JP3921522B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor, and more particularly to a compressor that can more effectively reduce the pulsation pressure during refrigerant discharge.

  The compressor that constitutes the air conditioner for automobiles condenses after compressing the engine power transmitted through pulleys by selectively transmitting the power of the engine by the intermittent action of the electromagnetic clutch and sucking the refrigerant into the interior from the evaporator. It is a device which discharges to a container. There are various types of such compressors depending on the compression structure, and among them, the type generally widely used for automobiles is a swash plate type compressor.

1 to 4 show the structure of a general swash plate compressor.
As shown in FIGS. 1 and 2, a general swash plate compressor is provided with a swash plate 40 fixed to a drive shaft 30 inside a pair of cylinders 10, 20. A plurality of pistons 50 are installed, and a suction valve 71 and a valve plate are used so that the piston 50 can reciprocate through the shoe 60 by the rotation of the swash plate 40 and suck and compress the refrigerant. ) 72 and a discharge valve 73, and a valve unit 70 and a gasket are sequentially provided outside the respective cylinders 10 and 20, so that these parts and the like can be housed and protected in the front housing (Front A housing 80 and a rear housing 90 are assembled together. It is made from the resulting structure.

  In the swash plate type compressor having such a structure, the power is transmitted by the pulley of the electromagnetic clutch 31 to rotate the swash plate 40 configured obliquely, and every time the swash plate 40 makes one rotation, Each stroke of the piston 50 located in the position moves back and forth and completes one stroke. As a result, the swash plate 40 configured to be inclined causes the piston 50 to discharge with the suction muffler 94 while part of the piston 50 is moved to the front housing 80 side and the other part is simultaneously moved to the rear housing 90 side. The refrigerant that has flowed into the respective housings 80 and 90 through the manifold 96 having the muffler 95 is compressed into the compression chambers 81 and 91 provided on the inner side walls of the respective housings 80 and 90. The refrigerant thus compressed is transferred to the rear housing 90 through a predetermined flow path, and is discharged to the outside of the compressor while being mixed with the compressed refrigerant of the rear housing 90 to be discharged.

  When the configuration of the flow path for discharging the compressed refrigerant to the outside and the action thereof are examined in more detail, the compressed refrigerant is stored in the center of the inner wall of the front housing 80 as shown in FIGS. A compression chamber 81 is provided separately so that the refrigerant in the compression chamber 81 can be guided to the compression chamber 91 of the rear housing 90, so that the guide holes 11, The rear housing 90 is provided with a compression chamber 91 at the center of the inner wall in the same manner as the front housing 80, and the discharge passage for discharging and guiding the compressed refrigerant to the outside through the hole (H). 92 extends in a curved shape along the outside of the compression chamber 91 and is connected to the discharge chamber 93.

  As a result, when the swash plate 40 rotates at a high speed, the refrigerant is compressed in the compression chambers 81 and 91 of the front housing 80 and the rear housing 90 while the multiple pistons 50 reciprocate forward and backward. Thereafter, the refrigerant compressed in the compression chamber 81 of the front housing 80 is transferred to the discharge chamber 93 of the rear housing 90 through the guide holes 11 and 21 of the respective cylinders 10 and 20, and The compressed refrigerant is also transferred to the discharge chamber 93 through the discharge channel 92, and the refrigerant is discharged to the outside through the discharge hole 94 in a state of being mixed in the discharge chamber 93.

  However, in the conventional compressor configured as described above, a discharge passage 92 for discharging the compressed refrigerant of the rear housing 90 to the outside is separately provided in a semicircular shape on one side of the compression chamber 91. Therefore, the exposed part must be closed with a leak-proof device such as a gasket, and the structure must be sealed to maintain the airtightness of these closed parts. There was a problem.

Further, since the discharge channel 92 is narrow and long and is formed in a semicircular shape, the flow of the refrigerant is obstructed and not only pressure loss is induced, but also the high-pressure refrigerant hits the wall of the discharge channel. There is a problem that a pulsation noise phenomenon may occur.
Further, since the discharge flow path 92 occupies the semicircular area of the suction chamber, a part of the suction hole 72a that is concentrically formed in the valve plate 72 overlaps with the semicircular suction hole 72a. There was also a problem of being blocked through the refrigerant suction.

