JPH10115288A - Double head cam type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently ensure a setting space of an oil separator also perform efficient oil separation by making the most of a feature of double head type, in a double head cam type compressor of oil separator built-in type. SOLUTION: In an outer side of a side wall 14b of a housing 14, an oil separating chamber 50 is successively provided in line, in the inside of the oil separating chamber 50, an oil separator 55 separating lubricating oil contained in compressed gas is arranged, in a side wall (cover plate 52) of the oil separating chamber 50, a delivery port 57, separating lubricating oil by the oil separator 55 for delivering compressed gas to an external refrigerant circuit, is provided. Compressed gass communication passages 47, 48, respectively individually connecting a front/rear housing side delivery chamber 28A, 28B to the oil separating chamber 50, are constituted to be opened. The oil separator is formed in a centrifugal separating type, the oil separating chamber 50 is formed to be partitioned into an inlet side chamber 53 introducing compressed gas by separating walls 51b, 51c and an outlet side chamber 54 discharging compressed gas after separating oil.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double-headed cam compression system in which a front housing and a rear housing having a suction chamber and a discharge chamber are joined to front and rear end surfaces of a cylinder block having a plurality of cylinder bores for housing pistons formed in parallel with each other. More particularly, the present invention relates to a double-head cam type compressor such as a double-head swash plate type compressor incorporating a compressed gas oil separator.

[0002]

2. Description of the Related Art In a conventional double-headed cam type compressor, for example, in a double-headed swash plate type compressor used for an air conditioner for a vehicle, lubricating oil supplied to a movable portion is mist-like in a refrigerant gas in the compressor. Are mixed. Therefore, the mist-like lubricating oil is discharged to the refrigerant circuit together with the compressed gas (high-pressure refrigerant gas) discharged from the compressor. Therefore, the initial amount of lubricating oil must be many times the amount required only for lubrication, and the amount depends on the length of the refrigerant circuit and the portion of the refrigerant circuit where lubrication oil is likely to stagnate. It fluctuates depending on the presence or absence, and it is necessary to determine the amount of lubricating oil charged for each refrigeration system. Further, when the lubricating oil is contained in the refrigerant and discharged into the refrigerant circuit, the lubricating oil adheres to the inner wall of the heat exchanger, causing a reduction in heat exchange efficiency.

For this reason, in a conventional apparatus using a double-headed swash plate type compressor (for example, an air conditioner for a vehicle), an oil separator is provided in a high-pressure circuit from the compressor to the condenser to return the separated lubricating oil. Although it has been put into practical use to return to the compression chamber via oil piping, it requires additional equipment and piping, which complicates the refrigerant circuit, increasing the required space and increasing costs. In addition, the return oil piping becomes long,
There was a risk of accidents such as clogging. For this reason, there has been proposed a compressor having a built-in oil separator in a double-headed swash plate compressor. An example of this is disclosed in JP-A-7-332.
239 publication.

[0004]

However, this double-headed swash plate type compressor with a built-in oil separator has an oil separation mechanism (oil separator in the present application) installed in discharge chambers formed in a front housing and a rear housing. However, since the outer cylinder and the inner cylinder of the oil separation mechanism are provided in the direction of the drive shaft of the compressor, the length of these cylindrical bodies cannot be sufficiently taken, so that they have to be shortened. Therefore, it is difficult to increase the oil separation efficiency. Further, since the oil separation mechanism is provided in each of the discharge chambers of the two housings, the apparatus becomes complicated, and the double-headed feature that the compressed gas is discharged separately from front and rear does not take advantage of this point. There was still room for improvement. The present invention has been made from such a viewpoint, and in a double-headed cam compressor with a built-in oil separator,
An object of the present invention is to secure a sufficient space for installing an oil separator and to perform efficient oil separation by utilizing the characteristics of a double-headed type.

