WO2010140374A1 - 可変容量圧縮機 - Google Patents

可変容量圧縮機 Download PDF

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Publication number
WO2010140374A1
WO2010140374A1 PCT/JP2010/003724 JP2010003724W WO2010140374A1 WO 2010140374 A1 WO2010140374 A1 WO 2010140374A1 JP 2010003724 W JP2010003724 W JP 2010003724W WO 2010140374 A1 WO2010140374 A1 WO 2010140374A1
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WO
WIPO (PCT)
Prior art keywords
chamber
swash plate
intermediate pressure
suction
pressure
Prior art date
Application number
PCT/JP2010/003724
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
内門巌
Original Assignee
サンデン株式会社
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 サンデン株式会社 filed Critical サンデン株式会社
Priority to EP10783162.0A priority Critical patent/EP2423507A4/en
Priority to CN2010800251599A priority patent/CN102459897A/zh
Priority to US13/376,346 priority patent/US20120073430A1/en
Publication of WO2010140374A1 publication Critical patent/WO2010140374A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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 capacity compressor, and in particular, it can reduce pulsation, improve durability, and improve pressure resistance, and can control the inclination angle of a swash plate more smoothly and with high accuracy via an axially moving member.
  • the present invention relates to a variable capacity compressor.
  • a cylinder head having a suction chamber and a discharge chamber; a cylinder block having a cylinder bore into which a piston is reciprocally inserted; a crank chamber formed by the cylinder block and a front housing; and a crank chamber formed in the crank chamber.
  • a variable capacity compression comprising a swash plate that is rotated together with the main shaft and is supported so that its inclination angle can be changed with respect to the main shaft, and a motion conversion mechanism that converts the rotational motion of the swash plate into the reciprocating motion of the piston.
  • the machine is well known.
  • the above-mentioned motion conversion mechanism has been previously converted by the applicant of the present invention into the swing motion of the swash plate into its own swing motion.
  • the rotation prevention mechanism for the swing plate is (a) prevented from rotating in the housing.
  • An outer ring having a plurality of guide grooves for guiding the outer ring and having a swing plate coupled to the outer periphery and supported so as to be swingable together with the swing plate; and (c) facing each other formed on the inner ring and the outer ring.
  • Wobble plate type variable displacement compressor having a structure that consists mechanism having a plurality of balls for performing power transmission, has been proposed by being (Patent Document 1).
  • the inner ring constitutes an axial movement member that can move in a direction along the axis of the main shaft substantially corresponding one-to-one with respect to the inclination angle of the swash plate. Yes.
  • variable capacity compressor previously proposed by the applicant of the present invention has a structure as shown in FIGS. 11 and 12, for example.
  • FIG. 11 shows the maximum capacity (maximum cam angle [maximum swash plate angle]) state
  • FIG. 12 shows the minimum capacity (minimum cam angle [minimum swash plate angle]) state.
  • a swash plate 206 is capable of changing the inclination angle of a main shaft 204 inserted into a crank chamber 203 formed by a front housing 201 and a cylinder block 202 via a hinge mechanism 205 and is integrated with the main shaft 204. It is provided rotatably.
  • the rotational motion of the swash plate 206 is converted into the swing motion of the swing plate 207, and the swing motion is converted into the reciprocating motion of the piston 209 via the connecting rod 208.
  • the rotation prevention mechanism 210 of the rocking plate 207 is provided to be movable in the axial direction while being prevented from rotating via the spline engagement mechanism 211, and to be rotatable relative to the main shaft 204.
  • the inner ring 213 having a plurality of guide grooves for guiding a plurality of balls 212 provided for power transmission, and (ii) a swinging central member of the swinging motion of the swinging plate 207.
  • a sleeve 214 which is provided so as to be relatively rotatable and movable in the axial direction, and is engaged with the inner ring 213 so as to be movable in the axial direction together with the inner ring 213, and (iii) a ball at a position facing each guide groove of the inner ring 213
  • An outer ring 215 having a plurality of guide grooves for guiding 212, supported swingably on the sleeve 214, and fixedly supporting the swing plate 207 on the outer periphery; (iv) an inner ring 213; Held by opposing guide grooves of the wheels 215, a plurality of balls 212 that transmits power by being compressed between the guide grooves, and a mechanism having a.
  • a suction chamber 217 and a discharge chamber 218 are formed in the cylinder head 216.
  • the suction gas to the compressor is taken into the suction chamber 217 from the suction port 219 via the suction throttle valve 220 in the illustrated example, and the gas compressed by the piston 209 in the cylinder bore 221 is discharged to the discharge chamber 218. In the illustrated example, it is sent to an external circuit from there through the discharge cutoff valve 222 and the discharge port 223.