  Further, when the design of the compression chamber 91 of the rear housing 90 is changed due to the complexity of the structure due to the formation of the separate discharge flow path 92, the design of the discharge flow path 92 and related peripheral parts, etc. must be changed at the same time as a gasket. As a result, the number of work steps is increased, and of course, there are disadvantages incurring an increase in cost, and the flow of the sucked refrigerant and discharged refrigerant is not smoothly performed. Many problems occurred, such as the pressure was reduced and noise was generated due to the semicircular discharge pipe.

  In order to solve such a problem, the present applicant presented an example of a swash plate compressor in which a refrigerant discharge structure is improved by installing a discharge pipe in a rear housing (see Patent Document 1).

FIG. 5 shows the front structure of the rear housing of the compressor according to the prior art.
Referring to FIG. 5, the rear housing 100 has a predetermined thickness at the central portion of the bottom surface thereof, a polygonal inner wall 101 that is formed to project directly upward from the bottom surface, and an extension formed at one end of the inner wall 101. The refrigerant suction chamber 103 and the refrigerant discharge chamber 104 formed by the portion 102, the inner wall 101 and the inner peripheral wall of the rear housing 100, and the refrigerant formed in the refrigerant discharge chamber 104 and discharged into the refrigerant discharge chamber 104 to the outside of the compressor The discharge pipe 106 communicates with the outflow chamber 105 for discharging, and one end of the discharge pipe 106 is extended into the refrigerant discharge chamber 104 by a predetermined length, and the other end is connected to the outflow chamber 105. It has a linked structure.

The discharge pipe 106 of the rear housing 100 has a distance (L) between a point (B) where the center line is in contact with the inner surface of the inner wall 101 and a point A connecting the extension 102 with respect to the center line of the discharge pipe 106. It is extended to a point corresponding to about 1/2.
As described above, the compressor according to the prior art has a structure in which the discharge pipe 106 is formed inside the rear housing 100, and the refrigerant compressed from the front and the refrigerant compressed from the rear merge at the upper point of the discharge pipe 106. Thus, the pulsation pressure is reduced by discharging to the outside.

  However, even in such a prior art, since the pulsation pressure when refrigerant is discharged from the front housing to the outside of the compressor is not effectively reduced, there is a limit in reducing the overall pulsation pressure. In order to solve this problem, when a discharge muffler constituting a manifold is formed outside the compressor, there is a problem that the size of the compressor package increases.

US Pat. No. 6,068,453

  Therefore, the present invention has been made in view of the above problems in the conventional compressor, and an object of the present invention is to provide a compressor that can more effectively reduce the pulsation pressure during refrigerant discharge. There is to do.

In order to achieve the above object, a compressor according to the present invention includes a front / rear housing (200, 300) and a front / rear cylinder (400) arranged side by side between the front / rear housing (200, 300). 500) and a refrigerant inlet (520) and a refrigerant outlet (530) formed in one of the front and rear cylinders (400, 500) , the front and rear housings (200, 300) are provided. ) Include a refrigerant suction chamber (210, 310), a refrigerant discharge chamber (220, 320), a partition wall (230, 330) that partitions the refrigerant discharge chamber (220, 320) inward, and a partition wall (230, 330). Discharge pipes (240, 340) penetrating through the discharge pipe (240, 340) and auxiliary expansion portions (250, 350) communicating with the outlet side of the discharge pipe (240, 340). The compressed refrigerant passes through the refrigerant discharge chambers (220, 320), the discharge pipes (240, 340), and the auxiliary expansion portions (250, 350) in the front and rear housings (200, 300), and passes through the auxiliary expansion portions (250, 350). 350) and the front / rear discharge connecting flow passages (410, 510) and the main expansion portion (420), the refrigerant discharge port (530) is configured to be discharged .

