JPH10141229A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor capable of efficiently separating oil in compressed gaseous refrigerant to be supplied to an external refrigerant circuit, without enlarging the whole structure of a refrigerating circuit. SOLUTION: A discharge muffler chamber 48 is formed in housings 21, 22, the discharge muffler chamber 48 and discharge chambers 35, 36 are communicated with one another through discharge passages 46, 47. An oil separator 53 is provided in the discharge muffler chamber 48, supplying ports 54a, 55a for gaseous refrigerant are connected to the discharge passages 46, 47 in the oil separator 53, and discharge ports 56a for gaseous refrigerant are opened in the discharge muffler chamber 48.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor used in, for example, a vehicle air conditioner, and more particularly to a mechanism for separating oil contained in refrigerant gas discharged.

[0002]

2. Description of the Related Art In a compressor of this kind, a movable portion inside the compressor is lubricated with oil mixed in a mist state in a refrigerant gas. Therefore, during operation of the compressor, the compressed refrigerant gas discharged from the compressor may be supplied to the external refrigerant circuit in a state where a large amount of mist-like oil remains mixed. In such a case, the oil may adhere to the heat transfer surfaces of the heat exchangers such as the condenser and the evaporator in the external refrigerant circuit, which may cause a reduction in heat exchange efficiency. Further, when a large amount of oil in the compressor is taken out to the external refrigerant circuit, the amount of oil in the compressor may be reduced, and lubrication of the sliding portion may be insufficient.

In order to solve such a problem, for example, JP-A-2-308986 (hereinafter, referred to as a first publication), JP-A-7-332239 (hereinafter, referred to as a second publication), etc. Has been proposed. In the compressor described in the first publication, a cylindrical oil separating member is disposed in the compressed refrigerant gas flow in the discharge muffler chamber. In the compressor described in the second publication, a cylindrical oil separating member is disposed near the opening of the discharge passage to the external refrigerant circuit in the discharge chamber.

[0004]

By the way, in the compressor described in the first publication, the oil separating member is provided between the discharge passage for the refrigerant gas from the discharge chamber and the supply passage for the refrigerant gas to the external refrigerant circuit. It is provided between them. That is, the compressed refrigerant gas from the discharge chamber is once introduced into the discharge muffler chamber,
The oil is separated by the oil separating member and discharged to the external refrigerant circuit. Therefore, the flow of the compressed refrigerant gas may be hardly swirled along the oil separating member due to the influence of the shape of the discharge muffler chamber, and the oil may not be sufficiently separated from the compressed refrigerant gas. was there.

On the other hand, in the compressor described in the second publication, a discharge muffler chamber for guiding a compressed refrigerant gas is not formed in a housing. Therefore, in order to reduce the pulsation of the discharged compressed refrigerant gas, it is necessary to separately provide a discharge muffler in the piping of the external refrigerant circuit. As a result, the entire structure of the refrigeration circuit including the compressor becomes large, and the piping structure may become complicated.

[0006] The present invention has been made to solve the problems of the conventional technology and to achieve further optimization. An object of the present invention is to provide a compressor that can efficiently separate oil in compressed refrigerant gas discharged to an external refrigerant circuit without increasing the size of the entire configuration of the refrigeration circuit.

[0007]

In order to achieve the above object, according to the first aspect of the present invention, a working chamber whose volume is changed in conjunction with rotation of a drive shaft is provided in a housing;
A discharge chamber communicated with the working chamber via a discharge valve mechanism is formed so that the refrigerant gas compressed according to a change in the volume of the working chamber is discharged to an external refrigerant circuit through the discharge chamber. In the compressor, a discharge muffler chamber communicated with the discharge chamber via a discharge passage is formed in the housing, and an oil separator is provided in the discharge muffler chamber. The oil separator serves as a supply port for refrigerant gas. It is connected to the discharge passage and has an outlet for the refrigerant gas opened into the discharge muffler chamber.

According to a second aspect of the present invention, in the compressor according to the first aspect, the cylinder blocks forming a part of the housing are formed to form a pair at the front and rear, and a crank chamber is provided between the cylinder blocks. A cam plate is fixed to the drive shaft in the crank chamber, a double-headed piston is connected to the outer periphery of the cam plate, and a plurality of cylinder bores are formed in the cylinder block so as to be parallel to each other. The working chamber is partitioned and formed in the cylinder bore so as to form a pair at the front and rear, with the piston being reciprocally accommodated.