[0005]

In order to achieve the above object, an invention according to claim 1 is characterized in that a plurality of cylinder bores for accommodating a piston are formed in a front and rear end face of a cylinder block in parallel with each other. In a double-headed cam type compressor in which a front housing and a rear housing each having a chamber are joined to each other, an oil separation chamber is continuously provided outside a side wall of the rear housing, and lubricating oil contained in refrigerant gas is separated inside the oil separation chamber. And an outlet for discharging the compressed gas from which the lubricating oil has been separated by the oil separator to an external refrigerant circuit is provided on a side wall of the oil separator. The chamber and the discharge chamber on the rear housing side each separately constitute a compressed gas communication passage communicating with the oil separation chamber, and the compressed gas communication passage is separately provided in the oil separation chamber. Characterized in that was opened.

According to a second aspect of the present invention, the oil separator is a centrifugal separator, and the oil separation chamber houses the inlet side chamber through which a compressed gas is introduced from the discharge chamber by a separation wall, and the oil separator. And an outlet side chamber for discharging the compressed gas after the lubricating oil is separated by the oil separator, and an inlet hole of the oil separator is communicated with the inlet side chamber.

The invention according to claim 3 is characterized in that an inlet hole of the oil separator is located at an intermediate position between openings of the compressed gas communication passages.

The invention according to claim 4 is characterized in that a lower part of the oil separation chamber is an oil storage chamber.

The invention according to claim 5 is characterized in that a partition plate for allowing the passage of lubricating oil is provided at a lower portion of the oil separation chamber, and a portion below the partition plate is formed as an oil storage chamber.

According to a sixth aspect of the present invention, the peripheral wall and one side wall of the oil separation chamber are formed integrally with the rear housing, and the other side wall of the oil separation chamber is formed separately from the rear housing. It is characterized by having done.

In the double-headed cam compressor according to the first and second aspects of the present invention, the oil separation chamber is provided outside the side wall of the rear housing, so that the oil separation chamber is installed in the oil separation chamber. As the oil separator, it is possible to select an oil separator having a high oil separation efficiency with reduced space restrictions. Also,
The compressed gas flowing into the oil separation chamber from the front housing side discharge chamber and the rear housing side discharge chamber is separated into oil in the oil separation chamber by the expansion action, and the compressed gas flowing from the front housing side and the compression gas flowing from the rear housing side. Oil separation by the action of collision with gas, and in the apparatus according to claim 2, the impingement flow is guided to a centrifugal type oil separator, and the swirling flow of the compressed gas in the oil separator is accelerated to perform centrifugal separation. By improving the oil separation efficiency by improving the action, highly efficient oil separation is performed. Therefore, when the compressor is operated, the compressed gas discharged from the cylinder bore into the discharge chamber is introduced into the oil separation chamber from the compressed gas communication passage, and is separated with high efficiency in the oil separation chamber. Is discharged to an external refrigerant circuit from a discharge port provided on a side wall of the liquid crystal display. Then, the separated lubricating oil is stored in the oil sump chamber, and is supplied from the oil sump chamber to a portion requiring lubrication as lubricating oil. For this reason, the release of the lubricating oil to the external refrigerant pipe is sufficiently prevented, and the above-described problem in the case where the lubricating oil is discharged to the refrigerant circuit, that is, the increase or fluctuation of the initial filling amount of the lubricating oil is prevented, and the heat is prevented. Adhesion of lubricating oil to the inner wall of the heat exchanger, which causes a decrease in the capacity of the exchanger, is sufficiently prevented. Further, since the oil separator is built in the compressor as described above, there is no need to add equipment or refrigerant piping to the refrigerant circuit as in the case where the oil separator is provided in the conventional high-pressure refrigerant circuit.