  • control valve 224 or the throttle valve 226 is connected to the communication chamber 225 for introducing the discharge gas adjusted from the pressure Pd of the discharge chamber 218 to the crank chamber 203 by the throttle and the crank chamber gas to the suction chamber 217 side (pressure Ps).
  • a return passage 227 is provided, and the gas pressure Pc in the crank chamber 203 is controlled by changing the opening of the control valve 224.
  • variable capacity compressor having such a structure, the balance of the even moment in the compressor will be described for comparison with the present invention described later.
  • the even moment generated by the reciprocating motion of the system components is generated as shown in FIG. 13 according to the cam angle as the even moment in the cam bending direction acting by the compressor operation.
  • FIG. 13 shows, for example, the even moment (in the illustrated example, the total even moment acts in the direction of increasing the capacity (cam angle) at all cam angles.
  • the gas pressure distribution is generated in each space inside the compressor due to the compression action of the compressor and the pressure regulation action of the control valve.
  • the distribution causes an even moment in the direction in which the cam angle increases or decreases, for example, as shown in Fig. 14.
  • the compressor since the compression action is generated by the rotation of the main shaft 204 of the compressor, the compressor is in operation.
  • the even moment due to the rotation and reciprocation of the above parts and the even moment due to the gas pressure distribution act simultaneously, and the cam angle can be set to any predetermined value by the total balance of these two types of even moments (total balance).
  • the compressor capacity is controlled to a desired capacity.
  • the cam angle can be controlled so as to balance the even moment caused by the rotation and reciprocation of each component shown in FIG. Further, for M1 and M2 in FIG. 14, M1 and M2 are actually calculated for all pistons.
  • a relatively high temperature and high pressure control gas with a reduced discharge pressure is introduced into the crank chamber, which is disadvantageous in terms of durability to rotating / driving components and seals. Met.
  • pulsation reduction elements such as a throttle valve and muffler may be built in the cylinder head. The degree of freedom in designing the layout with the refrigerant shutoff valve or the like is reduced.
  • the capacity (swash plate tilt angle) is basically controlled by adjusting the differential pressure between the crank chamber pressure and the discharge chamber pressure or the crank chamber pressure and the suction chamber pressure by changing the opening of the control valve.
  • control is performed by controlling the gas pressure in the crank chamber, that is, capacity (swash plate tilt angle) control only by gas pressure control, the axial position and the swash plate tilt angle of the axially moving member in the present invention to be described later Compared with control using a one-to-one mechanical relationship, there is a limit in control accuracy.
  • a refrigerant gas suction hole connected to an external circuit is provided in the crank chamber.
  • a structure of a compressor that opens and guides intake gas from a crank chamber to a suction chamber formed in a cylinder head through a communication passage formed in a cylinder block for example, Patent Document 2).
  • Patent Document 2 a structure of a compressor that opens and guides intake gas from a crank chamber to a suction chamber formed in a cylinder head through a communication passage formed in a cylinder block.
  • an axial movement member according to the present invention as described later a crank chamber pressure is applied to one end side of the axial movement member, and an intermediate pressure between the discharge pressure and the suction pressure is applied to the other end side.
  • the structure, the structure and technical idea for controlling the intermediate pressure are not disclosed or suggested, and cannot be controlled as in the present invention.
  • JP 2008-138637 A JP-A-8-189464 Japanese Patent Laid-Open No. 9-273383
  • an object of the present invention is to achieve improvement in compressor performance such as reduction in pulsation, improvement in durability and pressure resistance, and smoothness with a target inclination angle of the swash plate via an axially moving member. It is another object of the present invention to provide a variable capacity compressor that can be controlled with high accuracy and is excellent in performance and characteristics.
  • a variable capacity compressor includes a cylinder head having a suction chamber and a discharge chamber, a cylinder block having a cylinder bore into which a piston is reciprocally inserted, and the cylinder block. And a crank chamber formed by the front housing, a swash plate disposed in the crank chamber and rotated together with the main shaft and supported to change its inclination with respect to the main shaft, and rotational movement of the swash plate
  • a suction path for taking in the suction gas to the compressor is formed to open to the crank chamber, and the crank chamber is formed in the cylinder block.
  • a communication passage that communicates with the suction chamber, and the shaft center of the main shaft substantially corresponds to the inclination angle of the swash plate around the main shaft.
  • An axially movable member that is movable in the vertical direction, and the axially movable member has an intermediate pressure between the pressure in the crank chamber at one end and the pressure in the discharge chamber and the pressure in the suction chamber at the other end.
  • an intermediate pressure control mechanism capable of controlling the intermediate pressure is provided.
  • the suction passage for taking in the suction gas from the outside to the compressor is not directly opened to the suction chamber formed in the cylinder head.