The main expansion portion (420) is formed integrally with the cylinder by expanding a part of each discharge connection channel (410, 510) in the front cylinder (400) or the rear cylinder (500). And
The main expansion part (420) is separately formed outside the front cylinder (400) or the rear cylinder (500).
At least one of the discharge pipes (240, 340) in the front / rear housing (200, 300) has the center of the end portion of the discharge chamber (220, 320) of the front / rear housing (200, 300). It is characterized by being formed at the shortest distance from the center.
At least one of the auxiliary expansion parts (250, 350) in the front and rear housings (200, 300) is characterized in that its volume is larger than the volume of the discharge pipe (240, 340) communicating therewith .
At least one of the front / rear discharge connecting flow paths (410, 510) has a flow path cross-sectional area larger than or equal to the flow path cross-sectional area of the discharge pipe (240, 340) upstream thereof. It is characterized by.

The volume of the main expansion part (420) is greater than or equal to the sum of the volumes of the front and rear auxiliary expansion parts (250, 350).
At least one of the discharge pipes (240, 340) in the front and rear housings (200, 300) is formed so as to communicate with the lower surface of the auxiliary expansion part (250, 350) communicating therewith. Features.
At least one of the discharge pipes (240, 340) in the front and rear housings (200, 300) increases gradually or gradually in the cross-sectional area of the flow path from the inlet toward the outlet. It is characterized by.
The lengths of the flow paths from the discharge pipes (240, 340) of the front and rear housings (200, 300) to the refrigerant discharge port (530) are the same.

  According to the compressor of the present invention, the pulsation pressure is reduced not only when the refrigerant is discharged from the rear refrigerant discharge chamber to the outside of the compressor but also when the refrigerant is discharged from the front refrigerant discharge chamber to the outside of the compressor. As a result, an excellent pulsation pressure reduction effect can be obtained, and pulsation noise can be significantly reduced.

  In addition, due to the excellent pulsation noise reduction effect, it is not necessary to form a separate expansion part space with a large flow path cross section outside the compressor, and even if a separate expansion part space is formed outside the compressor, The size can be greatly reduced, and the size of the compressor package can be reduced.

  Next, a specific example of the best mode for carrying out the compressor according to the present invention will be described with reference to the drawings.

  FIG. 6 is a side view of the compressor according to the first embodiment of the present invention, FIG. 7 is a front sectional view of the compressor according to the first embodiment of the present invention, and FIG. FIG. 9 is a front view of a front housing applied to the compressor according to the first embodiment, and FIG. 9 is a front view of a rear housing applied to the compressor according to the first embodiment of the present invention.

  As shown in FIGS. 6 and 7, the compressor according to the first embodiment of the present invention includes front and rear housings 200 and 300, and front and rear cylinders 400 sequentially disposed between the front and rear housings 200 and 300. 500, a drive shaft 600 rotatably supported at the center of the front and rear cylinders 400, 500, a swash plate 700 installed on the drive shaft 600, and a shoe 800 around the swash plate 700. In the following description, a detailed description of a swash plate type compressor including a plurality of pistons 900 and the like that are the same as or equivalent to those of the prior art will be omitted.

As shown in FIGS. 7 and 8, the front housing 200 is opened at the rear and coupled to the front cylinder 400. An inner wall surface of the front housing 200 (that is, an inner surface of the front wall surface) includes a front refrigerant suction chamber 210, a front refrigerant discharge chamber 220, a front partition 230 that divides the front refrigerant discharge chamber 220 inward, and a front that passes through the front partition 230. The discharge pipe 240 and a front auxiliary expansion portion 250 communicating with the outlet side of the front discharge pipe 240 are formed.

As described above , the front refrigerant suction chamber 210 is partitioned from the front refrigerant discharge chamber 220 by the front partition wall 230 having a substantially closed curved shape on the outer side, and the bearing is formed from the center of the front refrigerant discharge chamber 220 to the front wall front side of the front housing 200. pulley interposed a (not shown) while rotatably supporting the drive shaft 600 of the compressor as well as mounting rotatably the (not shown), the nose portion 202 for passing (see FIG. 8) Projectingly formed.

