120073430A1 (fr)
EP (1) EP2423507A4 (fr)
JP (1) JP5519193B2 (fr)
KR (1) KR20120024874A (fr)
CN (1) CN102459897A (fr)
WO (1) WO2010140374A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104929892A (zh) * 2014-03-20 2015-09-23 株式会社丰田自动织机 可变排量型斜板式压缩机
EP2927492A3 (fr) * 2014-03-25 2015-12-02 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau oscillant à déplacement variable
EP3026264A1 (fr) * 2014-11-27 2016-06-01 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau oscillant à déplacement variable
CN105649921A (zh) * 2014-11-27 2016-06-08 株式会社丰田自动织机 可变排量旋转斜板式压缩机

Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5999622B2 (ja) * 2012-02-06 2016-09-28 サンデンホールディングス株式会社 可変容量圧縮機
JP6013768B2 (ja) * 2012-04-25 2016-10-25 サンデンホールディングス株式会社 可変容量圧縮機及びその製造方法
DE102012015503A1 (de) * 2012-08-04 2014-02-06 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
JP6003547B2 (ja) 2012-11-05 2016-10-05 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP5870902B2 (ja) 2012-11-05 2016-03-01 株式会社豊田自動織機 容量可変型斜板式圧縮機
CN104755759B (zh) 2012-11-05 2016-12-07 株式会社丰田自动织机 容量可变型斜盘式压缩机
JP6028525B2 (ja) 2012-11-05 2016-11-16 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6003546B2 (ja) 2012-11-05 2016-10-05 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6028524B2 (ja) 2012-11-05 2016-11-16 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP5949626B2 (ja) 2013-03-27 2016-07-13 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6083291B2 (ja) 2013-03-27 2017-02-22 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6079379B2 (ja) 2013-03-29 2017-02-15 株式会社豊田自動織機 可変容量型斜板式圧縮機
CN105074209B (zh) * 2013-03-29 2017-03-08 株式会社丰田自动织机 容量可变型斜板式压缩机
WO2014157209A1 (fr) * 2013-03-29 2014-10-02 株式会社豊田自動織機 Compresseur à volume variable du type à plateau oscillant
CN105051368B (zh) * 2013-03-29 2017-03-08 株式会社丰田自动织机 可变容量型斜板式压缩机
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
JP5949678B2 (ja) * 2013-06-20 2016-07-13 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6115258B2 (ja) 2013-03-29 2017-04-19 株式会社豊田自動織機 両頭ピストン型斜板式圧縮機
JP6060925B2 (ja) * 2014-03-10 2017-01-18 株式会社豊田自動織機 可変容量型斜板式圧縮機
JP6032228B2 (ja) * 2014-03-04 2016-11-24 株式会社豊田自動織機 容量可変型斜板式圧縮機
KR101889628B1 (ko) * 2013-09-11 2018-08-17 가부시키가이샤 도요다 지도숏키 용량 가변형 사판식 압축기
JP6094456B2 (ja) 2013-10-31 2017-03-15 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6146263B2 (ja) 2013-11-06 2017-06-14 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6136906B2 (ja) * 2013-12-11 2017-05-31 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6135573B2 (ja) * 2014-03-27 2017-05-31 株式会社豊田自動織機 容量可変型斜板式圧縮機
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
JP2016102434A (ja) * 2014-11-27 2016-06-02 株式会社豊田自動織機 可変容量型斜板式圧縮機
JP2016151188A (ja) * 2015-02-16 2016-08-22 株式会社豊田自動織機 容量可変型斜板式圧縮機
JP6470086B2 (ja) * 2015-03-31 2019-02-13 サンデンホールディングス株式会社 揺動板式可変容量圧縮機