According to a third aspect of the present invention, in the compressor according to the second aspect, the discharge passages are formed so as to form a pair in front and rear, and at least one of the discharge passages is connected to the oil separator.

[0010] According to the invention described in claim 4, claims 1 to 3 are provided.
In the compressor according to any one of the above, the oil separator includes a refrigerant gas introduction part, a refrigerant gas discharge part, and a separation member disposed therein.

According to a fifth aspect of the present invention, in the compressor according to the fourth aspect, the separating member comprises a centrifugal separator. According to a sixth aspect of the present invention, in the compressor according to any one of the third to fifth aspects, the refrigerant gas introduction portion is formed so as to correspond to the pair of discharge passages, and one of the refrigerant gas introduction portions is formed. Into the opening of the opposed discharge passage, and the supply port of the other refrigerant gas introduction unit is disposed so as to be substantially continuous with the opening of the opposed discharge passage, so that the front side and the rear side The refrigerant gas is merged in the oil separator.

According to a seventh aspect of the present invention, in the compressor according to the sixth aspect, the respective refrigerant gas introduction portions respectively corresponding to the front and rear discharge passages are directed in mutually different directions into the centrifugal separator. It is an opening.

Therefore, in the compressor according to the first to third aspects, since the discharge muffler chamber is defined in the housing, there is no need to provide a separate discharge muffler in the piping of the external refrigerant circuit. In addition, an oil separator for separating oil from the compressed refrigerant gas supplied into the external refrigerant circuit is disposed in the discharge muffler chamber. Therefore, by providing the oil separator, a part of the outer shape of the housing does not protrude, and the compressor does not increase in size. And the whole structure of a refrigeration circuit including a compressor does not become large and a piping structure does not become complicated.

Also, since the supply port of the compressed refrigerant gas of the oil separator is connected to the discharge passage, the refrigerant gas in the discharge chamber is directly guided from the discharge passage to the oil separator. For this reason, oil separation can be reliably and efficiently performed in the oil separator without being affected by the shape of the discharge muffler chamber.

In the compressor according to the fourth aspect of the present invention, the refrigerant gas can be reliably guided to the separation member inside the oil separator via the refrigerant gas introduction part by the oil separator having a simple structure.

In the compressor according to the fifth aspect, the refrigerant gas in the discharge chamber is supplied from the discharge passage and the refrigerant gas introduction portion.
Guided directly to the centrifuge, a strong swirling flow is generated in the oil separator. Therefore, the mist-like oil dispersed in the compressed refrigerant gas is efficiently separated. Moreover,
The pressure loss when the compressed refrigerant gas passes through the oil separator can be reduced.

In the compressor according to the present invention, the compressed refrigerant gas from the front side and the rear side is merged in the oil separator. For this reason, the oil dispersed in the compressed refrigerant gas from both sides can be separated by one oil separator, so that an increase in the number of parts can be suppressed and the configuration can be simplified.

In the compressor according to the present invention, each of the refrigerant gas introduction portions corresponding to the front and rear discharge passages is opened in the centrifugal separator in a different direction. Therefore, the compressed refrigerant gas from both discharge passages is smoothly swirled without colliding with each other, and the oil is efficiently separated.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is embodied in a double-headed piston type compressor using a swash plate as a cam plate will be described below with reference to FIGS.

As shown in FIG. 3, a front cylinder block 21 and a rear cylinder block 22 are joined at a central portion. A front housing 24 is joined to a front end surface of the cylinder block 21 via a valve plate 23. A rear housing 25 is joined to a rear end surface of the cylinder block 22 via a valve plate 23. The cylinder blocks 21 and 22, the front housing 24, the rear housing 25, and the valve plate 23 are fastened and fixed to each other by a plurality of through bolts 26, thereby forming a compressor housing.

