EP2096308B1 - Taumelscheibe mit variablem Verschiebungsverdichter - Google Patents

Taumelscheibe mit variablem Verschiebungsverdichter Download PDF

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Publication number
EP2096308B1
EP2096308B1 EP09153858A EP09153858A EP2096308B1 EP 2096308 B1 EP2096308 B1 EP 2096308B1 EP 09153858 A EP09153858 A EP 09153858A EP 09153858 A EP09153858 A EP 09153858A EP 2096308 B1 EP2096308 B1 EP 2096308B1
Authority
EP
European Patent Office
Prior art keywords
valve
rotary shaft
swash plate
compressor
bleed passage
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.)
Expired - Fee Related
Application number
EP09153858A
Other languages
English (en)
French (fr)
Other versions
EP2096308A2 (de
EP2096308A3 (de
Inventor
Kenji Yamamoto
Shiro Hayashi
Hideki Mizutani
Hiroaki Kayukawa
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries 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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP2096308A2 publication Critical patent/EP2096308A2/de
Publication of EP2096308A3 publication Critical patent/EP2096308A3/de
Application granted granted Critical
Publication of EP2096308B1 publication Critical patent/EP2096308B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B2027/1886—Open (not controlling) fluid passage
    • F04B2027/1895—Open (not controlling) fluid passage between crankcase and suction chamber

Definitions

  • the present invention relates to a variable displacement compressor for use in an automotive air conditioner, and the like.
  • a variable displacement compressor (hereinafter referred to as "compressor”) is known as a compressor for use in an automotive air conditioner that is operable to variably control its displacement.
  • This type of compressor uses a displacement control valve for adjusting pressure in a crank chamber to change the inclination angle of a swash plate accommodated in the crank chamber, thereby to adjust the stroke length of pistons and hence to control the displacement of the compressor.
  • Japanese Unexamined Patent Application Publication No. 10-54350 discloses a compressor according to the preamble of claim 1.
  • the said compressor has a valve disposed in a bleed passage connecting the crank chamber to a suction pressure region of the compressor.
  • the valve includes a valve body, a coil spring and a counterweight.
  • the coil spring urges the valve body in the direction that causes the valve body to open a valve hole.
  • the valve body is moved in the direction that causes the valve body to close the valve hole by centrifugal force acting on the counterweight, which closes the bleed passage and stops the flow of refrigerant gas from the crank chamber into the suction region through the bleed passage.
  • the valve closes the bleed passage and the pressure in the crank chamber is gradually increased by blow-by gas flowing into the crank chamber.
  • the displacement of the compressor is decreased so that the compression load is reduced and the contact pressure acting on various sliding surfaces of the compressor is reduced, accordingly.
  • the bleed passage is closed by the valve when the rotational speed of the rotary shaft reaches the predetermined value or more, with the result that the amount of refrigerant gas drawn from the crank chamber into the suction pressure region becomes zero.
  • the present invention which has been made in light of the above problems, is directed to a swash plate type variable displacement compressor which ensures the performance to recover displacement of the compressor during the operation at a low rotational speed and to reduce power loss during the operation at a high rotational speed.
  • a swash plate type variable displacement compressor includes a housing including a cylinder block having a cylinder bore formed therein, a crank chamber formed in the housing, a rotary shaft extending through the crank chamber, and a swash plate connected to the rotary shaft.
  • the rotary shaft is rotatably supported by the housing.
  • the swash plate is integrally rotatable with the rotary shaft and inclinable relative to the rotary shaft.
  • the compressor further includes a piston received in the cylinder bore to be reciprocally movable, a discharge pressure region for receiving discharge pressure gas, a suction pressure region for receiving suction pressure gas, a supply passage connecting the crank chamber to the discharge pressure region and first and second bleed passages.
  • the supply passage is provided with a displacement control valve.
  • the pressure in the crank chamber is varied by adjusting the opening of the displacement control valve to change the inclination angle of the swash plate thereby to control the displacement of the compressor.
  • the first bleed passage connecting the crank chamber to the suction pressure region is provided with a valve and the second bleed passage constantly connecting the crank chamber to the suction pressure region is provided with a throttle. The valve operates to close the first bleed passage according to the magnitude of centrifugal force generated by the rotation of the rotary shaft.
