WO2003060325A1 - Compresseur - Google Patents

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Publication number
WO2003060325A1
WO2003060325A1 PCT/JP2001/011598 JP0111598W WO03060325A1 WO 2003060325 A1 WO2003060325 A1 WO 2003060325A1 JP 0111598 W JP0111598 W JP 0111598W WO 03060325 A1 WO03060325 A1 WO 03060325A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
chamber
valve
lubricating oil
check valve
Prior art date
Application number
PCT/JP2001/011598
Other languages
English (en)
Japanese (ja)
Inventor
Masaki Ota
Ken Suitou
Tomoji Tarutani
Kazuya Kimura
Ryo Matsubara
Taku Adaniya
Original Assignee
Kabushiki Kaisha Toyota Jidoshokki
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
Priority to JP2000192341A priority Critical patent/JP3864673B2/ja
Priority claimed from JP2000192341A external-priority patent/JP3864673B2/ja
Priority to US09/886,170 priority patent/US6511297B2/en
Priority to EP01115264A priority patent/EP1167762B1/fr
Application filed by Kabushiki Kaisha Toyota Jidoshokki filed Critical Kabushiki Kaisha Toyota Jidoshokki
Priority to PCT/JP2001/011598 priority patent/WO2003060325A1/fr
Priority to CN01809988.2A priority patent/CN1250873C/zh
Publication of WO2003060325A1 publication Critical patent/WO2003060325A1/fr

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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
    • F04B27/10—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
    • F04B27/109—Lubrication

Definitions

  • the present invention relates to a compressor, and more particularly, to a compressor in which movable parts in a housing are lubricated with mist lubricating oil mixed with a coolant.
  • a variable displacement compressor (hereinafter simply referred to as a compressor) applied to a vehicle air conditioner, for example, there is one as shown in FIG. That is, a crank chamber 102 is defined in a housing 101, and a drive shaft 103 is rotatably arranged.
  • the rib seal 104 is interposed between the housing 101 and seals a gap between the drive shaft 103 and the housing 101.
  • the drive shaft 103 is operatively connected to a vehicle engine Eg as an external drive source via an electromagnetic friction clutch 105 as a power transmission mechanism.
  • the friction clutch 105 includes a mouth 106 operatively connected to the vehicle engine Eg, an armature 107 fixed to the drive shaft 103 so as to be integrally rotatable, and a coil 108.
  • the coil 108 attracts the armature 107 to the rotor 106 by excitation, and fastens the two 106, 107, so that power can be transmitted between the vehicle engine Eg and the drive shaft 103. Yes (friction clutch 105 is on).
  • the rotary support 109 is fixed to the drive shaft 103 in the crank chamber 102, and a swash plate 110 is connected to the rotary support 109 via a hinge mechanism 111.
  • the swash plate 110 is connected to the rotary support 109 via a hinge mechanism 111 so that it can rotate integrally with the drive shaft 103 and change the inclination angle of the drive shaft 103 with respect to the axis L.
  • the minimum inclination angle defining section 112 is provided on the drive shaft 103 and abuts on the minimum inclination angle of the swash plate 110.
  • the cylinder pore 113, the suction chamber 114 and the discharge chamber 115 are formed in the housing 101.
  • the piston 116 is accommodated in the cylinder bore 113 so as to be able to reciprocate, and is connected to the swash plate 110.
  • the rotational movement of the drive shaft 103 is converted into a reciprocating movement of the biston 116 via the rotary support 109, the hinge mechanism 111 and the swash plate 110, and the suction port of the valve / port forming body 117 provided in the housing 101 is formed.
  • the compression cycle of discharging the compressed refrigerant gas to the discharge chamber 115 is repeated.
  • the suction chamber 114 and the discharge chamber 115 are connected by an external refrigerant circuit (not shown).
  • the refrigerant discharged from the discharge chamber 115 is introduced into the external refrigerant circuit. In this external refrigerant circuit, heat exchange using the refrigerant is performed.
  • the refrigerant discharged from the external refrigerant circuit is introduced into the suction chamber 114, is drawn into the cylinder bore 113, and undergoes a compression action again.
  • the bleed passage 119 communicates the crank chamber 102 with the suction chamber 114.
  • the air supply passage 120 connects the discharge chamber 115 and the crank chamber 102.
  • the control valve 121 is provided on the air supply passage 120, and is capable of adjusting the opening degree of the air supply passage 120.
  • the control valve 121 is based on a signal from a control computer (not shown).
  • the drive circuit is driven by a current output from a drive circuit (not shown) to adjust the opening degree of the air supply passage 120.
  • the control valve 121 operates to open the air supply passage 120 when power is not supplied from the drive circuit, and operates to adjust the opening degree of the air supply passage 120 when power is being supplied. It is like that.
  • the opening of the control valve 121 By adjusting the opening of the control valve 121, the balance between the amount of high-pressure gas introduced into the crank chamber 102 through the air supply passage 120 and the amount of gas discharged from the crank chamber 102 through the bleed passage 119 is increased. Is controlled to determine the crank pressure P c. In accordance with the change of the crank pressure P c, the difference between the crank pressure P c via the piston 116 and the internal pressure of the cylinder bore 113 is changed, and as a result, the inclination angle of the swash plate 110 is changed. In other words, the discharge capacity is adjusted.
