JP2007309281A - Vane rotary type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent increase in vane back pressure in the vicinity of an axial seal point. <P>SOLUTION: This vane rotary type compressor is provided with a cylinder 1 having a cylindrical inner wall; a rotor 2 arranged inside the cylinder 1 and provided with outer periphery partially forming a small gap between the rotor 2 and the cylinder 1 inner wall; vanes 4 slidably inserted into a plurality of vane grooves 3 provided in the rotor 2 and slid on the cylinder 1 inner wall; and a front side plate 6 and a rear side plate 7 closing both ends of the cylinder 1 and constituting an operation chamber 5. In at least one of the front side plate 6 or the rear side plate 7, an approximately arcuate groove 10 communicated with the vane grooves 3 is provided, and a closing section 9 for preventing communication of one vane pack pressure chamber 8 with the other vane back pressure chamber 8 is provided on the approximately arcuate groove 10. By forming a pressure relief space 21 communicated with the vane grooves 3 in a section from the discharge port 14 to the axial seal point 12, pressure increase in the vane back pressure chambers 8 is prevented. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a vane back pressure control structure suitable for a vane rotary compressor used for automobile air conditioning.

  Conventionally, this type of vane rotary type compressor uses the centrifugal force generated by the rotation of the rotor to press the vane tip against the inner circumferential surface of the cylinder, but that alone is the seal between the vane tip and the cylinder inner circumferential surface. Therefore, the pressure in the working chamber is applied to the back surface of the vane so that the vane protrudes from the rotor. Further, it is well known that a vane noise is generated due to vane jumping as a unique problem.

  In addition, the problem that this type of vane rotary compressor generates a vane noise is that the load applied to the tip of the vane becomes higher than the vane back pressure as the pressure in the cylinder rises due to compression, so that It is a sound that is generated when it is slightly disengaged from the cylinder and collides with the inner wall of the cylinder again (hereinafter referred to as vane chattering phenomenon). The problem of the vane noise is that the volume of the vane back pressure chamber at the back of the vane decreases as the gap between the cylinder and the rotor decreases by providing a closed section where the pressure in the working chamber does not act on the back surface of the vane. This has been basically overcome by setting the vane back pressure chamber to a high pressure (see, for example, Patent Document 1).

  4 and 5 show a conventional vane rotary compressor described in Patent Document 1. FIG. There are a cylinder 101 having a cylindrical hollow portion inside, and a substantially cylindrical rotor 102 in which at least a part of the outer peripheral portion is rotatably disposed close to the inner wall surface of the cylinder 101. The rotor has three vane grooves 103 substantially radially, and the vanes 104a, 104b, and 104c are inserted into the vane groove 103 so as to be freely protruded and configured.

In order to increase the vane back pressure, the oil in the oil reservoir 109 in the high-pressure case 108 is guided to the substantially arc-shaped groove 106, the back pressure in the vane back pressure chambers 105a and 105b is increased, and the cylinder 101 It is pressed against the inner wall. Further, as a closed section from the middle of the compression process to the axial seal point 107, the vane back pressure chamber 105c is pressed against the inner wall of the cylinder 101 at a higher pressure than the vane back pressure chambers 105a and 105b.
Japanese Patent Laid-Open No. 61-241481

  However, in the conventional configuration, since the section from the discharge port to the axial seal point is a closed section, the vane back pressure becomes too high. Therefore, the vane is excessively pressed against the inner wall of the cylinder, resulting in increased wear on the vane tip and the inner wall of the cylinder and power loss of the compressor, resulting in poor reliability and efficiency of the compressor. It was.

  The present invention solves the above-mentioned conventional problems, and prevents the vane back pressure from becoming excessively high in the section from the discharge port to the axial seal point, thereby increasing the wear of the vane tip and the cylinder inner wall, and compressing. An object of the present invention is to provide a vane rotary compressor that improves power loss and improves reliability and performance.

In order to solve the conventional problem, the vane rotary compressor of the present invention includes a pressure relief space communicating with the vane back pressure chamber or the vane groove in the closed section.

