JP2009209910A - Swash plate compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a swash plate compressor capable of exhibiting both superior sliding characteristics when a drive shaft is rotated at high speeds and high refrigerating capacity when the drive shaft is rotated at low speeds. <P>SOLUTION: This swash plate compressor comprises oil separating means 1c, 43, 51, 45, 69, 71, 77, 75, 81, 82 which act on the refrigerating gas in relief passages 37, 39, allows the refrigerating gas to flow into a suction chamber 11 by the increase in the rotational speed of a drive shaft 7 without separating a lubricating oil, allows the refrigerating gas from which the lubricating oil is separated to flow into the suction chamber 11 by the reduction in the rotational speed of a drive shaft 7, and recirculates the separated lubricating oil into the crankcase 15. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a swash plate compressor.

  Patent Document 1 discloses a conventional swash plate compressor. In the swash plate compressor, a housing is constituted by a front housing, a cylinder block, and a rear housing, and a plurality of cylinder bores, a suction chamber, a discharge chamber, and a crank chamber are formed by the housing. One end of the front housing is exposed from the front housing, and a drive shaft facing the crank chamber is rotatably supported. The cylinder block is formed with a storage chamber in which the other end of the drive shaft is located, and this storage chamber communicates with the suction chamber through a throttle hole of a valve unit provided between the cylinder block and the rear housing. .

  In the crank chamber, the swash plate is supported by the drive shaft so that the tilt angle can be varied. A piston is housed in each cylinder bore so as to be able to reciprocate. A pair of front and rear shoes is provided between the swash plate and each piston, and the swing motion of the swash plate is converted into the reciprocating motion of each piston by each pair of shoes. The discharge chamber and the crank chamber communicate with each other through an air supply passage, and a capacity control valve for adjusting the pressure in the crank chamber is provided on the air supply passage.

  Further, in this swash plate type compressor, a relief passage that allows the crank chamber to communicate with the suction chamber is formed in the drive shaft. This escape passage has a first diameter hole formed extending in the radial direction and an outflow hole formed extending in the axial direction and communicating the first diameter hole to the suction chamber.

  Further, in this swash plate type compressor, an opening / closing valve is provided on the drive shaft. This on-off valve is provided in the storage chamber, and reduces the opening degree of the escape passage by increasing the rotational speed of the drive shaft, and increases the opening degree of the escape passage by decreasing the rotational speed of the drive shaft.

  This swash plate type compressor constitutes a refrigeration circuit together with a condenser, an expansion valve and an evaporator, and this refrigeration circuit can be used for an air conditioner of a vehicle. A refrigerant gas mixed with lubricating oil is enclosed in the refrigeration circuit. In this swash plate type compressor, the capacity control valve adjusts the pressure in the crank chamber based on the pressure in the suction chamber and the flow rate of the refrigerant gas, and changes the angle of the swash plate with respect to the drive shaft to reduce the discharge capacity. It has changed.

  In this swash plate compressor, the opening of the escape passage is reduced by increasing the rotational speed of the drive shaft, for example, while the vehicle is traveling at high speed, so that the compressor is particularly in a high rotation state with a large discharge capacity. At times, it is possible to gradually increase the pressure in the crank chamber to reduce the discharge capacity, thereby reducing the compression load. Conversely, while the vehicle is traveling at a low speed, the swash plate compressor increases the opening of the escape passage due to a decrease in the rotational speed of the drive shaft, so that the pressure in the crank chamber depends on the required cooling capacity. Can be gradually reduced to increase the discharge capacity and improve the refrigerating capacity.

Japanese Patent Laid-Open No. 10-54350

  By the way, in the swash plate type compressor, when the drive shaft is rotated at a high speed, it is required to improve the sliding characteristics at sliding portions such as between the cylinder bore and the piston, and between the swash plate and each shoe. Further, when the drive shaft is rotated at a low speed, it is required to reduce the amount of lubricating oil in the refrigerant gas discharged to the refrigeration circuit outside the swash plate compressor and to exhibit a high refrigeration capacity.

  The present invention has been made in view of the above-described conventional situation, and exhibits excellent sliding characteristics when the drive shaft is rotated at a high speed, and a high refrigeration capacity when the drive shaft is rotated at a low speed. It is an issue to be solved to provide a swash plate compressor capable of realizing the above.

The swash plate compressor according to the present invention includes a housing having a cylinder bore, a suction chamber, a discharge chamber, and a crank chamber, a drive shaft that is rotatably supported by the housing and faces the crank chamber, and the drive shaft in the crank chamber. A swash plate supported by the cylinder, a piston accommodated in the cylinder bore so as to be reciprocally movable, and provided between the swash plate and the piston, and the swinging motion of the swash plate is converted into a reciprocating motion of the piston. A motion conversion mechanism that performs the above-described movement and a relief passage that allows the crank chamber to communicate with the suction chamber,
Acts on the refrigerant gas in the escape passage, increases the rotational speed of the drive shaft, allows the refrigerant gas to communicate with the suction chamber without separating the lubricating oil, and reduces the rotational speed of the drive shaft to reduce lubrication. An oil separating means is provided for allowing the refrigerant gas from which the oil has been separated to communicate with the suction chamber and for allowing the separated lubricating oil to flow back to the crank chamber.