  • the compressor when the compressor is rotated at the maximum discharge capacity, the force at which the friction clutch 105 is turned off in response to the operation of turning off the air conditioner switch (not shown), or the vehicle engine E g Stops and the compressor operation stops.
  • the power supply to the control valve 121 is also stopped (the input current value is set to zero), and the air supply passage 120 is suddenly fully opened. Therefore, the supply amount of the high-pressure refrigerant gas from the discharge chamber 115 to the crank chamber 102 is rapidly increased, and the pressure in the crank chamber 102 is excessively increased because the bleed passage 119 cannot fully escape the rapid increase. To rise. Further, the pressure in the cylinder bore 113 is reduced by trying to equalize the pressure in the suction chamber 114 due to the stoppage of the compressor. As a result, the pressure difference between the cylinder pore 113 and the crankcase 102 is excessively increased.
  • the swash plate 110 with the minimum inclination angle (indicated by a two-dot chain line in FIG. 7) is pushed through the hinge mechanism 111 so as to be pressed against the minimum inclination angle defining portion 112 with excessive force.
  • Rotating support 109 backward (right drawing) )) It will also pull strongly to the side.
  • the driving shaft 103 receives a strong moving force toward the rear side of the axis L, and slides against the urging force of the driving shaft urging panel 118. This may cause the following problems.
  • the compressor mixes the mist-like lubricating oil with the refrigerant so that the lubricating oil circulates together with the circulation of the refrigerant between the compressor and the external refrigerant circuit.
  • the compressor has a structure in which the movable parts are exposed to the refrigerant. Therefore, the movable part is also exposed to the mist lubricating oil, and the movable part can be lubricated.
  • the atomized lubricating oil is also introduced into the external refrigerant circuit by the refrigerant circulation.
  • the lubricating oil acts in the external refrigerant circuit in a direction to reduce the efficiency of heat exchange performed in the circuit. Further, since the lubricating oil is discharged from the inside of the compressor to the outside, the amount of the lubricating oil in the compressor decreases, and the lubricating efficiency in the compressor decreases.
  • the various problems caused by the increase in the pressure of the crank chamber 102 can be solved by, for example, the configuration disclosed in Japanese Patent Application Laid-Open No. 11-315875.
  • a check valve that regulates the refrigerant flow direction is provided between the discharge chamber and the external refrigerant circuit, so that the reverse flow of the refrigerant from the external refrigerant circuit side to the discharge chamber side is prevented. I'm sorry.
  • the high-pressure refrigerant gas present on the side of the external refrigerant circuit is introduced into the crank chamber 102 through the air supply passage 120 when the air supply passage 120 is fully opened as described above. Will not be done. As a result, the crank chamber The internal pressure of 102 does not rise excessively.
  • the problem due to the discharge of the lubricating oil to the external refrigerant circuit can be solved by, for example, the configuration disclosed in Japanese Patent Application Laid-Open No. H10-280160.
  • an oil separator that separates the mist of the lubricating oil mixed with the refrigerant from the refrigerant is provided in the discharge chamber, and discharge of the lubricating oil to the external refrigerant circuit is suppressed. I have.
  • An object of the present invention is to provide a compressor capable of preventing a backflow of refrigerant from an external refrigerant circuit to a discharge chamber and suppressing discharge of lubricating oil to the external refrigerant circuit.
  • the present invention provides, in a housing, a discharge chamber through which refrigerant discharged from a compression chamber passes, and a suction chamber through which refrigerant sucked into the compression chamber passes;
  • a compressor that connects the suction chamber and the external refrigerant circuit with a suction path while connecting the chamber and the external refrigerant circuit with a discharge path, and circulates the refrigerant with the external refrigerant circuit.
  • a check valve for preventing the refrigerant from flowing back from the external refrigerant circuit to the discharge chamber in the discharge path; an oil separator for separating mist-like lubricating oil mixed with the refrigerant; And an oil supply passage for introducing the separated lubricating oil into the low-pressure region.
  • the oil separator separates the refrigerant and the lubricating oil, and suppresses the discharge of the lubricating oil to the external refrigerant circuit. Since the lubricating oil causes a decrease in the heat exchange efficiency in the external refrigerant circuit, the separation can suppress the decrease in the heat exchange efficiency.
  • the lubricating oil separated from the refrigerant described above is introduced into the low-pressure region via the oil supply passage.
  • the low pressure region in the present invention refers to the suction chamber, the suction path, a crank chamber formed in the housing, and the like. As a result, it is possible to suppress a decrease in the amount of lubricating oil in the compressor including the suction path and to lubricate the inside of the compressor satisfactorily. Further, the check valve prevents the backflow of the refrigerant from the external refrigerant circuit to the discharge chamber.
  • FIG. 1 is a sectional view showing an outline of a compressor according to a first embodiment of the present invention.
  • FIG. 2 is an enlarged partial cross-sectional view (with a valve closed) of a unit 40, which is a main part of the compressor of FIG.