  As a result, the vane back pressure chamber and the pressure relief space communicate with each other in the closed section, so that the pressure in the vane back pressure chamber is released to the pressure relief space, thereby preventing the vane back pressure from becoming too high. This increases the wear of the tip and the cylinder inner wall, improves the power loss of the compressor, and improves the reliability and performance.

  In the vane rotary compressor according to the present invention, the pressure relief space communicates with the vane groove in the section from the discharge port to the axial seal point.

  Thereby, suppression of the vane back pressure by the pressure relief space can be performed only in the section where the vane back pressure is high. Further, the pressure relief space is not directly communicated with the vane back pressure chamber, but is communicated through the vane groove, so that a sudden change in the vane back pressure is prevented and the behavior of the vane is stabilized.

  The vane rotary compressor of the present invention is formed so that the substantially arc-shaped groove and the vane groove do not communicate until the vane and the vane groove reach the axial seal point.

  This prevents the vane back pressure from being lowered more than necessary by connecting the vane back pressure chamber through the vane groove to both the pressure relief space and the substantially arcuate groove in the closed section. Will be stabilized.

  The vane rotary compressor according to the present invention prevents the vane back pressure from becoming excessively high in the section from the discharge port to the axial seal point, thereby increasing the wear of the vane tip and the cylinder inner wall and the power loss of the compressor. Can improve reliability and performance.

  According to a first aspect of the present invention, there is provided a cylinder having a cylindrical hollow portion therein, a substantially cylindrical rotor in which at least a part of an outer peripheral portion is rotatably disposed close to an inner wall surface of the cylinder, and the rotor Has a plurality of vane grooves in a substantially radial manner, is slidably inserted into the vane groove, and has a tip abutting against the inner wall surface of the cylinder and at least a compression space formed between the cylinder and the rotor. A vane partitioning into the discharge space, a front side plate and a rear side plate constituting the working chamber by closing both ends of the cylinder, a vane back pressure chamber formed by the vane groove, the vane, the front portion and the rear side plate, and the front A closed section in which fluid adjusted to at least one of the front side plate and the rear side plate is guided to the vane back pressure chamber, and each of the plurality of vane back pressure chambers does not communicate with each other as the rotor rotates. In the vane rotary type compressor having a substantially arc-shaped groove, the vane is provided with a pressure relief space in the closed section so as to communicate with the vane back pressure chamber or the vane groove. By releasing the back pressure into the pressure relief space, the vane back pressure is prevented from becoming too high, increasing the wear of the vane tip and cylinder inner wall, improving the power loss of the compressor and improving the reliability and performance. can do.

  The second aspect of the invention is particularly a section in which the vane back pressure is suppressed by connecting the pressure relief space of the first invention to the vane groove in the section from the discharge port to the axial seal point. Therefore, wear and power loss can be improved within an appropriate range. In addition, the pressure relief space does not communicate directly with the vane back pressure chamber, but communicates with the vane groove, so that the vane groove space is a minute space formed by the vane, the rotor, and the rear side plate. It communicates with the pressure relief space through the minute space of the vane groove, so that a sudden change in the vane back pressure can be prevented and the behavior of the vane can be stabilized.

  In the third invention, in particular, the substantially arc-shaped groove of the first and second inventions is formed so that the substantially arc-shaped groove and the vane groove do not communicate until the vane and the vane groove reach the axial seal point. In the closed section, the vane back pressure chamber communicates with both the pressure relief space and the substantially arc-shaped groove through the vane groove, thereby preventing the vane back pressure from being lowered more than necessary. Back pressure can be stabilized.

  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)
1, 2, and 3 are a longitudinal sectional view and a transverse sectional view of a vane rotary compressor according to a first embodiment of the present invention, and a rear side plate in which a substantially arc-shaped groove and a pressure relief space are formed. It is shown.