  • the suction gas that is opened into the chamber and introduced into the crank chamber is introduced into the suction chamber through a communication passage provided in the cylinder block. Therefore, since the crank chamber having a large capacity becomes the suction chamber for the external circuit, noise due to suction pulsation is prevented or reduced. Further, this structure makes it possible to reduce the volume of the suction chamber formed in the cylinder head, and the volume of the discharge chamber can be increased correspondingly, so that noise caused by discharge pulsation is prevented or reduced.
  • crank chamber becomes an intake gas atmosphere and the temperature and pressure are lowered, the durability of the seal member of the main shaft and each drive component is improved, and the pressure resistance of the casing components forming the crank chamber is relatively improves.
  • the pressure resistance of the casing parts, particularly the front housing is improved, the weight can be reduced by reducing the thickness. Then, the pressure in the crank chamber and the intermediate pressure control mechanism are controlled on each end side of the axial movement member that can move in the direction along the axis of the main shaft substantially corresponding to the inclination angle of the swash plate.
  • the applied intermediate pressure is applied, whereby the axial position of the axial movement member is controlled with high accuracy, and the tilt angle of the swash plate and the capacity of the compressor are controlled with high accuracy through the position control. Therefore, compared to conventional capacity (swash plate tilt) control only by the total balance (total balance) of the even moment due to rotation / reciprocation of each part and the distribution of gas pressure, the axial direction of the axially moving member Since the displacement (swash plate tilt angle) control is performed via the position control, the stability of the control is improved and the control accuracy can be improved.
  • the axial position control of the axial movement member is performed between the gas pressure on the crank chamber side (intake gas pressure) applied to one end side of the axial movement member, the discharge gas pressure applied to the other end side, and the intake gas pressure.
  • this intermediate pressure cannot be made lower than the suction gas pressure applied to the opposite side, only the gas pressure applied to both ends of the axially moving member is used.
  • the axial movement member can be controlled only in the cam angle (swash plate inclination angle) increasing direction.
  • the cam angle swash plate tilt angle
  • the cam lofill is set so that the even moment in the direction of decreasing the cam angle is generated by the discharge gas pressure action on the piston
  • the swash plate tilt angle decreases direction, that is, the capacity decreases direction.
  • the compressor operation off mode that is, the mode in which the inclination angle of the swash plate is kept at the minimum inclination angle
  • the compressor operation off mode can be maintained without increasing the pressure in the crank chamber.
  • the amount of refrigerant circulating in the compressor at the time decreases, and the power consumption can be reduced accordingly.
  • the rotating parts such as the swash plate kept at the minimum inclination angle are rotated as they are in the compressor operation off mode, so that the compression power is reduced by reducing the power consumption at that time.
  • the total power consumption of the machine is also reduced.
  • the suction passage formed so as to open to the crank chamber may take various forms as follows.
  • the intake passage is formed in the front housing, and intake gas can be directly taken into the crank chamber from an external circuit.
  • the suction path is formed from the cylinder block to the front housing, and the intake gas from the external circuit is once taken into the cylinder block portion and then taken into the crank chamber through the front housing portion.
  • the suction path is formed from the cylinder head to the front housing via the cylinder block (with the cylinder block in between), and the suction gas from the external circuit is once formed in the cylinder head portion (in the cylinder head). It is also possible to take in into a crank chamber through a cylinder block part and a front housing part.
  • the intermediate pressure control mechanism may take various forms as follows, for example.
  • the intermediate pressure control mechanism includes a communication passage between the discharge chamber and the intermediate pressure chamber, a control valve provided in the communication passage, and capable of controlling pressure reduction from the pressure in the discharge chamber to a predetermined intermediate pressure.
  • a mechanism having a communication path between the intermediate pressure chamber and the suction chamber and a throttle provided in the communication path can be configured.
  • the intermediate pressure control mechanism is provided in the communication path between the discharge chamber and the intermediate pressure chamber, the communication path between the intermediate pressure chamber and the suction chamber, and the pressure in the discharge chamber.
  • the intermediate pressure control mechanism includes a communication path between the discharge chamber and the intermediate pressure chamber, a throttle provided in the communication path, a communication path between the intermediate pressure chamber and the suction chamber, and the communication.
  • a mechanism provided with a control valve provided in the passage and capable of controlling pressure reduction to a predetermined intermediate pressure in the intermediate pressure chamber can also be configured.
  • the seal member provided on the other end side of the axially moving member is between the intermediate pressure chamber and the suction chamber. It may be a seal member that allows leakage from the intermediate pressure chamber to the crank chamber corresponding to the flow rate of the gas passing through the throttle in this case.
  • the communication path from the intermediate pressure chamber to the suction chamber and its communication It is also possible to omit the restriction in the passage.
  • the motion conversion mechanism may take various forms as follows.
