JP6418024B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor.

  The refrigerant circulation circuit (refrigeration cycle) of the air conditioner is composed of a compressor and an external refrigerant circuit. The external refrigerant circuit includes a condenser that condenses the refrigerant compressed by the compressor and discharged from the compressor, an expansion valve connected to the condenser, and an evaporator that evaporates the refrigerant that has passed through the expansion valve and expanded. It has.

  The refrigerant includes oil (lubricating oil) used for lubricating each sliding portion inside the compressor. Here, when the refrigerant compressed by the compressor is discharged to the external refrigerant circuit, when the oil is discharged together with the refrigerant to the external refrigerant circuit, the oil adheres to the inner wall of the condenser or the evaporator, The heat exchange efficiency in the condenser or the evaporator is reduced. In order to prevent the oil from being discharged into the external refrigerant circuit together with the refrigerant, a compressor having a centrifugal oil separator that separates the oil contained in the refrigerant from the refrigerant is disclosed in Patent Document 1. It is disclosed. In the compressor of Patent Document 1, the refrigerant introduced into the separation chamber rotates in the circumferential direction in the separation chamber, and the oil contained in the refrigerant is centrifuged by centrifugal force.

JP 2009-221960 A

  By the way, in the centrifugal oil separator as in Patent Document 1, the refrigerant from which the oil is separated in the separation chamber maintains the swirled state, and the discharge passage on the downstream side in the refrigerant flow direction from the separation chamber. May flow. When the refrigerant flows through the discharge passage while turning, the refrigerant easily comes into contact with the inner wall forming the discharge passage, and pressure loss is likely to occur when the refrigerant flows through the discharge passage.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a compressor capable of suppressing the generation of pressure loss when the refrigerant flows through the discharge passage.

  A compressor that solves the above problems is formed inside a cylindrical inner surface, a discharge chamber formed in a housing, an oil separator that has a cylindrical inner surface and separates oil from a refrigerant discharged from the discharge chamber by centrifugation. And a discharge passage that is formed downstream of the separation chamber in the housing in the flow direction of the refrigerant and discharges the refrigerant separated from the oil by the oil separator to an external refrigerant circuit, The refrigerant introduced into the separation chamber swirls along the inner surface of the cylinder, so that the oil contained in the refrigerant is centrifuged from the refrigerant, and is generated in the discharge passage in the separation chamber. A collision unit is provided that changes the swirling flow of the refrigerant into a flow different from the swirling flow of the refrigerant when the refrigerant collides.

  According to this, when the refrigerant collides with the collision part, the swirling flow of the refrigerant changes to a flow different from the swirling flow of the refrigerant, so that the swirling state of the refrigerant can be eliminated. Therefore, it can suppress that the refrigerant | coolant which flows through a discharge passage flows while turning, and compared with the case where a refrigerant | coolant flows through a discharge passage while turning, a refrigerant | coolant becomes difficult to contact the inner wall which forms a discharge passage. As a result, it is possible to suppress the occurrence of pressure loss when the refrigerant flows through the discharge passage.

In the compressor, it is preferable that the discharge passage includes an extending passage that extends in a direction tangential to the inner surface of the cylinder and in a direction opposite to the swirling direction of the refrigerant.
According to this, when the refrigerant flowing while turning flows out to the extension passage, it becomes easy to collide with the opening portion on the inlet side of the extension passage on the inner wall of the housing forming the extension passage. Therefore, the opening on the inlet side of the extension passage in the inner wall of the housing forming the extension passage functions as a collision portion where the refrigerant collides. Therefore, compared with the case where a collision part is provided separately, the structure of a compressor can be simplified.

  According to this invention, generation | occurrence | production of the pressure loss at the time of a refrigerant | coolant flowing through a discharge channel can be suppressed.

A side sectional view showing a swash plate type compressor in an embodiment. The sectional side view which expands and shows a part of swash plate type compressor. (A) is the sectional view on the 3a-3a line in FIG. 2, (b) is the sectional view on the 3b-3b line in FIG.