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01182581A (ja) * 1988-01-14 1989-07-20 Honda Motor Co Ltd 容量可変式圧縮機の制御装置
JPH08189464A (ja) 1994-11-11 1996-07-23 Toyota Autom Loom Works Ltd 可変容量型圧縮機
JPH09273483A (ja) * 1996-04-04 1997-10-21 Toyota Autom Loom Works Ltd 可変容量型圧縮機
JPH10281060A (ja) * 1996-12-10 1998-10-20 Toyota Autom Loom Works Ltd 可変容量圧縮機
JP2000087848A (ja) * 1998-09-08 2000-03-28 Toyota Autom Loom Works Ltd 可変容量型圧縮機
US6352416B1 (en) * 1999-03-15 2002-03-05 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Device and method for controlling displacement of variable displacement compressor
DE19939131A1 (de) * 1999-08-18 2001-03-08 Zexel Gmbh Axialkolbentriebwerk mit einem stufenlos verstellbaren Kolbenhub
JP2001304108A (ja) * 2000-04-20 2001-10-31 Toyota Industries Corp 圧縮機
JP4829761B2 (ja) * 2006-12-05 2011-12-07 サンデン株式会社 揺動板式可変容量圧縮機
JP4425289B2 (ja) * 2007-03-30 2010-03-03 株式会社デンソー ピストン型圧縮機
WO2008146806A1 (fr) * 2007-05-29 2008-12-04 Sanden Corporation Compresseur de type à plateau oscillant à cylindrée variable

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2010140374A1 *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104929892A (zh) * 2014-03-20 2015-09-23 株式会社丰田自动织机 可变排量型斜板式压缩机
EP2921701A3 (fr) * 2014-03-20 2016-03-02 Kabushiki Kaisha Toyota Jidoshokki Compresseur à déplacement variable de type plateau oscillant
US9651035B2 (en) 2014-03-20 2017-05-16 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash plate type compressor
CN104929892B (zh) * 2014-03-20 2017-05-17 株式会社丰田自动织机 可变排量型斜板式压缩机
EP2927492A3 (fr) * 2014-03-25 2015-12-02 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau oscillant à déplacement variable
EP3026264A1 (fr) * 2014-11-27 2016-06-01 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau oscillant à déplacement variable
CN105649921A (zh) * 2014-11-27 2016-06-08 株式会社丰田自动织机 可变排量旋转斜板式压缩机
US9850886B2 (en) 2014-11-27 2017-12-26 Kabushiki Kaisha Toyota Jidoshokki Variable displacement swash-plate compressor

Also Published As

Publication number Publication date
CN102459897A (zh) 2012-05-16
EP2423507A4 (fr) 2013-08-14
JP5519193B2 (ja) 2014-06-11
JP2010281289A (ja) 2010-12-16
US20120073430A1 (en) 2012-03-29
WO2010140374A1 (fr) 2010-12-09
KR20120024874A (ko) 2012-03-14

Similar Documents

Publication Publication Date Title
EP2423507A1 (fr) Compresseur à déplacement variable
EP1599674B1 (fr) Pompe/moteur hydraulique hautement efficace a cylindree variable et grand angle
US20090007773A1 (en) Axial plunger pump or motor
US9228573B2 (en) Wabble plate type variable displacement compressor
EP2784317B1 (fr) Compresseur à plateau oscillant à déplacement variable
US7972118B2 (en) Variable capacity compressor
JP6740032B2 (ja) 油圧ポンプ
US6742439B2 (en) Variable displacement compressor
US20150167655A1 (en) Variable displacement swash plate type compressor
EP2306013B1 (fr) Compresseur à déplacement variable de type à plateau oscillant
US20150260175A1 (en) Variable displacement swash plate type compressor
US9719501B2 (en) Swash plate type variable displacement compressor
US20170145997A1 (en) Variable displacement type swash plate compressor
EP2525096A1 (fr) Compresseur
KR102235426B1 (ko) 피스톤식 압축기
US20060222513A1 (en) Swash plate type variable displacement compressor
JPH048875A (ja) 斜板型可変容量圧縮機
JP2010014034A (ja) 可変容量コンプレッサ
EP1970567A1 (fr) Compresseur a cylindree variable
KR20110045239A (ko) 용량 가변형 사판식 압축기
KR20110045225A (ko) 용량 가변형 사판식 압축기
JP2007315283A (ja) 斜板式可変容量コンプレッサ
JP2006009628A (ja) 可変容量圧縮機
JP2009221968A (ja) コンプレッサ

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20111123

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20130712

RIC1 Information provided on ipc code assigned before grant

Ipc: F04B 27/18 20060101AFI20130708BHEP

Ipc: F04B 27/10 20060101ALI20130708BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20140103