  In the swash plate compressor of the present invention, the oil separation means acts on the refrigerant gas in the escape passage. When the drive shaft is rotated at a high speed, the oil separating means causes the refrigerant gas to communicate with the suction chamber without separating the lubricating oil. For this reason, the refrigerant gas containing the lubricating oil in the crank chamber moves to the suction chamber. For this reason, the amount of lubricating oil in the crank chamber becomes appropriate, the swash plate or the like does not agitate the lubricating oil so much, the lubricating oil hardly generates heat due to shear, and the viscosity of the lubricating oil does not easily decrease. For this reason, lubrication of a sliding part is performed suitably. Further, the refrigerant gas sucked from the suction chamber contains a large amount of lubricating oil, and the sliding portion between the cylinder bore and the piston is also preferably lubricated. At this time, the amount of lubricating oil in the refrigerant gas discharged to the refrigeration circuit outside the swash plate compressor increases, but there is no problem in the refrigeration capacity because the piston reciprocates at high speed.

  When the drive shaft is rotated at a low speed, the oil separating means causes the refrigerant gas separated from the lubricating oil to communicate with the suction chamber and also causes the separated lubricating oil to recirculate to the crank chamber. For this reason, the amount of lubricating oil in the refrigerant gas discharged to the refrigeration circuit outside the swash plate compressor is reduced, and a high refrigeration capacity is exhibited. At this time, although the amount of lubricating oil in the crank chamber increases, the swash plate or the like merely stirs the lubricating oil at a low speed, the viscosity of the lubricating oil does not decrease so much, and the temperature of the lubricating oil hardly increases. For this reason, the lubrication of the sliding part is still preferably performed.

  Therefore, according to the swash plate compressor of the present invention, excellent sliding characteristics when the drive shaft is rotated at high speed and high refrigeration capacity when the drive shaft is rotated at low speed are realized. Is possible.

  The swash plate compressor of the present invention may be a fixed capacity type in which the inclination angle of the swash plate is not displaced, or may be a variable capacity type in which the inclination angle of the swash plate is displaced.

  In the swash plate compressor of the present invention, the escape passage only needs to communicate with the crank chamber to the suction chamber. In addition to the passage directly connecting the crank chamber to the suction chamber, the suction passage communicating with the suction chamber, etc. A passage that indirectly communicates the crank chamber with the suction chamber may be used.

  The escape passage may have a first passage that communicates with a region in the crank chamber where there is a lot of lubricating oil. The oil separating means preferably acts on the refrigerant gas in the first passage (claim 2).

  According to the test results of the inventors, the crank chamber of the swash plate compressor has a region with a large amount of lubricating oil and a region with a small amount of lubricating oil. For example, the region where the amount of lubricating oil in the crank chamber is high is the outer peripheral region of the crank chamber, and the region where the lubricating oil is low in the crank chamber is the inner peripheral region of the crank chamber, that is, a portion away from the wall surface of the crank chamber. This is because the swash plate or the like rotates together with the drive shaft in the crank chamber, and the lubricating oil is pushed to the outer peripheral area of the crank chamber by centrifugal force. Further, the bottom side of the crank chamber and the surface around the cylinder bore in the crank chamber are regions with a lot of lubricating oil. On the other hand, the upper side of the crank chamber is a region where there is little lubricating oil. If the oil separation means acts on the refrigerant gas in the first passage communicating with the region where the amount of lubricating oil in the crank chamber is large, the amount of lubricating oil that moves to the suction chamber increases at the time of high rotation and is returned to the crank chamber at the time of low rotation. Lubricating oil increases and the effects of the present invention are further increased.

  The first passage communicates with one of the regions where the lubricating oil is high. The region where the lubricating oil is high and the region where the lubricating oil is low are determined by relative comparison with each other.

The oil separating means is formed in the housing, communicates with the suction chamber through the throttle hole, and a storage chamber in which the other end of the drive shaft is located,
By dividing the storage chamber into a first chamber that is provided at the other end of the drive shaft and does not communicate with the throttle hole and a second chamber that communicates with the throttle hole, and by moving the refrigerant gas from the first chamber to the second chamber An oil separator for storing lubricating oil separated from the refrigerant gas in the first chamber;
A return passage for communicating the first chamber with the crank chamber;
An open / close valve that communicates the first passage with the second chamber by increasing the rotational speed of the drive shaft, and that does not communicate the first passage with the second chamber by decreasing the rotational speed of the drive shaft;
The escape passage may have a discharge hole for communicating the first passage and the first chamber (claim 3).

  In this case, when the drive shaft is rotated at a high speed, the on-off valve directly connects the first passage to the second chamber, so that the refrigerant gas in the first passage is separated from the oil without separating the lubricating oil. It moves from the throttle hole to the suction chamber through the second chamber of the vessel.

  Further, when the drive shaft is rotated at a low speed, the on-off valve does not allow the first passage to communicate with the second chamber. For this reason, the refrigerant gas in the first passage first reaches the first chamber of the oil separator via the discharge hole, and moves from the first chamber to the second chamber, whereby the lubricating oil is separated. Then, the refrigerant gas from which the lubricating oil has been separated moves from the second chamber to the suction chamber through the throttle hole. Further, the lubricating oil separated from the refrigerant gas is stored in the first chamber and returned to the crank chamber by the return passage.