Further, as shown in FIGS. 7 and 9, the rear housing 300 is coupled to the rear cylinder 500 with the front opened . On the inner wall surface of the rear housing 300 (that is, the inner surface of the rear wall surface), a rear refrigerant suction chamber 310, a rear refrigerant discharge chamber 320, a rear partition wall 330 that divides the rear refrigerant discharge chamber 320 inward, and a rear that penetrates the rear partition wall 330. The discharge pipe 340 and a rear auxiliary expansion portion 350 communicating with the outlet side of the rear discharge pipe 340 are formed, and the form thereof is the same as that of the front housing 200.
In addition, as with the front housing 200, a pulley (not shown) is rotatably mounted and a nose for projecting is formed while rotatably supporting the drive shaft of the compressor. is there.

As shown in FIG. 7, the front cylinder 400 and the rear cylinder 500 are connected to the front and rear auxiliary expansion portions (250, 350) to form discharge connection channels 410, 510, respectively. , 510 is formed by extending a part of the main expansion portion 420 integrally.

  In the present embodiment, the example in which the refrigerant inlet 520 and the refrigerant outlet 530 are formed in the rear cylinder 500 has been described. However, the refrigerant inlet 520 and the refrigerant outlet 530 are formed in the rear cylinder 500. However, the front cylinder 400 may be formed, and the front and rear cylinders 400 and 500 may be formed one by one.

In the compressor of the present invention having the above configuration, as shown in FIG. 7, when the drive shaft 600 is rotated by power transmission from the power source in the front and rear cylinders 400 and 500, the swash plate 700 is rotated together with the drive shaft 600. In accordance with the phase of the swash plate 700, the piston 900 moves forward and backward with the corresponding bores of the front and rear cylinders 400 and 500, respectively. Thus, while the piston 900 is pre-backward movement, since the vacuum pressure is formed inside the bore, before the evaporator refrigerant inlet 520 is connected to the (not shown) (see FIG. 6) -The refrigerant flows into the swash plate chamber (S) in the bores of the front and rear cylinders 400, 500 through the rear refrigerant suction chamber (210, 310) .

  The refrigerant sucked into the swash plate chamber (S) is sucked into the bores of the front and rear cylinders 400 and 500, respectively. The refrigerant sucked into the bore is compressed by the piston 900 and discharged into the refrigerant discharge chambers 220 and 320 of the front and rear housings 200 and 300 through the discharge holes of the suction reed valve and the discharge holes of the valve plate opened by the discharge reed valve. Is done.

The refrigerant discharged to the front / rear refrigerant discharge chambers 220, 320 passes through the front / rear discharge pipes 240, 340, the front / rear auxiliary expansion portions 250, 350, and further, the front / rear discharge connection flow paths 410, 510, and It is discharged to the refrigerant discharge port 530 through the main expansion portion 420.

For this reason, in this embodiment, as shown in FIGS. 6 and 7, the front and rear housings 200 and 300 pass through the partition walls 230 and 330 from the front and rear discharge chambers 220 and 320, respectively, and discharge front and rear. Tubes 240 and 340 are formed, and auxiliary expansion portions 250 and 350 are formed on the outlet sides of the front and rear discharge tubes 240 and 340.
Therefore, the refrigerant in the rear refrigerant discharge chamber 320 passes through the rear discharge pipe 340 and the auxiliary expansion part 350 and is transferred to the discharge connection flow path 510 of the rear cylinder 500, and the refrigerant in the front refrigerant discharge chamber 220 is transferred to the front discharge pipe 240 and The refrigerant is transferred to the discharge connection flow path 410 of the front cylinder 400 through the auxiliary expansion part 250, passes through the main expansion part 420 together with the refrigerant transferred along the discharge connection flow path 510 of the rear cylinder 500, and then externally through the refrigerant discharge port 530. It can be discharged.

Here, the front and rear discharge pipes 240 and 340 for discharging the refrigerant from the front and rear refrigerant discharge chambers 220 and 320 to the auxiliary expansion portions 250 and 350 communicate with the upper surfaces of the partition walls 230 and 330 forming the auxiliary expansion portions 250 and 350, respectively. In this case, when the refrigerant moves to the discharge connection flow path 410, 510 side, there is a possibility that the refrigerant stagnates at the lower ends of the auxiliary expansion portions 250, 350, and this is the limit for reducing the pulsation pressure. Will occur. Therefore, in the present invention, at least one of the front and rear discharge pipes 240 and 340 formed in the front and rear housings 200 and 300 is communicated with the lower surface of the auxiliary expansion parts 250 and 350, respectively. It is desirable to prevent stagnation .

