KR101336418B1 - Compressor - Google Patents

Abstract

According to the invention, a compressor is disclosed. The disclosed compressor includes: front and rear housings in which discharge chambers for discharging compressed refrigerant are formed; A cylinder block having a compressed refrigerant discharge path through which the compressed refrigerant discharged from the discharge chamber flows, and a muffler chamber having an expanded cross section for reducing the pulsating pressure of the compressed refrigerant discharged in communication with the compressed refrigerant discharge path; And front and rear valve units interposed between the front and rear housings and the cylinder block, respectively, in the compressed refrigerant discharge passages 131 and 231 formed in the cylinder blocks 130 and 230 to increase the flow rate of the discharged compressed refrigerant. Speed increasing portions 133 and 233 are formed. The compressed refrigerant discharged from the discharge chamber passes through a venturi-shaped speed increasing portion that is sequentially expanded, contracted, and expanded instead of a constant circular cross section, thereby increasing the flow rate of the discharged compressed refrigerant, thereby allowing the compressor to rotate at a low speed. In addition to preventing the degradation of the performance, it is possible to obtain an effect of improving the noise.

Compressor, Venturi

Description

Compressor

The present invention relates to a compressor, and more particularly, as a component part of a vehicle air conditioning system, in which a refrigerant gas discharged after evaporation is completed from an evaporator is sucked and compressed into a refrigerant gas in a high temperature and high pressure state, which is easily liquefied, and discharged into a condenser. Relates to a compressor.

Generally, a compressor for an air conditioner includes a swash plate type compressor in which a piston reciprocates by the rotation of an inclined swash plate, a scroll type compressor compressed by a rotational motion of two scrolls, and a vane type rotary compressor compressed by a rotary vane. There are various kinds.

In addition to the swash plate type compressor, the reciprocating compressor that compresses the refrigerant according to the reciprocating motion of the piston includes crank type and wobble plate type types. Compressors and the like.

1A is a cross-sectional view showing an example of a conventional swash plate compressor, and FIG. 1B is an exploded perspective view of the swash plate compressor shown in FIG. 1A. As shown, the conventional swash plate type compressor 1a includes the front and rear housings 10a and 20a having discharge chambers 11a and 21a formed therein, respectively, and the front and rear housings 10a and 20a. A cylinder block 30a having a cylinder bore 34a coupled therebetween so as to rotatably support the drive shaft 60a and having both ends of the piston 40a reciprocally coupled to both sides of the internal swash plate chamber 36a; And front and rear valve units 71a and 72a interposed between the cylinder block 30a and the front and rear housings 10a and 20a, respectively. A muffler chamber 32a is formed in the cylinder block 30a. The outer surface of the cylinder block (30a) is provided with a refrigerant discharge port 50 for discharging the refrigerant in the muffler chamber (32a) to the outside. In addition, the cylinder block 30a communicates with the discharge chambers 11a and 21a of the front and rear housings 10a and 20a and the muffler chamber 32a so that compressed refrigerant is discharged. Are each formed

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On the other hand, Figure 2a is a cross-sectional view showing a conventional swash plate type compressor employing a rotary suction valve structure, Figure 2b is a view seen from the "X" direction of Figure 2a.

As shown, a conventional compressor 1b employing a rotary suction valve structure includes front and rear housings 10b and 20b in which discharge chambers 11b and 21b for discharging compressed refrigerant are formed, and a swash chamber. The drive shaft 60b to which the swash plate 61 rotating at 31b is integrally coupled, the cylinder block 30b to which the drive shaft 60b is rotatably installed, and the rotational motion of the swash plate 61 are interlocked. A plurality of pistons 40b for reciprocating the inside of the cylinder bore 34b annularly arranged in the cylinder block 30b, and between the cylinder block 30b and the front and rear housings 10b and 20b, respectively. Interposed front and rear valve units 71b and 72b are provided. The compressed refrigerant discharge path 31b through which the compressed refrigerant discharged from the discharge chambers 11b and 21b flows in the cylinder block 30b, and the compressed refrigerant discharged in communication with the compressed refrigerant discharge path 31b. In order to reduce dynamic pressure, the muffler chamber 32b which extended the flow cross section is formed. Therefore, the compressed refrigerant discharged from the discharge chambers 11b and 21b passes through the compressed refrigerant discharge path 31b, moves to the muffler chamber 32b, and is eventually supplied to a condenser (not shown).