A plurality of cylinder bores 27 are formed through the cylinder blocks 21 and 22 so as to be parallel to each other. Inside each cylinder bore 27, a double-headed piston 28 is accommodated so as to be able to reciprocate. A pair of front and rear working chambers 29 is formed in each cylinder bore 27 between both ends of these pistons 28 and the valve plate 23.

As shown in FIGS. 2 and 3, the valve plate 23 is formed with a suction valve mechanism 30 and a discharge valve mechanism 31 corresponding to each cylinder bore 27.
A substantially annular pressure partition 32 is formed in the front housing 24 and the rear housing 25, and the pressure partition 32 defines suction chambers 33 and 34 on the outer peripheral side in each of the housings 24 and 25. On the center side, discharge chambers 35 and 36 are defined. The suction chambers 33 and 34 can communicate with the working chamber 29 via the suction valve mechanism 30 formed on the valve plate 23. The discharge chambers 35 and 36 are connected to the working chamber 2 via the discharge valve mechanism 31 formed on the valve plate 23.
9 can be communicated.

A crank chamber 37 is formed at the center of the cylinder blocks 21 and 22. The drive shaft 38 is rotatably supported by the shaft holes 21 a and 22 a of the cylinder blocks 21 and 22 via a pair of radial bearings 39. A lip seal 24b is interposed between the outer peripheral surface near the front end of the drive shaft 38 and the inner peripheral surface of the opening 24a of the front housing 24 to suppress leakage of refrigerant gas from inside the compressor. The drive shaft 38 is rotated by an external drive source such as a vehicle engine via a clutch (not shown).

On the intermediate outer peripheral portion of the drive shaft 38,
A swash plate 40 as a cam plate is fitted and fixed.
On the swash plate 40, the piston 28 has a pair of shoes 4
1 and is rotated by rotation of the swash plate 40 so that the piston 2
8 is reciprocated in the cylinder bore 27. The swash plate 4
The boss portion 40a of No. 0 passes through a pair of thrust bearings 42,
Cylinder blocks 21 and 22 forming crank chamber 37
It is supported on the front and rear side walls.

As shown in FIGS. 1 to 3, the crank chamber 37 is connected to the suction chamber 3 through a suction passage 43 formed in the cylinder blocks 21 and 22 and the valve plate 23.
It is communicated with 3,34. The crank chamber 37 is connected to an external refrigerant circuit 45 via a suction port 44 formed in the cylinder block 22. Further, the discharge chamber 35,
36 is the valve plate 23 and the cylinder block 2
The discharge muffler chamber 48 defined above the cylinder blocks 21 and 22 is communicated via discharge passages 46 and 47 formed in the cylinder blocks 21 and 22, respectively. The discharge muffler chamber 48
It is connected to an external refrigerant circuit 45 via a discharge port 49. The condenser 50, the expansion valve 51, and the evaporator 52 are connected to the external refrigerant circuit 45.

As shown in FIGS. 1 and 3 to 5, an oil separator 53 is provided in the discharge muffler chamber 48. The oil separator 53 has a substantially cylindrical shape with a bottom, and a pair of refrigerant gas introduction portions 54 and 55 project from the base end thereof. Refrigerant gas supply ports 54a, 55a are opened at the distal ends of the refrigerant gas introduction sections 54, 55. The distal end of the cylindrical refrigerant gas outlet 56 serves as a refrigerant gas outlet 56 a, which is open into the discharge muffler chamber 48. A cylindrical swirl shaft 57 is inserted into the refrigerant gas outlet 56, and a cylindrical swirl passage 58 is provided between the inner peripheral surface of the refrigerant gas outlet 56 and the outer peripheral surface of the swivel shaft 57. Are formed to constitute a centrifugal separator 59 as a separating member. A plurality of through holes 60 are provided at the bottom of the oil separator 53.

The front-side refrigerant gas introduction section 54 is press-fitted into the opening of the front-side discharge passage 46. On the other hand, the rear-side refrigerant gas introduction section 55 is arranged such that its opening is substantially continuous with the opening of the rear-side discharge passage 47. Thereby, both refrigerant gas introduction parts 54,
55, the supply ports 54a, 55a
6, 47.

