KR20040036973A - Apparatus for reducing face pressor of enclossed compressor - Google Patents

Abstract

PURPOSE: A surface pressure reducing apparatus for a hermetic compressor is provided to reduce surface pressure on trust bearing surfaces of a bearing plate or a rotating shaft by forming back pressure pockets to either trust bearing surfaces of the bearing plate and the rotating shaft. CONSTITUTION: A casing is closed. A cylinder is fixed inside the casing. The inside of the cylinder is a compressive room. A rotating shaft(30) penetrates the inside of the cylinder. The rotating shaft is combined with a rotator of a driving motor. Upper and lower bearing plates(10,20) are combined with the cylinder. A trust bearing surface of the bearing plate supports the rotating shaft and forms back pressure pockets(11a) to receive compressed gas. Back pressure passages(11b,21b) are formed to the bearing plate to communicate the back pressure pocket to the inside of the casing. A dividing plate is combined with the rotating shaft to divide the inside of the cylinder into more than two compressed rooms. The dividing plate moves fluid of each compressed room. Vanes are combined with each bearing plate. Vanes blocks fluid of each compressed room on the dividing plate and exhausts fluid inside the casing. A vane spring supports the vane elastically to move the vane up and down along a curved surface of the dividing plate. Thereby, wear of trust bearing surfaces(11,21) of the bearing plate and the rotating shaft is prevented by reducing surface pressure on trust bearing surfaces.

Description

Surface pressure reduction device for hermetic compressor {APPARATUS FOR REDUCING FACE PRESSOR OF ENCLOSSED COMPRESSOR}

The present invention relates to a hermetic compressor for dividing an inner space of a cylinder into a plurality of compression chambers by using a partition plate, and in particular, a surface pressure reduction device of a hermetic compressor that can reduce the surface pressure on a thrust surface between a rotating shaft and a corresponding bearing plate. It is about.

In general, the vane compressor presses a vane to a rotating body to rotate the rotating body in a state in which the inner space of the cylinder is divided into a suction area and a compression area so that the fluid is sucked and compressed while continuously changing the suction area and the compression area. It is.

1 is a longitudinal sectional view showing an example of a conventional vane-type hermetic compressor.

As shown in the drawing, a conventional vane-type hermetic compressor includes an electric mechanism part installed to generate power in the upper portion of the casing 1, and a compressor mechanism part installed in the lower part of the electric mechanism part to suction and discharge the fluid. Doing.

The compression mechanism has an internal space (V) for sucking and compressing refrigerant gas, and the cylinder (2) is fixed to the lower half of the casing (1) and the upper and lower surfaces of the cylinder (2), respectively, to form a cylinder assembly together. An upper bearing plate 3A and a lower bearing plate 3B, and a rotating shaft 4 which is coupled to the electric mechanism part and simultaneously coupled to the bearing plates 3A and 3B to transmit the power of the electric device part to the compressor sphere. Bent points on the upper and lower sides, respectively, in order to couple to or integrally form the rotating shaft 4 and partition the internal space V of the cylinder 2 into the first compression chamber S1 and the second compression chamber S2. The compression plate (S1) and the compression chamber (S2) in contact with the lower and upper ends of the partition plate (5) formed in a sinusoidal shape and the partition plate (5), respectively, so as to have a suction area. And first vanes 6A and second vanes 6B partitioned into compression regions, and each vane. (6A) and 6B are installed on the outer surfaces of the first vane spring 7A and the second vane spring 7B and the upper bearing plate 3A and the lower bearing plate 3B, which elastically support both ends together. The compressed gas discharged from the compression chambers S1 and S2 includes an upper muffler 8A and a lower muffler 8B for damping the discharge noise.

As shown in FIG. 2, the bearing plates 3A and 3B are formed in a disc shape to cover the upper and lower surfaces of the cylinder 2, and thrust for slidably supporting the expansion portion 4b of the rotating shaft 4 to be described later in the axial direction. The bearing part 3a and the radial bearing part 3b which form the shaft hole through which the rotating shaft 4 penetrates in the center, and rotatably support the shaft part 4a of the rotating shaft 4 mentioned later to be radially rotated. consist of.

The rotary shaft 4 is inserted into the shaft hole of the upper and lower bearing plates 3A and 3B, and is formed in the radial direction in the lower half of the shaft portion 4a and the shaft portion 4a which is radially supported by the radial bearing portion 3b. The partition plate 5 is integrally or post-assembled on its outer circumferential surface, and the upper and lower surfaces are made up of an extension part 4b supported on the thrust bearing part 3a of the upper and lower bearing plates 3A and 3B. have.

The expanded portion 4b is formed concentric with the central portion of the shaft portion 4a, that is, at the time of planar projection.

In the drawings, reference numeral L denotes a width of the thrust bearing surface, r1 denotes a radial bearing surface, and SP denotes a suction pipe.