  • FIG. 4 is an enlarged partial cross-sectional view (valve-opened state) of a unit 40, which is a main part of the compressor in FIG.
  • FIG. 5 is an enlarged sectional view (in a valve-opened state) of a unit 70, which is a main part of a compressor according to a second embodiment of the present invention.
  • the variable capacity compressor (hereinafter simply referred to as the compressor) C is a cylinder block 1, a front housing 2 joined to its front end, and a rear end of cylinder block 1. And a rear housing 4 joined to the housing via a valve forming body 3.
  • the cylinder hook 1, the front housing 2, the valve forming body 3, and the rear housing 4 are joined and fixed to each other by a plurality of through-ports 10 (only one is shown in FIG. 1), and a compressor is provided.
  • a crank chamber 5 is defined in a region surrounded by the cylinder opening 1 and the front housing 2.
  • a drive shaft 6 is rotatably supported by a pair of front and rear radial bearings 8A and 8B.
  • a panel 7 and a rear thrust bearing 9B are arranged in a housing recess formed in the center of the cylindrical hook 1.
  • a lug plate 11 is fixed on the drive shaft 6 in the crank chamber 5 so as to be rotatable, and a front thrust bearing 9 is provided between the lug plate 11 and the inner wall surface of the front housing 2.
  • A is provided.
  • the integrated drive shaft 6 and lug plate 11 are moved in the thrust direction (drive shaft axis direction) by the rear thrust bearing 9B and the front thrust bearing 9A urged forward by the panel 7.
  • a lip seal 2A is provided between the drive shaft 6 and the front housing 2 on the front side of the radial bearing 8A.
  • the rib seal 2A seals a gap between the drive shaft 6 and the front housing 2 so that the inside and the outside of the compressor C are pressure-isolated.
  • the front end of the drive shaft 6 is operatively connected to a vehicle engine E as an external drive source via a power transmission mechanism PT.
  • the power transmission mechanism PT may be a clutch mechanism (for example, an electromagnetic clutch) capable of selecting the transmission of power by an external electric control, or may be a constant transmission type that does not have such a clutch mechanism. It may be a clutchless mechanism (for example, a belt / pulley combination). In this embodiment, a clutchless type power transmission mechanism is employed.
  • a swash plate 12 as a cam plate is accommodated in the crank chamber 5.
  • the swash plate 12 has a through hole formed in the center thereof, and the drive shaft 6 is disposed through the through hole.
  • the swash plate 12 is operatively connected to the lug plate 11 and the drive shaft 6 via a hinge mechanism 13 as a connection guide mechanism.
  • the hinge mechanism 13 has two support arms 14 (only one is shown) protruding from the rear surface of the lag plate 11, and two support arms 14 protruding from the front surface of the swash plate 12.
  • Guide bin 15 (only one is shown).
  • the swash plate 12 is synchronized with the lug plate 11 and the drive shaft 6 by the linkage between the support arm 14 and the guide bin 15 and the contact with the drive shaft 6 in the central through hole of the swash plate 12. It is rotatable and tiltable with respect to the drive shaft 6 with sliding movement in the axial direction of the drive shaft 6. Note that the swash plate 12 has a power weight section 12 a on the opposite side of the hinge mechanism 13 across the drive shaft 6.
  • An inclination reducing panel 16 is provided around the drive shaft 6 between the lag plate 11 and the swash plate 12.
  • the inclination decreasing panel 16 urges the swash plate 12 in a direction approaching the cylinder block 1 (the inclination decreasing direction).
  • a return panel 17 is provided around the drive shaft 6 between the restriction ring 18 fixed to the drive shaft 6 and the swash plate 12. In this return panel 17, the swash plate 12 is in the state of large inclination (indicated by the two-dot chain line). Sometimes the swash plate 12 is simply wound around the drive shaft 6 and does not exert any urging action on the swash plate or other members.
  • each cylinder bore la contains a single-headed piston 20 in a reciprocating manner.
  • Each cylinder pore 1a has a compression chamber 1 whose volume changes according to the reciprocating movement of the piston 20.
  • b is partitioned.
  • the front end of each biston 20 is moored to the outer periphery of the swash plate 12 via a pair of showers 19, and via this shower 19 each of the toner 20 is connected to the swash plate 12. It is operatively connected. Therefore, when the swash plate 12 rotates synchronously with the drive shaft 6, the rotational motion of the swash plate 12 is changed to the reciprocating linear motion of the piston 20 in the stroke corresponding to the tilt angle. Is converted.
  • a suction chamber 21 located in the central area and a discharge chamber 22 surrounding the suction chamber 21 are formed between the valve forming body 3 and the rear housing 4.
  • the valve forming body 3 is formed by stacking a suction valve forming plate, a port forming plate, a discharge valve forming plate, and a retainer forming plate.
  • the valve forming body 3 has a suction valve 24 for opening and closing the suction port 23 and the port 23, and a discharge valve for opening and closing the discharge port 25 and the port 25 corresponding to each cylinder bore 1a.
  • Valve 26 is formed.
  • the suction chamber 21 communicates with each cylinder bore 1 a via the suction port 23, and the cylinder pore 1 a communicates with the discharge chamber 22 via the discharge port 25.
