JP3430818B2 - Double head cam compressor - Google Patents

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 type compression system in which a front and a rear housing having a suction chamber and a discharge chamber are joined to front and rear end faces of a cylinder block in which a plurality of cylinder bores for accommodating pistons are formed in parallel with each other. More particularly, the present invention relates to a double-headed cam compressor such as a double-headed swash plate compressor having a built-in oil separator for compressed gas.

[0002]

2. Description of the Related Art In a conventional double-headed cam type compressor, for example, a double-headed swash plate type compressor used in a vehicle air conditioner, the lubricating oil supplied to the moving parts is mist-like in the refrigerant gas in the compressor. Mixed in. 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 amount of the lubricating oil initially filled must be many times larger than the amount required only for lubrication, and the amount of the lubricating oil must be set in the length of the refrigerant circuit or in a portion of the refrigerant circuit where the lubricating oil is likely to stagnate. It varies depending on the presence or absence, and it is necessary to determine the amount of lubricating oil enclosed for each refrigeration system. Further, when the lubricating oil is contained in the refrigerant and is discharged into the refrigerant circuit, the lubricating oil adheres to the inner wall of the heat exchanger and causes a decrease in heat exchange efficiency.

Therefore, in a conventional device using a double-headed swash plate compressor (for example, a vehicle air conditioner), an oil separator is provided in the high pressure circuit from the compressor to the condenser, and the separated lubricating oil is returned. Although a device configured to return to the compression chamber via an oil pipe has been put to practical use, it requires additional equipment, piping, etc. and complicates the refrigerant circuit, increasing the required space and increasing the cost. In addition, the return oil pipe becomes long,
There was a risk of causing an accident such as clogging. For this reason, it has been proposed to incorporate an oil separator in the double-headed swash plate compressor. An example of this is Japanese Patent Laid-Open No. 7-332.
Some are listed in Japanese Patent No. 239.

[0004]

However, in this double-headed swash plate compressor with a built-in oil separator, the oil separation mechanism (the oil separator of the present invention) is installed in the discharge chambers formed in the front housing and the rear housing. However, since the outer cylinder and the inner cylinder of the oil separation mechanism are provided in the drive shaft direction of the compressor, the lengths of these cylindrical bodies cannot be taken sufficiently and must 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 both housings, the device becomes complicated, and the double-headed feature that the compressed gas is discharged separately at the front and rear is not utilized. But there was still room for improvement. The present invention has been made from such a point of view, and in an oil separator built-in double-headed cam type compressor,
The objective is to secure a sufficient installation space for the oil separator and to utilize the double-headed type characteristics to perform efficient oil separation.

[0005]

In order to achieve the above object, the present invention according to claim 1 provides a suction chamber and a discharge chamber at front and rear end surfaces of a cylinder block in which a plurality of cylinder bores for accommodating pistons are formed 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, an oil separation chamber is provided continuously outside the side wall of the rear housing, and lubricating oil contained in the refrigerant gas is separated inside the oil separation chamber. And an outlet for discharging the compressed gas, in which the lubricating oil is separated by the oil separator, to the external refrigerant circuit on the side wall of the oil separation chamber, and the discharge on the front housing side. The discharge chamber and the rear housing side discharge chamber, respectively, to form a compressed gas communication passage that communicates 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 of a centrifugal separation type, and the oil separation chamber accommodates the inlet side chamber for introducing the compressed gas from the discharge chamber through a separation wall and the oil separator. The oil separator separates the lubricating oil from the outlet side chamber that releases the compressed gas, and the inlet hole of the oil separator communicates with the inlet side chamber.

The invention according to claim 3 is characterized in that the inlet hole of the oil separator is located in the middle of the openings of both the compressed gas communication passages.

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

A fifth aspect of the present invention is characterized in that a partition plate that allows passage of lubricating oil is provided in a lower portion of the oil separation chamber, and a lower portion thereof is formed as an oil sump chamber.

