KR20040036975A - Asymmetry volume type enclossed compressor - Google Patents

Abstract

PURPOSE: An asymmetric capacity type hermetic compressor is provided to reduce vibration and noise of the compressor by generating different pressure of compressed gas on both sides of a dividing plate and rotating a shaft asymmetrically. CONSTITUTION: A casing is closed. A cylinder(20) is fixed inside the casing. The cylinder has an inner room to form a compressed room. Upper and lower bearing plate(31,32) is combined to both open surface of the cylinder to shut the inner space. A rotating shaft is combined to a rotator of a driving motor. The rotating shaft is supported by the bearing plate by expanding from a shaft portion(41) and the inner space of the cylinder concentrically. The rotating shaft has an expanded portion(42) for different diameter of both sides. A dividing plate(50) is formed to an outer peripheral surface of the expanding portion to contact an inner peripheral surface of the cylinder. Therein, the dividing plate divides the inner space of the cylinder into compressed rooms and moves fluid of each compressed room. Vanes(61,62) is combined to bearing plates to block fluid of each compressed room and exhaust fluid inside the casing. A vane spring supports the vane elastically and makes the vane move up and down along a curved surface of the dividing plate. Thereby, vibration and noise of a compressor is reduced due to shaking of the rotating shaft by rotating the rotating shaft asymmetrically.

Description

Asymmetrical capacitive hermetic compressor {ASYMMETRY VOLUME TYPE 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. In particular, an asymmetrical capacity for rotating the shaft to be biased in one of the upper and lower directions by biasing the compression load of each compression chamber in one direction. It relates to a type hermetic compressor.

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. Moreover, the expansion part 4b is formed symmetrically so that the diameter of both upper and lower sides may be the same when the partition plate 5 is centered.

The partition plate 5 is formed in a disk shape in planar projection such that the outer circumferential surface is in sliding contact with the inner circumferential surface of the cylinder 2, and both sides are curved in a sinusoidal shape. Moreover, the partition plate 5 forms the area (or width | variety) of both upper and lower sides similarly as upper and lower ends of the expansion part 4b of the rotating shaft 4 are formed in the same diameter.

The first vane 6A and the second vane 6B are formed in a rectangular parallelepiped having the same surface area in front projection, and the upper end thereof is supported by each vane spring 7A and 7B, and the lower end thereof is each bearing plate 3A, As above-mentioned, it penetrates through 3B), and is couple | bonded so that it may contact each of the upper and lower side surface curved parts 5a of the partition plate 5, respectively.

SP, which is not described in the drawings, is 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, as shown in Figs. 2 and 3, the capacity of the first compression chamber S1 and the second compression chamber S2 is the same, and the compression chambers S1 and S2 When the two compression chambers S1 and S2 are compressed alternately with a phase difference of 180 ° because of the same cross-sectional area of the partition plate 5 subjected to gas force, the two compression chambers S1 and S2 are viewed at any point in time. There is a pressure difference reversed at regular intervals between the upper and lower bearing plates (3A) (3B) in which the rotating shaft (4) swings up and down by a gap (t) at regular intervals and forms a thrust bearing surface (r2). ), There is a problem that causes compressor vibration and noise.

4, when the shaft portion 4a and the expansion portion 4b of the rotating shaft 4 are formed concentrically, the torsional moment of the rotating shaft 4 is reduced compared to other compressors, and the radial bearing portion ( The load applied to the bearing surfaces r1 and r1 of 3b) and 3b becomes small, but the concentrated load is applied to the bearing surfaces r2 and r2 of the thrust bearing parts 3a and 3a, and thus the upper and lower bearing plates 3A) ( While severe wear occurs on the thrust bearing portions 3a and 3a of 3B) and the corresponding extensions 4b of the rotating shaft 4, in consideration of this, the area of the thrust bearing surfaces r2 and r2 is adjusted. In the case of widening, the frictional loss is increased by that much, and the efficiency of the compressor is lowered.

The present invention has been made in view of the problems of the conventional hermetic compressor as described above, and provides an asymmetrical capacitive hermetic compressor that can prevent compressor rotation and noise by preventing the rotating shaft from swinging up and down by the pressure difference between the two pressure chambers. It is an object of the present invention.

Another object of the present invention is to provide an asymmetric displacement hermetic compressor which can prevent the rise of friction loss while reducing the surface pressure generated in the expansion portion and the thrust bearing portion when the shaft portion and the expansion portion of the rotating shaft are formed concentrically. There is this.