  1, 2, and 3, a cylinder 1 having a cylindrical hollow portion inside, and a substantially cylindrical shape in which at least a part of the outer peripheral portion is rotatably disposed near the inner wall surface of the cylinder 1. The rotor 2 and the rotor 2 have a plurality of vane grooves 3 in a substantially radial manner. The rotor 2 is slidably inserted into the vane groove 3, and the tip abuts against the inner wall surface of the cylinder 1. A vane 4 that partitions a compression space formed between the two into at least a suction space and a discharge space, a front side plate 6 and a rear side plate 7 that close both ends of the cylinder 1 to form a working chamber 5, and the vane groove 3 The vane back pressure chamber 8 formed by the vane 4, the front side plate 6 and the rear side plate 7, and the fluid adjusted to at least one of the front side plate 6 or the rear side plate 7, the vane back pressure. Led to chamber 8 and several Each of the vane back pressure chambers 8 includes a substantially arc-shaped groove 10 that is provided with a closed section 9 that does not communicate with each other during one rotation of the rotor 2, and the rotor 2. And a drive shaft 11 that is rotatably supported, and a suction port 13 and a discharge port 14 that communicate with the working chamber 5 across an axial seal point 12 where the outer periphery of the rotor 2 and the inner wall of the cylinder 1 are close to each other. , A discharge valve 15 provided on the outlet side of the discharge port 14, an oil separation unit 16 that separates lubricating oil in the compressed high-pressure fluid that communicates with the discharge port 14, and the oil separation unit 16 A high-pressure case 18 having an oil sump 17 at the lower part, an oil supply passage 19 for communicating the vane back pressure chamber 8 and the oil sump 17, and the oil supply passage 19 are communicated during compressor operation. Oil supply passage opening and closing hand that shuts off when stopped In the vane rotary type compressor having the vane back pressure applying device 20, the pressure relief space 21 is communicated with the vane groove 3 in the section from the discharge port 14 to the axial seal point 12 in the closed section 9. The substantially arcuate groove 10 is formed so that the vane groove 3 and the substantially arcuate groove 10 do not communicate with each other, with the end point of the closed section 9 extending to the axial seal point 12. Yes.

  About the vane rotary type compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  First, a drive shaft 11 driven by a belt from a vehicle engine (not shown) and integrally formed with the rotor 2 is axially supported by the front side plate 6 and the rear side plate 7. The volume changes, the refrigerant containing the lubricating oil is sucked and compressed, and discharged from the discharge port 14.

  The discharged refrigerant containing the lubricating oil is separated in the oil separating portion 16 formed in the high pressure case 18 and stored in the oil reservoir 17 formed in the lower direction of the high pressure case 18.

The stored lubricating oil is supplied to the substantially arc-shaped groove 10 through the vane back pressure applying device 20 and the oil supply passage 19 of the rear side plate 7 due to the differential pressure between the internal pressure of the high pressure case 18 and the internal pressure of the cylinder 1. The vane back pressure chamber 8 is set to a high pressure, and the vane 4 is pressed against the inner wall of the cylinder 1. Further, the sliding portions such as the rotor 2, the vane 4, the front side plate 6, the rear side plate 7 and the like are lubricated. As the rotor 2 rotates and the vane 4 enters the closed section 9, the pressure in the vane back pressure chamber 8 becomes higher.

  In the section from the discharge port 14 to the axial seal point 12, the vane back pressure chamber 8 and the pressure relief space 21 communicate with each other, thereby preventing an increase in the vane back pressure. Further, the vane back pressure chamber 8 and the pressure relief space 21 communicate with each other through the vane groove 3, thereby preventing the vane back pressure from rapidly decreasing.

  In the closed section 9, the vane back pressure chamber 8 communicates only with the pressure relief space 21, and when the vane 4 reaches the axial seal point 12, the communication between the vane back pressure chamber 8 and the pressure relief space 21 is interrupted, The vane back pressure chamber 8 communicates with the substantially arc-shaped groove 10.