As shown in FIGS. 1 and 4, between the oil separator 53 and the first bolt hole 62 adjacent to the oil separator 53 on the joint end faces of the front and rear cylinder blocks 21 and 22. Is formed with a rough surface 61. The rough surface 61 forms a gap having a predetermined degree of throttle between the oil separator 53 and the first bolt hole 62 in a state where the two cylinder blocks 21 and 22 are joined. The first bolt hole 62 communicates with a first oil supply groove 63 formed in the rear end surface of the rear cylinder block 22, and communicates with the oil storage chamber 64 through the first oil supply groove 63.

The oil storage chamber 64 includes the rear cylinder block 2
Bottomed cylindrical sleeve 65 fitted into the second shaft hole 22a
Inside, it is formed at the center of the valve plate 23 and the rear housing 25. The oil storage chamber 64 communicates with the shaft hole 22 a of the rear cylinder block 22 via a communication hole 66 formed in the sleeve 65. In addition, the oil storage chamber 64
Are connected to the cylinder block 2 via a second oil supply groove 67 formed in the rear end face of the rear cylinder block 22.
1, 22 are connected to the second bolt hole 68 at the lower end. The second bolt hole 68 is formed in the front cylinder block 21 via a third oil supply groove 69 formed in the front end surface of the front cylinder block 21.
Of the shaft hole 21a. That is, the oil storage chamber 6
4 communicates with the shaft hole 21 a of the front cylinder block 21.

Next, the operation of the double-headed piston type compressor constructed as described above will be described. When the drive shaft 38 is rotated by an external drive source such as a vehicle engine, the swash plate 40 in the crank chamber 37 is rotated, and the plurality of pistons 28 reciprocate in the cylinder bore 27 via the shoes 41. By the movement of the piston 28, the refrigerant gas guided from the external refrigerant circuit 45 to the crank chamber 37 via the suction port 44 is guided from the crank chamber 37 to the suction chambers 33 and 34 via the suction passage 43. In the re-expansion and suction stroke of the piston 28 from the top dead center to the bottom dead center, the working chamber 29
With the pressure drop, the refrigerant gas in the suction chambers 33 and 34
It is sucked into the working chamber 29 via the suction valve mechanism 30. Next, in the compression / discharge stroke in which the piston 28 moves from the bottom dead center to the top dead center, after the refrigerant gas in the working chamber 29 is compressed to reach a predetermined pressure, the discharge chamber 35 is discharged through the discharge valve mechanism 31. , 36.

The compressed refrigerant gas discharged into the discharge chambers 35 and 36 is directly guided into the refrigerant gas introduction portions 54 and 55 of the oil separator 53 through the discharge passages 46 and 47. The compressed refrigerant gas from the front-side and rear-side discharge passages 46 and 47 guided to the refrigerant gas introduction portions 54 and 55 first collides with the swirl shaft 57 and the flow direction is changed. Then, the compressed refrigerant gas from both sides is merged, and the flow direction is changed again.

The swirl path 5 of the refrigerant gas outlet 56
In the inside 8, the swirl is strongly swirled around the outer peripheral surface of the swivel shaft 57 without being affected by the shape of the discharge muffler chamber 48. In addition, the discharge passages 46 and 47 and the refrigerant gas introduction portions 54 and 55 serve as throttle passages, and when passing through them, the flow velocity of the compressed refrigerant gas is increased, and the swirling flow becomes stronger. With the swirling of the compressed refrigerant gas flow, oil dispersed in the refrigerant gas is separated by centrifugal force. Then, the compressed refrigerant gas from which the oil has been separated is discharged into the discharge muffler chamber 48 via the discharge port 56a. The compressed refrigerant gas in the discharge muffler chamber 48
The air is supplied to a condenser 50, an expansion valve 51, and an evaporator 52 forming an external refrigerant circuit 45 via the air conditioner 9, and is used for air conditioning in a vehicle compartment.