  As long as the on-off valve is displaced according to the number of rotations, various types can be employed. For example, an on-off valve using a solenoid that detects the rotational speed by a rotational speed sensor or detects the centrifugal force by an acceleration sensor and electromagnetically displaces based on these signals can be employed. Further, a mechanical on-off valve in which the mass body is displaced by the centrifugal force and the valve body is actuated can be employed.

  It is preferable that the return passage communicates with an area where the lubricating oil in the crank chamber is low.

  In this case, the lubricating oil separated from the refrigerant gas easily returns to the crank chamber through the return passage.

  The return passage preferably communicates the lower portion of the first chamber with the crank chamber when mounted on the vehicle.

  In this case, the lubricating oil stored in the first chamber easily returns to the crank chamber via the return passage. It is more preferable that the return passage is inclined downward from the storage chamber to the crank chamber when mounted on the vehicle. Thereby, the lubricating oil in the first chamber can be further returned to the crank chamber.

  It is preferable that the on-off valve is displaced by centrifugal force.

  In this case, the on-off valve can be displaced in the direction of increasing the opening degree of the first passage by increasing the centrifugal force, and can be displaced in the direction of decreasing the opening degree of the first passage by decreasing the centrifugal force.

  The on-off valve can be provided on the drive shaft or on the oil separator. If the oil separator is provided with an opening / closing valve, the oil separator and the opening / closing valve are integrated, and the number of parts can be reduced.

  In the swash plate compressor of the present invention, the swash plate can be supported so that the tilt angle can be varied. Further, a lug plate that receives a compression reaction force can be fixed to the drive shaft so as to be integrally rotatable. Furthermore, an oil guide path extending from the outer peripheral area of the crank chamber to the space between the housing and the lug plate can be formed in the housing. The first passage preferably communicates with the oil guide path (claim 7).

  According to the test results of the inventors, in the swash plate compressor, the outer peripheral area of the crank chamber is an area where there is a lot of lubricating oil, so that the lubricating oil can be easily guided to the first passage through the oil guide path. Is possible.

  A shaft seal device for sealing the drive shaft exposed from the housing may be provided between the housing and the drive shaft. The first passage preferably communicates with the oil guide path via the shaft seal device.

  In this case, a large amount of lubricating oil can be supplied to the shaft seal device to improve the durability of the rubber material of the shaft seal device.

  Embodiments 1 to 4 embodying the present invention will be described below with reference to the drawings.

  The swash plate compressor of the first embodiment is of a variable capacity type used for air conditioning of vehicles. As shown in FIG. 1, the compressor includes a cylinder block 1, a front housing 3, and a rear housing 5. The cylinder block 1 has a cylinder bore 1 a extending in parallel with the axis of the drive shaft 7. A plurality are provided. In FIG. 1, the left side is the front of the compressor and the right side is the rear of the compressor.

  The rear housing 5 is formed with a suction chamber 11 and a discharge chamber 13 that communicate with each cylinder bore 1a via a valve unit 9. A crank chamber 15 is formed by the front housing 3 and the cylinder block 1, and shaft holes 3 a and 1 b are formed in the front housing 3 and the cylinder block 1. A shaft sealing device 17 is provided in the shaft hole 3a. A rubber material is used for the shaft seal device 17. A plain bearing 19 is provided in the shaft hole 1b. A storage chamber 1 c communicating with the shaft hole 1 b is formed at the center side of the rear end of the cylinder block 1, and the storage chamber 1 c faces the valve unit 9.

  The drive shaft 7 is rotatably supported by the front housing 3 and the cylinder block 1 with one end exposed from the front housing 3 and the center facing the crank chamber 15. A pulley or an electromagnetic clutch (not shown) is connected to the drive shaft 7, and the drive shaft 7 is driven to rotate by a drive source such as an engine via a belt wound around the pulley or the electromagnetic clutch. Further, pistons 21 are accommodated in the respective cylinder bores 1a so as to be able to reciprocate. Each piston 21 forms a compression chamber in the cylinder bore 1a.

  In the crank chamber 15, a lug plate 23 that receives a compression reaction force is fixed to the drive shaft 7, and a thrust bearing 25 and a plain bearing 27 are provided between the lug plate 23 and the front housing 3. Further, a swash plate 29 that can change an inclination angle formed with a virtual plane perpendicular to the axis of the drive shaft 7 is inserted into the drive shaft 7. The lug plate 23 is formed with a hinge portion 23a toward the swash plate 29. The swash plate 29 is provided with a hinge portion 29a toward the lug plate 23, and the hinge mechanism 23a, 29a constitutes a link mechanism 31. Yes. A pressing spring 33 is provided between the lug plate 23 and the swash plate 29 to urge the two in a direction away from each other.

  Further, a pair of shoes 35 are provided between the swash plate 29 and each piston 21 in the front-rear direction. The front shoe 35 is provided between the front surface of the swash plate 29 and the front seat surface of the piston 21, and the rear shoe 35 is provided between the rear surface of the swash plate 29 and the rear seat surface of the piston 21. It has been. Each shoe 35 has a substantially hemispherical shape. Each shoe 35 is a motion conversion mechanism.