Further, in the double-headed cam type compressor according to the second aspect, only the compressed gas in the inlet side chamber is introduced into the oil separator, and only the compressed gas discharged from the oil separator is supplied to the inlet of the oil separator. Since all the liquid is discharged from the discharge port without reflux, the oil separation efficiency is further improved. Also, in the double-headed cam type compressor according to the third aspect, the compressed gas flowing from the front housing side and the compressed gas flowing from the rear housing collide efficiently, and the oil separation efficiency due to the collision is improved. Also, in the double-headed cam type compressor according to the fourth aspect, the lower part of the oil separation chamber is an oil storage chamber, and the space is effectively used. Further, in the double-headed cam compressor according to the fifth aspect, the lubricating oil stored in the oil reservoir is prevented from being hoisted by the compressed gas flow by the partition plate, and a decrease in oil separation efficiency is prevented. Further, in the double-headed cam type compressor according to the sixth aspect, since the main body of the oil separation chamber is formed integrally with the rear housing, the formation of the separation chamber is simplified.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is embodied in a double-headed swash plate type compressor which is a kind of a double-headed cam type compressor will be described in detail with reference to FIGS. As shown in FIG. 1, a gasket 34, a suction valve forming plate 33, a valve plate 13, a discharge valve forming plate 35, and a gasket 36 also serving as a retainer plate are provided at both ends of the cylinder block 11 opposed to the front and rear. The front housing 12 and the rear housing 14 are joined. An oil separation chamber 50 is integrally formed outside the side wall 14b of the rear housing 14 as described later. That is, the side wall 14b serves as one side wall of the oil separation chamber 50. These parts are fastened and fixed to both end surfaces of the cylinder block 11 by screwing a plurality of bolts 15 into the screw holes 16 of the rear housing 14.

At the center of the cylinder block 11 and the front housing 12, a pair of radial bearings 1 is provided.
8, a drive shaft 17 is rotatably supported, and an outer periphery of a front end of the drive shaft 17 and the front housing 12 are supported.
A lip seal 19 is interposed between the two. The drive shaft 17 is connected to an external drive source such as a vehicle engine (not shown), and is driven to rotate by the external drive source.

A plurality of cylinder bores 20 are formed through the cylinder block 11 at predetermined intervals on the same circumference between both ends of each cylinder block 11 so as to extend in parallel with the drive shaft 17. Inside, a double-headed piston 21 is inserted and supported so as to be able to reciprocate. A compression chamber 22 is formed in each cylinder bore 20 between the cylinder block 11 and the valve plate 13.

A crank chamber 23 is defined in the middle of the two cylinder blocks 11.
Inside, the swash plate 24 is fitted and fixed to the drive shaft 17. Further, at a plurality of locations on the outer peripheral portion of the swash plate 24, the front and rear surfaces of the swash plate 24 are moored to an intermediate portion of the piston 21 via a pair of hemispherical shoes 25, and when the drive shaft 17 is rotated, Piston 2 through swash plate 24
1 is reciprocated. A pair of thrust bearings 26 are interposed between both end faces of the swash plate 24 and inner end faces of the cylinder blocks 11, and the swash plate 24 is interposed between the two cylinder blocks 11 via the thrust bearing 26. It is clamped and held.

The suction chamber 27 and the front housing side discharge chamber 28A and the rear housing side discharge chamber 28B are formed in the outer peripheral part and the inner peripheral part in the housings 12 and 14 by annular partitions 12a and 14a. I have. The suction chamber 27 communicates with the crank chamber 23 via a suction passage 11a formed in the cylinder block 11, the gasket 34, the suction valve forming plate 33, the valve plate 13, and the gasket 36 also serving as a retainer plate. Are connected to an external refrigerant circuit via a suction port (not shown).

The front housing side discharge chamber 28A
Is connected to the oil separation chamber 50 via a cylinder block 11, a gasket 34, a suction valve forming plate 33, a valve plate 13, a gasket 36 also serving as a retainer plate, and a compressed gas communication passage 47 formed in the rear housing 14. . The compressed gas communication passage 47 is shown in FIGS. 3 and 2. The communication passage in the cylinder block 11, the gasket 34, the suction valve forming plate 33, the valve plate 13, and the gasket 36 also serving as a retainer plate is Although not shown in any of the drawings, these parts are provided at positions corresponding to the positions of the compressed gas communication passages 47 shown in FIGS. 2 and 3. The rear housing side discharge chamber 28B is provided between the rear housing 14 and the oil separation chamber 5.
It communicates with the oil separation chamber 50 via a compressed gas communication passage 48 provided in the side wall 14b of the rear housing 14 which forms a boundary wall with the oil separation chamber 50.