Hereinafter, an embodiment in which the compressor is embodied as a variable displacement swash plate compressor will be described with reference to FIGS. The swash plate compressor is used for a vehicle air conditioner.
As shown in FIG. 1, the housing 11 of the swash plate compressor 10 includes a cylinder block 12, a front housing 13 connected to the front end of the cylinder block 12, and a valve / port forming body 14 at the rear end of the cylinder block 12. And a rear housing 15 connected through the rear housing 15. In the housing 11, a crank chamber 16 is defined in a space surrounded by the front housing 13 and the cylinder block 12. A rotating shaft 17 is rotatably supported by the cylinder block 12 and the front housing 13 via a radial bearing 18, and the rotating shaft 17 is supported so as to penetrate the crank chamber 16.

  The rotating shaft 17 is operatively connected to an engine E, which is a vehicle driving source of the vehicle, via a clutchless type (always transmission type) power transmission mechanism PT. Accordingly, when the engine E is in operation, the rotating shaft 17 is always rotated by receiving power from the engine E.

  In the crank chamber 16, a rotary support 19 is fixed to the rotary shaft 17 so as to be integrally rotatable. The rotary support 19 is supported on the front housing 13 via a thrust bearing 20. Further, the swash plate 21 is supported on the rotating shaft 17 so as to be slidable and tiltable in the direction in which the rotating axis L extends with respect to the rotating shaft 17 (the axial direction of the rotating shaft 17). A hinge mechanism 22 is interposed between the rotary support 19 and the swash plate 21. The swash plate 21 can be tilted with respect to the rotation axis L of the rotation shaft 17 and can rotate integrally with the rotation shaft 17 by the intervention of the hinge mechanism 22 between the rotation support 19. .

  In the cylinder block 12, a plurality of cylinder bores 12a are arranged around the rotation shaft 17, and a single-headed piston 23 is accommodated in each cylinder bore 12a so as to be capable of reciprocating. The piston 23 is anchored to the outer peripheral portion of the swash plate 21 via a pair of shoes 24, and the piston 23 is reciprocated in the cylinder bore 12a by the rotational motion of the swash plate 21. In the cylinder bore 12a, a compression chamber 25 whose volume changes in accordance with the reciprocating motion of the piston 23 is formed.

  In the housing 11, an annular suction chamber 26 is defined between the valve / port forming body 14 and the rear housing 15, and a discharge chamber 27 is defined inside the suction chamber 26. The valve / port forming body 14 is formed with a suction port 28 and a suction valve 29 so as to be positioned between the compression chamber 25 and the suction chamber 26, respectively. A discharge port 30 and a discharge valve 31 are formed so as to be positioned between each other.

  A suction passage 32 communicating with the suction chamber 26 is formed in the rear housing 15. The discharge chamber 27 includes a storage chamber 40 formed in the rear housing 15. The storage chamber 40 stores a disk-shaped oil separator 50 that separates oil contained in the refrigerant (carbon dioxide in the present embodiment) by centrifugation.

  As shown in FIG. 2, the storage chamber 40 includes a wide portion 40a and a narrow portion 40b that is continuous with the wide portion 40a and narrower than the wide portion 40a. A recess 41 is formed on the bottom surface 40e of the narrow portion 40b. An annular groove 43 is formed on the bottom surface 40e of the narrow portion 40b and on the inner peripheral surface of the recess 41 near the narrow portion 40b.

  The oil separator 50 has a perfect circular shape in plan view and is a separate member from the rear housing 15. The oil separator 50 includes a substrate 51 and a columnar turning shaft 52 provided on the substrate 51. An annular portion 53 formed in an annular shape around the turning shaft 52 is extended on the substrate 51. The extending direction of the annular portion 53 coincides with the axial direction of the rotating shaft 17. The axial direction of the turning shaft 52 coincides with the axial direction of the rotary shaft 17.

  The annular portion 53 has a cylindrical inner surface 53a. A separation chamber 53b is formed inside the cylindrical inner surface 53a. Inside the recess 41 is a refrigerant discharge space 45 from which the refrigerant from which oil has been separated by the oil separator 50 is discharged. The separation chamber 53b and the refrigerant discharge space 45 are continuous. An inner peripheral surface 41a of the recess 41 is formed on a cylindrical inner surface similar to the cylindrical inner surface 53a.