  • the compressor designated by numeral 10 has a housing 11 forming the outer shell of the compressor 10.
  • the housing 11 includes a cylinder block 12, a front housing 13 joined to the front end of the cylinder block 12, and a rear housing 14 joined to the rear end of the cylinder block 12.
  • the cylinder block 12 has a plurality of cylinder bores 12A formed therein.
  • the left side of the drawing corresponds to the front side of the compressor 10
  • the right side of the drawing corresponds to the rear side of the compressor 10.
  • the front housing 13, the cylinder block 12 and the rear housing 14 are fastened together in the longitudinal direction of the compressor 10 by a plurality of bolts 15 (only one bolt being shown) inserted through the front housing 13, the cylinder block 12 and the rear housing 14, thus the housing 11 of the compressor 10 is formed thereby.
  • the front housing 13 has a crank chamber 16 formed therein, whose rear end is closed by the cylinder block 12.
  • a rotary shaft 17 extends through the center of the crank chamber 16 and is rotatably supported by the front housing 13 and the cylinder block 12 through radial bearings 18, 19, respectively.
  • a shaft seal mechanism 20 is disposed in slide contact with the circumferential surface of the rotary shaft 17 at a position forward of the radial bearing 18 supporting the front part of the rotary shaft 17.
  • the seal mechanism 20 has a lip seal member to prevent refrigerant gas in the crank chamber 16 from leaking out through the clearance between the front housing 13 and the rotary shaft 17.
  • the rotary shaft 17 is connected at the front end thereof to an external drive source (not shown) through a power transmission mechanism (not shown either) so as to be rotated by the external drive source.
  • a lug plate 21 is fixedly mounted on the rotary shaft 17 in the crank chamber 16 so as to rotate integrally therewith.
  • a swash plate 23 as a part of displacement changing mechanism 22 of the compressor 10 is provided on the rotary shaft 17 behind the lug plate 21 and supported in such a way that it is slidable in the axial direction of the rotary shaft 17 and inclinable relative to the axis of the rotary shaft 17.
  • a hinge mechanism 24 is interposed between the swash plate 23 and the lug plate 21, through which the swash plate 23 and the lug plate 21 are connected such that the swash plate 23 is integrally rotatable with the lug plate 21 and the rotary shaft 17, while inclinable relative to the rotary shaft 17.
  • a coil spring 25 is disposed on the rotary shaft 17 between the lug plate 21 and the swash plate 23.
  • a sleeve 26 is slidably disposed on the rotary shaft 17 and urged rearward by the pressing force of the coil spring 25.
  • the swash plate 23 is urged by the coil spring 25 through the sleeve 26 rearward or in the direction that decreases the inclination angle of the swash plate 23.
  • the inclination angle of the swash plate 23 means an angle between the swash plate 23 and an imaginary plane that is perpendicular to the axis of the rotary shaft 17.
  • the swash plate 23 has a restricting portion 23A projecting from the front end thereof and abutable with the lug plate 21, thereby restricting the maximum inclination angle of the swash plate 23.
  • the rotary shaft 17 has a snap ring 27 fitted thereon behind the swash plate 23.
  • the rear end of the swash plate 23 is abutable with the snap ring 27, thereby restricting the minimum inclination angle of the swash plate 23.
  • the swash plate 23 indicated by the solid line represents the position at the maximum inclination angle thereof
  • the swash plate 23 indicated by the double-dashed line represents the position at the minimum inclination angle thereof.
  • Each cylinder bore 12A of the cylinder block 12 receives therein a reciprocally movable single-headed piston 29.
  • the piston 29 engages at the neck portion thereof with the outer periphery of the swash plate 23 through a pair of shoes 30.
  • each piston 29 is reciprocated in its associated cylinder bore 12A through the pair of shoes 30.
  • the front end of the rear housing 14 is joined to the rear end of the cylinder block 12 through a valve plate 32.
  • the rear housing 14 has a suction chamber 38 which serves as a suction pressure region formed at a center region thereof.
  • the suction chamber 38 is in communication with a compression chamber 31 defined by the cylinder bore 12A through a suction port 36 formed through the valve plate 32.
  • the rear housing 14 also has a discharge chamber 39 which serves as a discharge pressure region formed at a circumferential region thereof.
