CN220667821U - Vortex disc sealing antifriction device for electric vortex compressor - Google Patents

Abstract

The utility model relates to the field of automobile air conditioner compressors, in particular to a vortex disc sealing antifriction device for an electric vortex compressor, which comprises a movable vortex disc, a static vortex disc and a sealing strip. The fixed vortex disc and the movable vortex disc are oppositely arranged in the cylinder body. The fixed scroll is fixed on the cylinder body, and the back side of the movable scroll is abutted against a cylinder body supporting seat fixed on the cylinder body. And sealing grooves are arranged on the tooth end surfaces of the movable vortex disc and the fixed vortex disc. The sealing strip is embedded and installed in the sealing groove. The utility model utilizes the floating sealing strip with the multi-point groove design to replace a complex back pressure structure, reduces the axial leakage of the axial clearance of the movable vortex disk, thereby reducing the power consumption and improving the performance of the compressor. Meanwhile, because the back pressure of the movable vortex plate is canceled, the end face of the vortex tooth of the movable vortex plate is not in direct contact with the bottom face of the vortex tooth, and the abrasion of the movable vortex plate is greatly reduced. In addition, the sealing strip made of plastic materials can adsorb fine impurities in the movable vortex plate, so that abrasion of the movable vortex plate caused by impurity problems is reduced.

Description

Vortex disc sealing antifriction device for electric vortex compressor

Technical Field

The utility model relates to the field of automobile air conditioner compressors, in particular to a vortex disc sealing antifriction device for an electric vortex compressor.

Background

The wraps of the orbiting scroll of an electric scroll compressor are formed by a pair of conjugate curves. The movable vortex plate is controlled by the anti-rotation limiting mechanism in direction, and the movable vortex plate is driven by the crankshaft to rotate around the fixed vortex plate. After the movable vortex plate is inserted, the vortex teeth are meshed with each other to form a plurality of pairs of crescent volume cavities, the volume of the crescent volume cavities gradually decreases towards the vortex center along with the rotation of the movable vortex plate, sucked low-pressure refrigerant is continuously compressed in the crescent volume cavities, and finally compressed high-temperature high-pressure refrigerant is discharged to the rear cover high-pressure cavity through the central exhaust hole of the fixed vortex plate.

The pressure in each crescent volume cavity of the movable vortex disk can enable the movable vortex disk and the fixed vortex disk to be separated along the axial direction during working, so that the end face of the teeth of the movable vortex disk is separated from the bottom face of the teeth of the fixed vortex disk, and the end face of the teeth of the fixed vortex disk is separated from the bottom face of the teeth of the movable vortex disk. Here a solution for such axial leakage needs to be considered.

In the conventional electric scroll compressor design, a back pressure structure is generally designed, and the axial force applied to the movable scroll is offset by the back pressure. The movable vortex plate is assembled on the middle machine body, a back pressure cavity is arranged in the middle machine body, compressed high-pressure oil gas is introduced into the back pressure cavity of the middle machine body through an oil return channel, and the pressure in the back pressure cavity is controlled through pressure relief of a pressure relief channel, so that the stable back pressure is maintained to balance the gas force exerted on the movable vortex plate. In this design, the oil return passage and the pressure relief passage are structured in accordance with the optimum performance state that can be achieved under the design conditions. However, the actual working condition of the compressor is not stable, and the compressor with the back pressure structure cannot meet the condition that all working conditions of the compressor are in an optimal performance state, and in some working conditions, back pressure is possibly larger than the axial force of gas borne by the movable scroll, the movable scroll is in contact with the fixed scroll more tightly due to the large back pressure, the power consumption is increased, and the movable scroll is worn due to extreme conditions. In some working conditions, the back pressure may be smaller than the axial force of the gas borne by the movable vortex plate, the bearing clearance of the movable vortex plate becomes larger, the leakage of the tooth end is increased, the volumetric efficiency is reduced, and the performance is deteriorated. Such back pressure structural design and control of back pressure is complex and difficult.