In this embodiment, the lengths of the flow paths from the front and rear discharge pipes 240 and 340 to the refrigerant discharge port 530 of the front and rear housings 200 and 300 are the same, so The pulsation pressure can be reduced by making the pressure difference of the discharged refrigerant uniform.
In order to effectively reduce the pulsation pressure when the refrigerant is discharged from the front and rear housings 200 and 300 to the outside of the compressor, the volumes of the auxiliary expansion portions 250 and 350 are respectively It is preferable to make it larger than the volume of the rear discharge pipes 240 and 340. That is, the refrigerant discharged from the front and rear refrigerant discharge chambers 220 and 320 flows toward the auxiliary expansion portions 250 and 350 having a large volume through the front and rear discharge pipes 240 and 340 having a small volume, respectively. Reduced.

Furthermore, it is desirable that the cross-sectional area of the flow paths of the front and rear discharge pipes 240 and 340 gradually increase from the inlet to the outlet side or increase stepwise, from the center of the front and rear housings 200 and 300. It is desirable that the distance (L1, L2) to the center of the entrance of the front / rear discharge pipes 240, 340 is the shortest distance.
In addition, if the cross-sectional area of the front and rear discharge pipes 240 and 340 is larger than the cross-sectional area of the discharge connection flow paths 410 and 510, the refrigerant flowing into the auxiliary expansion portions 250 and 350 will be larger than the refrigerant flowing out. As a result, the refrigerant may stagnate from the auxiliary expansion portions 250 and 350, so that the cross-sectional area of the discharge connecting flow paths 410 and 510 is larger than the cross-sectional area of the front and rear discharge pipes 240 and 340. It is desirable to form the same.

In particular, as described above, in the case of the main expansion portion 420 and the front / rear auxiliary expansion portions 250 and 350, the volume of the main expansion portion 420 is increased in order to prevent the refrigerant from stagnation from the auxiliary expansion portions 250 and 350. It is desirable to form larger than or equal to the sum of the volumes of the rear auxiliary expansion portions 250 and 350.
Since the cross-sectional areas of the main expansion portions of the discharge connection channels 410 and 510 are different, the muffler effect appears in the process of the refrigerant passing through the discharge connection channels 410 and 510 and the main expansion portion, thereby reducing the pulsation pressure. Can do.

  Thus, in this embodiment, not only when the refrigerant is discharged from the rear refrigerant discharge chamber 320 to the outside of the compressor, but also when the refrigerant is discharged from the front refrigerant discharge chamber 220 to the outside of the compressor, Since the pressure is reduced, an excellent effect of reducing the pulsation pressure can be obtained.

FIG. 10 is a front sectional view of a compressor according to the second embodiment of the present invention.
In the compressor according to the second embodiment of the present invention, as shown in FIG. 10, the main expansion portion 410 is connected to the discharge connection passages 410 and 510 in the front and rear cylinders 400 and 500, and the front cylinder 400 or Except for being formed outside the rear cylinder 500, it has the same configuration and operation as the compressor according to the first embodiment described above.

  Even in the case of the second embodiment in which the main expansion portion 410 is formed outside the front cylinder 400 or the rear cylinder 500, the discharged refrigerant has already pulsated pressure through the discharge pipes 240 and 340 and the auxiliary expansion portions 250 and 350. Since it is in a reduced state, the size of the main expansion portion 420 can be formed much smaller than the size of the conventional manifold or discharge muffler, so that the package size of the compressor can be reduced.

  The above-described embodiments of the present invention have been described with respect to the compressor structure in which the front and rear housings 200 and 300 and the front and rear cylinders 400 and 500 are abutted and joined. Similarly, the present invention can be applied to a compressor structure in which the front and rear cylinders 400 and 500 are positioned inside and assembled.