The conventional vane compressor as described above operates as follows.

That is, when the rotary shaft 4 is rotated by applying power to the electric drive unit, the partition plate 5 rotates in one direction together with the rotary shaft 4, and vanes are in contact with the upper and lower sides of the partition plate 5, respectively. 6A and 6B reciprocate in the opposite direction up and down along the height of the partition plate 5, varying the volume of the first compression chamber S1 and the second compression chamber S2 of the cylinder 2, together with New refrigerant gas is continuously sucked into the first compression chamber S1 and the second compression chamber S2 through the suction pipe SP provided at one side of the cylinder 2, and the refrigerant gas is divided into a partition plate ( It is gradually compressed with the rotation of 5), and is discharged alternately through each discharge port (unsigned) at the moment when both convex curved portions of the partition plate 5 reach the discharge start point.

At this time, the shaft portion 4a of the rotating shaft 4 is radially supported corresponding to the shaft hole of the upper and lower bearing plates 3A and 3B, while the expansion portion 4b is in the plane of the upper and lower bearing plates 3A and 3B. Correspondingly, it was supported in the axial direction and continued to rotate stably.

However, in the conventional vane-type compressor as described above, the shaft portion 4a and the expansion portion 4b are radial bearing portions 3b and 3b of the upper and lower bearing plates 3A and 3B while the rotating shaft 4 rotates. Loads are applied to the thrust bearing parts 3a and 3a, respectively, and the radial pressures are generated on the radial bearing parts 3b and 3b and the thrust bearing parts 3a and 3a in response to the loads. As described above, in the case of the compressor which concentrically forms the shaft portion 4a and the expansion portion 4b of the rotating shaft 4, the torsional moment of the rotating shaft 4 is smaller than that of other compressors as shown in FIGS. While the load applied to the radial bearing portion 3b decreases, the concentrated load is applied to the thrust bearing portion 3a, and thus the thrust bearing portion 3a of the upper and lower bearing plates 3A and 3B and the corresponding rotating shaft 4 There was a fear that severe wear occurs in the extension portion 4b.

In addition, when the area of the thrust bearing surface r2 is increased in order to reduce the surface pressure in the thrust bearing portion 3a, there is a problem in that the frictional loss increases and the efficiency of the compressor decreases.

The present invention has been made in view of the above problems of the conventional hermetic compressor, and when the shaft portion and the expansion portion of the rotating shaft are formed concentrically, the increase in friction loss while reducing the surface pressure generated in the expansion portion and the thrust bearing portion is prevented. It is an object of the present invention to provide a surface pressure reduction device of a hermetic compressor.

1 is a longitudinal sectional view showing a compression mechanism of a conventional vane compressor;

2 and 3 are a longitudinal sectional view and a schematic view showing the relationship between the load, the surface pressure and the load on the thrust surface between the bearing plate and the rotating shaft,

Figure 4 is a perspective view showing an exploded compression mechanism of the vane compressor of the present invention,

Figure 5 is a longitudinal cross-sectional view showing the relationship between the load and surface pressure on the thrust surface between the bearing plate and the rotating shaft in the vane compressor of the present invention,

6 and 7 are respective bottom views of the bearing plate,

8 is a schematic view showing the relationship between the load and the surface pressure on the thrust surface between the bearing plate and the rotating shaft in the vane compressor of the present invention,

9 is a longitudinal sectional view showing a modification to the compression mechanism of the present invention.

** Description of symbols for the main parts of the drawing **

10,20: Upper and lower bearing plate 11,21: Thrust bearing part

11a, 21a, 32a: back pressure pocket 11b, 21b: back pressure flow path

12,22: radial bearing part 30: rotating shaft

31: shaft portion 32: expansion portion

In order to achieve the object of the present invention, a cylinder having a sealed casing, the inner space fixedly installed in the casing and forming a compression chamber therein, and through the inner space of the cylinder and coupled to the rotor of the drive motor At least one back pressure pocket having a predetermined volume so as to receive compressed gas on the rotating shaft and the thrust bearing surface which is coupled to the cylinder to support the rotating shaft in the axial direction and the radial direction to support the axial direction. An upper and lower bearing plate which is formed in a fork and penetrates at least one back pressure passage for communicating the back pressure pocket with the inside of the casing, and the inner space of the cylinder is divided into at least two compression chambers by being coupled to the rotating shaft, Partition plate for moving the fluid, each bearing plate is coupled to move up and down At the same time, the slide slides on the partition plate, blocks and compresses the fluid in each compression chamber, compresses and discharges them into the casing, and elastically supports the vanes so that the vanes move up and down along the curved surface of the partition plate. Provided is a surface pressure reduction device for a hermetic compressor including a vane spring for exercising.