  The drive shaft 7 has a first hole 37 extending in the radial direction, an outflow hole 39 communicating with the first hole 37 in the axial direction and extending coaxially with the shaft center to the rear end of the drive shaft 7, and the rear of the drive shaft 7. A discharge hole 41 extending in the radial direction and communicating with the outflow hole 39 is formed.

  The first hole 37 is formed between the lug plate 23 and the front housing 3 by the diameter of the drive shaft 7 from the axial center to the outer periphery of the drive shaft 7. The front housing 3 is formed with an oil guide groove 3 b that extends from the outer peripheral region of the crank chamber 15 to between the front housing 3 and the lug plate 23 and faces the thrust bearing 25. The front housing 3 is formed with an oil guide hole 3 c that communicates with the oil guide groove 3 b and faces the plain bearing 27 and the shaft seal device 17. The oil guide hole 3c communicates with the first hole 37 by facing the shaft seal device 17 through the shaft hole 3a. The oil guide groove 3b and the oil guide hole 3c are oil guide paths.

  As shown in FIGS. 2 and 3, the rear end of the drive shaft 7 protrudes into the storage chamber 1c, and the discharge hole 41 communicates with the storage chamber 1c. The discharge hole 41 is also formed by the diameter of the drive shaft 7 from the axis of the drive shaft 7 to the outer periphery. An oil separator 43 is provided at the rear end of the drive shaft 7, and an opening / closing valve 45 is inserted at the rear end of the outflow hole 39.

  The oil separator 43 includes a cylindrical portion 43a that is fitted to the drive shaft 7, a tapered portion 43b that is integrated with the cylindrical portion 43a, and has a diameter increased from the rear end of the cylindrical portion 43a toward the valve unit 9, and a tapered portion. It consists of a flange portion 43c formed in a flange shape from the rear end of the portion 43b. The flange portion 43 c faces the valve unit 9. The storage chamber 1c is divided by the oil separator 43 into a first chamber 47 that is outside the cylindrical portion 43a, the tapered portion 43b, and the flange portion 43c, and a second chamber that is inside the cylindrical portion 43a, the tapered portion 43b, and the flange portion 43c. It is divided into 49.

  The on-off valve 45 has a cap shape in which a portion inserted into the outflow hole 39 has a cylindrical shape and a rear end slightly bulges. As shown in FIG. 4, the rear end of the on-off valve 45 is divided into four parts so that they can be separated from each other against their own elastic force. A mass body 45a is fixed in the rear end of the on-off valve 45 as shown in FIGS.

  The valve unit 9 is provided with a throttle hole 9 a that communicates the second chamber 49 of the storage chamber 1 c with the suction chamber 11. Further, the cylinder block 1 is formed with a return passage 51 that communicates the first chamber 47 of the storage chamber 1c and the inner peripheral region of the crank chamber 15, that is, a portion close to the drive shaft 7. The return passage 51 communicates the lower part of the first chamber 1c with the crank chamber 15 when mounted on the vehicle. The oil guide groove 3b, the oil guide hole 3c, the first hole 37, the outflow hole 39, the discharge hole 41, the first chamber 47, the second chamber 49, and the throttle hole 9a are escape passages. And the oil guide groove 3b, the oil guide hole 3c, the 1st hole 37, and the outflow hole 39 are the 1st channel | paths. The storage chamber 1c, the oil separator 43, the return passage 51, and the on-off valve 45 are oil separation means.

  Further, as shown in FIG. 1, a capacity control valve 53 is accommodated in the rear housing 5. The capacity control valve 53 communicates with the suction chamber 11 through the detection passage 55 and communicates the discharge chamber 13 with the crank chamber 15 through the air supply passage 57. The capacity control valve 53 detects the pressure in the suction chamber 11 to change the opening of the air supply passage 57 and change the discharge capacity of the compressor.

  A pipe 59 is connected to the discharge chamber 13, and the pipe 59 is connected to the suction chamber 11 through a check valve 61, a condenser 63, an expansion valve 65 and an evaporator 67. The compressor, the check valve 61, the condenser 63, the expansion valve 65, the evaporator 67, and the pipe 59 constitute a refrigeration circuit. A refrigerant gas mixed with lubricating oil is enclosed in the refrigeration circuit.

  In the compressor configured as described above, the capacity control valve 53 adjusts the pressure in the crank chamber 15 based on the pressure in the suction chamber 11 and the flow rate of the refrigerant gas, and changes the angle of the swash plate 29 with respect to the drive shaft 7. Thus, the discharge capacity is changed.