  • the suction chamber 21 and the crank chamber 5 are connected by a bleed passage 27. Further, the discharge chamber 22 and the crank chamber 5 are connected by a communication path 28 via a unit 40 described later, and a control valve 30 is provided in the middle of the communication path 28. .
  • the control valve 30 includes a solenoid part 31 and a valve element 32 operatively connected to the solenoid part 31 via a rod.
  • Control (not shown)
  • a solenoid circuit 31 is driven by a current output from a drive circuit (not shown) based on a signal from a computer to change the position of the valve body 32 and adjust the opening of the communication passage 28. It has become.
  • the valve element 32 is arranged at a position that opens the communication path 28 when power is not supplied from the drive circuit, and adjusts the opening degree of the communication path 28 when power is supplied. I have.
  • the opening of the control valve 30 By adjusting the opening of the control valve 30, the balance between the amount of high-pressure gas introduced into the crankcase 5 through the communication passage 28 and the amount of gas discharged from the crankcase 5 through the bleed passage 27 is increased. It is controlled to determine the crank pressure Pc. In accordance with the change in the crank pressure P c, the difference between the crank pressure P c via the piston 20 and the internal pressure of the cylinder pore 1 a is changed, and as a result, the inclination angle of the swash plate 12 is changed. The stroke of the ton 20, that is, the discharge capacity (refrigerant circulation amount) is adjusted. In this case, the communication passage 28 and the control valve 30 function as a part of an air supply passage for introducing the refrigerant in the discharge chamber 22 into the crank chamber 5.
  • the rear housing 4 is provided with a suction port 21A serving as an inlet for introducing a refrigerant into the suction chamber 21. Further, the rear housing 4 is provided with a mounting port 22 A communicating with the discharge chamber 22, and a unit 40 having a discharge port 42 F described later is mounted on the mounting port 22 A. An external refrigerant circuit 50 is interposed between the suction port 21A and the discharge port 42F.
  • the unit 40 is a cylindrical case 42 with a substantially bottomed shape attached to the mounting opening 22A of the rear housing 4, and is housed in the case 42.
  • Check valve 41 is provided.
  • the check valve 41 includes a disc 44 press-fitted into the discharge port 42F, and a substantially bottomed cylindrical casing 43 having an open end face joined and fixed to the disc 44.
  • a valve chamber 43A is formed by covering the opening-side end face of the casing 43 with a disk 44.
  • a valve inlet 43B as a refrigerant inlet is formed at the bottom of the casing 43, and a valve outlet 44A as a refrigerant outlet is formed at the disc 44.
  • a valve body 45 is housed so as to be able to reciprocate between a valve inlet 43B and a valve outlet 44A. The valve body 45 is urged toward the valve inlet 43 B by a valve closing panel 46.
  • the urging force on the valve body 45 by the refrigerant pressure on the upstream side of the check valve 41 and the urging force on the valve body 45 by the refrigerant pressure on the downstream side of the check valve 41 are determined.
  • the opening and closing operation of the valve inlet 43B is performed by the balance between the biasing force and the biasing force by the valve closing panel 46, and the backflow of the refrigerant is prevented.
  • the check valve 41 allows the flow of the refrigerant. .
  • the opening side of the case 42 is covered with the disk 44 to define the separation chamber 42A.
  • the downstream side (opening side) of the disk 42 of the case 42 functions as a discharge port 42F as a refrigerant discharge port.
  • FIGS. 1, 2 and 4 for convenience, illustration of a mechanism for connecting and fixing the discharge port 42F and the flow pipe 22B is omitted.
  • the case 42 has an inlet 42B for introducing the refrigerant in the discharge chamber 22 into the separation chamber 42A.
  • the inlet 42B and the discharge chamber 22 are connected by an inlet passage 42C. In the inlet 42B, the refrigerant introduced into the separation chamber 42A swirls inside the separation chamber 42A.
  • case 42 it is formed along the circumferential direction of case 42. Since the casing 43 of the check valve 41 is disposed in the separation chamber 42A, the refrigerant introduced into the separation chamber 42A from the inlet 42B is actually a case 4. It turns in the gap between the inner peripheral surface of 2 and the outer peripheral surface of the casing 43. By this swirling, the lubricating oil mixed with the refrigerant is centrifuged and adheres to the inner peripheral surface of the case 42.
  • a tapered inclined recess 42D is provided at the bottom of the case 42, and the lubricating oil attached to the inner peripheral surface of the case 42 and drooping is provided at the bottom of the inclined recess 42D. It is easy to gather in the back.
  • a discharge passage 42E for discharging the lubricating oil out of the unit 40 is formed in the innermost portion of the inclined concave portion 42D. As shown in FIG. 1, the lubricating oil discharged out of the unit 40 through the discharge passage 42E is introduced into the crank chamber 5 as a low pressure region through the communication passage 28 and the control valve 30. It is supposed to be.
  • the case 42, the casing 43, and the disk 44 constitute an oil separator for separating mist-like lubricating oil mixed with the refrigerant.
  • the discharge passage 42 E, the communication passage 28 and the control valve 30 function as an oil supply passage for supplying the lubricating oil separated by the oil separator to the crank chamber 5.