When the mechanism is manufactured and operated for each part with predetermined dimensions, the pressure change in the working chamber 5 and the vane back pressure chamber 8 is shown below. Since they correspond to the suction pressure and the internal pressure of the high-pressure case 18, respectively, they are about 1.5 kg / cm ² and 30 kg / cm ² . Thereafter, the pressure in the working chamber 5 rises because it is compressed, and the pressure in the vane back pressure chamber 8 also rises after being compressed by entering the closed section. When the vane 4 is positioned at the discharge port 14, the pressure in the working chamber 5 is about 40 kg / cm ² , and the pressure in the vane back pressure chamber 8 is about 50 kg / cm ² when there is no pressure relief space. The pressure in the vane back pressure chamber 8 necessary to press the vane 4 against the inner wall of the cylinder 1 so that the vane 4 does not cause jumping with respect to the pressure in the working chamber 5 is 0.8 due to the component force of the force applied to the vane 4. Since a pressure of about twice or more is required, the pressure of the vane back pressure chamber 8 when it is located at the discharge port 14 may be 32 kg / cm ² or more, so that the pressure of 18 kg / cm ² is higher than the necessary pressure. As a result of this overpressure, the inner wall of the cylinder 1 and the tip of the vane 4 have increased wear, resulting in power loss. Therefore, it can be said that it is optimal that the pressure relief space has a volume that is sufficient to escape 18 kg / cm ^{2 and} that does not escape more than necessary.

  Further, the pressure relief space of the mechanism can be formed at low cost because it can be formed only by processing the groove in the front side plate 6 or the rear side plate 7.

  As described above, the vane rotary compressor according to the present invention improves the wear and loss of the vane tip and the inner wall of the cylinder and the power loss of the compressor, and improves reliability and performance. It can be applied to other uses such as compressors.

FIG. 2 is a longitudinal sectional view of the vane rotary type compressor according to the first embodiment of the present invention (cross-sectional view taken along line AA in FIG. 2). 1 is a cross-sectional view of a vane rotary compressor according to Embodiment 1 of the present invention. Rear side plate view forming the oil supply passage in the first embodiment of the present invention Cross-sectional view of a conventional vane rotary compressor (A-A cross-sectional view in FIG. 5) Longitudinal sectional view of a conventional vane rotary compressor

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylinder 2 Rollover 3 Vane groove 4 Vane 5 Actuation chamber 6 Front side plate 7 Rear side plate 8 Vane back pressure chamber 9 Containment section 10 Substantially circular groove 11 Drive shaft 12 Axial seal point 13 Discharge valve 16 Oil separator 17 Oil reservoir 18 High pressure case 19 Oil supply passage 20 Vane back pressure applying device 21 Pressure relief space

Claims (3)

A cylinder having a cylindrical hollow portion therein, a substantially cylindrical rotor in which at least a part of the outer peripheral portion is rotatably disposed close to the inner wall surface of the cylinder, and a plurality of the rotor in a substantially radial manner The vane groove is slidably inserted into the vane groove, the tip abuts against the inner wall surface of the cylinder, and the compression space formed between the cylinder and the rotor is divided into at least a suction space and a discharge space. A front side plate and a rear side plate that close both ends of the cylinder to form a working chamber, a vane back pressure chamber formed by the vane groove, the vane, the front and rear side plates, and the front side plate. Alternatively, the fluid adjusted to at least one of the rear side plates is guided to the vane back pressure chamber, and the plurality of vane back pressure chambers do not communicate with each other during one rotation as the rotor rotates. In the vane rotary type compressor having a substantially arc-shaped groove that is provided with a gap (hereinafter referred to as a closed section), the closed section includes a pressure relief space, and the pressure relief space is the vane back pressure. A vane rotary compressor that communicates with the chamber or the vane groove. 2. The vane rotary compression according to claim 1, wherein the pressure relief space communicates with the vane groove in a section between a discharge port and a proximity point (hereinafter referred to as an axial seal point) between the rotor and the cylinder. Machine. The substantially arc-shaped groove is characterized in that the end point of the confining section is set to the axial seal point and does not communicate with the vane groove until the vane groove and the vane reach the axial seal point. Item 3. A vane rotary compressor according to item 1 or 2.

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