JP2008025349A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent lubricating oil separation efficiency in a separation chamber at the time of high speed rotation of a compressor since the reliability and durability of the compressor is damaged due to a reduced amount of lubricating oil (OCR) at the time of high speed rotation regarding OCR in an air-conditioning system. <P>SOLUTION: The separation chamber 51 has two columnar space sections in which an introduced air body is whirled, and introductory holes 53 are provided on respective columnar space sections. When a flow velocity of coolant gas becomes fast at the time of high speed rotation of the compressor by communication between a high pressure chamber 14 and separation chamber 51, the coolant gas led to an oil storage chamber 52 through a second re-introductory hole 56 is again led to the separation chamber 51 through a first re-introductory hole 55, and is discharged into the air-conditioning system through a gas discharge outlet 57. Therefore, the reliability and durability of the compressor can be improved so that the OCR does not become too low at the time of high speed rotation of the compressor. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a compressor used in an automobile air conditioner or the like.

  Conventionally, in this type of compressor, part of the lubricating oil that lubricates the sliding portion of the compression mechanism is discharged from the compressor together with the compressed fluid and circulates in the refrigeration / air conditioning cycle. The system efficiency (thermal efficiency) decreases as the amount of lubricating oil discharged along with the fluid increases in the cycle. In addition, it has been well known that lubricating parts mixed in refrigerant gas are used to lubricate sliding portions of compressors such as vanes and rotors.

  For this reason, in order to improve the system efficiency, the lubricating oil contained therein is separated as much as possible from the fluid compressed by the compression mechanism, and then the fluid is discharged into the refrigeration cycle. As such an example, a compressor in which a centrifugal separation chamber that separates lubricating oil from a compressed fluid is provided on the discharge side of the compression mechanism is known (for example, see Patent Document 1).

  In such a compressor, a high-pressure refrigerant gas compressed by a compression mechanism and containing lubricating oil is guided to a centrifugal separation chamber, swirls in a substantially cylindrical separation chamber, and mist contained in the refrigerant gas by centrifugal force due to swirling. The lubricating oil is separated from the refrigerant gas by contacting the separation chamber wall.

FIG. 4 shows a conventional compressor described in Patent Document 1. In FIG. As shown in FIG. 4, the cylinder 101, the front side plate 106, the rear side plate 107, the high pressure case 112, the drive shaft 105, the vane 104, the high pressure chamber 114, the separation chamber 151, and the introduction hole 153 The oil drain hole 154, the oil storage chamber 152, and the communication path (reintroduction hole) 157 are configured.
JP 2003-336588 A

  However, in the conventional configuration, since the separation efficiency of the lubricating oil is good even when the compressor is operating at a low speed and a high speed, the amount of the lubricating oil in the refrigerant gas discharged during the refrigeration cycle during the high speed operation is slightly insufficient. Had the problem of becoming.

  In general, the cooling capacity of the air conditioning system is often sufficiently secured during high-speed operation of the compressor. In such a case, the separation chamber is intentionally used rather than improving the separation efficiency of the lubricating oil. It is desired to increase the lubricating oil circulating in the refrigeration cycle and further improve the reliability of the compressor by lowering the efficiency of separating the lubricating oil mixed with the high-pressure refrigerant gas in the factory (hereinafter referred to as separation efficiency) . Recently, there is a great demand for weight reduction, and in order to secure the capacity of the air-conditioning system by increasing the rotation speed of the compressor, the compression of high-speed rotation specifications has recently been made. A machine is desired.

  The present invention solves the above-mentioned conventional problems, and provides a compressor that improves the reliability and durability in consideration of the amount of lubricating oil in the refrigerant in the refrigeration cycle according to the operating speed of the compressor. Objective.