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

2 and 3 is a schematic view showing the axial variation of the rotating shaft according to the pressure difference of each compression chamber during the rotation of the rotating shaft in the conventional vane compressor,

4 is a longitudinal sectional view showing a relationship between a load, a surface pressure, and a load on a thrust surface between a bearing plate and a rotating shaft according to the related art;

5 is a longitudinal sectional view showing a compression mechanism of the vane compressor of the present invention;

6 is an exploded perspective view of the main portion of the compression mechanism of the present invention;

7 is a longitudinal sectional view showing the compression mechanism of the present invention;

8 and 9 are longitudinal cross-sectional view showing an operating state according to the pressure difference of each compression chamber in the vane compressor of the present invention;

10 and 11 are longitudinal cross-sectional view showing a modification of the compression mechanism of the present invention.

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

10 casing 20 cylinder

31,32: Bearing plate 31a, 32a: Thrust bearing part

31b, 32b: Radial bearing part 31c, 42c: Back pressure pocket

31d: back pressure flow path 40: rotating shaft

41: shaft portion 42: extension portion

42a: Large diameter side extension 42b: Small diameter side extension

50: partition plate 61,62: vane

71,72: vanes spring S1, S2: compression chamber

r1: Radial Bearing Surface r2: Thrust Bearing Surface

In order to achieve the object of the present invention, a cylinder having a closed casing, an inner space fixedly installed in the casing and opened up and down both sides to form a compression chamber therein, and coupled to both sides of the opening of the cylinder, the inner space The bearing plate coupled to the rotor of the drive motor and shielding the shaft and penetrates up and down the bearing plate and extends concentrically with the shaft in the inner space of the cylinder and the radially supported by each bearing plate and the cylinder. By rotating in the axial direction by the expansion shaft so that the diameters of the two sides are different, and the outer peripheral surface of the expansion portion of the rotating shaft so as to slide in contact with the inner circumferential surface of the cylinder to define the inner space of the cylinder into a plurality of compression chambers Partition plate for moving the shaft and moving up and down on each bearing plate A plurality of vanes that are coupled to each other and slide on the partition plate to block and compress the fluid in each compression chamber to be discharged to the inside of the casing, and the vanes are elastically supported so that the vanes move up and down along the curved surface of the partition plate. An asymmetrical capacitive hermetic compressor including a vanes spring for reciprocating motion is provided.

In addition, at least one back pressure pocket having a predetermined volume so as to be negatively formed on the thrust bearing surface of the bearing plate corresponding to the larger diameter of both sides of the extended portion of the rotary shaft negatively formed asymmetrical, characterized in that Provided is a capacitive hermetic compressor.

In addition, at least one back pressure pocket having a predetermined volume is formed negatively on the thrust bearing surface of the larger diameter in both sides of the expansion part of the rotating shaft, characterized in that the asymmetrical capacity hermetic compressor To provide.

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.

5 is a longitudinal sectional view showing the compression mechanism of the vane compressor of the present invention, Figure 6 is a perspective view showing the main portion of the compression mechanism of the present invention, Figure 7 is a longitudinal sectional view showing the compression mechanism of the present invention, Figure 8 and FIG. 9 is a longitudinal sectional view showing an operating state according to the pressure difference of each compression chamber in the vane compressor of the present invention, and FIGS. 10 and 11 are longitudinal sectional views showing a modified example of the compression mechanism of the present invention.

As shown therein, the compression mechanism of the vane compressor according to the present invention includes a cylinder 20 and a cylinder 20 fixed to the lower half of the casing 10 by having an internal space V for suction-compressing refrigerant gas. The upper bearing plate 31 and the lower bearing plate 32, which are fastened to the upper and lower surfaces of the upper and lower surfaces, respectively, to form a cylinder assembly, and are coupled to the rotor (not shown) of the electric machine part, respectively. The rotating shaft 40 which is coupled to the through 32 to transmit the power of the electric mechanism part to the compression mechanism part, and is coupled to or integrally formed with the rotating shaft 40 to form the inner space V of the cylinder 20 in the first compression chamber. In order to divide into S1 and the second compression chamber S2, the partition plate 50 is formed in a sinusoidal shape so as to have a bending point on each of the upper and lower sides, and the lower and upper ends are respectively formed on both sides of the partition plate 50. Each compression chamber in contact with the rotation of the rotary shaft 40 ( A first vane 61 and a second vane 62 which divide S1 and S2 into a suction zone and a compression zone, and a first vane spring 71 which elastically supports the vanes 61 and 62 together at both ends. ) And the second vane spring 72 and the upper bearing plate 31 and the lower bearing plate 32 to attenuate the discharge noise of the compressed gas discharged from each of the compression chambers S1 and S2. An upper muffler 81 and a lower muffler 82 are included.