  Further, in this compressor, when the drive shaft 7 is rotated at a high speed, for example, while the vehicle is traveling at a high speed, as shown in FIG. The opening of the outflow hole 39 is increased. For this reason, the outflow hole 39 communicates with the second chamber 49, and the refrigerant gas in the outflow hole 39 passes through the second chamber 49 of the oil separator 43 from the throttle hole 9a without being separated from the lubricating oil. Move to 11. At this time, the opening sectional area of the on-off valve 45 is larger than at least one of the opening sectional area of the discharge hole 41 and the opening sectional area of the passage formed by the gap between the flange 43c and the valve unit 9. Is set to

  The outer peripheral area of the crank chamber 15 is an area where there is a lot of lubricating oil, and the lubricating oil is guided from there to the first hole 37 by the oil guide groove 3b and the oil guide hole 3c. Thus, the refrigerant gas containing a large amount of lubricating oil in the crank chamber 15 moves to the suction chamber 11. For this reason, the amount of lubricating oil in the crank chamber 15 becomes appropriate, the swash plate 29 and the like do not agitate the lubricating oil so much, the lubricating oil hardly generates heat due to shear, and the viscosity of the lubricating oil does not easily decrease. For this reason, lubrication of a sliding part is performed suitably. Further, the refrigerant gas sucked from the suction chamber 11 contains a large amount of lubricating oil, and the lubrication of the sliding portion between the cylinder bore 1a and the piston 21 is also suitably performed.

  At this time, the amount of lubricating oil in the refrigerant gas discharged to the refrigeration circuit outside the swash plate compressor increases, but the piston 21 reciprocates at a high speed, so that there is no problem in the refrigeration capacity.

  During this time, since the lubricating oil is guided to the first hole 37 through the shaft sealing device 17, a large amount of lubricating oil is supplied to the shaft sealing device 17 and the durability of the rubber material of the shaft sealing device 17 is improved.

  When the drive shaft 7 is rotated at a low speed, such as when the vehicle is traveling at a low speed, the open / close valve 45 is bent by its own elastic force with a small centrifugal force and closes the rear end as shown in FIG. The opening degree of the outflow hole 39 is reduced. Then, the outflow hole 39 does not communicate with the second chamber 49, and the refrigerant gas in the outflow hole 39 reaches the first chamber 47 of the oil separator 43 through the discharge hole 41 and passes from the first chamber 47 to the second chamber 49. Move to. At this time, the coolant gas is separated from the refrigerant gas by passing through the gap between the valve unit 9 and the flange portion 43c. Then, the refrigerant gas from which the lubricating oil has been separated moves from the second chamber 49 to the suction chamber 11 through the throttle hole 9a. The lubricating oil separated from the refrigerant gas is stored in the first chamber 47 and returned to the crank chamber 15 by the return passage 51.

  For this reason, the amount of lubricating oil in the refrigerant gas discharged to the refrigeration circuit outside the swash plate compressor is reduced, and a high refrigeration capacity is exhibited.

  At this time, the amount of lubricating oil in the crank chamber 15 increases, but the swash plate 29 and the like merely agitate the lubricating oil at a low speed, the viscosity of the lubricating oil does not decrease so much, and the temperature of the lubricating oil hardly increases. Does not occur. For this reason, the lubrication of the sliding part is still preferably performed.

  Therefore, according to this compressor, it is possible to achieve excellent sliding characteristics when the drive shaft 7 is rotated at a high speed and high refrigeration capacity when the drive shaft 7 is rotated at a low speed. Is possible.

  As shown in FIGS. 5 and 6, the swash plate compressor of the second embodiment is different from the first embodiment in the on-off valve and the oil separator.

  The drive shaft 7 is formed with a discharge hole 73 that extends in the radial direction and communicates the outflow hole 39 with the first chamber 47. Further, on the drive shaft 7, a valve hole 7 a and a guide hole 7 b communicating with the outflow hole 39 are formed in the radial direction on the rear side of the discharge hole 73. The valve hole 7a is formed with a large diameter, and the guide hole 7b is coaxial with the valve hole 7a and formed with a small diameter. A valve element 69a is slidably accommodated in the valve hole 7a, and a connecting rod 69b is slidably accommodated in the guide hole 7b. One end of the connecting rod 69b is fixed to the valve body 69a, and the other end of the connecting rod 69b is fixed to a spring seat 69c located in the storage chamber 1c. Between the outer peripheral surface of the drive shaft 7 and the spring seat 69c, a spring 69d having a biasing force in a direction in which the valve body 69a closes the outflow hole 39 is provided. The valve body 69a, the connecting rod 69b, the spring seat 69c, and the spring 69d constitute an on-off valve 69. The valve body 69a also serves as a mass body.

  The oil separator 71 includes a cylindrical portion 71a fitted to the drive shaft 7, and a flange portion 71b that is formed integrally with the cylindrical portion 71a and extends in a flange shape from the rear end of the cylindrical portion 71a. The flange portion 71 b faces the valve unit 9. The oil guide groove 3b, the oil guide hole 3c, the first hole 37, the outflow hole 39, the discharge hole 73, the first chamber 47, the second chamber 49, and the throttle hole 9a are escape passages. The oil guide groove 3b, the oil guide hole 3c, the first hole 37, and the outflow hole 39 are the first passage. The storage chamber 1c, the oil separator 71, the return passage 51, and the on-off valve 69 are oil separation means. Other configurations are the same as those of the first embodiment.