  • the inlet passage 42C, the inlet 42B, the separation chamber 42A and the discharge passage 42E of the unit 40 supply the refrigerant in the discharge chamber 22 to the crank chamber 5 side. It functions as a part of the passage.
  • a discharge path connecting the discharge chamber 22 and the external refrigerant circuit 50 is constituted by the mounting port 22 A, the unit 40 and the flow pipe 22 B, and the suction port 21 A and the flow pipe 21 are formed.
  • B forms a suction path connecting the suction chamber 21 and the external refrigerant circuit 50.
  • the control computer issues a command signal to the drive circuit to increase the value of the current supplied to the solenoid unit 31. Due to a change in the current value from the drive circuit based on this signal, the solenoid portion 31 increases the urging force so that the valve body 32 further reduces the opening of the communication passage 28. As a result, the valve element 32 moves and the opening degree of the communication passage 28 decreases. As a result, the amount of high-pressure refrigerant gas supplied from the discharge chamber 22 to the crank chamber 5 via the communication path 28 decreases, the pressure in the crank chamber 5 decreases, and the inclination angle of the swash plate 12 increases. As a result, the discharge capacity of the compressor C increases. When the communication passage 28 is fully closed, the pressure in the crank chamber 5 drops significantly, the inclination angle of the swash plate 12 becomes maximum, and the discharge capacity (refrigerant circulation amount) of the compressor C becomes maximum. .
  • the mist mixed with the refrigerant together with the refrigerant Lubricating oil is introduced.
  • These refrigerant and lubricating oil circulate along the gap between the inner peripheral surface of the case 42 and the outer peripheral surface of the casing 43 of the check valve 41.
  • the lubricating oil is centrifuged, collected in the inclined recess 42D, and then introduced into the crank chamber 5 via the discharge passage 42E, the communication passage 28 and the control valve 30.
  • the lubricating oil introduced into the crankcase 5 lubricates mechanical components (bearings, hinge mechanisms, etc.) in the crankcase 5.
  • the refrigerant separated from the lubricating oil tries to enter the valve chamber 43A through the valve inlet 43B.
  • the refrigerant pushes up the valve body 45, passes through a gap formed between the bottom of the valve body 45 and the valve inlet 43B, enters the valve chamber 43A, and forms the groove 4 Pass 5 A to reach valve outlet 44 A.
  • the valve body 45 is in contact with the disk 44 by being pushed up by the refrigerant, the refrigerant is formed by the disk 44 and the notch 45B after passing through the groove 45A. It reaches the valve outlet 4 4 A through the gap.
  • the refrigerant that has reached the outside of the valve chamber 43A through the valve outlet 44A enters the external refrigerant circuit 50 through the circulation pipe 22B, and performs a heat exchange action.
  • the check valve 41 is provided between the discharge chamber 22 and the external refrigerant circuit 50, the backflow of the refrigerant from the external refrigerant circuit 50 to the discharge chamber 22 can be prevented. . That is, for example, when the compressor C is turned off, the power supply to the solenoid portion 31 of the control valve 30 is stopped, the abnormal passage 28 is fully opened, and the high-pressure refrigerant in the external refrigerant circuit 50 is discharged.
  • the crank pressure P c does not rise abnormally suddenly to the crank chamber 5 via the chamber 22, the unit 40 and the communication passage 28. Therefore, it is possible to prevent the slide movement of the drive shaft 6 and the trouble caused by the movement. This defect includes, for example, (a), (b) and (c) in the prior art.
  • a check valve 41 is provided to prevent abnormal increase of the crank pressure P c when power supply to the control valve 30 is stopped, so that accelerated deterioration of the rib seal 2A is suppressed and durability of the compressor C is reduced. Can be improved.
  • An oil separator is provided between the discharge chamber 22 and the external refrigerant circuit 50 to suppress the amount of lubricating oil discharged to the external refrigerant circuit 50 side, so that the heat of the refrigerant in the external refrigerant circuit 50 is reduced.
  • the exchange efficiency can be increased, and the lubrication efficiency in the compressor C can be increased.
  • the oil separator is arranged upstream of the check valve 41.
  • an oil supply passage for introducing the lubricating oil separated by the oil separator into the crank chamber 5 together with the oil separator is also arranged upstream of the check valve 41. That is, even if the downstream side of the check valve 41 has a higher pressure than the upstream side, the downstream side refrigerant does not flow backward to the upstream side through the oil supply passage. Therefore, the backflow of the refrigerant can be prevented without providing a means for opening and closing this passage in the oil supply passage.
  • the check valve 41 and the oil separator are integrated into the unit 40, the installation space for both can be reduced as a whole as compared with the case where both are provided separately. In addition, since the unit 40 is assembled to the rear housing 4, the assemblability and the maintainability are improved.
  • the check valve 41 is arranged in the case 42 to separate the lubricating oil on the outer peripheral side of the casing 43 and prevent the refrigerant from flowing back on the inner peripheral side. That is, the casing 43 is commonly used for both the lubricating oil separating function and the refrigerant backflow preventing function. Therefore, the number of parts can be reduced, and the cost can be reduced.