Disclosure of Invention

The utility model aims to provide a vortex disc sealing antifriction device for an electric vortex compressor, which is used for solving the problems in the prior art. The novel optimization and improvement scheme is provided for solving the problems of axial leakage and tooth end abrasion of the movable vortex plate.

The utility model provides a vortex disc sealing antifriction device for an electric vortex compressor, which is characterized by comprising an movable vortex disc, a fixed vortex disc and a sealing strip; the fixed vortex disc and the movable vortex disc are oppositely arranged in the cylinder body; the fixed vortex disc is fixed on the cylinder body, and the back side of the movable vortex disc is abutted against a cylinder body supporting seat fixed on the cylinder body; sealing grooves are formed in the tooth end faces of the movable vortex disc and the fixed vortex disc; and the sealing strip is embedded and installed in the sealing groove.

Further, a multipoint groove is formed in one side, facing the sealing groove, of the sealing strip, and the other side is a plane.

Further, the sealing groove is arranged along the trend of the tooth end of the fixed vortex disk or the movable vortex disk.

Further, the range occupied by the sealing groove on the fixed scroll or the movable scroll is smaller than the coverage range of the movable scroll and the fixed scroll after being relatively installed.

Further, gaps are reserved on two sides of the sealing strip and the sealing groove.

Further, the gap is preferably 0.1 mm.

Further, the thickness of the sealing strip is smaller than the depth of the sealing groove.

Further, the preferred value for the thickness to be less than the depth is 0.05 mm.

Further, after the movable scroll and the fixed scroll are relatively attached to each other, a gap is left between the movable scroll and the fixed scroll.

Further, the void is preferably 0.05 mm.

The utility model relates to a vortex plate sealing antifriction device for an electric vortex compressor, which utilizes a floating sealing strip with a multipoint groove design to be matched on an electric vortex plate of the electric vortex compressor to replace a complex back pressure structure, so that axial leakage caused by axial clearance of the electric vortex plate is reduced, and the power consumption is reduced, and the performance of the compressor is improved. Meanwhile, because the back pressure of the movable vortex plate is canceled, the end face of the vortex tooth of the movable vortex plate is not in direct contact with the bottom face of the vortex tooth, and the abrasion of the movable vortex plate is greatly reduced. In addition, the sealing strip is made of plastic materials, and fine impurities in the movable vortex plate can be adsorbed, so that abrasion of the movable vortex plate caused by impurity problems is reduced.

Drawings

FIG. 1 is a schematic view of the construction of a preferred embodiment of a scroll seal antifriction device for an electric scroll compressor of the present utility model;

FIG. 2 is a schematic illustration of the mating of seal grooves and seal strips in a preferred embodiment of a scroll seal antifriction device for an electric scroll compressor of the present utility model;

FIG. 3 is a schematic view of the assembly of a seal strip incorporated into an orbiting scroll of a preferred embodiment of a scroll seal antifriction device for an electric scroll compressor of the present utility model;

FIG. 4 is a schematic view of the assembly of a seal strip into a fixed scroll in a preferred embodiment of a scroll seal antifriction device for an electric scroll compressor of the present utility model;

FIG. 5 is a schematic view of the seal strip in a preferred embodiment of a scroll seal antifriction device for an electric scroll compressor of the present utility model;

fig. 6 is a cross-sectional view of A-A in fig. 5.

Wherein, 1-movable vortex disk, 2-static vortex disk, 3-cylinder body, 4-seal groove, 5-sealing strip, 6-cylinder body supporting seat.

Detailed Description

Specific embodiments of the present utility model will be described below with reference to the accompanying drawings.

Examples

Referring to fig. 1 to 6, the present utility model discloses a scroll sealing antifriction device for an electric scroll compressor, which comprises a movable scroll 1, a fixed scroll 2 and a sealing strip 3.