  In this compressor, when the drive shaft 7 is rotated at a high speed, as shown in FIG. 6, the on-off valve 69 is configured such that the valve body 69a resists the biasing force of the spring 69d by a large centrifugal force. The valve element 69a increases the opening degree of the outflow hole 39 away from the heart. Therefore, the refrigerant gas containing a large amount of lubricating oil in the crank chamber 15 reaches the second chamber 49 through the oil guide groove 3b, the oil guide hole 3c, the first hole 37, and the outflow hole 39, and is sucked from the throttle hole 9a. Move to chamber 11. At this time, the opening degree of the outflow hole 39, that is, the opening sectional area, is at least one of the opening sectional area of the discharge hole 73 and the opening sectional area of the passage formed by the gap between the flange portion 71b and the valve unit 9. It is set to be larger.

  When the drive shaft 7 is rotated at a low speed, as shown in FIG. 5, the opening / closing valve 69 causes the valve body 69a to bend by the urging force of the spring 69d with a small centrifugal force and approach the axis of the drive shaft 7. The valve body 69 a reduces the opening degree of the outflow hole 39. For this reason, the refrigerant gas containing a large amount of lubricating oil in the crank chamber 15 reaches the first chamber 47 through the oil guide groove 3b, the oil guide hole 3c, the first hole 37, the outflow hole 39, and the discharge hole 73. The refrigerant gas separates the lubricating oil when moving from the first chamber 47 to the second chamber 49. The refrigerant gas from which the lubricating oil has been separated moves from the throttle hole 9 a to the suction chamber 11, and the lubricating oil is recirculated from the first chamber 47 to the crank chamber 15 via the return passage 51.

  Thus, this compressor can achieve the same effects as those of the first embodiment.

  As shown in FIGS. 7 and 8, the swash plate compressor according to the third embodiment is different from the first and second embodiments in the on-off valve and the oil separator.

  The drive shaft 7 is formed with a first discharge hole 79 that extends in the radial direction and communicates the outflow hole 39 with the first chamber 47. Further, on the drive shaft 7, a second discharge hole 7 c communicating with the outflow hole 39 and a guide hole 7 d are both formed in the radial direction on the rear side of the first discharge hole 79. The second discharge hole 7 c is formed with a large diameter and communicates with the second chamber 49. The guide hole 7d is coaxial with the second discharge hole 7c, has a small diameter, and communicates with the second chamber 49. A valve body 75a is slidably provided outside the second discharge hole 7c, and a connecting rod 75b is slidably accommodated in the guide hole 7d. One end of the connecting rod 75a is fixed to the valve body 75a, and a spring seat 75c located in the storage chamber 1c is fixed to the other end of the connecting rod 75a. Between the outer peripheral surface of the drive shaft 7 and the spring seat 75c, a spring 75d having a biasing force in a direction in which the valve body 75a closes the second discharge hole 7c is provided. The valve body 75a, the connecting rod 75b, the spring seat 75c and the spring 75d constitute an on-off valve 75. The valve body 75a also serves as a mass body. The rear end of the outflow hole 39 is closed by a plug member 81. The valve body 75a is made of a material having a specific gravity greater than that of the connecting rod 75b and the spring seat 75c.

  The oil separator 77 includes a cylindrical portion 77a that is fitted to the drive shaft 7, a tapered portion 77b that is integral with the cylindrical portion 77a, and has a diameter increased from the rear end of the cylindrical portion 77a toward the valve unit 9, and a taper. It consists of a flange portion 77c formed in a flange shape from the rear end of the portion 77b. The flange portion 77 c faces the valve unit 9. The oil guide groove 3b, the oil guide hole 3c, the first hole 37, the outflow hole 39, the first discharge hole 79, the first chamber 47, the second discharge hole 7c, the second chamber 49, and the throttle hole 9a are escape passages. . And the oil guide groove 3b, the oil guide hole 3c, the 1st hole 37, and the outflow hole 39 are the 1st channel | paths. The storage chamber 1c, the oil separator 77, the return passage 51, and the on-off valve 75 are oil separating means. Other configurations are the same as those of the first embodiment.

  In this compressor, when the drive shaft 7 is rotated at a high speed, the on-off valve 75 has the shaft 75 of the drive shaft 7 against the urging force of the spring 75d by a large centrifugal force as shown in FIG. The valve body 75a increases the opening degree of the second discharge hole 7c away from the heart. Therefore, the refrigerant gas containing a large amount of lubricating oil in the crank chamber 15 reaches the second chamber 49 through the oil guide groove 3b, the oil guide hole 3c, the first hole 37, the outflow hole 39, and the second discharge hole 7c. Then, it moves from the throttle hole 9 a to the suction chamber 11.

  When the drive shaft 7 is rotated at a low speed, as shown in FIG. 7, the on-off valve 75 approaches the axial center of the drive shaft 7 because the valve body 75a is bent by the urging force of the spring 75d with a small centrifugal force. The valve body 75a reduces the opening degree of the second discharge hole 7c. Therefore, the refrigerant gas containing a large amount of lubricating oil in the crank chamber 15 reaches the first chamber 47 through the oil guide groove 3b, the oil guide hole 3c, the first hole 37, the outflow hole 39, and the first discharge hole 79. The refrigerant gas separates the lubricating oil when moving from the first chamber 47 to the second chamber 49. The refrigerant gas from which the lubricating oil has been separated moves from the throttle hole 9 a to the suction chamber 11, and the lubricating oil is recirculated from the first chamber 47 to the crank chamber 15 via the return passage 51.