  An annular plate-like flange portion 56 protruding outward is formed at the outer peripheral edge portion of the annular portion 53 opposite to the substrate 51. The oil separator 50 is accommodated in the accommodating chamber 40 with the end surface 56a of the flange portion 56 opposite to the substrate 51 being in contact with the bottom surface 40e of the narrow portion 40b, and is press-fitted into the narrow portion 40b. ing.

  The oil storage space 46 is defined by a part of the end surface 56 a of the flange portion 56, the end surface 53 e of the annular portion 53 on the side opposite to the substrate 51, and the annular groove portion 43. The oil storage space 46 is continuous with the separation chamber 53 b and extends further outward in the radial direction of the annular portion 53 than the separation chamber 53 b in the rear housing 15. The rear housing 15 is formed with an oil passage 48 through which oil separated from the refrigerant by the oil separator 50 is introduced into the crank chamber 16. The oil passage 48 includes an oil storage space 46. An annular gap 47 is formed outside the annular portion 53 in the storage chamber 40.

  As shown in FIG. 3A, the annular portion 53 is formed with a plurality (six in this embodiment) of introduction holes 57 for communicating the gap 47 (discharge chamber 27) and the separation chamber 53b. Each introduction hole 57 is formed so as to penetrate the annular portion 53 linearly, and extends along a tangential direction of the annular portion 53. Therefore, the opening on the separation chamber 53b side in each introduction hole 57 opens toward the tangential direction with respect to the cylindrical inner surface 53a. The refrigerant discharged into the discharge chamber 27 is guided to the gap 47 by the substrate 51 and the annular portion 53 and is introduced into the separation chamber 53 b through the introduction holes 57. The refrigerant flowing into the separation chamber 53b swirls along the direction indicated by the arrow R1 in FIG. 3A along the cylindrical inner surface 53a in the separation chamber 53b.

  As shown in FIG. 3B, the rear housing 15 is formed with an extending passage 33 a through which the refrigerant discharged into the refrigerant discharge space 45 flows out. The refrigerant discharge space 45 and the extension passage 33a are formed downstream of the separation chamber 53b in the rear housing 15 in the refrigerant flow direction, and discharge the refrigerant from which the oil is separated by the oil separator 50 to the external refrigerant circuit 35. A passage 33 is formed. Accordingly, the discharge passage 33 includes an extending passage 33a. The extending passage 33a extends in the direction tangent to the inner peripheral surface 41a of the recess 41 and in the direction opposite to the direction of refrigerant rotation (the direction indicated by the arrow R2 in FIG. 3B). The inner peripheral surface of the extension passage 33a is circular.

  As shown in FIG. 1, the suction passage 32 and the discharge passage 33 are connected by an external refrigerant circuit 35. The external refrigerant circuit 35 includes a condenser 35a connected to the discharge passage 33, an expansion valve 35b connected to the condenser 35a, and an evaporator 35c connected to the expansion valve 35b, and the evaporator 35c includes a suction passage. 32 is connected. The swash plate compressor 10 is incorporated in a refrigeration circuit.

  Refrigerant introduced into the suction chamber 26 from the outlet side of the evaporator 35 c in the external refrigerant circuit 35 moves from the top dead center position to the bottom dead center position side of each piston 23 through the suction port 28 and the suction valve 29. And is sucked into the compression chamber 25. The refrigerant sucked into the compression chamber 25 is compressed to a predetermined pressure by moving from the bottom dead center position to the top dead center position side of the piston 23 and discharged to the discharge chamber 27 via the discharge port 30 and the discharge valve 31. Is done.

  In the cylinder block 12 and the rear housing 15, an extraction passage 36 that connects the suction chamber 26 and the crank chamber 16 is formed. The cylinder block 12 and the rear housing 15 are formed with an air supply passage 37 that connects the discharge chamber 27 and the crank chamber 16, and a capacity control valve 38 is disposed in the air supply passage 37. The capacity control valve 38 is an electromagnetic valve, and opens and closes the air supply passage 37 by excitation and demagnetization of a solenoid (not shown). The oil storage space 46 is connected to the capacity control valve 38 through a passage 48a.