  • the motion conversion mechanism includes a swing plate that converts the rotational motion of the swash plate into its own swing motion, transmits the swing motion to the piston through a connecting rod, and reciprocates the piston, and the swing It can comprise from the mechanism provided with the rotation prevention mechanism of a board. That is, a so-called oscillating plate type variable displacement compressor is configured.
  • the rotation preventive mechanism for the swing plate is (a) provided with a plurality of balls for guiding a plurality of balls provided for power transmission, provided to be movable in the axial direction while being prevented from rotating in the housing.
  • An inner ring having a guide groove; and (b) a plurality of guide grooves for guiding the ball at positions opposed to the guide grooves of the inner ring, and the swing plate is connected to an outer periphery.
  • the rotation preventing mechanism of the swing plate further functions as a swing center member of the swing motion of the swing plate (d), and the spindle
  • the inner ring has a sleeve which is provided so as to be rotatable relative to the main shaft and movable in the axial direction.
  • the sleeve is engaged with the inner ring so as to be movable in the axial direction.
  • the outer ring is supported by the sleeve so as to be swingable. It is also possible to adopt the structure.
  • variable displacement compressor in addition to the configuration of the swing plate type variable displacement compressor as described above, for example, the motion conversion mechanism is slidably contacted on both outer peripheral sides of the swash plate. It is also possible to adopt a configuration constituted by a mechanism that converts the reciprocating motion of the piston through a pair of shoes.
  • the cam mechanism for changing the inclination angle of the swash plate in order to enable the inclination angle of the swash plate to be controlled to the target inclination angle efficiently and accurately can be changed via a cam mechanism interposed between the main shaft and the swash plate, and the compression reaction of at least one of the plurality of pistons in the compression stroke is made.
  • the cam profile of the cam mechanism is set so that the load due to the force acts on the swash plate as an even moment in the capacity decreasing direction so that the instantaneous rotation center of the swash plate is present. A specific example of this mechanism will be described in detail in an embodiment of the present invention described later.
  • the cam mechanism comprises a slide engagement mechanism of an elongated hole formed on one of an arm extending from the main shaft side and an arm extending from the swash plate side, and a pin provided on the other, and the cam profile includes the elongated hole. It is realizable by the mechanism set by forming the shape of this in S shape.
  • the total balance of the even moments generated in the tilt change plane of the swash plate by at least the rotation and reciprocation of each component is reduced in the tilt reduction direction at all swash plate tilt angles. It is preferable that each part is set so as to be. In such a configuration, the total balance of the even moment of the swash plate due to the rotation and reciprocation of each component always acts in the direction of decreasing the swash plate inclination angle, that is, always acts in one desired direction. By controlling even the intermediate pressure applied to the other end side of the axially moving member, it becomes possible to easily and accurately control the inclination angle of the swash plate to the target inclination angle.
  • the intermediate pressure applied to the other end of the axial movement member cannot be lower than the suction pressure applied to the opposite side, so that depending on only the gas pressure applied to both ends of the axial movement member,
  • the direction moving member can act only in the cam angle (swash plate inclination angle) increasing direction.
  • the cam angle (swash plate tilt angle) can be easily controlled by controlling the intermediate pressure. ) Can be controlled to any desired angle.
  • the swash plate since an even moment always acts on the swash plate in the direction of decreasing the tilt angle, for example, when it is desired to maintain the compressor operation off mode, the swash plate is naturally changed to the minimum tilt direction only by rotating the compressor. After being turned and changed to the minimum inclination, the minimum inclination is maintained.
  • a spring for urging at least the swash plate in the direction of decreasing the inclination angle, and the total of the even moment due to the rotation and reciprocation generated in the inclination change plane of the swash plate including the urging force of the spring is also possible to adopt a form in which the balance is set so as to be in the direction of decreasing the inclination angle at all inclination angles of the swash plate. As will be exemplified later, this form is effective when it is desired to always press the swash plate whose inclination angle is changed in the inclination decreasing direction regardless of the inclination angle change.
  • the center portion of the swash plate or the swash plate support member and the axial movement member are always aligned. It is possible to move both members together integrally in the axial direction by pressing each other in the direction so that the axial position of the axially moving member and the inclination angle of the swash plate can always correspond exactly one to one. It becomes possible to do.
  • the intake gas is introduced into the crank chamber through the intake passage that opens to the crank chamber, so that the noise caused by the suction pulsation with the large-capacity crank chamber as the intake chamber. Can be prevented or reduced. Further, since the suction throttle valve can be eliminated, the degree of freedom in designing the cylinder head layout is improved. In addition, the configuration in which the suction gas is introduced from the crank chamber into the suction chamber formed in the cylinder head via the communication path can reduce the suction chamber volume, and the discharge chamber volume can be increased correspondingly. The resulting noise can also be prevented or reduced.