Like a conventional scroll compressor, the orbiting scroll 1 and the fixed scroll 2 are relatively installed in the cylinder 3, and the fixed scroll 2 is fixed to the cylinder 3 to remain stationary. Unlike the conventional scroll compressor, in the present embodiment, the back side of the orbiting scroll 1 directly abuts against the cylinder support 6, and a back pressure mechanism is not required. The cylinder support 6 is either part of the cylinder 3 or is fixed to the cylinder 3. The electric vortex compressor with the sealing antifriction structure can cancel the traditional back pressure structure and simplify the structure of the compressor.

The seal grooves 4 are arranged on the tooth end surfaces of the movable vortex plate 1 and the fixed vortex plate 3, namely the surfaces which are relatively attached. The seal groove 4 is positioned in the center of the tooth end of the movable vortex disk 1 or the fixed vortex disk 2 and is arranged along the involute trend of the tooth end. The seal groove 4 extends along the involute on the orbiting scroll 1 or the fixed scroll 2, and the longer the seal groove is, the larger the covered area is. The present design requires that the area occupied by the seal groove 4 is smaller than the mutual coverage of the orbiting scroll 1 and the fixed scroll 2 after installation. That is, during the operation of the scroll compressor, no matter where the orbiting scroll 1 is located, the sealing groove 4 is located between the orbiting scroll 1 and the fixed scroll 2, otherwise, the sealing strip 5 embedded in the sealing groove 4 during operation has a risk of buckling and breaking. On the premise of meeting the conditions, the sealing groove 4 and the sealing strip 5 are as long as possible, so that the maximum sealing is realized.

The length of the sealing strip 5 is matched with the sealing groove 4, and the sealing strip is embedded and installed in the sealing groove 4. The sealing strip 5 is made of strip-shaped plastic, and the section of the sealing strip is rectangular. Wherein a multipoint groove is provided on one side of the sealing strip 5 embedded in the sealing groove 4. The other surface of the sealing strip 5, in particular the side facing the contralateral scroll, is planar. The multi-point grooves on the sealing strip 5 are used for storing oil, so that the sealing strip cannot be entirely clung to the bottom of the sealing groove 4, and the sealing strip is easy to separate from the sealing groove 4 to float upwards after the pressure at the bottom of the groove rises.

The sealing strip 5 is required to be slightly narrower than the sealing groove 4, so that pressure gas can enter the bottom of the sealing strip 5 from two sides, the sealing strip 5 is ejected out of the sealing groove 4 to float, and only the floating sealing strip 5 can realize the sealing of the axial gap. I.e. a gap is left between the sealing strip 5 and the sealing groove 4. This gap is preferably 0.1 mm.

Meanwhile, the sealing strip 5 is required to be slightly thinner than the sealing groove 4, so that the sealing strip 5 can move up and down in the sealing groove 4. The preferred sealing strip 5 has a thickness which is 0.05 mm less than the depth of the sealing groove 4.

After the movable vortex disc 1 and the fixed vortex disc 2 are relatively attached and installed, a gap is reserved between the movable vortex disc 1 and the fixed vortex disc 2, so that the movable vortex disc 1 can freely rotate without directly contacting the fixed vortex disc 2 to cause abrasion of tooth end surfaces. The gap is preferably 0.05 mm.

The working principle of the scroll sealing antifriction device for the electric scroll compressor of the present utility model is explained below.

When the scroll compressor starts to work, the refrigerant sucked from the air suction port is sucked into the outermost crescent volume cavity formed by the movable scroll 1 and the fixed scroll 2, and along with the operation of the movable scroll 1, the refrigerant is gradually compressed to the inner crescent volume cavity until being discharged into the rear cover from the central air outlet of the fixed scroll 2. As the refrigerant is compressed, the pressure in the crescent-shaped volume chamber formed by the orbiting scroll 1 and the fixed scroll 2 is also gradually increased. At this time, the fixed scroll 2 is pressed and fixed by the cylinder body, and the movable scroll 1 is used as a movable part and can be separated outwards under the action of the pressure in the crescent-shaped volume cavity, so as to lean against the cylinder body supporting seat 6. At this time, the movable gap is transferred to the tooth end formed by the movable scroll 1 and the fixed scroll 2, and the refrigerant leaks from this axial gap without sealing.