The two valve plates 13 are formed of a metal plate, and a suction port 31 and a discharge port 32 are formed at portions corresponding to the respective cylinder bores 20. The suction valve forming plate 33 and the discharge valve forming plate 35 are formed of a metal plate. The suction valve forming plate 33 has a suction valve 33a formed so as to face the suction port 31. Is formed with a discharge valve 35a so as to face the discharge port 32. The gasket 34 and the gasket 36 also serving as a retainer plate are formed by coating both sides of a metal plate (for example, a steel plate) with rubber, and the gasket 3 also serves as a retainer plate.
6, a retainer 40 is formed.

Next, the oil separation chamber 50 which is a characteristic part of the present invention will be described. 3 and FIG.
As shown in the figure, the main body 51 and a lid plate 52 as the other side wall of the oil separation chamber 50 are provided. The peripheral wall 51a of the oil separation chamber, which is the peripheral wall of the main body 51, is formed by extending the peripheral wall of the rear housing 14 as it is, and the sectional area of the oil separating chamber 50 and the sectional areas of the cylinder block 11 and the rear housing 14 are substantially equal. It has the same configuration. The interior of the main body 51 of the oil separation chamber 50 includes a vertical separation wall 51b and a horizontal separation wall 51b.
c, the inlet side chamber 53 for introducing compressed gas from the front housing side discharge chamber 28A and the rear housing side discharge chamber 28B, and the oil separator 55 are accommodated.
From the outlet side chamber 54, which receives the compressed gas discharged from the compressor and discharges the compressed gas to the external refrigerant circuit.

In the outlet side chamber 54, a centrifugal oil separator 55 made of a cylindrical body is provided. The tubular body of the oil separator is attached by welding or the like with the inlet hole closely contacting the upper surface side of the inclined wall at the junction of the vertical separation wall 51b and the horizontal separation wall 51c. A communication hole 56 is provided in the inclined wall in accordance with the inlet hole of the oil separator 55, and the inlet hole of the oil separator 55 communicates with the inlet-side chamber 53. Also,
The cover plate 52 is provided with a discharge port 57 at the side of the opening end of the oil separator 55, and the oil separation chamber 50 is connected to an external refrigerant pipe via the discharge port 57.

On the other hand, the compressed gas communication passages 47 and 48 are opened at separate positions in the inlet side chamber 53.
The compressed gas communication passage 47 is provided on the upper side of the vertical separation wall 51b,
Further, the compressed gas communication passage 48 is opened below the horizontal separation wall 51c, and is formed so that the inlet hole of the oil separator 55 is located in the middle thereof. An arc-shaped protruding wall 51d connected to the horizontal separation wall 51c is provided on a side peripheral wall 51a of the entrance-side chamber 53, and a lid plate 52 of the protruding wall 51d is provided.
An oil groove 60 whose upper end is open to the outlet side chamber 54 is formed in the side end surface. A partition plate 59 such as a wire mesh, a metal lath, or a punching metal (a plate with a round hole, a slit, or the like) is formed below the inlet side chamber 53, that is, below the compressed gas communication passage 48. An oil reservoir chamber 58 is sandwiched between the lid plate 52 and a lower portion thereof. An oil return port 63 communicating with the screw hole 16 of the fastening bolt 15 is provided in the side wall 14 b of the rear housing 14 in the oil sump chamber 58 portion, and opens to the oil sump chamber 58.

The peripheral wall 51a, the vertical separation wall 51b, the horizontal separation wall 51c, and the protruding wall 51d of the main body 51 are provided.
Are formed integrally with the rear housing 14 by casting. The cover plate 52 is detachably and air-tightly attached to an end surface of the main body 51 by a bolt nut 61 via an O-ring 52a.