  • the temperature and pressure in the crank chamber can be reduced, the durability of each driving component and the pressure resistance of the casing component can be improved, and the casing component can be made thinner and the entire compressor can be reduced in size and weight.
  • the axial position of the axially moving member is controlled with high accuracy. Through the control, the tilt angle of the swash plate and the capacity of the compressor can be stably controlled with high accuracy.
  • FIG. 2 is an enlarged partial cross-sectional view of the variable capacity compressor of FIG. 1. It is a longitudinal cross-sectional view at the time of the minimum swash plate inclination of the variable capacity compressor of FIG.
  • FIG. 4 is an enlarged partial cross-sectional view of the variable capacity compressor of FIG. 3.
  • FIG. 2 is a relationship diagram between a cam angle and an even moment, showing a balance of even moments due to rotation and reciprocation of each component of the variable capacity compressor of FIG. 1. It is explanatory drawing which shows the balance of the even moment by the gas pressure of the variable capacity compressor of FIG.
  • variable capacity compressor It is a partial longitudinal cross-sectional view of the variable capacity compressor which concerns on the 2nd embodiment of this invention. It is a longitudinal cross-sectional view of the variable capacity compressor which concerns on the 3rd embodiment of this invention. It is a longitudinal cross-sectional view of the variable capacity compressor which concerns on the 4th embodiment of this invention. It is a longitudinal cross-sectional view of the variable capacity compressor which concerns on 5th embodiment of this invention. It is a longitudinal cross-sectional view at the time of the maximum swash plate inclination of the conventional variable capacity compressor. It is a longitudinal cross-sectional view at the time of the minimum swash plate inclination of the variable capacity compressor of FIG. FIG.
  • FIG. 12 is a relationship diagram between a cam angle and an even moment, showing a balance of even moments due to rotation and reciprocation of each component of the variable capacity compressor of FIG. 11. It is explanatory drawing which shows the balance of the even moment by the gas pressure of the variable capacity compressor of FIG.
  • FIG. 1 shows the state of the variable capacity compressor 1 at the maximum capacity (maximum cam angle [maximum swash plate inclination angle]), and FIG. 3 shows the state at the minimum capacity (minimum cam angle [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, and a rotor 6 fixed to the main shaft 5 and rotated integrally with the main shaft 5 with respect to the main shaft 5.
  • a swash plate 7 is disposed so as to be capable of changing the tilt angle with respect to the main shaft 5 and to be rotatable integrally with the main shaft 5. Between the rotor 6 and the swash plate 7, there are an arm 8 extending from the rotor 6 side (main shaft 5 side) and an arm 9 extending from the swash plate 7 side.
  • a hinge mechanism 12 that forms a slide engagement mechanism provided with a pin 11 that engages with the elongated hole 10 is provided, and the inclination angle of the swash plate 7 can be changed through the hinge mechanism 12 and the spindle 5 And can be rotated integrally therewith.
  • a counterweight 13 is embedded or attached to the swash plate 7 on the side opposite to the hinge mechanism 12 in order to balance the rotation of the rotation mechanism including the swash plate 7 and the hinge mechanism 12.
  • the slide engagement mechanism between the long hole 10 and the pin 11 in the hinge mechanism 12 constitutes a cam mechanism for changing the inclination angle of the swash plate 7.
  • the long hole 10 is described later.
  • the load due to the compression reaction force of at least one piston among the plurality of pistons in the compression stroke acts on the swash plate 7 as an even moment in the capacity decreasing direction.
  • the suction port 14 is directly provided in the front housing 2, and the suction passage 15 for taking in the intake gas from the outside into the crank chamber 4 is formed only in the front housing 2.
  • a rocking plate 18 which is provided so as to be rotatable relative to the swash plate 7 via bearings 16 and 17 and which is allowed to swing only while preventing its own rotation.
  • the oscillating plate type variable displacement compressor 1 is configured.
  • the rotational motion of the swash plate 7 is converted into the swing motion of the swing plate 18, and the swing motion is converted into the reciprocating motion of the piston 21 reciprocally inserted into the cylinder bore 20 via the connecting rod 19.
  • the rotation preventing mechanism 22 of the swing plate 18 is provided so as to be movable in the axial direction, although the rotation is blocked via a spline engaging mechanism 24 formed between the central hole 23 of the cylinder block 3.
  • An inner ring 27 provided with a plurality of guide grooves 26 for guiding a plurality of balls 25 provided for power transmission, and relatively rotatable with respect to the main shaft 5 via a bearing 48, and (ii) a swing plate A sleeve 28 that functions as a swinging center member of the swinging motion 18 and is provided so as to be able to rotate relative to the main shaft 5 and move in the axial direction, and is engaged with the inner ring 27 so as to be movable in the axial direction together with the inner ring 27.