  • the discharge chamber 39 and the suction chamber 38 are separated by a partition wall 14A.
  • the valve plate 32 defining the compression chamber 31 with the piston 29 in the cylinder bore 12A has a discharge port 37 formed therethrough in communication with the discharge chamber 39.
  • the suction port 36 and the discharge port 37 for each cylinder bore 12A are provided with a suction valve 33 and a discharge valve 34, respectively.
  • a supply passage 42 is formed in the cylinder block 12 and the rear housing 14 to connect the discharge chamber 39 to the crank chamber 16.
  • An electromagnetic displacement control valve 35 is disposed in the supply passage 42.
  • the displacement control valve 35 is in communication with the suction chamber 38 through a pressure sensing passage 61.
  • the opening of the displacement control valve 35 is adjustable according to the detected pressure in the suction chamber 38 or in response to any external command signals. Adjusting the opening of the displacement control valve 35 varies the flow rate of high-pressure refrigerant gas introduced from the discharge chamber 39 into the crank chamber 16.
  • the pressure differential between the crank chamber 16 and the compression chamber 31 across the piston 29 is varied, thereby changing the inclination angle of the swash plate 23. Accordingly, the stroke length of the piston 29 is varied thereby to control the displacement of the compressor 10.
  • the center of the cylinder block 12 has a shaft hole 43 therethrough, and a recess 44 located behind and in communication with the shaft hole 43.
  • the rear end of the rotary shaft 17 is inserted into and supported by the shaft hole 43 through the radial bearing 19.
  • the compressor 10 of the first preferred embodiment includes a first bleed passage 48 and a second bleed passage 58.
  • a passage hole 45 forming a part of the first bleed passage 48 extends in the rotary shaft 17 along its center axis.
  • the front end portion of the passage hole 45 is opened to the crank chamber 16 at a position adjacent to the radial bearing 18 and the shaft seal mechanism 20.
  • the passage hole 45 is closed at the rear end by a plug 60.
  • a valve 50 is mounted on the rotary shaft 17 at the rear end portion thereof in the recess 44. The valve 50 will be described in detail later.
  • a thrust bearing 46 and a support spring 47 are interposed between the rear end of the rotary shaft 17 and the valve plate 32.
  • the recess 44 is in communication with the suction chamber 38 through a communication hole 49 formed at the center of the valve plate 32.
  • the communication hole 49 serves as a throttle for restricting flow rate of refrigerant gas drawn from the crank chamber 16 into the suction chamber 38.
  • the aforementioned first bleed passage 48 includes the passage hole 45, the recess 44, the valve 50 and the communication hole 49 so as to connect the crank chamber 16 to the suction chamber 38.
  • the valve 50 is provided for opening or closing the first bleed passage 48.
  • the rotary shaft 17 has plane seating surfaces 51, 52 formed by cutting off the top and bottom of the circumferential surface of the rear end portion of the rotary shaft 17, respectively.
  • a valve hole 53 is formed in the radial direction of the rotary shaft 17, or the compressor 10 so as to provide fluid communication between the seating surfaces 51, 52 and also to be in communication with the passage hole 45.
  • the valve hole 53 is larger in diameter on the side opened to the seating surface 51 than the opposite side opened to the seating surface 52.
  • a valve body 54 is movably mounted on the rotary shaft 17 so as to open or close the valve hole 53.
  • the valve body 54 is disposed on the side of the seating surface 51, and a counterweight 55 connected to the valve body 54 through a connecting portion 56 is disposed on the side of the seating surface 52.
  • a coil spring 57 serving as an urging member is provided between the seating surface 51 and the valve body 54 for urging the valve body 54 toward its opened position.
  • a centrifugal force acting on the counterweight 55 is increased with an increase in rotational speed of the rotary shaft 17, with the result that the counterweight 55 is moved away from the axis of the rotary shaft 17. Accordingly, the valve body 54 is moved toward the axis of the rotary shaft 17 against the urging force of the coil spring 57 and brought into contact with the seating surface 51, thereby to close the valve hole 53. On the other hand, the centrifugal force acting on the counterweight 55 is decreased with a decrease in rotational speed of the rotary shaft 17, with the result that the urging force of the coil spring 57 becomes greater than the centrifugal force acting on the counterweight 55.