The double-headed swash plate type compressor of the present embodiment is constructed as described above, and each piston 21 is connected to each cylinder bore 20 through the swash plate 24 by the rotation of the drive shaft 17.
The refrigerant gas is reciprocated inside, whereby the refrigerant gas is sucked and compressed. The compressed gas compressed in the cylinder bore 20 is discharged to the front housing side discharge chamber 28A and the rear housing side discharge chamber 28B. The compressed gas discharged to the front housing-side discharge chamber 28A passes through the compressed gas communication passage 47, and the compressed gas discharged to the rear housing side discharge chamber 28B passes through the compressed gas communication passage 48. Each of them is separately led to 50 inlet-side chambers 53.

Both compressed gases are supplied to the inlet side chamber 5 which is a large space.
3, the lubricating oil contained in the compressed gas is separated. Also, as indicated by the dotted arrows in FIG. 3, the vertical separation wall 51b and the horizontal separation wall 51c flow toward the communication hole 56 as a guide plate and collide near the entrance of the communication hole 56, and the collision causes lubrication in the compressed gas. Oil is separated. The mixed compressed gas flow colliding near the inlet of the communication hole is guided to the oil separator 55 through the communication hole 56 and swirled in the oil separator 55. The speed of the swirling flow in the separator 55 is increased. In the oil separator 55, the mist-like lubricating oil having a large mass contained in the compressed gas is formed on the inner wall of the cylindrical body of the oil separator 55 by the centrifugal force of the accelerated swirling flow of the compressed gas. Be splattered. The scattered lubricating oil flows down the inner wall of the oil separator 55, drops from the communication hole 56, passes through the partition plate 59, and is collected and stored in the oil storage chamber 58. The lubricating oil in the oil sump chamber 58 is returned to the crank chamber 23 through the oil return port 63 and the screw hole 16 due to the pressure difference between the oil sump chamber 58 and the crank chamber 23 communicating with the inlet side chamber 53, and Provided for lubrication.

On the other hand, the compressed gas that has left the oil separator 55 is discharged to the external refrigerant circuit through the outlet chamber 54 and the discharge port 57. At this time, the compressed gas is supplied to the peripheral wall 51 of the outlet side chamber 54.
There is a possibility that the lubricating oil remaining in the compressed gas may be further separated by colliding with the inner surface of a, or undergoing a slight expansion action in the outlet side chamber 54. The oil drops down along the inner wall of the outlet side chamber 54 and is collected in the oil storage chamber 58 via the oil groove 60 provided in the protruding wall 51d.

According to the present embodiment configured as described above, the following excellent effects can be obtained. (1) In the refrigerant circuit using the double-headed swash plate type compressor of the present embodiment, since the oil separator 55 is built in the compressor,
Compared to a conventional refrigerant circuit in which an oil separator is provided, the refrigerant circuit is simplified because it is not necessary to provide any equipment or piping. Therefore, the space required for an application device such as an air conditioner to which the double-head swash plate type compressor is applied can be reduced, and the cost can be reduced. (2) Since the main body 51 of the oil separation chamber 50 in which the oil separator 55 is built is integrally formed with the conventional rear housing 14, the structure in which the oil separator 55 is built in the compressor does not become complicated. .

(3) The oil separation chamber 50 has a shape in which the rear housing 14 is extended rearward as it is, and has a margin in space as compared with the conventional one, so that the oil separation chamber 50 is not much restricted by space restrictions. An oil separator with high oil separation efficiency can be built in. For example, in the case of the oil separator according to the present embodiment, the length and diameter of the cylindrical body can be set to a sufficient size. Therefore, the oil separator 55 having high separation efficiency can be built in the double-headed swash plate compressor.

(4) Front housing side discharge chamber 28
A and the oil separation chamber 5 from the rear housing side discharge chamber 28B.
The oil separation efficiency of the compressed gas introduced into the
The oil separation by the expansion action in the inside, the oil separation by the collision action of these compressed gases, and the collision of the compressed gas increase the speed of the swirling flow in the oil separator to improve the oil separation efficiency. As a result, the lubricating oil content in the compressed gas discharged to the refrigerant circuit is reduced as compared with the conventional compressor with a built-in oil separator, and therefore the amount of lubricating oil adhering to the inner wall of the heat exchanger is also reduced. , The performance of the heat exchanger is improved.