Here, the oil separated in the oil separator 53 is temporarily stored in the bottom of the discharge muffler chamber 48 through the through hole 60 on the bottom surface of the centrifuge 59. Here, the discharge muffler chamber 48 is a high-pressure discharge area,
The oil storage chamber 64 is a low pressure suction area. Due to this pressure difference, the oil stored in the bottom of the discharge muffler chamber 48 passes through the gap formed by the rough surface 61 on the joint end surfaces of the two cylinder blocks 21 and 22, the first bolt hole 62, and the first oil supply groove 63. Through the oil storage chamber 64 and stored.
A part of the lubricating oil in the oil storage chamber 64 is
Is supplied to the shaft hole 22a of the rear cylinder block 22 through the communication hole 66, and is used for lubrication and cooling of the rear radial bearing 39. Another part of the lubricating oil in the oil storage chamber 64 is supplied to the shaft hole 21a of the front cylinder block 21 via the second oil supply groove 67, the second bolt hole 68, and the third oil supply groove 69. Is done. Then, the lubrication and cooling of the radial bearing 39 on the front side and the lip seal 24 b in the front housing 24 are provided.

According to this embodiment configured as described above, the following effects can be obtained. (A) In the compressor of this embodiment, a discharge muffler chamber 48 is defined in the cylinder blocks 21 and 22. Therefore, there is no need to provide a separate discharge muffler in the piping of the external refrigerant circuit 45. In addition, since the oil separator 53 is disposed in the discharge muffler chamber 48, the provision of the oil separator 53 prevents a part of the outer shape of the compressor from protruding and the compressor from being enlarged. Therefore, the entire configuration of the refrigeration circuit including the compressor does not become large and the piping configuration does not become complicated.

Since the coolant gas supply ports 54a and 55a of the oil separator 53 are connected to the discharge passages 46 and 47, the refrigerant gas in the discharge chambers 35 and 36 flows directly from the discharge passages 46 and 47 to the oil separator 53. Guided inside. That is, almost all of the compressed refrigerant gas in the discharge chambers 35 and 36 is guided to the oil separator 53 through the discharge passages 46 and 47. Accordingly, oil separation can be performed reliably and efficiently in the oil separator 53 without being affected by the shape of the discharge muffler chamber 48.
As a result, the amount of oil taken out of the compressor to the external refrigerant circuit 45 is reduced, and the formation of an oil layer on the heat transfer surfaces of the heat exchanger such as the condenser 50 and the evaporator 52 in the external refrigerant circuit 45 is suppressed. Can be. And
A decrease in the heat exchange efficiency of these heat exchangers can be suppressed. Also, a large amount of oil in the compressor can be prevented from being taken out to the external refrigerant circuit 45, and the oil can be retained in the compressor.

(B) In the compressor of this embodiment, the oil separator 53 is provided with the refrigerant gas introduction portions 54 and 55.
And a refrigerant gas outlet 56 and a centrifugal separator 59 formed therein. Therefore, with a simple configuration, the compressed refrigerant gas from the discharge passages 46 and 47 can be reliably guided to the centrifugal separator 59 through the refrigerant gas introduction portions 54 and 55, and the centrifugal separator 59 has a strong swirl. A flow can be generated. Therefore, the oil dispersed in the mist state in the refrigerant gas can be reliably and efficiently separated.

Further, by employing a centrifugal separator as the separating member, the pressure loss when the compressed refrigerant gas passes through the oil separator 53 is suppressed to a small value. Therefore,
Power loss of the compressor can be reduced.

(C) In the compressor of this embodiment, the compressed refrigerant gas in the discharge chambers 35 and 36 is supplied to the discharge passage 4
The liquid is guided to the centrifugal separator 59 via 6, 47 and the refrigerant gas inlets 54, 55. For this reason, by the throttle effect in the discharge passages 46 and 47 and the refrigerant gas introduction parts 54 and 55,
The compressed refrigerant gas is supplied to the centrifugal separator 59 at an increased flow rate.
It is led to. Therefore, the compressed refrigerant gas is swirled more strongly in the centrifugal separator 59, and the oil can be separated more efficiently.

(D) In the compressor of this embodiment, the refrigerant gas from the front side and the rear side is merged in the oil separator 53. For this reason, the oil dispersed in the compressed refrigerant gas from both sides can be separated by one oil separator 53, so that an increase in the number of parts can be suppressed and the configuration can be simplified.

(E) In the compressor of this embodiment, the oil separator 53 is provided on the front side discharge passage 46.
Are supported by press-fitting. Therefore, there is no need for a separate supporting member, and there is no increase in the number of components.