  • Figs.1 and 2 show the valve 50 in its opened position during compressor operation at a high rotational speed of the rotary shaft 17, and Fig.3 shows the valve 50 in its closed position during compressor operation at a low rotational speed of the rotary shaft 17.
  • the second bleed passage 58 connecting the crank chamber 16 to the suction chamber 38 is formed in the cylinder block 12.
  • the second bleed passage 58 has a throttle hole 59 formed in the valve plate 32 which functions as a fixed throttle for throttling the flow rate of the refrigerant gas.
  • the crank chamber 16 is in constant communication with the suction chamber 38 through the second bleed passage 58.
  • the discharge chamber 39 is in communication with the crank chamber 16 through the supply passage 42 in which the displacement control valve 35 is disposed.
  • the crank chamber 16 is in communication with the suction chamber 38 through the first bleed passage 48 and the second bleed passage 58.
  • the first bleed passage 48 is provided with the valve 50 operable to open or close according to the magnitude of the centrifugal force and the second bleed passage 58 is provided with the throttle hole 59 serving as a fixed throttle.
  • Fig.5 is a schematic graph showing a relation between rotational speed N of the rotary shaft 17 of the compressor 10 and total cross-sectional area AS of the throttle opening which is the sum of the cross-sectional areas of the throttle openings formed in the first and second bleed passages 48, 58 according to the first preferred embodiment.
  • the cross-sectional areas of the communication hole 49 provided in the first bleed passage 48 and the throttle hole 59 provided in the second bleed passage 58 are designated by reference symbols AA, AB, respectively.
  • the valve 50 is in its opened position.
  • the cross-sectional areas AA and AB are previously set at any values suitable to ensure both of the displacement recovery and power loss reduction during the operation of the compressor 10.
  • the diameter of the fully opened valve hole 53 is set such that the cross-sectional area of such valve hole 53 is larger than the cross-sectional area AA of the communication hole 49.
  • the swash plate 23 is rotated with the rotary shaft 17 through the lug plate 21 and the hinge mechanism 24. Accordingly, the rotational movement of the swash plate 23 is converted into reciprocating movement of the piston 29 by way of the shoes 30.
  • the piston 29 is reciprocated in the cylinder bore 12A, thereby causing refrigerant gas to be drawn from the suction chamber 38 into the compression chamber 31 through the suction port 36 and the suction valve 33. Then the refrigerant gas is compressed in the compression chamber 31 to a predetermined pressure and discharged into the discharge chamber 39 through the discharge port 37 and the discharge valve 34.
  • the opening of the displacement control valve 35 provided in the supply passage 42 is adjusted to control the relation between the flow rate of refrigerant gas introduced from the discharge chamber 39 into the crank chamber 16 and the flow rate of refrigerant gas flowing out from the crank chamber 16 into the suction chamber 38 through the first and second bleed passages 48, 58.
  • a crank chamber pressure PC in the crank chamber 16 is determined by this relation of the refrigerant gas.
  • a suction pressure PS in the suction chamber 38 is high and there is substantially no pressure differential between the pressures in the compression chambers 31 and the crank chamber pressure PC in the crank chamber 16 through the piston 29. (or PS ⁇ PC).
  • the displacement control valve 35 is controlled to be closed so that the supply passage 42 prevents high-pressure refrigerant gas in the discharge chamber 39 from flowing into the crank chamber 16. Since the crank chamber pressure PC in the crank chamber 16 is substantially the same as the suction pressure PS, refrigerant gas does not flow from the crank chamber 16 through the first and second bleed passages 48, 58 into the suction chamber 38.
  • the swash plate 23 is moved to its maximum inclination angle position to increase the stroke of the piston 29, thereby to increase the displacement of the compressor 10.
  • the refrigerant gas does not circulate through the supply passage 42, the first and second bleed passages 48, 58, with the result that the compressor 10 is efficiently operated.
  • the suction pressure PS in the suction chamber 38 is also decreased.
  • the displacement control valve 35 is controlled to be opened in accordance with the decrease in the suction pressure PS. Accordingly, high-pressure refrigerant gas in the discharge chamber 39 is introduced into the crank chamber 16 through the supply passage 42.
  • the crank chamber pressure PC in the crank chamber 16 is increased and the pressure differential between the crank chamber 16 and the compression chambers 31 through the piston 29 increases.