However, in the conventional swash plate type compressors 1a and 1b as described above, the compressed refrigerant discharged from the discharge chambers 11a, 11b, 21a and 21b has a constant circular cross section as shown in FIGS. 1A to 2B. It passes through furnaces 31a and 31b and moves to muffler chambers 32a and 32b. That is, since the discharged compressed refrigerant passes through the compressed refrigerant discharge paths 31a and 31b having a constant circular cross section, when the drive shafts 60a and 60b rotate at a low speed, the passage refrigerant of the compressed refrigerant discharge paths 31a and 31b is prevented. There is a disadvantage in that the performance of the compressor is lowered due to the slow speed of the refrigerant.

In particular, in the conventional swash plate type compressor 1b employing the rotary suction valve structure as shown in Figs. 2A and 2B, the main refrigerant suction flow path formed inside the drive shaft 60b through the swash plate chamber 36b ( The refrigerant sucked into 62 is supplied to each cylinder bore 34b through the suction passage 35 formed in the cylinder block 30b as the drive shaft 60b rotates, and then compressed by the piston 40b to discharge the chamber. Since the drive shaft 60b rotates at a low speed, the amount of refrigerant discharged to each cylinder bore 34b is not enough, and the speed of the refrigerant discharged is lowered, so that the performance of the compressor is reduced. Serious problems arise.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and an object of the present invention is to provide a compressor having an improved structure to maintain a compressor level or more even when the drive shaft of the compressor rotates at a low speed.

Other objects and advantages of the invention will be described below and will be appreciated by the embodiments of the invention. Further, the objects and advantages of the present invention can be realized by the means and the combination shown in the claims.

In order to achieve the above object, the compressor of the present invention, the front and rear housing is formed with a discharge chamber for discharging the compressed refrigerant; A cylinder block including a compressed refrigerant discharge path through which the compressed refrigerant discharged from the discharge chamber flows, and a muffler chamber having an expanded cross section to reduce the pulsating pressure of the compressed refrigerant discharged in communication with the compressed refrigerant discharge path; And front and rear valve units interposed between the front and rear housings and the cylinder block, respectively, in the compressed refrigerant discharge paths 131 and 231 formed in the cylinder blocks 130 and 230, respectively. Speed increasing portions 133 and 233 are formed to increase.

In this case, the speed increasing portion is preferably a Venturi shape in which the flow cross-section is sequentially expanded, contracted, and expanded.

Further, the speed increasing section is preferably formed on each opposing surface of the cylinder block facing the front and rear housings, respectively.

Further, the compressor has a main refrigerant suction passage in which the refrigerant sucked into the drive shaft is formed in the drive shaft, and the refrigerant sucked in the main refrigerant suction passage in the cylinder block is rotated by the main refrigerant suction passage. And a rotary suction valve structure in which a plurality of suction passages for sequentially communicating cylinder bores formed in the cylinder block are formed.

As described above, in the compressor according to the present invention, the compressed refrigerant discharged from the discharge chamber passes through a venturi-shaped speed increasing portion that is sequentially expanded, contracted, and expanded instead of a constant circular cross section, thereby allowing the flow of the compressed refrigerant to be discharged. When the drive shaft rotates at a low speed by increasing the speed, not only the performance of the compressor can be prevented, but also the effect of improving the noise can be obtained. Particularly, when the drive shaft rotates at a low speed, it is effective for a swash plate type compressor employing a rotary suction valve structure in which the performance of the compressor is deteriorated due to the lack of compressed refrigerant discharged.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is clearly understood that the same is by way of illustration and example only and is not to be taken by way of limitation, I will understand. Therefore, the true scope of protection of the present invention should be determined by the technical idea of the appended claims.

Hereinafter, with reference to the accompanying drawings to help understand the present invention will be described a preferred embodiment. However, the following examples are illustrative of the present invention and the scope of the present invention is not limited to the following examples.

Therefore, the embodiments described in the present specification and the configurations shown in the drawings are merely preferred embodiments of the present invention, and are not intended to represent all of the technical ideas of the present invention. Therefore, various equivalents And variations are possible.

3A is a cross-sectional view illustrating a compressor according to an embodiment of the present invention, and FIG. 3B is an exploded perspective view of the compressor shown in FIG. 3A.