In order to solve the above-described conventional problems, the compressor of the present invention includes a first reintroduction hole that opens a reintroduction hole that communicates between the oil storage chamber and the separation chamber to a circumferential inner circumferential surface of the substantially cylindrical separation chamber; A second reintroduction hole is provided that opens from the circumferential inner peripheral surface of the cylindrical separation chamber into the oil storage chamber in the direction in which the fluid enters.

  As a result, the high-pressure refrigerant gas enters the oil storage chamber from the second reintroduction hole, disturbs the oil storage surface, and pushes out the lubricating oil from the first reintroduction hole. Since the amount of oil increases, the reliability and durability of the compressor will be improved.

  Also, since the separation efficiency can be changed by changing the size of the cross-sectional area of the second reintroduction hole, the amount of lubricating oil required during the refrigeration cycle can be adjusted according to the type and characteristics of the compressor. Become.

  The compressor of the present invention can solve the shortage of lubricating oil in the refrigerant gas, which is a problem at the time of high-speed operation of the compressor, and improve the reliability and durability while sufficiently securing the capacity of the air conditioning system.

  In the first invention, the introduction hole communicates in a tangential direction of the circumferential inner circumferential surface of the substantially cylindrical separation chamber, and the reintroduction hole extends from the oil storage chamber to the circumferential inner circumferential surface of the substantially cylindrical separation chamber. And a second reintroduction hole that opens in a direction in which the fluid enters the oil storage chamber from the circumferential inner circumferential surface of the substantially cylindrical separation chamber. During operation, the separation efficiency in the separation chamber is slightly reduced, and the amount of lubricating oil discharged during the refrigeration cycle is increased, which solves the lack of lubricating oil in refrigerant gas, which is a problem during high-speed operation, and is reliable -Durability can be improved.

  In the second invention, by changing the size of the cross-sectional area of the second reintroduction hole, the amount of high-pressure refrigerant gas entering the oil storage chamber is changed, and the separation efficiency in the separation chamber is changed. It becomes possible to change the required amount of lubricating oil. This makes it possible to make adjustments for each system to be developed, or for the displacement and type of compressor.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a compressor to which a part of the invention according to the present application is applied, and FIG. 2 is an AA sectional view (working chamber sectional view) of FIG.

  The compressor shown in the figure is a so-called vane rotary type compressor, and as illustrated, a substantially columnar rotor 2 is disposed in a cylinder 1 having a cylindrical inner wall. The rotor 2 is disposed at a position where a part of the outer periphery forms a minute gap with the inner wall of the cylinder 1. The rotor 2 is provided with a plurality of vane slots 3, and vanes 4 are slidably inserted into the vane slots 3. The rotor 2 is formed integrally with a drive shaft 5 that is rotatably supported.

  The cylinder 1 and the rotor 2 are sandwiched between the front side plate 6 and the rear side plate 7 in the rotation axis direction of the rotor 2, and both ends of the cylinder 1 are closed by these, and a working chamber for fluid compression in the cylinder. 8 is formed.

  A suction port 9 and a discharge port 10 communicate with the working chamber 8, and a gas fluid such as a refrigerant gas is sucked into the working chamber 8 from the suction port 9 and compressed and then discharged from the discharge port 10. A discharge valve 11 made of, for example, a reed valve is disposed at the outlet of the discharge port 10.

  A high pressure case 12 is attached to the rear side of the rear side plate 7, and the high pressure case 12 has a separation chamber 51 that separates and collects mist-like lubricating oil contained in the refrigerant gas compressed in the working chamber 8. Is provided.

  The gas fluid compressed in the working chamber 8 and discharged from the discharge port 10 is guided by the guide passage 13 continuously provided in the cylinder 1, the rear side plate 7 and the high pressure case 12, and formed on the side wall of the separation chamber 51. It is introduced into the separation chamber 51 from the high-pressure chamber 14 through the introduced introduction hole 53. A gas discharge port 57 for exhausting the refrigerant gas from which the lubricating oil has been separated in the separation chamber 51 into the refrigeration cycle is opened at the upper portion of the separation chamber 51. An oil drain hole 55 through which lubricating oil separated and collected from the gas is discharged to the oil storage chamber 52 is opened.