According to the 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 type compressor according to the present invention configured as described above, since the oil separation chamber is connected to the outside of the side wall of the rear housing, it is installed in this oil separation chamber. As for the oil separator, it is possible to select one having a high oil separation efficiency because the space constraint is relaxed. Also,
The compressed gas that has flowed into the oil separation chamber from the front housing side discharge chamber and the rear housing side discharge chamber is subjected to oil separation due to the expansion action in the oil separation chamber, and the compressed gas that has flowed in from the front housing side and the compressed gas that has flowed in from the rear housing side. Separation of oil by collision with gas, and further according to claim 2, the collision flow is guided to a centrifugal separation type oil separator to accelerate the swirling flow of the compressed gas in the oil separation unit and to perform centrifugal separation. Highly efficient oil separation is achieved by improving the oil separation efficiency due to the improved action. 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, is highly efficiently separated in the oil separation chamber, and then is separated into the oil separation chamber. Is discharged to the external refrigerant circuit from the discharge port provided on the side wall of the. Then, the separated lubricating oil is stored in the oil sump chamber, and is supplied from this oil sump chamber to a portion where lubrication is required as lubricating oil. Therefore, the discharge of the lubricating oil to the external refrigerant pipe is sufficiently prevented, and the above-mentioned problem when the lubricating oil is discharged to the refrigerant circuit, that is, the increase or fluctuation of the initial sealed amount of the lubricating oil is prevented, Adhesion of lubricating oil to the inner wall of the heat exchanger, which causes deterioration of the capacity of the exchanger, is sufficiently prevented. Further, since the oil separator is built in the compressor as described above, it is not necessary to add a device or a refrigerant pipe to the refrigerant circuit unlike the conventional high pressure refrigerant circuit provided with the oil separator.

In the double-headed cam 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 enters the inlet of the oil separator. All the oil is discharged from the discharge port without recirculation, so that the oil separation efficiency is further improved. Further, in the double-headed cam compressor according to the third aspect, the compressed gas flowing from the front housing side and the compressed gas flowing from the rear housing efficiently collide with each other, and the oil separation efficiency due to the collision improves. In the double-headed cam compressor according to the fourth aspect of the present invention, the space below the oil separation chamber is used as an oil storage chamber, and the space is effectively used. Further, in the double-headed cam compressor according to the fifth aspect, the partition plate prevents the lubricating oil stored in the oil sump chamber from being taken up by the compressed gas flow, thereby preventing the oil separation efficiency from decreasing. Further, in the double-headed cam type compressor according to the sixth aspect, since the main body portion of the oil separation chamber is formed integrally with the rear housing, the formation of the separation chamber is simplified.

[0013]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments in which the present invention is embodied in a double-headed swash plate type compressor, which is a type of 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 which also serves as a retainer plate are interposed at both ends of the cylinder block 11 which is arranged in front and back, The front housing 12 and the rear housing 14 are joined together. An oil separation chamber 50 is integrally formed and connected to the outside of 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. Then, the plurality of bolts 15 are screwed into the screw holes 16 of the rear housing 14 so that these parts are fastened and fixed to both end surfaces of the cylinder block 11.

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 the outer periphery of the front end of the drive shaft 17 and the front housing 12
A lip seal 19 is interposed between and. The drive shaft 17 is connected to an external drive source such as a vehicle engine (not shown) and rotationally driven by the external drive source.

A plurality of cylinder bores 20 are formed in the cylinder block 11 so as to extend in parallel with the drive shaft 17, and are formed at both ends of each cylinder block 11 on the same circumference at predetermined intervals. A double-headed piston 21 is reciprocally fitted and supported therein. 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 both cylinder blocks 11, and the crank chamber 23 is formed.
Inside, a swash plate 24 is fitted and fixed to the drive shaft 17. Further, at a plurality of positions on the outer peripheral portion of the swash plate 24, when the front and rear surfaces of the swash plate 24 are moored to the intermediate portion of the piston 21 via a pair of hemispherical shoes 25, 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 surfaces of the swash plate 24 and the inner end surface of each cylinder block 11, and the swash plate 24 is interposed between the cylinder blocks 11 via the thrust bearings 26. It is sandwiched and held.

A suction chamber 27, a front housing-side discharge chamber 28A and a rear housing-side discharge chamber 28B are formed in an annular shape by partition walls 12a and 14a at the outer and inner peripheral portions of the two housings 12 and 14, respectively. There is. The suction chamber 27 is communicated with the crank chamber 23 through 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. , Is connected to an external refrigerant circuit via a suction port (not shown).

Further, the discharge chamber 28A on the front housing side
Is communicated with 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, and the communication passages 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 the retainer plate are 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. Further, the rear housing side discharge chamber 28B includes the rear housing 14 and the oil separation chamber 5.
It is communicated with the oil separation chamber 50 through a compressed gas communication passage 48 provided in the side wall 14b of the rear housing 14 which forms a boundary wall with the zero.