The back pressure pocket is formed on the thrust bearing surface of the rotating shaft, and the back pressure flow path is provided by penetrating the respective bearing plates.

EMBODIMENT OF THE INVENTION Hereinafter, the surface pressure reduction apparatus of the hermetic compressor by this invention is demonstrated in detail based on one Example shown in an accompanying drawing.

Figure 4 is a perspective view showing an exploded compression mechanism of the vane compressor of the present invention, Figure 5 is a longitudinal cross-sectional view showing the relationship between the load and the surface pressure on the thrust surface between the bearing plate and the rotating shaft in the vane compressor of the present invention, Figure 7 is a respective bottom view of the bearing plate, Figure 8 is a schematic diagram showing the relationship between the load and the surface pressure on the thrust surface between the bearing plate and the rotating shaft in the vane compressor of the present invention.

As shown therein, the compression mechanism of the vane compressor according to the present invention includes an inner space (shown in FIG. 1) V for suction-compressing refrigerant gas, and a lower half of the casing (shown in FIG. 1) 1. A cylinder assembly which is fastened to the upper and lower surfaces of the cylinder 2 fixed to the upper and lower surfaces of the cylinder 2, respectively, and forms back pressure pockets 11a and 21a on the respective thrust bearing surfaces r2 and r2. An upper bearing plate 10 and a lower bearing plate 20, a rotating shaft 30 which is coupled to the electric drive part and simultaneously coupled to the bearing plates 10 and 20 to transmit the power of the electric drive part to the compression mechanism, Bending points are formed on the upper and lower sides, respectively, to be coupled to or integrally formed on the rotating shaft 30 and partition the internal space V of the cylinder 2 into the first compression chamber S1 and the second compression chamber S2. On both sides of the partition plate 5 and the partition plate 5 formed in a sine wave shape so as to have To contact the respective lower and upper end comprises a respective compression chamber (S1) the first vanes (6A) and second vanes (6B) for partitioning the suction region and a compression region for (S2) during the rotation of the rotary shaft 30.

The bearing plates 10 and 20 are formed in a disc shape so as to cover the upper and lower surfaces of the cylinder 2, and thrust bearing portions 11 and 21 for sliding the shaft 30 in the axial direction. It consists of a radial bearing part 12 (22) which forms a shaft hole through which the rotating shaft 30 penetrates in the center thereof and rotatably supports the rotating shaft 30 in the radial direction.

The thrust bearing surface r2 of the thrust bearing parts 11 and 21 has back pressure pockets 11a and 12a having a predetermined width and depth so that the area of the bearing surface r2 can be reduced to a certain extent with respect to the same diameter. And at least one back pressure passage (11b) (21b) through which the back pressure pockets (11a) (21a) communicate with the inside of the casing (1).

The back pressure pockets 11a and 12a may be formed in an annular shape or an arc shape in planar projection as shown in FIGS. 5 and 6.

The back pressure flow passages 11b and 21b are formed smaller than the lateral area of the back pressure pockets 11a and 21a, and are easily formed to have the same diameter up and down, but in some cases, the back pressure pockets 11a and 21a may be used. The discharge gas in the casing 1 may be extended toward the back pressure pockets 11a and 21a so as to smoothly flow therein.

The rotating shaft 30 is inserted into the shaft hole of the upper and lower bearing plates 10 and 20 to support the radial bearing portion 12 and 22 in the radial direction, and the radial portion in the lower half of the shaft portion 31. Expansion to form an outer peripheral surface and the partition plate 5 is integrally or post-assembled and the upper and lower surfaces are mounted on and supported on the thrust bearing parts 11 and 21 of the upper and lower bearing plates 10 and 20. It consists of a part (32).

The extension part 32 is formed concentrically with the shaft part 31 in planar projection so that the center thereof may coincide with the center of the shaft part 31.

9, the above-mentioned back pressure pockets 32a and 32a may be formed on the upper and lower thrust bearing surfaces r2 of the expansion part 32. As shown in FIG. Also in this case, the back pressure pockets 32a and 32a are formed in an annular or circular arc shape, and the back pressure flow paths 11b and 21b are the thrust bearing portions 11 and the top and bottom bearing plates 10 and 20 as described above. 21) in the same shape.

In the drawings, the same reference numerals are given to the same parts as in the prior art.

In the drawings, reference numerals 13 and 23 are vaneslit, 14 and 24 are bolt holes, and r1 is a radial bearing surface.

Effects of the present invention hermetic compressor as described above are as follows.

That is, when the rotary shaft 30 is rotated by applying power to the electric mechanism, the partition plate 5 coupled to the rotary shaft 30 rotates in the internal space V of the cylinder 2, and thus the first compression chamber S1. And alternately suck the refrigerant gas into the second compression chamber (S2), and the refrigerant gas moves along the partition plate (5) and is blocked by each vane (6A) 6B to be compressed and then compressed into each compression chamber (S1). It is alternately discharged through the discharge port (not shown) of (S2).

