KR950007475B1 - Scroll type compressor - Google Patents

Abstract

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Description

Scroll compressor

1 to 3 show a scroll compressor according to Embodiment 1 of the present invention, wherein FIG. 1 is a longitudinal sectional view.

2 is a cross-sectional view taken along the line a-a of FIG.

3 is a cross-sectional view taken along line b-b of FIG.

4 is a longitudinal sectional view showing a scroll compressor according to a second embodiment of the present invention.

5 is a longitudinal sectional view showing a conventional scroll compressor.

* Explanation of symbols for main parts of the drawings

2: fixed scroll 4: movable scroll

8: fluid inlet port 9: suction path

10: rear housing 21: fixed side plate

22 cell 23 fixed spiral member

30 front housing 31 shaft sealing device

32: main bearing 33: drive shaft

34: eccentric pin 35, 351: counterweight

35a: circumferential surface 35b: inclined surface

36: drive bush 37: rotation prevention mechanism

38: bearing 39: compression chamber

41: movable side plate 42: movable spiral member

[Industrial use]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly, to a scroll compressor having improved lubricity such as a shaft sealing device, a bearing, and an anti-rotation mechanism.

[Prior art]

A general scroll compressor (hereinafter simply referred to as a compressor) is disclosed in Japanese Patent Laid-Open No. 57-62988. In the compressor, as shown in FIG. 5, a fixed scroll 52 composed of the fixed side plate 521 and the fixed spiral member 522 is fixed to the housing 51, and the fixed scroll 52 has a housing ( The compression chamber 56 is formed by joining the movable scroll 54 which consists of the movable side plate 541 and the movable helical member 542 arrange | positioned at 51 and 53. As shown in FIG. The drive shaft 59 is supported by the shaft sealing apparatus 57 and the main bearing 58 in the housings 51 and 53, and the eccentric pin 60 is eccentrically attached to the inner end of the drive shaft 59. The counterweight 61 is fixed to the main bearing 58 side of the eccentric pin 60, and the movable scroll 54 is moved to the other end side of the eccentric pin 60 via the bearing 63 in cooperation with the anti-rotation mechanism 62. ) Is fitted with a driving bush 64 supporting only the orbital motion.

In the compressor, since the fixed helical member 522 and the movable helical member 542 are formed in an involute curve or the like that meshes with each other, the compression chamber 56 formed by the two scrolls 52 and 54 has a movable scroll ( The volume changes due to the orbital motion of 54). For this reason, refrigerant gas flows into the compression chamber 56 from the fluid suction port 55 formed in the housing 51, and the pressure in the compression chamber 56 becomes high gradually, and the discharge port of the center part of both scrolls 52 and 54 is carried out. It is discharged from the fluid discharge port 67 to the refrigerant circuit not shown in the figure via the discharge chamber 66 from 65.

[Problem to Solve Invention]

In general, in the compressor of the above-mentioned type, the front side lubrication necessary parts, such as the shaft sealing apparatus 57, the main bearing 58, the anti-rotation mechanism 62, the bearing 63, are lubricated by the oil particle mixed in refrigerant gas. I adopt the method.

However, in the conventional compressor, in order to suppress the refrigerant gas suction resistance extremely small, the fluid suction port 55 penetrates behind the front lubrication necessary portion, that is, the compression chamber 56 side, The refrigerant gas is directly sucked into the compression chamber 56. For this reason, in such a compressor, refrigerant gas is less likely to be delivered to the front side lubrication necessary portion, and at the same time, lubricating oil in the refrigerant gas is hardly supplied sufficiently to the front side lubrication necessary portion. It may cause crushing and premature wear.

In order to prevent the above drawbacks, a means for installing a through-flow passage through which the fluid intake port and the shaft sealing device communicate with each other is also known (see Japanese Patent Application Laid-Open No. 59-24992). However, the above means has to form a complicated stepped portion at the inlet of the inlet passage in order to surely introduce lubricating oil in the refrigerant gas into the inlet passage, which has difficulty in productivity.

This invention makes it a subject to solve that supplying lubricating oil easily and fully to a front side lubrication required part, without increasing the suction resistance of refrigerant gas.

[Means for solving the problem]

In order to solve the above problems, the compressor of the present invention adopts a new means of allowing a fluid inlet port to penetrate the circumferential surface of the counterweight and communicating the fluid inlet port with a suction passage that communicates directly with the compression chamber.