Both of the valve plates 13 are formed of a metal plate, and an intake port 31 and a discharge port 32 are formed in a portion corresponding to each cylinder bore 20. Further, the intake valve forming plate 33 and the discharge valve forming plate 35 are formed of metal plates, and the intake valve forming plate 33 is formed with an intake valve 33 a so as to face the intake port 31, and the discharge valve forming plate 35. A discharge valve 35 a is formed in the container so as to face the discharge port 32. The gasket 34 and the gasket 36 also serving as the retainer plate are formed by coating both sides of a metal plate (for example, a steel plate) with rubber.
A retainer 40 is formed at 6.

Next, the oil separation chamber 50, which is a characteristic part of the present invention, will be described. The oil separation chamber 50 is shown in FIGS.
As shown in FIG. 5, the main body 51 and the lid plate 52 as the other side wall of the oil separation chamber 50 are included. Further, the peripheral wall 51a of the oil separating chamber, which is the peripheral wall of the main body 51, has a form in which the peripheral wall of the rear housing 14 is extended as it is, and the cross-sectional area of the oil separating chamber 50 and the cross-sectional areas of the cylinder block 11 and the rear housing 14 are substantially the same. It has the same configuration. The inside of the main body 51 of the oil separation chamber 50 has a vertical separation wall 51b and a horizontal separation wall 51b.
With c, 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 the oil separator 55 is accommodated.
It is partitioned into an outlet side chamber 54 that receives the compressed gas discharged from the unit and discharges the compressed gas to the external refrigerant circuit.

A centrifugal separation type oil separator 55, which is a cylindrical body, is disposed in the outlet side chamber 54. The cylindrical body of the oil separator is attached by welding or the like with the inlet hole being in close contact with the upper surface side of the inclined wall of the joint between the vertical separating wall 51b and the horizontal separating wall 51c. A communication hole 56 is provided in the inclined wall in accordance with the inlet hole of the oil separator 55 so that 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 the external refrigerant pipe via the discharge port 57.

On the other hand, in the inlet side chamber 53, the compressed gas communication passages 47 and 48 are opened at separate positions.
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 formed below the horizontal separation wall 51c, and the inlet hole of the oil separator 55 is located in the middle thereof. Further, an arcuate projecting wall 51d connected to the horizontal separating wall 51c is provided on the side peripheral wall 51a of the inlet side chamber 53, and the lid plate 52 of the projecting wall 51d is provided.
An oil groove 60 having an upper end opening to the outlet side chamber 54 is engraved on the side end surface. Further, a partition plate 59 which allows oil to be dropped, such as a wire mesh, a metal lath, and punching metal (a plate having a round hole or a slit), is formed in the lower part of the inlet side chamber 53, that is, below the compressed gas communication passage 48. It is sandwiched by the lid plate 52, and the lower portion thereof serves as an oil sump chamber 58. The side wall 14b of the rear housing 14 in the oil sump chamber 58 is provided with a return oil port 63 communicating with the screw hole 16 of the fastening bolt 15 and opens into the oil sump chamber 58.

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

The double-headed swash plate type compressor according to the present embodiment is constructed as described above, and each piston 21 is caused to rotate through the swash plate 24 by the rotation of the drive shaft 17 into each cylinder bore 20.
It is reciprocated inside, and thereby, 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 into the front housing-side discharge chamber 28A passes through the compressed gas communication passage 47, and the compressed gas discharged into the rear housing-side discharge chamber 28B passes through the compressed gas communication passage 48. 50 are separately guided to the inlet side chambers 53.

Both of the compressed gases have a wide space and are located in the inlet side chamber 5
When it is guided to 3, it expands and the lubricating oil contained in this compressed gas is separated. Further, as indicated by a dotted arrow in FIG. 3, the vertical separating wall 51b and the horizontal separating wall 51c are used as guide plates to flow toward the communicating hole 56 and collide with each other near the inlet of the communicating hole 56, and the collision causes lubrication in the compressed gas. The oil is separated. Further, 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 swirl flow in the separator 55 is accelerated. Then, in the oil separator 55, the mist-like lubricating oil with a large mass contained in the compressed gas is applied to the inner wall of the cylindrical body of the oil separator 55 by the centrifugal force of the swirling flow of which the compressed gas is accelerated. Be scattered. 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 sump chamber 58. Then, due to the pressure difference between the oil reservoir chamber 58 communicating with the inlet side chamber 53 and the crank chamber 23, the lubricating oil in the oil reservoir chamber 58 is returned to the crank chamber 23 through the return oil port 63 and the screw hole 16, and each part Used for lubrication.