  • the inclination angle of the swash plate 23 becomes small in accordance with the increase of the pressure differential, thereby decreasing the displacement of the compressor 10.
  • the valve body 54 of the valve 50 provided in the first bleed passage 48 is positioned so as to open the valve hole 53, as shown in Fig. 2 .
  • the second bleed passage 58 has the throttle hole 59 for constant communication between the crank chamber 16 and the suction chamber 38. That is, the first bleed passage 48 provided with the valve 50 and the second bleed passage 58 provided with the throttle hole 59 are opened.
  • the refrigerant gas is drawn from the crank chamber 16 into the suction chamber 38 rapidly and, therefore, the displacement of the compressor 10 is controlled appropriately in accordance with a change in the cooling load.
  • the centrifugal force generated by the rotation of the rotary shaft 17 is increased. That is, the centrifugal force acting on the counterweight 55 of the valve 50 is also increased.
  • the valve body 54 is moved toward the axis of the rotary shaft 17 by the centrifugal force acting against the urging force of the coil spring 57 so as to be brought into contact with the seating surface 51, thereby to close the valve hole 53.
  • the first bleed passage 48 provided with the valve 50 is closed and only the second bleed passage 58 provided with the throttle hole 59 is opened.
  • the decrease of the flow rate of refrigerant gas circulating within the compressor means the increase the flow rate of refrigerant gas in the external refrigeration circuit, thus reducing the power loss of the compressor 10.
  • the suction pressure PS in the suction chamber 38 is further decreased accordingly and the displacement control valve 35 becomes fully opened.
  • a large amount of high-pressure refrigerant gas is introduced from the discharge chamber 39 into the crank chamber 16 through the supply passage 42, thereby to increase the crank chamber pressure PC in the crank chamber 16.
  • the pressure differential between the crank chamber 16 and the compression chamber 31 through the piston 29 is increased.
  • the swash plate 23 is moved to its minimum inclination angle position to decrease the stroke length of the piston 29, thereby to change the displacement of the compressor 10 to the minimum.
  • the displacement of the compressor 10 is not zero.
  • the flow rate of refrigerant gas circulating within the compressor 10 is further decreased thereby to decrease the level of the minimum displacement.
  • the power loss during the minimum displacement operation is reduced.
  • the following will describe the recovery of the compressor 10 from the minimum displacement state.
  • the increase of the displacement of the compressor 10 from the OFF operation is dependent on the rate of refrigerant gas from the crank chamber 16 into the suction chamber 38.
  • the first bleed passage 48 provided with the valve 50 and the second bleed passage 58 provided with the throttle hole 59 are both opened. Therefore, the refrigerant gas is drawn from the crank chamber 16 into the suction chamber 38 rapidly and the crank chamber pressure PC in the crank chamber 16 is decreased accordingly rapidly
  • the recovery of the compressor 10 from the minimum displacement state is improved.
  • the swash plate type variable displacement compressor 10 offers the following advantageous effects.
  • the compressor of the second preferred embodiment differs from that of the first preferred embodiment in that the rotary shaft 17 is equipped with the function of the second bleed passage 58 of the first embodiment. That is, the second bleed passage of the second embodiment shares a part of the first bleed passage.
  • the rest of the structure of the compressor according to the second preferred embodiment is substantially the same as that of the first preferred embodiment. For the sake of convenience of explanation, therefore, like or same parts or elements will be referred to by the same reference numerals as those that have been used in the first preferred embodiment, and the description thereof will be omitted.
  • the rotary shaft 17 of the compressor 10 has a throttle hole 70 radially bored therethrough at a position adjacent to the valve 50 for providing fluid communication between the passage hole 45 in the rotary shaft 17 and the recess 44 in the cylinder block 12.
  • the throttle hole 70 functions as a fixed throttle.
  • the diameter D1 of the throttle hole 70 is formed smaller than the diameter D2 of the communication hole 49 (or D1 ⁇ D2).
  • the rotary shaft 17 has the throttle hole 70 for providing constant communication between the crank chamber 16 and the suction chamber 38.
  • the flow rate of the refrigerant gas drawn from the crank chamber 16 into the suction chamber 38 depends on the diameter D2 of the communication hole 49.