(5) The inside of the oil separation chamber 50 is a vertical separation wall 5
1b and the horizontal separation wall 51c, the inlet side chamber 53 for introducing the compressed gas from the front housing side discharge chamber 28A and the rear housing side discharge chamber 28B, and the oil separator 55 are housed and discharged from the oil separator 55. The compressed gas discharged from the oil separator is introduced into the oil separator, and the compressed gas discharged from the oil separator is divided into the outlet chamber that receives the compressed gas and discharges the compressed gas to the external refrigerant circuit. Only the oil is discharged from the discharge port without being returned to the inlet side of the oil separator, and the oil separation efficiency is further improved. (6) The compressed gas separately introduced into the oil separation chamber 50 from the front housing side discharge chamber 28A and the rear housing side discharge chamber 28B flows into the inlet hole of the oil separator 55 using the separation walls 51b and 51c as guide walls. Therefore, the collision of the compressed gas is performed efficiently, and the oil separation efficiency due to the collision is improved.

(7) Since the oil reservoir chamber 58 is provided below the inlet side chamber 53, that is, below the compressed gas communication passage 48, the space can be effectively used. (9) Since the upper surface of the oil reservoir 58 is defined by a partition plate such as a wire mesh, a slit plate, or a perforated plate, the lubricating oil stored in the oil reservoir 58 is taken up by the compressed gas and scattered again. Thus, the oil separation efficiency is prevented from lowering. (10) Since the oil sump chamber 58 is returned to the crank chamber 23 via the screw holes 16 of the fastening bolts 15 for fastening the housings 12, 14 and the cylinder block 11, etc., the oil return path is simplified, and the oil return path is simplified. The man-hours and costs for providing are reduced. In addition, since the annular gap formed between the inner surface of the screw hole in the screw hole 16 and the outer surface of the fastening bolt 15 serves as an oil passage, this return oil passage can be said to be a structure that is unlikely to cause dust clogging.

The present invention can be embodied with the following modifications. (1) The present invention is embodied in a double-headed swash plate type compressor, but may be embodied in a double-headed web cam compressor. (2) The separation wall between the inlet-side chamber 53 and the outlet-side chamber 54 in the oil separation chamber 50 includes a vertical separation wall 51 b and a horizontal separation wall 5.
Instead of 1c, an appropriate configuration such as only a horizontal separation wall or only an arc-shaped separation wall can be adopted. The shape of the separation wall is such that the compressed gas flowing from the two compressed gas communication passages 47 and 48 can be efficiently collided with the oil separator 5.
Those which can be guided to the entrance hole of No. 5, that is, to the communication hole are preferable. (3) In the oil separation chamber 50, the outlet side chamber 54 can be widened, or the oil separator 55 can have another structure. For example, a centrifugal separation type oil separator having a tubular body longer than that of the present embodiment is disposed horizontally or obliquely with the upper half of the oil separation chamber 50 as the outlet side chamber only by the horizontal separation wall. Can be.

(4) The lubricating oil collected in the outlet side chamber 54 of the oil separation chamber 50 is changed to an oil groove 60 for collecting the oil in the oil storage chamber 58, and the protruding wall 51d is abolished. A through hole may be provided at the joint.

(5) The screw hole 16 is not used as the oil return passage, but communicates with a shaft hole passing through the drive shaft 17 of the cylinder block 11 through another type of passage, for example, the rear housing 14, the valve plate 13, and the like. A separate passage may be provided, and the gas may be returned to the crank chamber 23 through the shaft hole. (6) According to the first to fifth aspects of the present invention, the oil separation chamber 50 is formed separately from the rear housing 14 and is connected to the rear housing 14 by appropriate means such as bolts and nuts. Is also good.