  The refrigerant gas discharged from the separation chamber 51 through the gas discharge port 57 circulates in the refrigeration cycle, eventually returns to the suction port 9 described above, is compressed again, and circulates in the aforementioned cycle. The oil drain hole 55 opened at the lower part of the separation chamber 51 communicates with an oil storage chamber 52 formed between the high pressure case 12 and the rear side plate 7. Therefore, the lubricating oil separated and collected from the refrigerant gas in the separation chamber is stored in the oil storage chamber 52 through the oil drain hole 55.

  The lubricating oil stored in the oil storage chamber 52 is supplied to the rotor 2, the vane 4, the inner wall of the cylinder 1, and the like constituting the compression mechanism via the oil supply passage 17, lubricates each part, and is supplied to the vane back pressure chamber 16. The pressure acts to urge the vane 4 to the outside of the rotor 2. Lubricating oil is supplied through an oil supply passage 17 for supplying the lubricating oil from the oil storage chamber 52 to the compression mechanism, and the lubricating oil stored in the oil storage chamber 52 through the vane back pressure adjusting device 15 is supplied to the oil supply passage 17. Oil is supplied. The vane back pressure adjusting device 15 controls the oil supply pressure and the amount of oil supplied to the compression mechanism according to the refrigerant gas pressure around the compression mechanism. The gas accumulated in the upper part of the oil storage chamber 52 is introduced again into the separation chamber 52 through the first reintroduction hole 55.

  Thereby, the oil level rise in the oil storage chamber 52 is promoted, and the separation ability can be improved.

  In addition, the swirling flow of the high-pressure refrigerant enters the oil storage chamber 52 from the separation chamber 51 from the second reintroduction hole 56. As a result, the gas accumulated in the upper portion of the oil storage chamber 52 and the high-pressure refrigerant gas introduced into the oil storage chamber from the second reintroduction hole 56 are again introduced into the separation chamber 52 and discharged from the gas discharge hole 57 during the cycle. Therefore, the separation efficiency in the separation chamber is reduced.

  Hereinafter, the operation of the compressor according to the above-described embodiment will be described.

  When power is transmitted from a drive source such as an in-vehicle engine and the drive shaft 5 and the rotor 2 rotate clockwise in FIG. 2, a low-pressure refrigerant gas flows into the working chamber 8 from the suction port 9 accordingly. The high-pressure refrigerant gas compressed with the rotation of the rotor 2 pushes up the discharge valve 11 from the discharge port 10 and flows into the guide passage 13. Further, the high-pressure refrigerant gas is introduced into the separation chamber 51 through the introduction hole 53, and the lubricating oil contained in the refrigerant gas is separated and collected in the separation chamber 51.

  By the way, the separation chamber 51 is a so-called centrifugal oil separator, and is composed of a cylindrical space portion X and an inverted conical space portion Y which are coupled to each other as shown in FIG. The introduction hole 53 is provided eccentrically from the central axis of the cylindrical space portion X of the separation chamber 51 so as to guide the refrigerant gas introduced into the separation chamber 51 in the tangential direction of the cylindrical space portion X, that is, the refrigerant It is provided so that gas can be introduced into the separation chamber 51 along the inner peripheral surface 50 of the cylindrical space portion X.

Accordingly, the refrigerant gas introduced into the separation chamber 51 rotates in the circumferential direction in the separation chamber 51, and the lubricating oil having a large specific gravity comes into contact with the inner wall of the separation chamber 51 and is separated from the refrigerant gas due to the centrifugal force caused by the rotation. The The separated lubricating oil moves downward along the inner peripheral surface 50 and is aggregated in the central portion by the inverted conical space portion Y.