As shown, the compressor 100 according to an embodiment of the present invention, the front and rear housings 110 and 120 having discharge chambers 111 and 121 formed therein, respectively, and the front and rear housings 110 ( A cylinder block having a cylinder bore 134 is coupled between the 120 to rotatably support the drive shaft 160 and the two ends of the piston 140 are reciprocally coupled to both sides of the internal swash plate chamber 136 ( 130 and front and rear valve units 171 and 172 interposed between the cylinder block 130 and the front and rear housings 110 and 120, respectively. In addition, a muffler chamber 132 is formed in the cylinder block 130. The muffler chamber 132 serves to reduce the pulsating pressure of the compressed refrigerant by expanding the flow cross section of the compressed refrigerant. The outer side of the cylinder block 130 is provided with a refrigerant discharge port 150 for discharging the refrigerant in the muffler chamber 132 to the outside. In addition, the cylinder block 130 has a compressed refrigerant discharge path 131 communicating the discharge chambers 111 and 121 of the front and rear housings 110 and 120 and the muffler chamber 132 to discharge the compressed refrigerant, respectively. Formed

In one embodiment of the present invention as described above, in the compressed refrigerant discharge path 131 formed in the cylinder block 130, a speed increasing portion 133 for increasing the flow rate of the discharged compressed refrigerant is formed. The speed increasing part 133 may have a venturi shape in which a flow cross section of the discharged compressed refrigerant is sequentially expanded (133a), reduced (133b), and expanded (133c). In addition, the speed increasing unit 133 is preferably formed on each opposing surface of the cylinder block 130 facing the front and rear housings 110 and 120, respectively, as shown in FIGS. 3A and 3B.

Compressed refrigerant passing through the venturi-like speed increasing portion 133 as described above is faster in accordance with the principle of Venturi. Therefore, even when the drive shaft 160 of the compressor rotates at a low speed, since the compressed refrigerant can flow above a certain level, it is possible to prevent the compressor from deteriorating. In addition, noise can be improved because the compressed refrigerant passes through a venturi-shaped flow path that is sequentially enlarged, reduced, or enlarged.

Hereinafter, a compressor according to another embodiment of the present invention will be described. 4A is a cross-sectional view of a compressor according to another embodiment of the present invention, FIG. 4B is a view from the “Y” direction of FIG. 4A, and FIG. 5 is a partial cross-sectional perspective view of the compressor shown in FIG. 4A.

As shown, the compressor 200 according to another embodiment of the present invention, the front and rear housings 210, 220 and the swash plate chamber 236 in which discharge chambers 211 and 221 for discharging the compressed refrigerant are formed. Drive shaft 260 is integrally coupled to the swash plate 261 to rotate in the cylinder block 230, the drive shaft 260 is rotatably installed, and the cylinder block in conjunction with the rotational movement of the swash plate 261 A plurality of pistons 240 for reciprocating the inside of the cylinder bore 234 annularly arranged in 230, and interposed between the cylinder block 230 and the front and rear housings 210, 220, respectively Front and rear valve units 271 and 272 are provided. The swash plate 261 rotating in the swash plate chamber 236 is inclinedly coupled to the drive shaft 260. The cylinder block 230 includes a compressed refrigerant discharge path 231 through which the compressed refrigerant discharged from the discharge chambers 211 and 221 flows, and a pulsation pressure of the compressed refrigerant discharged in communication with the compressed refrigerant discharge path 231. In order to reduce, the muffler chamber 232 which extended the flow cross section is formed.

On the other hand, the compressor 200 adopts a rotary suction valve structure. This is explained in more detail as follows. As shown in FIG. 4A, a swash plate 261 rotating in the swash plate chamber 236 is inclinedly coupled to the drive shaft 260, and refrigerant sucked into the swash plate chamber 236 passes through the swash plate 261. The main refrigerant suction passage 262 is formed to communicate the swash plate chamber 236 and the cylinder bore 234 so as to move to the cylinder bore 234. The refrigerant sucked into the main refrigerant suction passage 262 of the drive shaft 260 from the swash plate chamber 236 is connected to the main refrigerant suction passage 262 and each cylinder bore 234 as the drive shaft 260 rotates. It is sucked into the cylinder bore 234 through a plurality of suction passages 235 to sequentially communicate. The refrigerant sucked in this way is compressed by the reciprocating piston 240 and is discharged to the discharge chambers 211 and 221.