  • the valve body 45 is arranged so as to be able to reciprocate within the inner peripheral side of the bottomed cylindrical casing 43, and a groove 45A is formed on the outer periphery of the valve body 45, and the valve body is formed. Refrigerant from a valve inlet 43 B formed below 45 was passed through the groove 45 A to reach a valve outlet 44 A formed above the valve body 45. If the groove 45 A is not provided on the outer circumference of the valve body 45, the refrigerant cannot pass from below to above the valve body 45, so that the refrigerant flows inside the casing 43. It is necessary to provide a hole on the peripheral surface of the casing 43 to escape from the outside.
  • an external casing for housing the casing 43 is further provided so that the refrigerant from the inlet 42B does not enter the casing 43 through the hole, and the outer periphery of the outer casing is provided. It is necessary to make the refrigerant and lubricating oil swirl.
  • the groove 45A is formed in the valve body 45 so that the refrigerant can pass from below to above the valve body 45, thereby reducing the number of parts and reducing the cost. It is possible to achieve.
  • the disk 44 is formed as the separation chamber 42A and is commonly used as the member forming the valve chamber 43A, so that the cost can be reduced by reducing the number of parts.
  • a part of an air supply passage for supplying the refrigerant in the discharge chamber 22 to the crank chamber 5 is an oil supply passage for supplying lubricating oil separated by an oil separator to the crank chamber 5,
  • a control valve 30 for adjusting the opening degree of the passage was provided in the middle of the passage (oil supply passage).
  • the compressor C of the second embodiment is obtained by changing the configuration of the unit 40 in the first embodiment. It has the same configuration as the compressor C of the embodiment. Therefore, the same components as those in the first embodiment are denoted by the same reference numerals in the drawings, and duplicate description will be omitted.
  • the unit 70 is attached to the mounting port 22A. As shown in FIGS. 5 and 6, the unit 70 includes a check valve 71 and a substantially bottomed cylindrical unit unit 72 that houses the check valve 71.
  • the check valve 71 includes a substantially cylindrical casing 73 and a disk 74.
  • the casing 73 is provided with an entry-side cylindrical portion 73A as a cylindrical portion formed to have a smaller diameter than the upper portion, from the middle to the lower part in the axial direction of the casing 73. ing.
  • a valve chamber 73B is formed in a portion of the casing 73 not having the small diameter (above the inlet cylindrical portion 73A) by covering the upper end portion of the casing 73 with a disk 74. I have.
  • the casing 73 has a valve outlet 73C communicating the valve chamber 73B with the outer peripheral side of the casing 73.
  • a step 73D is formed in a portion of the casing 73 between the valve chamber 73B and the inlet cylindrical portion 73A.
  • a communication hole 74A is formed in the disk 74 so that the outside and the inside of the valve chamber 73B can communicate with each other.
  • a valve body 75 is housed in the valve chamber 73B so as to be able to reciprocate in the axial direction of the casing 73. The valve body 75 is urged toward the inlet cylindrical portion 73A by the valve closing panel 76.
  • the valve body 7.5 has a bottomed cylindrical shape. When the valve body 75 is pressed against the stepped portion 73D by the valve closing panel 76, it closes the passage between the valve chamber 73B and the inlet cylindrical portion 73A. (See Figure 6).
  • the urging force to the valve element 75 due to the refrigerant pressure on the upstream side of the check valve 71 and the check valve 7 Due to the balance between the urging force of the valve body 75 due to the refrigerant pressure on the downstream side of 1 and the urging force of the valve closing panel 76, the downstream side (external refrigerant The backflow of the refrigerant from the circuit 50 side) to the upstream side (discharge chamber 22 side) is regulated, and the flow starts.
  • the unit case 72 has a separation chamber 72A formed therein, and a cylindrical projecting wall 72B extends above the separation chamber 72A.
  • An insertion hole 72C is formed above the separation chamber 72A, and a check valve 71 is mounted in the insertion hole 72C.
  • the opening at the upper end of the protruding wall 72B functions as a discharge port 72H for discharging the refrigerant. 5 and 6, a mechanism for connecting and fixing the discharge port 72H and the flow pipe 22B is omitted for convenience.
  • the inlet side cylindrical portion 73 A of the check valve 71 is press-fitted and fixed in the inlet hole 72 C, and is arranged so that the lower end opening of the inlet side cylindrical portion 73 A reaches near the bottom of the separation chamber 72 A.
  • an inlet 72D for introducing the refrigerant in the discharge chamber 22 into the separation chamber 72A is formed in the unit case 72.
  • the inlet 72D and the discharge chamber 22 are connected by an inlet passage 72E.
  • the inlet 72D is formed along the circumferential direction of the unit case 72 so that the refrigerant introduced into the separation chamber 72A swirls inside the separation chamber 72A.
  • the coolant introduced into the separation chamber 72A from the inlet 72D is actually supplied to the separation chamber 72A. Swivel the gap between the peripheral surface of 2 A and the outer peripheral surface of the entry cylindrical part 73 ⁇ A. By this swirling, the lubricating oil mixed with the refrigerant is centrifugally separated and adheres to the peripheral surface of the separation chamber 72A.