  The capacity control valve 38 opens and closes the air supply passage 37 to change the supply amount of high-pressure refrigerant from the discharge chamber 27 to the crank chamber 16, and from the crank chamber 16 to the suction chamber 26 via the extraction passage 36. The pressure in the crank chamber 16 is changed from the relationship with the refrigerant discharge amount. As a result, the pressure difference between the crank chamber 16 and the cylinder bore 12a via the piston 23 is changed, the inclination angle of the swash plate 21 is changed, and the discharge capacity is adjusted.

  Specifically, excitation / demagnetization of the solenoid of the capacity control valve 38 is controlled by a control computer (not shown), and an air conditioner switch is signal-connected to the control computer. When the air conditioner switch is turned off, the control computer demagnetizes the solenoid of the capacity control valve 38. Then, the air supply passage 37 is opened by the capacity control valve 38 and the discharge chamber 27 and the crank chamber 16 are communicated with each other. Accordingly, the high-pressure refrigerant in the discharge chamber 27 is supplied to the crank chamber 16 via the air supply passage 37. Further, the pressure in the crank chamber 16 is released to the suction chamber 26 through the extraction passage 36. As a result, the difference between the pressure in the crank chamber 16 and the pressure in the cylinder bore 12a via the piston 23 is changed, and the inclination angle of the swash plate 21 is minimized and the discharge capacity is minimized.

  On the other hand, when the air conditioner switch is turned on and the solenoid is excited, the opening of the air supply passage 37 is reduced by the capacity control valve 38, and the pressure in the crank chamber 16 is released to the suction chamber 26 through the bleed passage 36. Decrease based on. By this pressure reduction, the swash plate 21 is separated from the minimum inclination angle and the inclination angle becomes large, and the swash plate compressor 10 performs compression with a discharge capacity exceeding the minimum discharge capacity.

Next, the operation of this embodiment will be described.
As shown in FIGS. 3A and 3B, the refrigerant discharged into the discharge chamber 27 is guided to the gap 47 by the substrate 51 and the annular portion 53 and is introduced into the separation chamber 53b through the respective introduction holes 57. Is done. The refrigerant flowing into the separation chamber 53b is swung along the cylindrical inner surface 53a, whereby oil contained in the refrigerant is centrifuged and attached to the cylindrical inner surface 53a. The oil adhering to the cylindrical inner surface 53a is discharged to the oil storage space 46 through the cylindrical inner surface 53a. The oil stored in the oil storage space 46 is supplied to the crank chamber 16 through the passage 48a, the capacity control valve 38 and the air supply passage 37, and lubricates each sliding portion.

  On the other hand, the refrigerant from which the oil is separated by the oil separator 50 is discharged into the refrigerant discharge space 45. Then, the refrigerant discharged into the refrigerant discharge space 45 is swung along the inner peripheral surface 41 a of the recess 41.

  As shown in FIG. 3B, the extending passage 33a is tangential to the inner peripheral surface 41a of the concave portion 41 formed on the cylindrical inner surface similar to the cylindrical inner surface 53a, and is opposite to the swirling direction of the refrigerant. It extends in the direction. For this reason, when the refrigerant flowing while turning flows out to the extension passage 33a, it easily collides with the opening 33b on the inlet side of the extension passage 33a on the inner wall of the rear housing 15 forming the extension passage 33a. When the refrigerant collides with the opening 33b, the swirling flow of the refrigerant changes to a flow different from the swirling flow of the refrigerant, so that the swirling state of the refrigerant is eliminated. Therefore, the opening 33b on the inlet side of the extension passage 33a on the inner wall of the rear housing 15 that forms the extension passage 33a collides with the swirling flow of the refrigerant generated in the separation chamber 53b. It functions as a collision part that changes to a flow different from the swirl flow. Therefore, the discharge passage 33 includes a collision portion. And it is suppressed that the refrigerant | coolant which flows through the extended channel | path 33a flows, turning, compared with the case where the refrigerant | coolant flows through the extended channel | path 33a, turning, the inner wall of the rear housing 15 which forms the extended channel | path 33a It becomes difficult for the refrigerant to come into contact. As a result, the occurrence of pressure loss when the refrigerant flows through the extending passage 33a is suppressed.