(F) In the compressor of this embodiment, the oil separated in the oil separator 53 is collected in the oil storage chamber 64, and is used for lubrication and cooling of the radial bearings 39 and the lip seal 24b. ing. For this reason, the possibility that the amount of oil in the compressor decreases and the lubrication of the sliding portion tends to be insufficient is reduced. Therefore,
The durability of these sliding parts is improved, and thus the durability of the compressor is improved. (Another Example) The present invention can be embodied with the following modifications.

(1) As shown in FIG. 6, the refrigerant gas introduction part 54 on the front side and the refrigerant gas introduction part 55 on the rear side of the oil separator 53 are oriented in different directions from each other in the centrifuge 59. May be opened.

In the case of this alternative example (1), the compressed refrigerant gas from the two discharge passages 46 and 47 does not collide with each other in the centrifugal separator 59, and the inner peripheral surface of the refrigerant gas outlet portion 56 Is smoothly turned along. Then, the oil dispersed in the compressed refrigerant gas can be efficiently separated by the centrifugal force.

(2) As shown in FIG. 7, inside the refrigerant gas outlet 56 of the oil separator 53, on both sides of the openings of the refrigerant gas inlets 54 and 55, instead of the turning shaft 57 as a separating member, A plurality of filters 71 having air permeability may be arranged.

In the case of this alternative example (2), there are many opportunities for the material constituting the filter 71 to come into contact with the compressed refrigerant gas flow, and the oil dispersed in the compressed refrigerant gas is removed from the filter 71 at each contact. Adheres to Therefore, the oil separating ability of the oil separator 53 can be further improved.

(3) As shown in FIG. 8, a plurality of baffle plates 72 may be disposed inside the refrigerant gas outlet 56 of the oil separator 53 as a separating member instead of the rotating shaft 57.

In the case of this alternative example (3), the passage of the compressed refrigerant gas in the refrigerant gas outlet 56 is meandered by the baffle plate 72. For this reason, the flow direction of the compressed refrigerant gas passing through the refrigerant gas outlet 56 is repeatedly changed. When the flow direction is changed, the oil dispersed in the compressed refrigerant gas collides with and adheres to the opposed baffle plate 72 due to inertial force. Therefore,
The oil dispersed in the compressed refrigerant gas can be separated with a simple configuration.

(4) A gap is formed between the supply port 55a of the refrigerant gas inlet 55 on the rear side of the oil separator 53 and the opening of the discharge passage 47 on the rear side. With this configuration, it is easy to absorb the tolerance when the housing is assembled, and there is no need to strictly process each part, and the manufacturing cost can be reduced.

(5) Independent oil separators 53 may be connected to the front discharge passage 46 and the rear discharge passage 47, respectively. In this case, the discharge passage 4 in the refrigerant gas introduction portions 54 and 55 of the oil separator 53
6, 47, the refrigerant gas introduction portion 54 on the side not used for connection with the
55 may be omitted.

(6) The front discharge passage 46 and the rear discharge passage 47 are made continuous with each other, and a branch passage is provided at a connection portion between the discharge passages 46 and 47. An oil separator 53 is provided at the tip of the branch passage. You may connect.

(7) The present invention relates to a compressor different from the compressor described in the above embodiment, for example, a wave cam plate type double-headed piston type compressor, a single-headed piston type compressor, a wobble type compressor, The present invention may be embodied in a vane compressor, a scroll compressor, or the like.

Even with the constructions of the other examples (4) to (7), substantially the same effects as those of the above embodiment can be obtained. Next, a technical idea grasped by the above embodiment will be described.

(1) The compressor according to any one of claims 4 to 7, wherein the oil separator supports the refrigerant gas introduction part by press-fitting the opening of the opposed discharge passage.

With this configuration, there is no need to separately provide a member for supporting the oil separator, and the number of components does not increase.

[0055]

As described in detail above, the present invention has the following excellent effects. According to the first to third aspects of the present invention, it is not necessary to separately provide a discharge muffler in the piping of the external refrigerant circuit. Further, by providing the oil separator, a part of the outer shape of the housing does not protrude, and the compressor does not increase in size. Therefore, the entire configuration of the refrigeration circuit including the compressor does not become large and the piping configuration does not become complicated. Further, the oil separator can reliably and efficiently perform oil separation without being affected by the shape of the discharge muffler chamber.