  • an inclined recess 72 F is provided at the bottom of the separation chamber 72 A, and the lubricating oil attached to the peripheral surface of the separation chamber 72 A and drooping is formed by the inclined recess 72 F. It is easy to gather at the innermost part of the building.
  • a discharge passage 72 G for discharging the lubricating oil out of the unit 70 is formed in the innermost portion of the inclined recess 72 F, and the lubricating oil is discharged through the discharge passage 72 G and the communication passage. 28 and the control valve 30 to the crankcase 5 as a low pressure area. Is to be entered.
  • the lower part of the unit case 72 and the inlet cylindrical part 73 A constitute an oil separator for separating mist-like lubricating oil mixed with the refrigerant.
  • the discharge passage 72 G, the communication passage 28 and the control valve 30 function as an oil supply passage for supplying the lubricating oil separated from the oil separator to the crank chamber 5.
  • the inlet passage 72 E, inlet 72 D, separation chamber 72 A, and discharge passage 72 G of the unit 70 serve as an air supply passage for supplying the refrigerant in the discharge chamber 22 to the crank chamber 5 side. Functioning as a part.
  • a discharge path for connecting the discharge chamber 22 and the external refrigerant circuit 50 is formed by the mounting port 22A, the unit 70, and the flow pipe 22B from the cylinder pore 1a to the discharge chamber 22.
  • the discharged refrigerant is introduced into the separation chamber 72A via the introduction passage 72E and the introduction port 72D.
  • the mixture of the refrigerant and the lubricating oil swirls in the gap between the outer peripheral surface of the separation chamber 72A and the outer peripheral surface of the inlet cylindrical portion 73A of the check valve 71. Due to this swirling, the lubricating oil is centrifuged, drawn into the discharge passage 72G by the inclined recess 72F, and introduced into the crank chamber 5 via the communication passage 28 and the control valve 30.
  • the refrigerant separated from the lubricating oil tries to enter the valve chamber 73B via the inner peripheral side of the inlet cylindrical portion 73A.
  • the refrigerant pushes up the valve body 75, passes through a gap formed between the bottom of the valve body 75 and the stepped portion 73D, enters the valve chamber 73B, and the valve outlet 7 After passing through 3C and reaching the outside of the valve chamber 73B, it enters the external refrigerant circuit 50 via the circulation pipe 22B to perform a heat exchange action.
  • Valve urging force due to pressure and valve closing panel 4 When it becomes smaller than the sum of the biasing force by 6, the valve body 75 shuts off the space between the valve chamber 73B and the inlet cylindrical portion 73A. That is, the check valve 71 prevents the backflow of the refrigerant from the downstream side (the external refrigerant circuit 50 side) to the upstream side (the discharge chamber 22 side).
  • Embodiments are not limited to the above, and may be, for example, in the following modes.
  • the unit 40 (or 70) may be installed so as to fit inside the housing 4 instead of protruding toward the outside of the housing 4.
  • the unit 40 (or 70) may be provided in the discharge chamber 22. That is, the unit 40 (or 70) may be assembled to the rear housing 4 before joining the rear housing 4 to the valve forming body 3 side so that the housing 40 cannot be attached or detached after the housing is completed. Conversely, the rear housing 4 may be assembled with the cylinder hook 1, the front housing 2, and the valve body 3 to form a housing of the compressor C, and then retrofitted from outside the housing. When the retrofitting is possible, the maintainability is improved.
  • the lubricating oil separated from the refrigerant may be supplied to the suction chamber 21, the suction inlet 21 A or the circulation pipe 21 B as a low-pressure region.
  • the upstream portion of the communication path 28 may be connected to the discharge chamber 22.
  • Inhalation chamber 2 1 The lubricating oil supplied to the suction port 21A or the distribution pipe 21B is sucked into the cylinder bore 1a together with the refrigerant by the reciprocating motion of the biston 20 to lubricate the inside of the cylinder pore 1a. Then, a part of the lubricating oil leaks to the crank chamber 5 side through a gap between the cylinder bore 1a and the biston 20 to lubricate a sliding portion of a mechanism in the crank chamber 5.
  • the lubricating oil separated from the refrigerant may be directly supplied to the crankcase 5 without passing through the control valve 30.
  • the amount of lubricating oil for lubricating the sliding portion of the mechanism in the crank chamber 5 increases, and the lubricating efficiency improves, as compared with the case where oil is supplied via the control valve 30.
  • the oil supply passage and the air supply passage may not be shared and may be provided separately.
  • the inclined recess 42D (or 72F) may not be provided.
  • the case 42 (or the unit case 72) is made separate from the rear housing 4, but it may be integrated. That is, the case 42 (or the unit case 72) may be formed integrally with the rear housing 4. Even in this case, if the check valve 41 (or 71) can be assembled into the case 42 (or the unit case 72) from the outside of the rear housing 4, assemblability and maintenance can be achieved. Can be prevented from deteriorating.
  • the check valve 71 and the oil separator may be provided separately in the unit case 72 without using common parts.
  • the inlet cylindrical portion 73A is separated from the casing 73, and the inlet cylindrical portion 73A is fixed to the insertion hole 72C separately from the check valve 71.