  • the diameter D1 of the throttle hole 70 is smaller than the diameter D2 of the communication hole 49 (or D1 ⁇ D2).
  • the refrigerant gas in the crank chamber 16 is drawn rapidly into the suction chamber 38 trough the recess 44 and the crank chamber pressure PC in the crank chamber 16 is decreased accordingly rapidly, with the result that the performance of the compressor 10 to recover the displacement of the compressor 10 from the minimum displacement state is improved.
  • the centrifugal force generated by the rotation of the rotary shaft 17 acting on the counterweight 55 is increased and the valve body 54 is moved toward the axis of the rotary shaft 17 against the urging force of the coil spring 57 until it is brought into contact with the seating surface 51, thereby to close the valve hole 53.
  • the first bleed passage 48 provided with the valve 50 is closed and only the throttle hole 70 is opened. Accordingly, the flow rate of refrigerant gas drawn from the crank chamber 16 into the suction chamber 38, which depends on the diameter D1 of the throttle hole 70, is decreased.
  • the inertial force acting on the piston 29 and the swash plate 23 is increased so as to principally affect the motion of the piston 29 and the swash plate 23 to change in the direction that increases the compression displacement.
  • the desired compression displacement is achieved rapidly from the minimum displacement state despite the decrease of the flow rate of refrigerant gas drawn from the crank chamber 16 into the suction chamber 38.
  • the decreased flow rate of refrigerant gas circulating within the compressor 10 during its variable displacement operation means the increase of the flow rate of refrigerant gas in the external refrigeration circuit, thereby to reduce the power loss.
  • the level of the minimum displacement of the compressor is further decreased.
  • the power loss during the minimum displacement operation is also reduced.
  • Fig.6 shows the valve 50 in its closed position.
  • the first bleed passage 48 and the throttle hole 70 are both provided in the rotary shaft 17. This structure contributes to reduction in production time and cost as compared with a structure wherein the first bleed passage 48 and the throttle hole 70 are provided separately.
  • the compressor 10 of the third preferred embodiment differs from that of the second preferred embodiment in that a groove 80 corresponding to the throttle hole 70 of the second preferred embodiment is formed in the valve hole 53 of the valve 50.
  • the rest of the structure of the compressor 10 according to the third preferred embodiment is substantially the same as that of the second preferred embodiment.
  • like or same parts or elements will be referred to by the same reference numerals as those which have been used in the first and second preferred embodiments, and the description thereof will be omitted.
  • the groove 80 having a certain depth is formed at the opening of the valve hole 53 of the valve 50 on the side of the seating surface 51.
  • the valve body 54 and the groove 80 cooperate to form a groove slit 81.
  • the passage hole 45 is communicated with the recess 44 through the groove slit 81 which functions as a throttle.
  • the cross-sectional area of the groove slit 81 when the valve body 54 is in contact with the seating surface 51 is set smaller than that (D2) of the communication hole 49 and set substantially the same as that (D1) of the throttle hole 70 of the second preferred embodiment.
  • the centrifugal force generated by the rotation of the rotary shaft 17 is increased and the centrifugal force acting on the counterweight 55 of the valve 50 is also increased.
  • the valve body 54 is then moved toward the axis of the rotary shaft 17 by the centrifugal force against the urging force of the coil spring 57 until it is brought into contact with the seating surface 51, thereby to close the valve hole 53.
  • only the groove slit 81 whose diameter is smaller than that of the communication hole 49, is opened, so that the flow rate of the refrigerant gas drawn from the crank chamber 16 into the suction chamber 38 is decreased.
  • the inertial force acting on the piston 29 and the swash plate 23 is increased so as to principally affect the motion of the piston 29 and the swash plate 23 to change in the direction that increases the compression displacement.
  • the desired compression displacement is achieved rapidly from the minimum displacement state despite the decrease of the flow rate of refrigerant gas drawn from the crank chamber 16 into the suction chamber 38.
  • the decreased flow rate of refrigerant gas circulating within the compressor 10 during its variable displacement operation means the increase of the flow rate of refrigerant gas in the external refrigeration circuit, thereby reducing the power loss.
  • the compression displacement is decreased further than the minimum displacement.
  • the power loss during the minimum displacement operation is also reduced.
  • Fig.7 shows the valve 50 in its closed position.