Here, the rotating shaft 30 is inserted into the shaft hole of the bearing plate 10, 20 coupled to the upper and lower sides of the cylinder 2, and rotates, wherein the shaft portion 31 of the rotating shaft 30 is each bearing plate 10 ( 20 is supported by the radial bearing parts 12 and 22, while the upper and lower sides of the extension part 32 are supported by the thrust bearing parts 11 and 21 of the respective bearing plates 10 and 20 to support the cylinder ( Keep perpendicular to 2).

In the hermetic compressor, as the shaft portion 31 and the expansion portion 32 of the rotating shaft 30 are formed concentrically, the torsional moment of the rotating shaft 30 is theoretically generated so that the radial bearing portion 12 ( Concentrated load is applied to the thrust bearing parts 11 and 21 as compared to 22, which causes a large increase in the surface pressure in the thrust bearing parts 11 and 21 of each bearing plate 10 and 20, but FIG. Back pressure pockets 11a and 21a on the bearing surface r2 of each thrust bearing part 11 and 21 or the upper and lower thrust bearing surface r2 of the expansion part 32 of the corresponding rotation shaft 30 as shown in FIG. As a result, a portion of the compressed gas discharged into the casing 1 flows into the back pressure pockets 11a and 21a through the back pressure passages 11b and 21b to generate a new surface pressure. By the expansion part 32 of the rotating shaft 30 to the thrust bearing parts 11 and 21 of each bearing plate 10 and 20 by To some extent, it is possible to compensate not reduce the total surface pressure to be formed reduce the area of the same diameter compared to the thrust bearing surface (r2) corresponding to the load of the rotary shaft 30 can be supported in the axial direction of the rotary shaft effectively.

In addition, as described above, the width length L of the thrust bearing surface r2 is reduced by the width length L1 of the back pressure pockets 11a and 21a, and as the absolute area becomes smaller, the friction loss becomes smaller so that the motor and the compressor are smaller. Can increase the efficiency.

On the other hand, even in the case where the back pressure pockets 32a and 32a are formed in the extension portion 32 of the rotation shaft 30, the effects thereof are the same as in the above-described example.

The surface pressure reduction device of the hermetic compressor according to the present invention includes at least one back pressure pocket on at least one of the thrust bearing surfaces of the respective bearing plates supporting the axial direction of the rotating shaft or the thrust bearing surfaces of the corresponding rotating shaft. By forming and penetrating the back pressure passage in the bearing plate, the surface pressure acting on the thrust bearing surface of the bearing plate or the thrust bearing surface of the rotating shaft can be reduced to prevent wear of the two members. In addition, by reducing the absolute area of the bearing surface to reduce the friction loss it can increase the efficiency of the motor and compressor.

Claims (6)

With sealed casing, A cylinder having an internal space fixedly installed in the casing and forming a compression chamber therein; A rotating shaft that penetrates the inner space of the cylinder and is coupled to the rotor of the driving motor to rotate together; The thrust bearing surface which is coupled to the cylinder to support the rotating shaft in the axial direction and the radial direction, and at least one back pressure pocket having a predetermined volume so as to accommodate the compressed gas to the negatively formed thrust bearing surface to be negatively formed An upper and lower bearing plate for penetrating at least one back pressure passage to communicate with the inside of the casing; A partition plate coupled to the rotating shaft to partition the inner space of the cylinder into at least two compression chambers and to move the fluid in each compression chamber; At least one vane coupled to each bearing plate so as to be movable up and down and at the same time sliding on a partition plate to block and compress the fluid in each compression chamber to be discharged into the casing after compression; A surface pressure reduction device of a hermetic compressor including a vanes spring that elastically supports a vane to allow the vane to reciprocate up and down along a curved surface of a partition plate. The surface pressure reduction device of the hermetic compressor of claim 1, wherein the back pressure pocket is formed on the thrust bearing surface of the rotating shaft, and the back pressure flow path is formed through each bearing plate as in claim 1. The method according to claim 1 or 2, The back pressure pocket is a surface pressure reduction device of a hermetic compressor, characterized in that formed in an annular shape during projection. The method according to claim 1 or 2, The back pressure pocket is a surface pressure reduction device of a hermetic compressor, characterized in that formed in an arc shape when projecting. The method according to any one of claims 1 to 4, The back pressure pocket is a surface pressure reduction device of a hermetic compressor characterized in that the front projection is formed symmetrically in the axial direction or radial direction. The method according to any one of claims 1 to 4, A surface pressure reduction device for a hermetic compressor, characterized in that the cross-sectional area of the back pressure pocket is formed larger than that of the back pressure flow path.