  In this way, this compressor can achieve the same effects as those of the first and second embodiments.

  As shown in FIGS. 9 and 10, the swash plate compressor according to the fourth embodiment is different from the first to third embodiments in the on-off valve, the oil separator, and the outflow hole.

  A unit body 80 in which an on-off valve 81 and an oil separator 82 are integrally formed is press-fitted and fixed to the rear end of the drive shaft 7. In the unit body 80, both the valve hole 7e and the guide hole 7f are formed in the radial direction. The valve hole 7e and the guide hole 7f are coaxial and formed with substantially the same diameter. A valve seat 7g is formed around the valve hole 7e, and a mass body 81a is slidably accommodated in the guide hole 7f. In this embodiment, a discharge hole 83 is constituted by the valve hole 7e and the valve seat 7g. One end of the connecting rod 81b is fixed to the valve body 81c, and the mass body 81a is fixed to the other end of the connecting rod 81b. A spring seat 81d having a smaller diameter than the valve hole 7e and the guide hole 7f is formed between the valve hole 7e and the guide hole 7f, and a spring 81e is disposed between the valve body 81c and the spring seat 81d, and the spring 81e. Applies a biasing force in a direction in which the valve body 81c opens the discharge hole 83. The mass body 81a, the connecting rod 81b, the valve body 81c, the spring seat 81d and the spring 81e constitute an on-off valve 81.

  Further, the unit body 80 is formed with a second outflow hole 39 b that communicates with the first outflow hole 39 a formed in the drive shaft 7 and whose diameter is changed inside the unit body 80. The first outflow hole 39a and the second outflow hole 39b constitute an outflow hole 39. An on-off valve 81 is arranged at the boundary where the diameter of the second outflow hole 39b is changed.

  The oil separator 82 includes a base portion 82a, a tapered portion 82b having a diameter increased from the rear end of the base portion 82a toward the valve unit 9, and a flange portion 82c formed to expand in a flange shape from the rear end of the tapered portion 82b. Consists of. The flange portion 82 c faces the valve unit 9. The oil guide groove 3b, the oil guide hole 3c, the first hole 37, the outflow hole 39, the discharge hole 83, the first chamber 47, the second chamber 49, and the throttle hole 9a are escape passages. The oil guide groove 3b, the oil guide hole 3c, the first hole 37, and the outflow hole 39 are the first passage. The storage chamber 1c, the oil separator 82, the return passage 51, and the on-off valve 81 are oil separating means. Other configurations are the same as those of the first embodiment.

  In this compressor, when the drive shaft 7 is rotated at a high speed, the on-off valve 81 has a large centrifugal force acting on the mass body 81a as shown in FIG. 10, and the valve body 81c resists the biasing force of the spring 81e. As a result, the valve body 81c decreases the opening degree of the discharge hole 83 while increasing the opening degree of the second outflow hole 39b. When the valve body 81c is seated on the valve seat 7g, the discharge hole 83 is closed, and the opening cross-sectional area of the second outflow hole 39b is maximized. Therefore, the refrigerant gas containing a large amount of lubricating oil in the crank chamber 15 reaches the second chamber 49 through the oil guide groove 3b, the oil guide hole 3c, the first hole 37, and the outflow hole 39, and is sucked from the throttle hole 9a. Move to chamber 11.

  Further, when the drive shaft 7 is rotated at a low speed, the on-off valve 81 is driven while the centrifugal force acting on the mass body 81a is reduced and the valve body 81c is bent by the urging force of the spring 81e as shown in FIG. The valve element 81 c increases the opening degree of the outflow hole 83 away from the axis of the shaft 7. When the mass body 81a is seated on the spring seat 81d, the second outflow hole 39b is closed, and the opening cross-sectional area of the discharge hole 83 is maximized. Therefore, the refrigerant gas containing a large amount of lubricating oil in the crank chamber 15 reaches the first chamber 47 through the oil guide groove 3b, the oil guide hole 3c, the first hole 37, the outflow hole 39, and the discharge hole 83. The refrigerant gas separates the lubricating oil when moving from the first chamber 47 to the second chamber 49. The refrigerant gas from which the lubricating oil has been separated moves from the throttle hole 9 a to the suction chamber 11, and the lubricating oil is recirculated from the first chamber 47 to the crank chamber 15 via the return passage 51.

  Thus, this compressor can achieve the same effects as those of the first embodiment. Moreover, in this compressor, since the on-off valve 81 and the oil separator 82 are integrated as a unit body 80, it is only necessary to press-fit the unit body 80 assembled in advance into the rear shaft of the drive shaft 7 at the time of manufacture. Manufacturing man-hours can be reduced.

  In the above, the present invention has been described with reference to the first to fourth embodiments. However, the present invention is not limited to the first to fourth embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, the link mechanism 31 is not limited to that of the above embodiment, and various types can be adopted.

  The present invention is applicable to a vehicle air conditioner.