In the compressor of the present invention, it is preferable to employ a counterweight of a shape that actively guides the refrigerant gas to the front side. For example, it is possible to employ a counterweight of an inclined surface in which the side of the front side becomes thinner from the rotation center toward the circumferential direction.

[Action]

In the compressor of the present invention, the refrigerant gas flows into the front lubrication necessary portion such as the shaft sealing device, the main bearing, the anti-rotation mechanism, and the like by the negative pressure caused by the rotation of the counterweight from a fluid inlet installed through the circumferential surface of the counterweight. And then guided to the compression chamber. In addition, when the counterweight circumferential surface is present on the fluid inlet side, the refrigerant gas is guided directly into the compression chamber through a suction passage communicating with the fluid inlet. Therefore, the refrigerant gas is introduced into the compression chamber without roughness, and the lubricating oil in the refrigerant gas is easily and sufficiently supplied to the front side lubrication necessary portion.

When a counterweight having a shape that actively guides the refrigerant gas to the front side is employed, the refrigerant gas is further introduced into the front side lubrication necessary portion by the rotation of the counterweight, so that the lubricating oil in the refrigerant gas is more easily and sufficiently lubricated. It is supplied to the required part.

EXAMPLE

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

Example 1

In the compressor of the present invention, as shown in FIG. 1, the fixed side plate 21, the shell portion 22 which is integrally formed with the fixed side plate 21, and forms an outer shell, and the fixed side plate 21 inside. The fixed scroll 2 which consists of the fixed spiral member 23 formed by the involute curve etc. has the movable side plate 41 and the movable spiral member 42 formed by the involute curve etc. inside the said movable side plate 41. The compression chamber 39 is formed by meshing with the movable scroll 4 made of). The drive shaft 33 is rotatably supported through the shaft sealing device 31 and the main bearing 32 in the front housing 30 coupled by the shell portion 22 of the fixed scroll 2 by the fastening means, An eccentric pin 34 is eccentrically provided at the inner end of the large diameter portion of the drive shaft 33, and the eccentric pin 34 is moved through the bearing 38 by cooperation with the anti-rotation mechanism 37 to be described later. The drive bush 36 supporting 4) only in orbital motion is fitted, and the counterweight 35 is attached to the eccentric pin 34 and the drive bush 36 to absorb the dynamic imbalance of the movable scroll 4. It is. The anti-rotation mechanism 37 has a fixing ring 371 having a fixing race 371 fixed to the front housing 30 and a plurality of regulating holes 372a fixed to the fixing race 371 and arranged in the circumferential direction. ), A plurality of regulating holes to be matched in the circumferential direction in which the bearing element 373 disposed in the regulating hole 372 of the fixing ring 372 and the bearing element 373 are disposed opposite the fixing ring 372. And a movable ring 374 having 374a. The movable side plate 41 of the movable scroll 4 is fixed to the movable ring 374 of the rotation prevention mechanism 37. Moreover, the discharge port 11 which communicates with the compression chamber 39 of a discharge step is penetrated in the center part of the fixed side plate 21 of the fixed scroll 2. As shown in FIG. The rear housing 10 is fixed to the fixed scroll 2, and the discharge port 11 communicates with the discharge chamber 13 formed inside the rear housing 10 via the check valve 12, and discharge chamber 13. ) Is in communication with the refrigeration circuit at the fluid discharge port (not shown).

As a characteristic constitution of this embodiment, the front housing 30 is provided with a fluid inlet 8 through which a refrigeration circuit communicates with the circumferential surface 35a of the counterweight 34. The fluid inlet 8 penetrates a part of the front housing 30 and the fixing race 371 and also penetrates a part of the fixing ring 372 as shown in FIG. The suction path 9 which communicates with the compression chamber 39 directly avoids communication.