  • the groove 80 is merely formed at the opening of the valve hole 53 of the valve 50. This contributes to simplified structure and further reduction in the production time and cost of the compressor 10.
  • the present invention is not limited to the first through third preferred embodiments, but it may be variously modified within the scope of the invention.
  • the above embodiments may be modified as exemplified below.
  • the throttle hole 70 or the groove slit 81 is provided at one end of the rotary shaft 17 as a throttle.
  • a fixed throttle may be formed through the plug 60 closing rear end of the passage hole 45 so that the passage hole 45 and the recess 44 are in constant communication with each other.
  • the groove 80 is provided on the side of the seating surface 51 of the valve hole 53.
  • the groove 80 may be provided on the surface of the valve body 54.
  • the valve body 54 may have an elongated hole formed therein as a throttle providing fluid communication between the passage hole 45 and the recess 44.
  • any kind of refrigerant may be used, including preferably fluorocarbon gas or carbon dioxide.
  • the compressor 10 according to the foregoing embodiments have been described as a compressor for compressing refrigerant gas, the present invention does not limit the refrigerant only to gaseous refrigerant.

Claims (10)

  1. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart, der Folgendes aufweist:
    ein Gehäuse (11), das einen Zylinderblock (12) aufweist mit einer darin ausgebildeten Zylinderbohrung (12A);
    eine Kurbelkammer (16), die in dem Gehäuse (11) ausgebildet ist;
    eine Drehwelle (17), die sich durch die Kurbelkammer (16) erstreckt, wobei die Drehwelle (17) durch das Gehäuse (11) drehbar gestützt ist;
    eine Taumelscheibe (23), die mit der Drehwelle (17) verbunden ist, wobei die Taumelscheibe (23) mit der Drehwelle (17) einstückig drehbar ist und relativ zu der Drehwelle (17) neigbar ist;
    einen Kolben (29), der in der Zylinderbohrung (12A) so aufgenommen ist, dass er hin- und hergehend bewegbar ist;
    eine Auslassdruckregion (39) zum Empfangen von Auslassdruckgas;
    eine Ansaugdruckregion (38) zum Empfangen von Ansaugdruckgas, und
    einen Lieferkanal (42), der die Kurbelkammer (16) mit der Auslassdruckregion (39) verbindet, wobei der Lieferkanal (42) mit einem Verdrängungssteuerventil (35) versehen ist, wobei der Druck in der Kurbelkammer (16) variiert wird, indem die Öffnung des
    Verdrängungssteuerventils (35) eingestellt wird, um den Neigungswinkel der Taumelscheibe (23) zu ändern, wodurch die Verdrängung des Kompressors (10) gesteuert wird, und
    einen ersten Ablaufkanal (48), der die Kurbelkammer (16) mit der Ansaugdruckregion (38) verbindet, wobei der erste Ablaufkanal (48) mit einem Ventil (50) versehen ist,
    wobei das Ventil (50) so arbeitet, dass es den ersten Ablaufkanal (48) gemäß der Größe einer Zentrifugalkraft schließt, die durch die Drehung der Drehwelle (17) erzeugt wird,
    gekennzeichnet durch
    einen zweiten Ablaufkanal (58), der die Kurbelkammer (16) mit der Ansaugdruckregion (38) konstant verbindet, wobei der zweite Ablaufkanal (58) mit einer Drossel (59, 70, 80) versehen ist.
  2. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß Anspruch 1, wobei der erste Ablaufkanal (48) ein Kanalloch (45) aufweist, das sich in der Drehwelle (17) entlang der Mittelachse erstreckt, wobei ein Ende des Kanallochs (45) zu der Kurbelkammer (16) offen ist, wobei das Ventil (50) an dem anderen Ende des Kanallochs (45) angeordnet ist.
  3. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß Anspruch 1 oder 2, wobei der zweite Ablaufkanal (58) separat von dem ersten Ablaufkanal (48) ausgebildet ist, wobei die Drossel (70) des zweiten Ablaufkanals (58) eine fixierte Drossel ist.
  4. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß Anspruch 1 oder 2, wobei sich der zweite Ablaufkanal (48) zumindest einen Teil des ersten Ablaufkanals (48) mit diesem teilt.
