JP2008014175A - Vane rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of maintaining high compression performance and suppressing operation sound caused by minute vane jumping. <P>SOLUTION: The width of a suction channel 9 formed in a cylinder 4 is in parallel with a direction of movement of a vane. The cross-sectional shape of the channel is trapezoidal. The suction channel 9 has a shape such that the channel width gradually becomes smaller toward a termination end of the suction channel and it is zero at the termination end. Thus, a large channel area can be secured so as to prevent performance deterioration of the compressor in a high rotation region. Concurrently, since the suction channel has the shape such that the channel width gradually becomes smaller toward the termination end, it is possible to decrease the operation sound caused by vane stepped wear. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a compressor that compresses a fluid, for example, an air conditioning compressor for an automobile.

  In recent years, many vane rotary type compressors have been adopted as compressors used in vehicle air conditioner systems. However, there is a strong demand for weight reduction, noise reduction, and high performance of this type of compressor. Compressors have been used.

  A conventional compressor will be described below with reference to the drawings. 1 and 2, the rotor 1 is provided with a plurality of vane grooves 2 extending at an equal angle with respect to the tangent line of the rotor 1, and a vane 3 is slidably accommodated in each vane groove 2. The vane 3 slides on the inner wall of the cylinder 4, and the cylinder 4, the rotor 1, the vane 3, the front side plate 5 and the rear side plate 6 form a compression chamber.

  When power is transmitted from an engine (not shown) to the compressor via a belt (not shown), the rotor 1 rotates, whereby the refrigerant is sucked into the cylinder 4 from the suction port 7 and the compression chamber. And discharged from the discharge port 8 formed in the cylinder 4.

  On the inner surface of the cylinder 4, there is a suction groove 9 extending in the circumferential direction of the cylinder 4 and communicating with the suction port as shown in the figure.

  In the shape of this suction groove, if the suction passage area is small, the suction resistance generated when sucking the refrigerant in the high rotation range becomes large, and sufficient refrigerant cannot be sucked before entering the compression process. High cooling performance cannot be obtained. Therefore, it is necessary to secure a passage area as large as possible so that the refrigerant can be sufficiently sucked.

On the other hand, when the compressor having the suction groove is operated and the vane passes through the suction groove, the vane tip sliding surface has a portion in contact with the suction groove and the cylinder inner wall, so that the vane tip does not contact the cylinder. There is a part. For this reason, as the operation is continued, convex stepped wear is gradually formed at the tip of the vane. When this stepped wear part passes through the suction groove, the vane of the tip wear causes a slight jumping, resulting in a collision sound (operation sound). For this reason, some compressors have a suction groove having a shape in which the width of the groove gradually decreases at a portion where the depth of the groove gradually decreases by making the cross-sectional shape of the suction groove triangular as shown in FIG. (For example, refer to Patent Document 1).
Japanese Patent Laid-Open No. 2005-2821

  However, in the shape of the suction groove as shown in FIG. 4, the passage area just before the end becomes extremely narrow, so that the cooling performance is remarkably lowered when the compressor is operated in a high rotation range. Further, if it is intended to secure the passage area with the groove shape as shown in FIG. 4, it is necessary to deepen the groove, and as a result, the thickness of the cylinder increases and the weight increases. There was a problem that the needs as a compressor could not be met.

The present invention solves the above-described conventional problems, and provides a suction groove having a shape that secures a high passage area and suppresses sliding wear of the vane tip, and thus is lightweight, high-performance, and It aims to provide a compressor with quiet operation noise.

  In order to solve the above-described conventional problems, a compressor according to the present invention includes a cylinder having a cylindrical inner wall and a suction groove, a rotor disposed rotatably in the vicinity of the inner wall surface of the cylinder, and the rotor. A plurality of vanes inserted into and retracted into a plurality of vane slots provided, the tips of which are in contact with the inner wall of the cylinder, and the rotor are rotatably supported, and both ends of the cylinder are closed to form a compression chamber inside. In the suction groove of the compressor in which a compression mechanism is configured by a front side plate and a rear side plate, a discharge port opened to a compression chamber in a cylinder, and a high pressure chamber formed by a high pressure case, as shown in FIG. A shape in which the width of the suction groove is parallel to the vane traveling direction, and the cross-sectional shape of the groove is trapezoidal, the groove width gradually decreases toward the end of the suction groove, and the groove width at the end is zero. Possessed Is obtained by it said.

  As a result, the groove width gradually decreases at the portion where the groove depth gradually decreases toward the end of the suction groove, so that step wear of the sliding portion of the vane tip is suppressed, and as a result, the operation is performed by minute jumping of the vane While having the effect of suppressing sound, it is possible to secure a passage area close to a shape that does not have a shape in which the groove width gradually decreases at the end portion of the suction groove as represented in FIG. In addition, sufficient cooling performance can be ensured even in a high rotation range.

  The compressor of the present invention can maintain high cooling performance and suppress operation noise caused by minute jumping of vanes due to sudden pressure fluctuations of the refrigerant.