In the compressor, rotation of the engine (not shown) is transmitted to the drive shaft 33 shown in FIG. 1 by the connection of the electromagnetic clutch (not shown), and the drive bush 36 is the anti-rotation mechanism 37. The movable scroll 4 is orbitally moved in cooperation with. At this time, as shown in the compression chamber 39 which causes the volume change in FIG. 3, and the positions of the counterweight 35, the suction path 9, etc. are shown, since the counterweight 35 of substantially fan shape rotates, as shown in FIG. , Negative pressure is generated at the rear of the counterweight 35 in the rotational direction. The refrigerant gas is easily introduced into the interior from the fluid inlet 8 by the negative pressure, and is actively supplied to the main bearing 32 and the shaft sealing device 31 which are in proximity as shown in FIG. After the anti-rotation mechanism 37, the bearing 38, and the like have passed, the volume change is introduced into the compression chamber 39 which is in a negative pressure state. In addition, when the circumferential surface 35a of the counterweight 35 is present on the fluid intake port 8 side, the refrigerant gas passes through the intake passage 9 in communication with the fluid intake port 8 as shown in FIG. It is introduced into the compression chamber under negative pressure.

For this reason, in such a compressor, the refrigerant gas is smoothly introduced into the compression chamber 39 without inhibiting suction, and the lubricating oil in the refrigerant gas is transferred to the shaft sealing device 31, the main bearing 32, and the anti-rotation mechanism 37. And the front side lubrication necessary parts, such as the bearing 38, are supplied easily and fully. Thereafter, the refrigerant gas gradually increases in pressure in the compression chamber 39 due to the orbital motion of the movable scroll 4, and pressurizes and discharges the discharge valve 12 shown in FIG. 1 from the discharge port 11. It is led out to the chamber 13 and is sent to the refrigeration circuit from the fluid discharge port.

Therefore, in the above compressor, a highly efficient production is possible by a relatively easy design or processing, and the engine burden is not increased by increasing the suction resistance of the refrigerant gas, and the front lubrication necessary part is properly lubricated by the front. It can effectively prevent the seizure of the side lubrication necessary and premature wear.

Example 2

The compressor of the embodiment shown in FIG. 4 is basically the same as that of the first embodiment, but the shape of the counterweight 351 is different. Therefore, about the structure similar to Example 1, the same code | symbol is attached | subjected and description is abbreviate | omitted. That is, in the said compressor, the counterweight 351 which consists of the inclined surface 35b which becomes thinner toward the circumferential direction from the rotation center to the front side is employ | adopted.

In such a compressor, the lubricating oil can be further supplied to the front lubrication necessary portion so that the refrigerant gas is introduced to the front side by being actively guided to the inclined surface 35b at the time of rotation of the counterweight 351.

In the compressors of the first and second embodiments described above, the fluid inlet port is installed at a position opposite to the counterweight of the front housing. However, the fluid inlet port is not limited to be installed through the front housing depending on the configuration of the compressor.

In the compressors of the first and second embodiments, the suction raceway is provided through the fixed race and the like, but this is not limited depending on the configuration of the compressor.

[Effects of the Invention]

As described above, in the scroll compressor of the present invention, the fluid suction port is provided through the counterweight circumferential surface, and the suction path directly communicating with the compression chamber communicates with the fluid suction port. Therefore, the suction resistance of the refrigerant gas is increased. A lubricating oil can be suitably supplied to the front side lubrication necessity parts, such as a shaft sealing apparatus, a bearing, an anti-rotation mechanism, by the relatively simple design or processing, without increasing.

In the compressor of the present invention, when a counterweight of a shape that actively guides the refrigerant gas is employed, the lubricant can be further supplied to the front lubrication necessary portion.

Therefore, in the scroll compressor, it is possible to produce efficiently with high efficiency, and does not burden driving systems such as engines, and it is possible to appropriately prevent lubrication failure of the front lubrication necessary portion, and further improve durability.

Claims (1)

Through the housings 10 and 30, a fixed scroll 2 fixed to the housing, a movable scroll 4 which meshes with the fixed scroll 2 to form a compression chamber 39, and a bearing 32. The drive shaft 33 is rotatably supported, the eccentric pin 34 eccentrically provided at the inner end of the drive shaft 33, and the eccentric pin 34, which are fitted to the eccentric pin 34 and cooperate with the anti-rotation mechanism 37. A driving bush 36 for supporting the movable scroll 4 only in orbital motion, and a balancing weight 35 connected to the driving shaft 33 to absorb dynamic imbalance of the movable scroll 4. And a compression compressor (39) which sucks the refrigerant gas from the fluid inlet (8) by the orbital motion of the movable scroll (4) and simultaneously increases the pressure of the refrigerant gas to discharge the fluid. The suction port 8 penetrates the circumferential surface of the counterweight 35 oppositely. And in communication with a suction passage (9) directly communicating with the compression chamber (39).