  • the hinge mechanism 13 includes a first arm provided on the swash plate 12, a second arm provided on the lug plate 11, a guide hole provided on one of the first and second arms.
  • the vehicle may further include a mounting hole provided in the other arm, and a pin penetrating the mounting hole and having a protruding portion inserted into the guide hole.
  • the control valve 30 may not be an external control type controlled by an external device such as the control computer or the drive circuit, but may be an internal control type that performs completely autonomous control.
  • the compressor C may be a fixed capacity type in which the stroke of the piston 20 cannot be changed.
  • the oil separator may be provided downstream of the check valve 41. In that case, it is desirable to provide an opening / closing means in the oil supply passage.
  • the check valve and the oil separator may be separate units. In this case, since each unit is separate, the degree of freedom of arrangement of each unit increases.
  • the check valve includes a substantially cylindrical casing and a valve body having a substantially circular cross section, and the valve body is housed in the casing so as to reciprocate in the axial direction of the casing, and is provided on one of upper and lower sides of the casing.
  • a coolant inlet is provided on the other side, and a coolant outlet is provided on the other side.
  • a groove extending in an axial direction of the valve body is formed on an outer periphery of the valve body, and a coolant that has entered the casing from the coolant inlet through the groove has the coolant outlet. May be reached.

Abstract

Un logement contient un chambre de distribution (22) traversée par un réfrigérant provenant d'une chambre de compression (1b) et une chambre d'aspiration (21) traversée par le réfrigérant à aspirer dans ladite chambre de compression (1b). La chambre de distribution (22) est reliée à un circuit de refroidissement (50) extérieur au moyen d'un chemin de distribution, et la chambre d'aspiration (21) est également reliée au circuit de refroidissement (50) extérieur au moyen d'un chemin d'aspiration. La chambre de distribution (22) ou le chemin de distribution est doté d'un clapet de non-retour destiné à empêcher le réfrigérant de s'écouler du circuit de refroidissement extérieur dans la chambre de distribution (22), et d'un séparateur d'huile destiné à séparer le réfrigérant de l'huile de graissage en pulvérisation. L'huile de graissage ainsi séparée est ensuite introduite dans une chambre de vilebrequin (5) par l'intermédiaire d'un passage de communication (28). De ce fait, il est possible d'empêcher à la fois le réfrigérant de s'écouler du circuit de refroidissement (50) extérieur dans la chambre de distribution (22) et l'huile de graissage de s'écouler dans le circuit de refroidissement (50) extérieur.
PCT/JP2001/011598 2000-06-27 2001-12-27 Compresseur WO2003060325A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP2000192341A JP3864673B2 (ja) 2000-06-27 2000-06-27 圧縮機
US09/886,170 US6511297B2 (en) 2000-06-27 2001-06-21 Compressor having check valve and oil separator unit
EP01115264A EP1167762B1 (fr) 2000-06-27 2001-06-23 Compresseur à plateau en biais avec mécanisme de lubrification
PCT/JP2001/011598 WO2003060325A1 (fr) 2000-06-27 2001-12-27 Compresseur
CN01809988.2A CN1250873C (zh) 2001-12-27 2001-12-27 压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000192341A JP3864673B2 (ja) 2000-06-27 2000-06-27 圧縮機
PCT/JP2001/011598 WO2003060325A1 (fr) 2000-06-27 2001-12-27 Compresseur

Publications (1)

Publication Number Publication Date
WO2003060325A1 true WO2003060325A1 (fr) 2003-07-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2001/011598 WO2003060325A1 (fr) 2000-06-27 2001-12-27 Compresseur

Country Status (1)

Country Link
WO (1) WO2003060325A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009006281A (ja) * 2007-06-28 2009-01-15 Sanden Corp 遠心分離装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0835485A (ja) * 1994-07-25 1996-02-06 Toyota Autom Loom Works Ltd 圧縮機における油回収構造
JPH09177671A (ja) * 1995-10-26 1997-07-11 Toyota Autom Loom Works Ltd カムプレート式可変容量圧縮機
US5823294A (en) * 1996-06-06 1998-10-20 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Lubrication mechanism in compressor
JP2000027756A (ja) * 1998-07-09 2000-01-25 Toyota Autom Loom Works Ltd 圧縮機
JP2001153042A (ja) * 1999-11-25 2001-06-05 Toyota Autom Loom Works Ltd 空調装置および容量可変型圧縮機の制御弁

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0835485A (ja) * 1994-07-25 1996-02-06 Toyota Autom Loom Works Ltd 圧縮機における油回収構造
JPH09177671A (ja) * 1995-10-26 1997-07-11 Toyota Autom Loom Works Ltd カムプレート式可変容量圧縮機
US5823294A (en) * 1996-06-06 1998-10-20 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Lubrication mechanism in compressor
JP2000027756A (ja) * 1998-07-09 2000-01-25 Toyota Autom Loom Works Ltd 圧縮機
JP2001153042A (ja) * 1999-11-25 2001-06-05 Toyota Autom Loom Works Ltd 空調装置および容量可変型圧縮機の制御弁

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009006281A (ja) * 2007-06-28 2009-01-15 Sanden Corp 遠心分離装置

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