In the above embodiment, the following effects can be obtained.
(1) When the refrigerant flowing while turning flows out to the extension passage 33a, it collides with the opening 33b on the inlet side of the extension passage 33a on the inner wall of the rear housing 15 forming the extension passage 33a. According to this, when the refrigerant collides with the opening 33b, the swirling flow of the refrigerant changes to a flow different from the swirling flow of the refrigerant, so that the swirling state of the refrigerant can be eliminated. Therefore, the refrigerant flowing through the discharge passage 33 can be prevented from flowing while swirling, and compared with the case where the refrigerant flows through the discharge passage 33 while swirling, the refrigerant contacts the inner wall forming the discharge passage 33. It becomes difficult. As a result, the generation of pressure loss when the refrigerant flows through the discharge passage 33 can be suppressed.

  (2) The discharge passage 33 includes an extending passage 33a that extends in the tangential direction of the cylindrical inner surface 53a and in the direction opposite to the swirling direction of the refrigerant. According to this, when the refrigerant that flows while turning flows out to the extension passage 33a, it easily collides with the opening 33b on the inlet side of the extension passage 33a in the inner wall of the rear housing 15 that forms the extension passage 33a. . Therefore, the opening 33b on the inlet side of the extension passage 33a on the inner wall of the rear housing 15 forming the extension passage 33a functions as a collision portion where the refrigerant separated from the oil collides. Therefore, compared with the case where a collision part is provided separately, the structure of the swash plate type compressor 10 can be simplified.

In addition, you may change the said embodiment as follows.
In the embodiment, the inner peripheral surface of the extension passage 33a may be a square shape. According to this, compared with the case where the extended passage 33a is circular, the refrigerant flowing through the extended passage 33a is less likely to turn.

In the embodiment, the oil separator 50 may not include the pivot shaft 52.
In the embodiment, the number of introduction holes 57 is not particularly limited.

  In the embodiment, the oil storage space 46 may be connected to the suction chamber 26 via a passage formed in the rear housing 15. In this case, the oil stored in the oil storage space 46 is supplied to the suction chamber 26 through the passage and is mixed with the refrigerant introduced into the suction chamber 26 from the outlet side of the evaporator 35c in the external refrigerant circuit 35. Each sliding part of the swash plate compressor 10 is lubricated.

In the embodiment, the oil separator 50 may be arranged so that the extending direction of the annular portion 53 is a direction intersecting the axial direction of the rotating shaft 17.
In the embodiment, the oil separator 50 may be elliptical in plan view.

In the embodiment, part of the oil separator 50 may be formed from part of the housing 11.
In the embodiment, the swash plate compressor 10 is embodied as a variable capacity type, but may be a fixed capacity type.

In the embodiment, the swash plate compressor 10 is a single-head piston type, but it may be a double-head piston type.
(Circle) in embodiment, the swash plate type compressor 10 may not be used for a vehicle air conditioner, and may be used for another air conditioner.

In the embodiment, the compressor is not limited to the swash plate compressor 10, and may be, for example, a scroll type, vane type, or roots type compressor.
In the embodiment, carbon dioxide is used as the refrigerant. However, for example, chlorofluorocarbon may be used as the refrigerant.

  DESCRIPTION OF SYMBOLS 10 ... Swash plate type compressor as a compressor, 11 ... Housing, 27 ... Discharge chamber, 33 ... Discharge passage, 33a ... Extension passage, 33b ... Opening which functions as a collision part, 35 ... External refrigerant circuit, 50 ... Oil Separator, 53a ... cylindrical inner surface, 53b ... separation chamber.

Claims (1)

A discharge chamber formed in the housing;
An oil separator having a cylindrical inner surface and separating oil from a refrigerant discharged from the discharge chamber by centrifugation;
A separation chamber formed inside the cylindrical inner surface;
A discharge passage that is formed downstream of the separation chamber in the housing in the refrigerant flow direction and discharges the refrigerant from which the oil has been separated by the oil separator to an external refrigerant circuit,
The refrigerant introduced into the separation chamber is swirled along the inner surface of the cylinder, so that the oil contained in the refrigerant is centrifuged from the refrigerant,
The discharge passage includes a collision portion that changes the swirling flow of the refrigerant generated in the separation chamber to a flow different from the swirling flow of the refrigerant when the refrigerant collides ,
The compressor is characterized in that the discharge passage includes an extending passage extending in a direction tangential to the inner surface of the cylinder and opposite to the swirling direction of the refrigerant .