  • a plurality of guide grooves 29 for guiding the balls 25 are provided at positions facing the respective guide grooves 26 of the inner ring 27, are supported by the sleeve 28 so as to be swingable, and the swing plate 18 is fixed to the outer periphery. Outside to support 30 and (iv) a plurality of balls 25 that are held by guide grooves 26 and 29 facing each other in the inner ring 27 and the outer ring 30 and that transmit power by being compressed between the guide grooves 26 and 29.
  • a suction chamber 32 is formed on the radially outer side, and a discharge chamber 33 is formed on the radially inner side.
  • the suction gas to the compressor is first taken into the crank chamber 4 from the suction port 14 through the suction passage 15, and from the crank chamber 4 to the inside of the suction chamber 32 through the communication passage 34 formed in the cylinder block 3. And is taken into the cylinder bore 20 from there and used for the compression stroke by the piston 21.
  • the gas compressed by the piston 21 in the cylinder bore 20 is discharged into the discharge chamber 33, and in the example shown in the figure, is sent to an external circuit through the discharge cutoff valve 35 and the discharge port 36.
  • the gas pressure (Ps) on the crank chamber 4 side is applied to one end side of the inner ring 27 as the axially moving member, and the pressure (Pd) in the discharge chamber 33 and the pressure in the suction chamber 32 are applied to the other end side.
  • An intermediate pressure (Pm) with respect to (Ps) is applied.
  • an intermediate pressure chamber 38 is formed that is sealed by seal members 37 and 45 with respect to the crank chamber 4 side, and the pressure in the intermediate pressure chamber 38 is changed by the intermediate pressure control mechanism 39.
  • the predetermined intermediate pressure (Pm) is controlled as described above.
  • the intermediate pressure control mechanism 39 is configured as follows in this embodiment.
  • a communication passage 40 is provided between the discharge chamber 33 and the intermediate pressure chamber 38, and pressure reduction from the pressure (Pd) in the discharge chamber 33 to a predetermined intermediate pressure (Pm) is performed in the communication passage 40.
  • a control valve 41 that can be controlled is disposed, and a communication passage 42 is provided between the intermediate pressure chamber 38 and the suction chamber 32, and the suction passage is provided in the communication passage 42 from the intermediate pressure (Pm).
  • a throttle 43 orifice that can be depressurized to a pressure (Ps) in the cylinder 32 is formed.
  • the intermediate pressure chamber 38 is formed at the rear end portion of the main shaft 5 between the rear end portion (the other end portion) of the inner ring 27 and the valve plate 44.
  • This intermediate pressure chamber 38 is in the state shown in FIG. 2 and is interposed between the main shaft 5 and the inner ring 27, supports both members so as to be relatively rotatable, and supports the inner ring 27 so as to be movable in the axial direction with respect to the main shaft 5.
  • the above-described seal members 37 and 45 are pressure-sealed against the crank chamber 4 side.
  • the inner ring 27 as the axially moving member has an intermediate pressure Pm applied to the annular pressure receiving surface 46 surrounded by the seal members 37 and 45, and a pressure on the crank chamber 4 side on the opposite side.
  • a load in the axial direction is generated by the differential pressure.
  • the intermediate pressure chamber 38 is in the state shown in FIG. 4 corresponding to the state in FIG. 3, and the sealing members 37 and 45 are sealed so as to be slidable in the axial direction.
  • the volume of the intermediate pressure chamber 38 is reduced.
  • the rotary drive force from the power source is illustrated as a clutchless type compressor that is directly transmitted to the main shaft 5 via the pulley 47. It is also possible to constitute a clutch type compressor having a clutch (particularly an electromagnetic clutch) (not shown) capable of switching between the power transmission state and the power transmission state.
  • the intake passage 15 for taking in the intake gas from the outside to the compressor 1 is formed only in the front housing 2, and the intake gas taken in through the intake passage 15 is first cranked. It is sucked into the chamber 4 and introduced into the suction chamber 32 through the communication path 34 from there. Therefore, since the crank chamber 4 having a large capacity serves as a suction chamber for the external circuit, noise caused by suction pulsation is prevented or reduced. Further, since the suction throttle valve can be eliminated, the degree of freedom in designing the cylinder head 31 in the layout is improved. Further, the volume of the suction chamber 32 formed in the cylinder head 31 may be smaller than that in the case where the suction gas is directly sucked into the conventional suction chamber.