In another embodiment of the present invention as described above, in the compressed refrigerant discharge path 231 formed in the cylinder block 230 as in the above-described embodiment, the flow cross-section of the discharged compressed refrigerant is sequentially expanded (233a) The venturi-shaped speed increasing part 233 is formed to be reduced, 233b, and expanded 233c. In addition, the speed increasing unit 233 is preferably formed on each opposing surface of the cylinder block 230 facing the front and rear housings 210 and 220, respectively, as shown in FIGS. 4A and 5.

Therefore, even when the drive shaft 260 of the compressor 200 rotates at a low speed, since the compressed refrigerant can flow above a certain level, not only can the performance of the compressor be prevented from being lowered, but also the effect of noise is improved. On the other hand, when the drive shaft 260 rotates at a low speed, the performance degradation of the compressor due to the decrease in the speed of the compressed refrigerant is prominent in the compressor employing the rotary suction valve structure, and the venturi-shaped speed increasing portion 233 is formed as described above. As a result, the performance of the compressor can be prevented even when the drive shaft 260 rotates at a low speed.

In the above-described embodiment of the present invention, the swash plate compressor having a piston is a double head piston and a cylinder bore is formed on both sides of the swash plate chamber. However, the characteristics of the present invention are exemplary and the swash plate compressor having a migraine piston Applicable to

1A is a cross-sectional view showing an example of a conventional swash plate compressor;

1B is an exploded perspective view of the swash plate compressor shown in FIG. 1A;

Figure 2a is a cross-sectional view showing a conventional swash plate compressor employing a rotary suction valve structure,

FIG. 2B is a view from the “X” direction of FIG. 2A;

Figure 3a is a cross-sectional view showing a compressor according to an embodiment of the present invention,

3b is an exploded perspective view of the compressor shown in FIG.

Figure 4a is a cross-sectional view showing a compressor according to another embodiment of the present invention,

4B is a view from the “Y” direction in FIG. 4A;

FIG. 5 is a partial cross-sectional perspective view of the compressor shown in FIG. 4A. FIG.

BRIEF DESCRIPTION OF THE DRAWINGS FIG.

100,200 ... compressor 110,210 ... front housing

120,220 ... Rear housing 111,121,211,221 ... Discharge chamber

130,230 Cylinder block 131,231 Compressed refrigerant discharge furnace

132,232 Muffler chamber 133,233 Speed increase

134,234 Cylinder Bore 136,236 Judge Room

140,240 ... piston 160,260 ... drive shaft

171,271 Front valve unit 172,272 Rear valve unit

235 ... suction passage

Claims (4)

Front and rear housings (110,210) (120,220) having discharge chambers (111,121,211,221) for discharging the compressed refrigerant; In order to reduce the pulsating pressure of the compressed refrigerant discharged in communication with the compressed refrigerant discharge passage (131, 231) and the compressed refrigerant discharge passage (131, 231), the compressed refrigerant discharged from the discharge chamber (111, 121, 211, 221) is expanded Cylinder blocks 130 and 230 having muffler chambers 132 and 232 formed therein; In the compressor (100,200) having a front and rear valve unit (171,271) (172,272) interposed between the front and rear housing (110,210) (120,220) and the cylinder block (130,230), respectively: The compressed refrigerant discharge paths 131 and 231 formed in the cylinder blocks 130 and 230 have a venturi shape in which flow sections of the discharged compressed refrigerant are sequentially expanded (133a, 233a), reduced (133b, 133b) and expanded (133c, 233c). Compressor , characterized in that the speed increasing section (133,233) for increasing the flow rate of the discharged compressed refrigerant. delete The method of claim 1, wherein the speed increasing unit (133, 233), Compressor, characterized in that formed on each opposing surface of the cylinder block (130,230) facing the front and rear housing (110,210) (120,220), respectively. The method according to claim 1 or 3, The compressor 200 The swash plate 261 that rotates in the swash plate chamber 236 includes a drive shaft 260 integrally formed obliquely, The drive shaft 260 is formed with a main refrigerant suction passage 262 through which the refrigerant sucked into the inner flow , The cylinder block 230 has refrigerant sucked into the main refrigerant suction passage 262 formed in the main refrigerant suction passage 262 and the cylinder block 230 as the driving shaft 260 rotates. Compressor characterized in that it employs a rotary suction valve structure formed with a plurality of suction passages (235) for sequentially communicating.

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