  The present invention provides a cylinder having a cylindrical inner wall and a suction groove, a rotor in which a part of the outer peripheral surface is always formed so as to form a minute gap at the axial seal point with the cylinder inner wall, and the rotor. A plurality of vanes inserted into and retracted into a plurality of vane slots, the tips of which are in contact with the inner wall of the cylinder, the rotor being rotatably supported, and both ends of the cylinder being closed to form a compression chamber therein. In the suction groove of the compressor in which the compression mechanism is configured by the front side plate and the rear side plate, the discharge port opening to the compression chamber in the cylinder, and the high pressure chamber formed by the high pressure case, the width of the groove is the vane traveling direction And the groove cross-sectional shape is trapezoidal, the groove width gradually decreases toward the end of the suction groove, and the groove width at the end is zero. Ri, while suppressing the minute jumping of the vane, it is possible to ensure a high passage area, while suppressing the deterioration of the operating noise by vanes jumping as a result, it is possible to maintain a high cooling performance.

  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 show a vane rotary type compressor according to an embodiment of the present invention.

1, 2, and 3, a cylinder 4 having a suction groove 9, a front side plate 5 and a rear side plate 6 that close both ends of the cylinder, and a drive shaft 10 that rotates in a clockwise direction by receiving a driving force. A compression chamber 11 that varies in volume by a vane 3 that is a sliding body that divides high and low pressure that slides by receiving a driving force from the drive shaft 10, a suction port 7 that guides the refrigerant to the compression chamber 11, and The discharge port 8 through which the refrigerant compressed in the compression chamber 11 discharges and the high-pressure chamber 14 formed by the high-pressure case 13 communicated by the high-pressure passage 12 constitute a compressor body, and the shape of the suction groove 9 is As shown in FIG. 3, the groove width is parallel to the vane traveling direction, the groove has a trapezoidal cross-sectional shape, and the groove width gradually decreases toward the end of the suction groove.

  In the compressor configured as above, the operation and action will be described below.

  First, when power is transmitted from an engine (not shown) to a compressor via a belt (not shown), the rotor 1 rotates, whereby the refrigerant is sucked into the cylinder 4 from the suction port 7 and compressed. It is compressed in the chamber and discharged from a discharge port 8 formed in the cylinder 4.

  When the rotor 1 rotates, the vane 3 moves while sliding on the inner wall surface of the cylinder 4. When passing over the suction groove 9, the passage area of the suction groove is sufficiently secured in the initial stage of suction, so that the refrigerant is smoothly sucked into the cylinder. At the end portion of the suction groove, the width gradually decreases as the groove depth gradually decreases, and the groove width disappears at the portion where the groove depth disappears. Therefore, even when the compressor is operated for a long time, the formation of convex stepped wear at the tip of the vane is suppressed, and the vane can enter the compression stroke while being in contact with the inner wall of the cylinder without jumping.

  In addition, in the cross section bb in FIGS. 3 to 5, the cross-sectional area of the passage is as shown in FIG. 5> FIG. 3> FIG. Therefore, the passage area of the suction groove in the present invention is always larger than that of the shape represented by FIG. 4, and the suction passage resistance is small even in a state where the compressor is operated in a high rotation range, and enters the compression stroke. By that time, the refrigerant can be sufficiently sucked. Therefore, the cooling performance close to that of the compressor having the suction groove of the shape of FIG. 5 can be secured. As described above, in the present embodiment, the width of the suction groove is parallel to the vane traveling direction, the groove has a trapezoidal cross-sectional shape, and the groove width gradually decreases toward the end of the suction groove. By setting the end portion to have a groove width of zero, it is possible to provide a low noise compressor while maintaining high performance.

The cross-sectional view of the compressor in Embodiment 1 of this invention Sectional drawing in the aa line of the compressor in Embodiment 1 of this invention Sectional drawing of the cylinder which has a suction groove in Embodiment 1 of this invention Sectional view of a cylinder having a suction groove in another conventional compressor Sectional view of a cylinder having a suction groove in a conventional compressor

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rotor 2 Vane groove 3 Vane 4 Cylinder 5 Front side plate 6 Rear side plate 7 Suction port 8 Discharge port 9 Suction groove 10 Drive shaft 11 Compression chamber 12 High pressure passage 13 High pressure case 14 High pressure chamber

Claims (1)

A cylinder having a cylindrical inner wall and a suction groove; a rotor rotatably disposed near the inner wall surface of the cylinder; and a tip inserted into and retracted into a plurality of vane slots provided in the rotor. A plurality of vanes that contact the inner wall of the cylinder, a front side plate and a rear side plate that rotatably support the rotor and close both ends of the cylinder to form a compression chamber therein; and a compression chamber in the cylinder In a vane rotary compressor having a high-pressure chamber formed by an opening discharge port and a high-pressure case, the width of the suction groove is substantially parallel to the vane traveling direction, and the cross-sectional shape of the groove is trapezoidal. A vane rotary compressor having a shape in which the groove width becomes narrower toward the groove end and the groove width at the end becomes zero.

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