According to the present invention, the compressed refrigerant gas is reliably guided to the separating member inside the oil separator via the refrigerant gas introduction portion by the oil separator having a simple structure, and the oil separation is reliably performed. It can be carried out.

According to the fifth aspect of the invention, a strong swirling flow is generated in the oil separator, and the oil dispersed in the refrigerant gas can be efficiently separated. According to the invention described in claim 6, an increase in the number of components can be suppressed, and the configuration can be simplified.

According to the seventh aspect of the present invention, the compressed refrigerant gas from the two discharge passages is smoothly swirled without colliding with each other, and the oil can be separated efficiently.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an entire compressor according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along line 2-2 of FIG. 1;

FIG. 3 is a sectional view taken along line 3-3 of FIG. 2;

FIG. 4 is a side view of the front side cylinder block as viewed from the rear side.

FIG. 5 is a plan sectional view showing an oil separator.

FIG. 6 is a sectional view showing an oil separator described in another example (1).

FIG. 7 is a sectional view showing an oil separator described in another example (2).

FIG. 8 is a sectional view showing an oil separator described in another example (3).

[Explanation of symbols]

21, 22: a cylinder block forming a part of the housing; 24, a front housing forming a part of the housing; 25, a rear housing forming a part of the housing; 27, a cylinder bore; 28, a piston; 29, a working chamber , 31 ... discharge valve mechanism, 35, 36 ... discharge chamber, 37 ...
Crank chamber, 38 drive shaft, 40 swash plate as cam plate, 45 external refrigerant circuit, 46, 47 discharge passage, 48 discharge muffler chamber, 53 oil separator,
54, 55 ... refrigerant gas introduction part, 54a, 55a ... supply port, 56 ... refrigerant gas outlet part, 56a ... discharge port, 59 ... centrifugal separator constituting a separation member, 71 ... filter constituting a separation member, 72 ... A baffle that constitutes a separating member.

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Masanobu Yokoi 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation

Claims (7)

[Claims] 1. A working chamber in which a volume is changed in conjunction with rotation of a drive shaft and a discharge chamber communicated with the working chamber via a discharge valve mechanism in the housing. A compressor that discharges a refrigerant gas compressed according to a change in volume of the refrigerant to an external refrigerant circuit through the discharge chamber, wherein the discharge muffler communicates with the discharge chamber through the discharge passage in the housing. A compressor in which a chamber is defined, an oil separator is provided in the discharge muffler chamber, and the oil separator has a refrigerant gas supply port connected to the discharge passage and a refrigerant gas discharge port opened in the discharge muffler chamber. 2. A cylinder block constituting a part of the housing is formed so as to form a pair in front and rear, a crank chamber is defined between the cylinder blocks, and a cam plate is stopped by the drive shaft in the crank chamber. A double-headed piston is connected to the outer periphery of the cam plate, a plurality of cylinder bores are arranged in the cylinder block so as to be parallel to each other, and the piston is accommodated in the cylinder bore so as to be able to reciprocate. The compressor according to claim 1, wherein the working chambers are formed so as to form a pair in front and rear. 3. The compressor according to claim 2, wherein the discharge passages are formed so as to form a pair at the front and rear, and at least one of the discharge passages is connected to the oil separator. 4. The compressor according to claim 1, wherein the oil separator includes a refrigerant gas introduction part, a refrigerant gas discharge part, and a separation member disposed therein. 5. The compressor according to claim 4, wherein said separation member comprises a centrifuge. 6. The refrigerant gas introduction portion is formed so as to correspond to the pair of discharge passages, and one of the refrigerant gas introduction portions is inserted into an opening of the opposed discharge passage, and the other refrigerant gas introduction portion. The refrigerant gas from the front side and the rear side is merged in the oil separator by arranging the supply port of the section so as to be substantially continuous with the opening of the opposed discharge passage. A compressor according to any of the claims. 7. The compressor according to claim 6, wherein the respective refrigerant gas introduction portions respectively corresponding to the front and rear discharge passages are opened in the centrifugal separator in directions different from each other.