The bearing plates 31 and 32 are formed in a disk shape to cover the upper and lower surfaces of the cylinder 20, and thrust bearing portions 31a for slidingly supporting the expansion portion 42 of the rotating shaft 40 to be described later in the axial direction. Radial bearing portions 31b and 32b for forming a shaft hole through which the rotating shaft 40 penetrates in the center thereof and supporting the shaft portion 41 of the rotating shaft 40 in a radial direction. Is made of.

The rotary shaft 40 is inserted into the shaft hole of the upper and lower bearing plates 31 and 32, and the shaft portion 41 is radially supported by the radial bearing portions 31b and 32b, and the lower half of the shaft portion 41 in the radial direction. The upper and lower surfaces of the upper and lower surfaces are formed of the expansion part 42 mounted on and supported by the thrust bearing parts 31a and 32a of the upper and lower bearing plates 31 and 32.

The expansion part 42 is formed concentrically with the shaft part 41 during planar projection so that the center thereof coincides with the center of the shaft part 41, and the upper and lower sides of the partition plate 50 are centered on the partition plate 50. The diameters of the upper and lower sides of the expansion part 42 are different from each other so that the pressure of the compressed gas applied to the curved surface is different. That is, as shown in FIGS. 6 and 7, when the axis of the rotary shaft 40 is centered, the diameter L1 of the large diameter side expansion part 42a is made larger than the diameter L2 of the small diameter side expansion part 42b. As a result, the widths of the upper and lower curved surfaces of the partition plate 50 to which the compressed gas is applied are differently formed.

The partition plate 50 is formed in a disk shape in planar projection such that its outer circumferential surface is in sliding contact with the inner circumferential surface of the cylinder 20. In addition, both sides are formed to be curved in the shape of a sinusoidal wave, but the upper and lower sides of the partition plate 50 are formed by differently forming the diameters of the large diameter side extension portion 42a and the small diameter side extension portion 42b of the rotating shaft 40. Both side widths are also formed differently. That is, the upper side surface of the partition plate 50 is formed smaller in width than the lower side surface of the opposite side.

The first vane 61 and the second vane 62 support the upper ends of the vane springs 71 and 72 so as to contact the upper and lower sides of the partition plate 50, respectively, and each vane 61. The width 62 of the first vane 61 is smaller than the width of the second vane 62 during front projection in preparation for the width of each partition plate 50.

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

The effect of the asymmetric displacement hermetic compressor of the present invention as described above is as follows.

That is, when the rotating shaft 40 is rotated by applying power to the electric mechanism, the partition plate 50 coupled to the rotating shaft 40 rotates together with the rotating shaft 40 in the inner space V of the cylinder 20. The refrigerant gas is alternately sucked into the first compression chamber S1 and the second compression chamber S2, and the refrigerant gas moves along the partition plate 50 when the rotating shaft 40 rotates, and then each vane 61 is moved. A series of processes that are compressed by being blocked by 62 and alternately discharged through the discharge ports (not shown) of the respective compression chambers S1 and S2 are repeated.

In this case, as shown in FIG. 7, the lower cross-sectional area of the partition plate 50 forming the second compression chamber S2 is wider than the upper cross-sectional area of the partition plate 50 forming the first compression chamber S1. ) Is relatively larger than the capacity of the first compression chamber (S1), as well as the pressure of the compressed gas applied to the partition plate 50 to the first compression chamber (S1). It is largely formed.

Accordingly, the partition plate 50 is pushed up together with the rotation shaft 40 by the pressure of the second compression chamber S2 so that the large diameter side extension portion 42a of the rotation shaft 40 is the thrust bearing surface of the upper bearing plate 31. While in close contact with (r2), the small-diameter side expansion portion 42b is opened by a predetermined gap t from the thrust bearing surface r2 of the lower bearing plate 32.

As a result, the rotating shaft 40 has a relatively large capacity when the second compression chamber S2 performs the compression stroke as shown in FIG. 8, as well as when the first compression chamber S1 performs the compression stroke as shown in FIG. 9. As the rotary shaft 40 is rotated in a state of being always raised by a certain height by being pushed by the pressure of the large second compression chamber S2, it is possible to prevent the rotating shaft 40 from swinging in the vertical direction, thereby preventing the vibration of the compressor and the resulting compressor noise. To prevent it.

On the other hand, even if the rotating shaft 40 is pushed up by the pressing force of the compressed gas as described above, even if the upper surface of the expansion portion 42 rotates in contact with the upper bearing plate 31, the thrust of the upper bearing plate 31 The bearing surface (r2) area can be widened by the width of the large diameter side expansion portion (42a) to lower the surface pressure, while the friction area is also increased to increase the friction loss, but as shown in Fig. 10 or 11 the upper bearing On the thrust bearing surface r2 of the plate 31 or on the upper surface of the expansion part 42 of the rotating shaft 40 opposite thereto, the back pressure pockets 31c and 42c and the back pressure flow path 31d which can receive the compressed gas are respectively provided. In each case, the friction loss can be reduced without lowering the above-mentioned surface pressure.