  Here, generally, the lubricating oil circulation rate (OCR) in the refrigeration cycle is desired to have the following characteristics as described above with respect to the rotational speed of the compressor. First, when the vehicle speed is low to medium speed, that is, when the compressor speed is low to medium speed, the OCR is low. Next, when the vehicle speed is high speed, the compressor speed is high. It is desired that the OCR is relatively high in the region.

  In the present embodiment, as shown in FIG. 1, two columnar separation chambers 51 are provided, and the columnar portion of the separation chamber 51 close to the gas discharge port 57 is enlarged by about 1 mm in diameter. The size of the introduction hole differs depending on the displacement of the compressor, but when the displacement of the compressor is about 80 cc, the introduction hole 53 is about φ6.5, the oil discharge hole is φ4.0, One reintroduction hole 55 is preferably φ3.5 and the second reintroduction hole 56 is preferably about φ1.0.

  However, since the optimum size of the introduction hole varies depending on the air conditioning system and the displacement of the compressor, the optimal size cannot be said to be the same depending on the air conditioning system even if the displacement is the same. It is necessary to confirm and set.

  As a result, the gas accumulated in the upper portion of the second reintroduction hole 56 oil storage chamber 52 is again introduced into the separation chamber 52 and discharged from the gas discharge hole 57 during the cycle, so that the separation efficiency in the separation chamber decreases. And OCR increases. Therefore, the lower the rotation speed of the compressor, that is, the smaller the flow velocity of the swirling flow of the high-pressure refrigerant gas, the less the effect on the reduction in separation efficiency, and the higher the speed, the greater the effect. It will be.

  Therefore, since the cooling capacity of the air conditioning system is sufficiently secured during high-speed operation of the compressor, the OCR is not lowered more than necessary. Rather, the reliability is improved by slightly increasing the OCR during high-speed rotation of the compressor. Will improve.

  In the above-described embodiment, the vane type rotary compressor is described as an example of the compressor. However, the present invention is not limited to this and can be applied to other compressors such as a rolling piston type and a scroll type. It is.

The longitudinal cross-sectional view of the compressor which shows embodiment to which a part of this invention was applied AA sectional view of FIG. BB sectional view of FIG. Sectional view of a conventional compressor

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylinder 2 Rollover 3 Vane slot 4 Vane 5 Drive shaft 6 Front side plate 7 Rear side plate 8 Working chamber 9 Suction port 10 Discharge port 11 Discharge valve 12 High pressure case 13 Guide passage 14 High pressure chamber 15 Vane back pressure adjustment device 16 Vane Back pressure chamber 17 Oil supply passage 50 Inner peripheral surface 51 Separation chamber 52 Oil storage chamber 53 Introduction hole 54 Oil drain hole 55 First reintroduction hole 56 Second reintroduction hole 57 Gas exhaust port

Claims (2)

A compression mechanism for compressing a fluid containing lubricating oil; a discharge chamber into which the fluid compressed by the compression mechanism is guided; a substantially cylindrical separation chamber for separating a part of the lubricating oil contained in the fluid; and the fluid An oil storage chamber for storing the lubricating oil separated from the discharge chamber, an introduction hole that communicates the discharge chamber and the substantially cylindrical separation chamber, a discharge hole that communicates the separation chamber and the oil storage chamber, the oil storage chamber, and the In the compressor having a reintroduction hole that communicates with the separation chamber, the introduction hole communicates with a tangential direction of a circumferential inner peripheral surface of the substantially cylindrical separation chamber, and the reintroduction hole extends from the oil storage chamber to the substantially cylindrical shape. A first reintroduction hole that opens to the circumferential inner circumferential surface of the cylindrical separation chamber, and a second reintroduction hole that opens in the direction in which the fluid enters the oil storage chamber from the circumferential inner circumferential surface of the substantially cylindrical separation chamber A compressor comprising: The compressor according to claim 1, wherein the second reintroduction hole has a smaller cross-sectional area than the first reintroduction hole.

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