[0035]

Since the present invention is configured as described above, the following effects can be obtained. According to the first aspect of the present invention, the space limitation of the oil separator built in the double-headed cam type compressor is eased, and it becomes easy to install an efficient oil separator. The compressed gas introduced from the front housing side discharge chamber and the rear housing side discharge chamber into the oil separation chamber is separated into oil by expansion action in the oil separation chamber, oil separation by collision action of compressed gas flow, and oil separation in the oil separator. The oil separation efficiency is remarkably improved by improving the oil separation effect due to the speed of the swirling of the compressed gas affected by the collision effect. In addition, since an efficient oil separator is built in this way, without complicating the refrigerant circuit,
Lubricating oil discharged to the refrigerant circuit together with the compressed gas is reduced, and the heat exchange performance is improved. Further, the space and cost required for a device to which the double-head cam compressor is applied is reduced.

According to the second aspect of the invention, only the compressed gas in the inlet chamber is guided to the oil separator, and only the compressed gas discharged from the oil separator is discharged to the external refrigerant circuit.
Oil separation efficiency is further improved. According to the third aspect of the present invention, the collision of the compressed gas is performed efficiently. According to the invention described in claim 4, the space is effectively used. According to the fifth aspect of the present invention, re-scattering of the lubricating oil stored in the oil storage chamber due to hoisting is prevented, and a decrease in oil separation efficiency is prevented. According to the invention described in claim 6,
The formation of the oil separation chamber is simplified.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing an overall configuration of a double-headed swash plate type compressor according to an embodiment.

FIG. 2 is a sectional view taken along line AA in FIG.

FIG. 3 is a sectional view taken along the line BB in FIG. 1;

[Explanation of symbols]

11: cylinder block, 12: front housing,
14: Rear housing, 14b: Side wall of rear housing, 20: Cylinder bore, 21: Piston, 28A: Discharge chamber on the front housing side, 28B: Discharge chamber on the rear housing side, 47, 48: Compression gas communication passage, 50: Oil Separation chamber, 51 body, 51a peripheral wall, 51b vertical separation wall, 51c horizontal separation wall, 52 lid plate as a side wall of oil separation chamber, 53 inlet side chamber, 54 outlet side chamber, 55 oil separator , 56: communication hole, 57: discharge port, 58: oil reservoir,
59: partition plate, 60: oil groove, 63: oil return port.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Yuji Kaneshige 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation

Claims (6)

[Claims] 1. A double-headed cam compressor in which a front housing and a rear housing having a suction chamber and a discharge chamber are respectively joined to front and rear end faces of a cylinder block having a plurality of cylinder bores for housing pistons formed in parallel to each other. An oil separation chamber is continuously provided outside the side wall of the housing, an oil separator for separating lubricating oil contained in the refrigerant gas is provided inside the oil separation chamber, and the oil separator is provided on a side wall of the oil separation chamber. And a discharge port for discharging the compressed gas from which the lubricating oil has been separated to the external refrigerant circuit, and the front housing side discharge chamber and the rear housing side discharge chamber respectively communicate with the oil separation chamber separately. A double-headed cam compressor, wherein a compressed gas communication passage is formed, and the compressed gas communication passage is separately opened in the oil separation chamber. 2. The oil separator is of a centrifugal separation type, and the oil separation chamber houses the inlet side chamber through which a compressed gas is introduced from the discharge chamber by a separation wall, and the oil separator is housed by the oil separator. 2. The double-headed cam type compression according to claim 1, wherein a partition is formed between the lubricating oil and an outlet-side chamber for discharging a compressed gas after separation, and an inlet hole of the oil separator is connected to the inlet-side chamber. Machine. 3. The double-headed cam type compressor according to claim 1, wherein an inlet hole of said oil separator is located at an intermediate position between openings of said compressed gas communication passages. 4. The double-headed cam type compressor according to claim 1, wherein a lower part of said oil separation chamber is an oil sump chamber. 5. The double-headed cam type compressor according to claim 1, wherein a partition plate for allowing the passage of lubricating oil is provided at a lower portion of said oil separating chamber, and a lower portion thereof is formed as an oil reservoir chamber. 6. A peripheral wall and one side wall of the oil separation chamber are formed integrally with the rear housing, and the other side wall of the oil separation chamber is formed separately from the rear housing. The double-headed cam type compressor according to any one of claims 1 to 5.