On the other hand, the compressed gas discharged from the oil separator 55 is discharged to the external refrigerant circuit via the outlet side chamber 54 and the discharge port 57. At this time, the compressed gas is 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 drips downward along the inner wall of the outlet side chamber 54 and is collected in the oil sump 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 are obtained. (1) In the refrigerant circuit using the double-headed swash plate compressor of the present embodiment, since the oil separator 55 is built in the compressor,
Compared to the conventional refrigerant circuit in which an oil separator is provided, the refrigerant circuit does not need to be provided with any device or piping, which simplifies. Therefore, it is possible to reduce the space required for an application device such as an air conditioner to which the double-headed swash plate compressor is applied and to reduce the cost. (2) Since the main body 51 of the oil separation chamber 50 containing the oil separator 55 is integrally formed with the conventional rear housing 14, the structure of incorporating the oil separator 55 in the compressor is not 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 space in comparison with the conventional one, so that it is not so much restricted by the space. An oil separator with good 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 tubular body can be set to a sufficient size. Therefore, the oil separator 55 with good separation efficiency can be built in the double-headed swash plate compressor.

(4) Discharge chamber 28 on the front housing side
A and the oil separation chamber 5 from the discharge chamber 28B on the rear housing side
The oil separation efficiency of the compressed gas introduced into
The oil separation due to the expansion action inside the oil, the oil separation due to the collision action of these compressed gases, and the collision of the compressed gas accelerate the swirling flow in the oil separator, thereby improving the oil separation efficiency. As a result, compared with the conventional compressor with a built-in oil separator, the content of lubricating oil in the compressed gas discharged to the refrigerant circuit is reduced, 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 the vertical separation wall 5
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 by the 1b and the horizontal separation wall 51c, and the oil is discharged from the oil separator 55. Since it is divided into the outlet side chamber that receives the compressed gas and discharges this compressed gas to the external refrigerant circuit, only the compressed gas in the inlet side chamber is introduced into the oil separator and the compressed gas discharged from the oil separator. Only the gas 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 efficiently performed, and the oil separation efficiency due to the collision is improved.

(7) Since the oil sump chamber 58 is provided below the inlet side chamber 53, that is, below the compressed gas communication passage 48, the space can be effectively utilized. (9) Since the upper surface of the oil sump chamber 58 is partitioned and formed by a partition plate such as a wire net, a slit plate, and a perforated plate, the lubricating oil stored in the oil sump chamber 58 is rolled up by the compressed gas and re-scattered. This prevents the oil separation efficiency from decreasing. (10) Since the oil sump chamber 58 is returned to the crank chamber 23 through the screw holes 16 of the fastening bolts 15 that fasten the housings 12, 14 and the cylinder block 11, the return oil passage is simplified and the return oil passage is formed. The man-hours and costs for providing the are reduced. Further, this return oil passage has a ring-shaped gap formed between the inner surface of the screw hole 16 and the outer surface of the fastening bolt 15 and serves as an oil passage, so it can be said that clogging of dust is unlikely to occur.

The present invention can be modified and embodied as follows. (1) Although the present invention is embodied in a double-headed swash plate compressor, it may be embodied in a double-headed web cam compressor. (2) The separation walls of the inlet side chamber 53 and the outlet side chamber 54 in the oil separation chamber 50 are the vertical separation wall 51b and the horizontal separation wall 5
Instead of 1c, it is possible to have an appropriate configuration such as only a horizontal separation wall or only an arc-shaped separation wall. In addition, the shape of the separation wall is such that the compressed gas flowing from the two compressed gas communication passages 47 and 48 is efficiently collided with each other.
It is preferable that it can be guided toward the inlet hole of 5, that is, toward the communication hole. (3) In the oil separation chamber 50, the outlet side chamber 54 can be widened, and the oil separator 55 can have another structure. For example, the upper half of the oil separation chamber 50 is defined as the outlet side chamber only by the horizontal separation wall, and the centrifugal separation type oil separator having the cylinder longer than that of the present embodiment is horizontally or obliquely arranged therein. You can

(4) The lubricating oil accumulated in the outlet side chamber 54 of the oil separation chamber 50 is changed to an oil groove 60 for collecting in the oil sump chamber 58, and the protruding wall 51d is eliminated, and the horizontal separation wall 51c and the peripheral wall 51a are separated from each other. You may provide a through hole in a joining part.