  5. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß Anspruch 4, wobei die Drossel des zweiten Ablaufkanals (58) eine fixierte Drossel ist, die an der Drehwelle (17) vorgesehen ist.
  6. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß Anspruch 4, wobei das Ventil (50) einen Ventilkörper (54) und einen Ventilsitz (51) für einen Kontakt mit dem Ventilkörper (54) hat, wobei die Drossel des zweiten Ablaufkanals (58) eine Nut (80) ist, die an dem Ventilsitz (51) ausgebildet ist.
  7. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß einem der Ansprüche 1 bis 6, wobei das Ventil (50) einen Ventilkörper (54), ein Drängelement (57), das den Ventilkörper (54) zu der offenen Position hin drängt, und ein Gegengewicht (55) aufweist, wobei eine durch die Drehung der Drehwelle (17) erzeugte Zentrifugalkraft auf das Gegengewicht (55) einwirkt, um den Ventilkörper (54) zu der geschlossenen Position hin entgegen der Drängkraft des Drängelements (57) zu bewegen.
  8. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß Anspruch 6, wobei ein Ventilloch (53) an der Drehwelle (17) in der radialen Richtung der Drehwelle (17) ausgebildet ist, wobei der Ventilkörper (54) des Ventils (50) an der Drehwelle (17) montiert ist, um das Ventilloch (53) zu öffnen und zu schließen.
  9. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß Anspruch 7, wobei das Drängelement (57) eine Schraubenfeder ist.
  10. Kompressor (10) mit variabler Verdrängung der Taumelscheibenart gemäß einem der Ansprüche 1 bis 9, wobei das Verdrängungssteuerventil (35) ein elektromagnetisches Ventil ist.
EP09153858A 2008-02-28 2009-02-27 Taumelscheibe mit variablem Verschiebungsverdichter Expired - Fee Related EP2096308B1 (de)

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JP4924464B2 (ja) * 2008-02-05 2012-04-25 株式会社豊田自動織機 斜板式圧縮機
EP2088318A1 (de) * 2008-02-05 2009-08-12 Kabushiki Kaisha Toyota Jidoshokki Taumelscheibenverdichter
JP2015034510A (ja) * 2013-08-08 2015-02-19 株式会社豊田自動織機 可変容量型斜板式圧縮機
JP6115393B2 (ja) * 2013-08-08 2017-04-19 株式会社豊田自動織機 可変容量型斜板式圧縮機
JP6127994B2 (ja) * 2014-01-30 2017-05-17 株式会社豊田自動織機 可変容量型斜板式圧縮機
JP6127999B2 (ja) * 2014-02-03 2017-05-17 株式会社豊田自動織機 可変容量型斜板式圧縮機
JP2015183615A (ja) * 2014-03-25 2015-10-22 株式会社豊田自動織機 可変容量型斜板式圧縮機
CN106460816B (zh) * 2014-06-27 2018-12-07 法雷奥日本株式会社 可变容量斜板式压缩机
CN109899268A (zh) * 2017-12-08 2019-06-18 长城汽车股份有限公司 压缩机、空调系统和车辆
KR20200086068A (ko) * 2019-01-08 2020-07-16 한온시스템 주식회사 압축기
CN115997073A (zh) * 2020-09-02 2023-04-21 法雷奥日本株式会社 可变容量斜盘式压缩机

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JP3282457B2 (ja) * 1995-08-21 2002-05-13 株式会社豊田自動織機 片頭ピストン型圧縮機
JP3758244B2 (ja) * 1996-08-12 2006-03-22 株式会社豊田自動織機 可変容量圧縮機
JPH11287181A (ja) * 1998-04-02 1999-10-19 Toyota Autom Loom Works Ltd 可変容量圧縮機
JP2000320454A (ja) * 1999-05-13 2000-11-21 Toyota Autom Loom Works Ltd 可変容量圧縮機
JP2005315176A (ja) * 2004-04-28 2005-11-10 Toyota Industries Corp ピストン式可変容量圧縮機
JP4479504B2 (ja) * 2004-04-28 2010-06-09 株式会社豊田自動織機 可変容量圧縮機
JP2006220048A (ja) * 2005-02-09 2006-08-24 Toyota Industries Corp 容量可変型斜板式圧縮機

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