In order to reduce such axial leakage, in this embodiment, seal grooves 4 are added on the end faces of the scroll teeth of the movable scroll 1 and the fixed scroll 2, and then seal strips 5 with multi-point groove design are filled in the seal grooves 4, and after the movable scroll 1 and the fixed scroll 2 are mutually faced and attached, the seal strips 5 float in the seal grooves 4. At this time, crescent volume intracavity pressure when the compressor operates for part high pressure refrigerant enters into the inside of seal groove 4 through the peripheral clearance of sealing strip 5 and seal groove 4, is ejecting sealing strip 5 from the rear side in seal groove 4, makes sealing strip 5 come up, and laminating is rather than relative vortex tooth bottom surface, fills the axial clearance between movable vortex dish 1 and the quiet vortex dish 2 that produces because of receiving axial force influence, reduces axial leakage.

In addition, when the compressor is installed, a gap is reserved between the movable vortex disc 1 and the fixed vortex disc 2, so that even when enough pressure is not established at the beginning of the operation of the compressor, the tooth end surfaces of the vortex disc 1 and the fixed vortex disc 2 are not contacted, and the abrasion between metals is avoided. After the compressor pressure is built up, the movable scroll 1 is affected by axial force, separated from the fixed scroll 2 and leans against the cylinder support seat 6, so that metal-to-metal abrasion between the tooth end surfaces of the scroll 1 and the fixed scroll 2 is further avoided.

Finally, the sealing strip 5 is made of plastic, the hardness of the sealing strip is far lower than that of the metal material of the movable vortex disc 1 or the fixed vortex disc 2, and abrasion to the vortex tooth surface can be greatly reduced. When fine impurities enter between the movable scroll 1 and the fixed scroll 2 along with the refrigerant, the fine impurities can be embedded into the sealing strip 5 material, so that the sealing performance of the compressor is not affected, and the impurity resistance of the compressor is further improved.

The foregoing description is merely illustrative of the preferred embodiments of the present utility model, and is not intended to limit the scope of the present utility model. Equivalent changes and modifications are intended to be within the scope of the present utility model as defined in the appended claims.

Claims (8)

1. A vortex plate sealing antifriction device for an electric vortex compressor is characterized by comprising an movable vortex plate, a fixed vortex plate and a sealing strip; the fixed vortex disc and the movable vortex disc are oppositely arranged in the cylinder body; the fixed vortex disc is fixed on the cylinder body, and the back side of the movable vortex disc is abutted against a cylinder body supporting seat fixed on the cylinder body; sealing grooves are formed in the tooth end faces of the movable vortex disc and the fixed vortex disc; the sealing strip is embedded and installed in the sealing groove;

the seal groove is positioned in the center of the tooth end face of the movable vortex disk or the fixed vortex disk and is arranged along the involute trend of the tooth end face;

and the range occupied by the sealing groove on the fixed scroll or the movable scroll is smaller than the coverage area of the movable scroll and the fixed scroll after being relatively installed.

2. The scroll sealing antifriction device for an electric scroll compressor according to claim 1, characterized in that a multipoint groove is provided on the side of the sealing strip facing the sealing groove, the other side being a plane.

3. The scroll sealing antifriction device for an electric scroll compressor of claim 1 wherein a gap is left on both sides of the seal strip and the seal groove.

4. A scroll sealing antifriction device for an electric scroll compressor in accordance with claim 3 wherein the clearance is 0.1 mm.

5. The scroll sealing antifriction device for an electric scroll compressor of claim 1 wherein the seal strip has a thickness less than a depth of the seal groove.

6. The scroll sealing antifriction device for an electric scroll compressor of claim 5 wherein said thickness is less than said depth by a value of 0.05 millimeters.

7. The scroll sealing antifriction device for an electric scroll compressor of claim 1 wherein a gap is left between said orbiting scroll and said fixed scroll after said orbiting scroll and said fixed scroll are relatively snugly installed.

8. The scroll sealing antifriction device for an electric scroll compressor of claim 7 wherein said clearance is 0.05 millimeters.