  The present invention is not limited to the above-described embodiments. Various modifications can be made without departing from the technical scope of the present invention.

It is a schematic exploded perspective view of a general compressor. It is front sectional drawing of a common compressor. It is a front view of the front housing of a common compressor. It is a front view of the rear housing of a general compressor. It is a front view of the rear housing of the compressor by an example of a prior art. 1 is a side view of a compressor according to a first embodiment of the present invention. 1 is a front sectional view of a compressor according to a first embodiment of the present invention. It is a front view of the front housing applied to the compressor by the 1st example of the present invention. It is a front view of the rear housing applied to the compressor by the 1st example of the present invention. It is front sectional drawing of the compressor by the 2nd Example of this invention.

Explanation of symbols

200 Front housing 210 Front refrigerant suction chamber 220 Front refrigerant discharge chamber 230, 330 Partition 240 Front discharge pipe 250, 350 Auxiliary expansion part 300 Rear housing 310 Rear refrigerant suction chamber 320 Rear refrigerant discharge chamber 340 Rear discharge pipe 400 Front cylinders 410, 510 Discharge connection flow path 420 Main expansion part 500 Rear cylinder 520 Refrigerant inflow port 530 Refrigerant discharge port 600 Drive shaft 700 Swash plate 800 Shoe 900 Piston

Claims (10)

Front / rear housings (200, 300), front / rear cylinders (400, 500) arranged side by side between the front / rear housings (200, 300), and front / rear cylinders (400, 500) in the refrigerant inlet is formed in one of (520) and a compressor having a refrigerant discharge port (530),
Each of the front and rear housings (200, 300) includes a refrigerant suction chamber (210, 310), a refrigerant discharge chamber (220, 320), and a partition wall (230) that divides the refrigerant discharge chamber (220, 320) inside. 330), discharge pipes (240, 340) penetrating the partition walls (230, 330), and auxiliary expansion portions (250, 350) communicating with the outlet side of the discharge pipes (240, 340) are formed, The refrigerant compressed in the cylinders (10, 20) is supplied to the refrigerant discharge chambers (220, 320), the discharge pipes (240, 340), and the auxiliary expansion parts (250, 250) in the front and rear housings (200, 300). 350) through the front and rear discharge connection flow paths (410, 510) connected to the auxiliary expansion part (250, 350) and the main expansion part (420), the refrigerant discharge port ( Compressor, characterized in that arranged to be discharged from the 30).   The main expansion portion (420) is formed integrally with the cylinder by expanding a part of each discharge connection channel (410, 510) in the front cylinder (400) or the rear cylinder (500). The compressor according to claim 1.   The compressor according to claim 1, wherein the main expansion part (420) is separately formed outside the front cylinder (400) or the rear cylinder (500). At least one of the discharge pipes (240, 340) in the front / rear housing (200, 300) has a center of an end portion of each of the discharge chambers (220, 220) of the front / rear housing (200, 300). 320. The compressor according to claim 1, wherein the compressor is formed at the shortest distance from the center of the center. At least one of the auxiliary expansion parts (250, 350) in the front and rear housings (200, 300) is larger in volume than a discharge pipe (240, 340) communicating therewith. The compressor according to claim 1. At least one of the front / rear discharge connecting flow paths (410, 510) has a flow path cross-sectional area larger than or equal to the flow path cross-sectional area of the discharge pipe (240, 340) upstream thereof. The compressor according to claim 1.   The compressor according to claim 1, wherein the volume of the main expansion part (420) is greater than or equal to the sum of the volumes of the front and rear auxiliary expansion parts (250, 350). At least one of the discharge pipes (240, 340) in the front / rear housing (200, 300) is formed to communicate with a lower surface of the auxiliary expansion part (250, 350) communicating therewith. The compressor according to claim 1. At least one of the discharge pipes (240, 340) in the front and rear housings (200, 300) gradually increases or gradually increases in cross-sectional area of the flow path from the inlet toward the outlet. The compressor according to claim 1. Claims the flow path length from the discharge pipe (240, 340) to said coolant discharge ports (530) of said front and rear housings (200, 300), characterized by being formed to be identical to each other Item 2. The compressor according to Item 1.

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