  • crank chamber 4 since the volume of the discharge chamber 33 can be increased, the noise resulting from discharge pulsation is also prevented or reduced. Further, since the inside of the crank chamber 4 becomes an intake gas atmosphere, the temperature and pressure are reduced as compared with the conventional structure, so the seal member of the main shaft 5 (for example, the seal member provided on the front side), the rotor 6 and its The durability of each drive component including the support bearing, the hinge mechanism 12 and the like is improved, and the pressure resistance of the housing component (particularly the front housing 2) forming the crank chamber 4 is relatively improved. In particular, when the pressure resistance of the front housing 2 is improved, the thickness of the front housing 2 can be reduced, and the size and weight can be reduced.
  • the axial movement member (inner ring 27) is controlled in such a way that the pressure in the crank chamber 4 and the pressure in the intermediate pressure chamber 32 controlled by the intermediate pressure control mechanism 39 are applied to each end side of the axial movement member.
  • the axial position of the axially moving member is controlled with high accuracy by the differential pressure between them, and the tilt angle of the swash plate 7 and the capacity of the compressor 1 are stabilized with high accuracy through the position control of the axially moving member. To be controlled.
  • FIG. 5 shows a balance of even moments due to rotation and reciprocation of each component in the compressor 1
  • FIG. 6 shows a balance of even moments due to gas pressure acting on each part in the compressor 1. The meaning of each symbol in FIG. 6 is as follows.
  • the moment of the piston 21 in the suction stroke is canceled out because the front-rear differential pressure is the same pressure (Ps). Further, in the state where the position of the instantaneous rotation center (C) is set to an appropriate position (that is, the cam profile in the cam mechanism is set appropriately) and the pressure receiving area of the inner ring 27 is set to an appropriate size, Pm
  • the swash plate cam angle can be optimally controlled. More precisely, the moment of the system including the piston 21 is determined by the differential pressure between Pd and Ps, and the moment of the system including the inner ring 27 is determined by the differential pressure between Pm and Ps, and each moment is balanced.
  • the balance of even moments due to the rotation and reciprocation of each component in the compressor 1 is preferably set to have the characteristics shown in FIG. That is, the even moment balance due to the gas pressure of the compressor 1 described above is a moment that urges toward the cam angle increasing side when the intermediate pressure Pm is increased. As shown in FIG. 5, it is preferable to set so that the cam angle is urged in all cam angles. That is, in FIG. 5, even when the cam angle is minimum, the total even moment is always set in the cam angle decreasing direction. By such setting, more desirable stable high-accuracy capacity control is realized.
  • the counterweight 13 can also contribute to this desirable setting.
  • the axially moving member cannot make Pm applied to the rear side surface smaller than Ps on the opposite pressure receiving surface side, it can act only in the cam angle increasing direction, and can be decreased once the cam angle is increased. Disappear. Therefore, when the even moment due to the gas pressure is such that the moment M2 in the cam angle decreasing direction does not act as described above, the even moment due to rotation or reciprocation (or in combination with the reduce spring 109) is changed to the characteristic shown in FIG. Therefore, it is necessary to always ensure an even moment in the cam angle decreasing direction.
  • the characteristics shown in FIG. 5 have a small effect when the rotational speed of the compressor is small. Therefore, when maintaining the off mode, it is necessary to secure an even moment in the cam angle decreasing direction by another method. For this purpose, the characteristics shown in FIG. 6 are preferable.
  • FIG. 7 shows a main part of the variable capacity compressor 51 according to the second embodiment of the present invention.
  • the intermediate pressure (Pm) is a control valve in which the discharge gas is disposed in the communication passage 40 from the discharge chamber 33 in the cylinder head 31 to the intermediate pressure chamber 38. After being controlled by 52, it is introduced into the intermediate pressure chamber 38, and returns to the suction chamber 32 through the control valve 52 again in the communication path 53 from the intermediate pressure chamber 38 to the suction chamber 32. That is, the intermediate pressure (Pm) is controlled by adjusting the introduction amount into the intermediate pressure chamber 38 and the escape amount from the intermediate pressure chamber 38 under the control of the control valve 52.
  • Other configurations are in accordance with the first embodiment shown in FIG. Even in such a configuration, the same effects as those of the first embodiment can be obtained, and the intermediate pressure control mechanism can be simplified.
  • FIG. 8 shows a variable capacity compressor 61 according to the third embodiment of the present invention.
  • the suction passage 62 is formed from the suction port 64 provided in the cylinder head 63 to the cylinder block 65 and the front housing 66.
  • a communication path 68 from the crank chamber 67 to the suction chamber 32 in the cylinder head 63 is formed by using the insertion holes of the front housing 66, the cylinder block 65, and the fastening bolt 69 of the cylinder head 63.
  • the intermediate pressure (Pm) is introduced into the intermediate pressure chamber 38 as a pressure reduced by the throttle 70 from the pressure (Pd) of the discharge chamber 33, and is disposed in the communication path 71 from the intermediate pressure chamber 38 to the suction chamber 32.