(5) The return oil passage does not utilize the screw hole 16 and communicates with a shaft hole through which the drive shaft 17 of the cylinder block 11 is inserted through another type of passage, for example, the rear housing 14, the valve plate 13 and the like. It is also possible to separately provide a passage for recirculation to the crank chamber 23 through this shaft hole. (6) In the inventions according to claims 1 to 5, the oil separation chamber 50 is formed separately from the rear housing 14, and the oil separation chamber 50 is connected to the rear housing 14 by appropriate means such as bolts and nuts. Good.

[0035]

Since the present invention is constructed as described above, it has the following effects. According to the invention described in claim 1, the space restriction of the oil separator built in the double-headed cam type compressor is relaxed, and it becomes easy to install an efficient oil separator. Further, the compressed gas introduced into the oil separation chamber from the front housing side discharge chamber and the rear housing side discharge chamber is subjected to the oil separation due to the expansion action in the oil separation chamber, the oil separation due to the collision action of the compressed gas flow, and the inside of the oil separator. The swirling of the compressed gas is affected by the collision action and is accelerated to improve the oil separation action, thereby significantly improving the oil separation efficiency. Moreover, since an efficient oil separator is built in in this way, without complicating the refrigerant circuit,
The 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 the device to which the double-headed cam compressor is applied are reduced.

According to the second aspect of the invention, only the compressed gas in the inlet side chamber is guided to the oil separator, and only the compressed gas discharged from the oil separator is discharged to the external refrigerant circuit.
The oil separation efficiency is further improved. According to the invention of claim 3, the collision of the compressed gas is efficiently performed. According to the invention described in claim 4, the space is effectively used. According to the fifth aspect of the present invention, the re-scattering of the lubricating oil stored in the oil sump chamber due to the rolling up is prevented, and the reduction of the oil separation efficiency is prevented. According to the invention of claim 6,
The formation of the oil separation chamber is simplified.

[Brief description of drawings]

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

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

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

[Explanation of symbols]

11 ... Cylinder block, 12 ... Front housing,
14 ... Rear housing, 14b ... Rear housing side wall, 20 ... Cylinder bore, 21 ... Piston, 28A ... Front housing side discharge chamber, 28B ... Rear housing side discharge chamber, 47, 48 ... Compressed gas communication passage, 50 ... Oil Separation chamber, 51 ... Main body, 51a ... Peripheral wall, 51b ... Vertical separation wall, 51c ... Horizontal separation wall, 52 ... Lid plate as 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 sump chamber,
59 ... Partition plate, 60 ... Oil groove, 63 ... Return oil port.

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yuji Kaneshige 2-chome Toyota-cho, Kariya city, Aichi Prefecture Toyota Industries Corporation (56) Reference JP-A-7-332239 (JP, A) JP-A 8-35485 (JP, A) JP-A-3-61680 (JP, A) Actually developed 55-163484 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F04B 39/04 F04B 27/08

Claims (6)

(57) [Claims] 1. A double-headed cam compressor in which a front housing having a suction chamber, a front housing having a discharge chamber, and a rear housing are joined to the front and rear end surfaces of a cylinder block having a plurality of cylinder bores accommodating pistons in parallel with each other. An oil separation chamber is connected to the outside of 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 the side wall of the oil separation chamber. A discharge port is provided 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 are separately communicated with the oil separation chamber. A double-headed cam compressor characterized in that a compressed gas communication passage is formed, and the compressed gas communication passage is opened separately in the oil separation chamber. 2. The oil separator is of a centrifugal separation type, the oil separation chamber accommodates an inlet side chamber for introducing compressed gas from the discharge chamber by a separation wall, and the oil separator, The double-headed cam type compression according to claim 1, characterized in that it is partitioned into an outlet side chamber that releases compressed gas after separating the lubricating oil, and that an inlet hole of the oil separator is communicated with the inlet side chamber. Machine. 3. The double-headed cam compressor according to claim 1, wherein an inlet hole of the oil separator is located in the middle of the openings of the compressed gas communication passages. 4. The double-headed cam type compressor according to claim 1, wherein a lower portion of the oil separation chamber is an oil storage chamber. 5. The double-headed cam type compressor according to claim 1, wherein a partition plate that allows passage of lubricating oil is provided in a lower portion of the oil separation chamber, and a lower portion thereof is formed as an oil sump chamber. 6. 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. The double-headed cam type compressor according to any one of claims 1 to 5.