1 is a cross-sectional view of a swash plate compressor according to Embodiment 1. FIG. FIG. 3 is an enlarged cross-sectional view of a main part of the swash plate compressor according to the first embodiment while the drive shaft rotates at a low speed. FIG. 3 is an enlarged cross-sectional view of a main part of the swash plate compressor according to the first embodiment while the drive shaft rotates at a high speed. It is a perspective view of the on-off valve concerning the swash plate type compressor of Example 1. FIG. FIG. 10 is an enlarged cross-sectional view of a main part of the swash plate compressor according to the second embodiment while the drive shaft rotates at a low speed. FIG. 5 is an enlarged cross-sectional view of a main part of a swash plate compressor according to a second embodiment while a drive shaft is rotating at a high speed. FIG. 6 is an enlarged cross-sectional view of a main part of a swash plate compressor according to a third embodiment while a drive shaft is rotating at a low speed. FIG. 10 is an enlarged cross-sectional view of a main part of a swash plate compressor according to a third embodiment while a drive shaft is rotating at a high speed. FIG. 9 is an enlarged cross-sectional view of a main part of a swash plate compressor according to a fourth embodiment while a drive shaft is rotating at a low speed. FIG. 6 is an enlarged cross-sectional view of a main part of a swash plate compressor according to a fourth embodiment while a drive shaft is rotating at a high speed.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1a ... Cylinder bore 11 ... Suction chamber 13 ... Discharge chamber 15 ... Crank chamber 1, 3, 5 ... Housing (1 ... Cylinder block, 3 ... Front housing, 5 ... Rear housing)
7 ... Drive shaft 29 ... Swash plate 21 ... Piston 35 ... Motion conversion mechanism (shoe)
3b, 3c, 37, 39, 41, 47, 49, 9a, 73, 79, 7c ... Relief passage (3b ... first passage (oil guide groove), 3c ... first passage (oil guide hole), 37 ... first 1 passage (first hole), 39 ... 1st passage (outflow hole), 41 ... discharge hole, 47 ... 1st chamber, 49 ... 2nd chamber, 9a ... throttle hole, 73 ... discharge hole, 79 ... 1st discharge Hole, 7c ... second discharge hole)
1c, 43, 51, 45, 71, 69, 77, 75 ... oil separation means (1c: storage chamber, 43, 71, 77 ... oil separator, 51 ... return passage, 45, 69, 75 ... on-off valve)
23 ... Lug plate 3b, 3c ... Oil guide path (3b ... Oil guide groove, 3c ... Oil guide hole)
17 ... Shaft seal device

Claims (8)

A housing having a cylinder bore, a suction chamber, a discharge chamber, and a crank chamber; a drive shaft rotatably supported by the housing and facing the crank chamber; and a swash plate supported by the drive shaft in the crank chamber; A piston housed in a cylinder bore so as to be capable of reciprocating; a motion conversion mechanism provided between the swash plate and the piston, wherein the oscillating motion of the swash plate is converted into reciprocating motion of the piston; and the crank chamber And an escape passage for communicating with the suction chamber,
Acts on the refrigerant gas in the escape passage, increases the rotational speed of the drive shaft, allows the refrigerant gas to communicate with the suction chamber without separating lubricating oil, and reduces the rotational speed of the drive shaft to lubricate the refrigerant gas. A swash plate type compressor comprising oil separation means for allowing refrigerant gas separated from oil to communicate with the suction chamber and for causing the separated lubricating oil to flow back to the crank chamber. The escape passage has a first passage communicating with a region where the lubricating oil in the crank chamber is large,
The swash plate compressor according to claim 1, wherein the oil separation means acts on the refrigerant gas in the first passage. The oil separating means is formed in the housing, communicates with the suction chamber by a throttle hole, and a storage chamber in which the other end of the drive shaft is located;
The storage chamber is divided into a first chamber that is provided at the other end of the drive shaft and does not communicate with the throttle hole, and a second chamber that communicates with the throttle hole, and refrigerant is transferred from the first chamber to the second chamber. An oil separator for storing lubricating oil separated from the refrigerant gas in the first chamber by moving gas;
A return passage for communicating the first chamber with the crank chamber;
An open / close valve that communicates the first passage with the second chamber by increasing the rotational speed of the drive shaft, and that does not communicate the first passage with the second chamber by decreasing the rotational speed of the drive shaft;
The swash plate compressor according to claim 2, wherein the escape passage has a discharge hole for communicating the first passage with the first chamber.   4. The swash plate compressor according to claim 3, wherein the return passage communicates with a region where the lubricating oil in the crank chamber is low.   5. The swash plate compressor according to claim 3, wherein the return passage communicates a lower portion of the first chamber with the crank chamber when mounted on a vehicle.   The swash plate compressor according to any one of claims 3 to 5, wherein the on-off valve is displaced by centrifugal force. The swash plate is supported so that the tilt angle can be changed,
A lug plate that receives a compression reaction force is fixed to the drive shaft so as to be integrally rotatable,
An oil guide path extending from the outer peripheral area of the crank chamber to the space between the housing and the lug plate is formed in the housing,
The swash plate compressor according to claim 2, wherein the first passage communicates with the oil guide path. Between the housing and the drive shaft, a shaft seal device for sealing the drive shaft exposed from the housing is provided,
The swash plate compressor according to claim 7, wherein the first passage communicates with the oil guide path through the shaft seal device.

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