  • the control valve 72 returns to the suction chamber 32.
  • FIG. 9 shows a variable capacity compressor 81 according to the fourth embodiment of the present invention.
  • a suction chamber 83 is formed on the inner diameter side and a discharge chamber 84 is formed on the outer diameter side in the cylinder head 82 as compared with the first embodiment described above.
  • a suction passage 86 for suction gas to the crank chamber 85 is formed across the front housing 90 via a suction port 88 and a suction muffler chamber 89 provided in the cylinder block 87.
  • a communication path 91 from the crank chamber 85 to the suction chamber 83 in the cylinder head 82 is linearly arranged on the inner diameter side between the cylinder bores 20 of the cylinder block 87.
  • the intermediate pressure (Pm) is introduced into the intermediate pressure chamber 38 after being controlled by the control valve 93 disposed in the communication passage 92 from the discharge chamber 84 to the intermediate pressure chamber 38.
  • the pressure is reduced by the throttle 94 and then returned to the suction chamber 32.
  • Other configurations are in accordance with the first embodiment shown in FIG. Even in such a configuration, the same effects as those of the first embodiment can be obtained, and the formation of the communication passage 91 to the cylinder block 87 can be facilitated.
  • the suction pulsation attenuated in the suction muffler chamber 89 is further attenuated in the crank chamber 85, the suction pulsation can be attenuated more reliably.
  • the discharge gas can be discharged through the discharge muffler chamber 95 through the discharge cutoff valve 96 and the discharge port 97, the discharge pulsation can be attenuated.
  • FIG. 10 shows a variable capacity compressor 101 according to the fifth embodiment of the present invention.
  • the oscillating plate 18 as in the first to fourth embodiments described above is not provided, but is configured in a so-called swash plate type variable displacement compressor 101. That is, the mechanism for converting the rotational movement of the swash plate 102 to the reciprocating motion of the piston 103 is converted from the mechanism for converting the reciprocating motion of the piston 103 through a pair of shoes 104 slidably in contact with both outer peripheral sides of the swash plate 102. It is configured.
  • a sleeve 106 is provided so as to be movable in the axial direction on the main shaft 105.
  • a thrust bearing 107 is provided on the front side of the sleeve 106, and the central portion of the swash plate 102 is movable in the axial direction integrally with the sleeve 106 together with the thrust bearing 107 and a collar 108 that is movable in the axial direction.
  • a reduction spring 109 is provided on the front side of the collar 108 to urge the swash plate 102 in the direction of decreasing the tilt angle (that is, in the cam angle decreasing direction of the cam mechanism constituted by the hinge mechanism 12). Is biased in the direction of the minimum inclination.
  • the collar 108 and the reduce spring 109 rotate integrally with the main shaft 105 together with the swash plate 102.
  • the swash plate 102 is supported on the collar 108 so that the tilt angle can be changed in the tilt change plane.
  • An intermediate pressure chamber 38 is formed at the other end of the sleeve 106 in the same manner as in the first embodiment.
  • a swash plate 102 that has been deformed to the minimum inclination side is urged in an increasing direction of inclination.
  • a return spring 110 is provided. Since the other configuration conforms to the first embodiment, the same reference numerals as those in FIG. Even with such a swash plate type variable displacement compressor 101, the same operational effects as in the first embodiment can be obtained.
  • the present invention can be applied regardless of the variable displacement compressor of the swing plate type and the variable displacement compressor of the swash plate type.
  • variable capacity compressor is applicable to any variable capacity 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)
PCT/JP2010/003724 2009-06-05 2010-06-03 可変容量圧縮機 WO2010140374A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP10783162.0A EP2423507A4 (en) 2009-06-05 2010-06-03 VARIABLE DISPLACEMENT COMPRESSOR
CN2010800251599A CN102459897A (zh) 2009-06-05 2010-06-03 可变容量压缩机
US13/376,346 US20120073430A1 (en) 2009-06-05 2010-06-03 Variable Displacement Compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-136544 2009-06-05
JP2009136544A JP5519193B2 (ja) 2009-06-05 2009-06-05 可変容量圧縮機

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WO2010140374A1 true WO2010140374A1 (ja) 2010-12-09

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US (1) US20120073430A1 (zh)
EP (1) EP2423507A4 (zh)
JP (1) JP5519193B2 (zh)
KR (1) KR20120024874A (zh)
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WO (1) WO2010140374A1 (zh)

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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
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KR20120024874A (ko) 2012-03-14
CN102459897A (zh) 2012-05-16
JP2010281289A (ja) 2010-12-16
JP5519193B2 (ja) 2014-06-11
EP2423507A4 (en) 2013-08-14
US20120073430A1 (en) 2012-03-29
EP2423507A1 (en) 2012-02-29

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