Looking at this in more detail as follows.

That is, as shown in FIG. 10, the back pressure pocket 31c having a predetermined width and depth can be reduced to a certain extent from the diameter of the bearing surface r2 on the bearing surface r2 of the upper thrust bearing portion 31a. ) Is formed in an annular shape or an arc shape in planar projection. The back pressure pocket 31c may be formed symmetrically with respect to the axial center so as to be square or similar in front projection.

The back surface of the bearing surface r2 of the upper thrust bearing portion 31a forms a back pressure passage 31d for communicating the back pressure pocket 31c into the casing 10. The back pressure flow path 31d is formed smaller than the cross-sectional area of the back pressure pocket 31c, and both ends are formed to have the same diameter. However, in some cases, the back pressure pocket 31c smoothly discharges gas in the casing 10 to the back pressure pocket 31c. It may be formed to extend toward the back pressure pocket (31c) to be introduced.

In addition, in the above-mentioned example, although the back pressure pocket 31c was formed in the upper bearing plate 31, the back pressure pocket 42a was extended to the large diameter side part 42a of the rotating shaft 40 as shown in FIG. May be formed. In this case as well, the back pressure passage 31d must be formed in the axial direction through the upper bearing plate 31 as described above.

In this way, a part of the compressed gas discharged to the casing 10 flows into the back pressure pockets 31c and 42c through the above back pressure passage 31d to exert an air cushion, and thus the bearing plate 31 and the rotating shaft. Abrasion between the 40 will be prevented.

In the asymmetric displacement hermetic compressor according to the present invention, the bearing areas between the upper and lower bearing plates and the rotating shafts corresponding to the upper and lower bearing plates are formed differently to form the compression chamber capacities on both sides of the partition plate, thereby being applied to both sides of the partition plate. The pressing force of the compressed gas is generated differently and through this, the rotary shaft always rotates in one of the axial directions so as to effectively reduce the vibration and noise of the compressor due to the swing of the rotary shaft.

In addition, by forming a back pressure pocket on the thrust bearing surface between the bearing plate and the rotating shaft, it reduces the absolute area of the thrust bearing surface and reduces the frictional loss of the compressor, while offsetting the load of the rotating shaft by using the buffer force generated in the back pressure pocket. Wear can be prevented.

Claims (10)

With sealed casing, A cylinder having an inner space fixedly installed in the casing and opening up and down both sides to form a compression chamber therein; Upper and lower bearing plates coupled to the openings on both sides of the cylinder to shield the inner space; Coupling is coupled to the rotor of the drive motor and penetrates up and down the bearing plate radially supported by each bearing plate and extends concentrically with the shaft in the inner space of the cylinder and is supported axially by the bearing plate, both sides A rotating shaft having an extension so that the diameter of the A partition plate formed on the outer circumferential surface of the expansion part of the rotating shaft so as to be in sliding contact with the inner circumferential surface of the cylinder, and partitioning the inner space of the cylinder into a plurality of compression chambers to move the fluid in each compression chamber; A plurality of vanes which are coupled to each bearing plate so as to be movable up and down and at the same time slide while being mounted on a partition plate to block and compress the fluid in each compression chamber and to be discharged into the casing; An asymmetric displacement hermetic compressor including a vanes spring that supports the vanes elastically so that the vanes move up and down along the curved surface of the partition plate. The method of claim 1, Asymmetrical capacitive type characterized in that at least one back pressure pocket having a predetermined volume is formed negatively on the thrust bearing surface of the bearing plate corresponding to the larger diameter of both sides of the expansion part of the rotary shaft so as to receive the compressed gas. Hermetic compressor. The method of claim 1, An asymmetric displacement hermetic compressor comprising negatively forming at least one back pressure pocket having a predetermined volume so as to receive compressed gas on a thrust bearing surface having a larger diameter among both sides of an extended portion of the rotary shaft. The method according to claim 2 or 3, An asymmetrical capacity hermetic compressor, characterized in that the at least one back pressure passage through which the back pressure pocket communicates with the inside of the casing through the bearing plate. The method according to claim 2 or 3, The back pressure pocket is an asymmetrical capacity hermetic compressor characterized in that it is formed in an annular shape when projecting. The method according to claim 2 or 3, The back pressure pocket is an asymmetrical capacity hermetic compressor characterized in that it is formed in an arc shape when projecting. The method according to claim 2 or 3, The back pressure pocket is an asymmetrical capacity hermetic compressor characterized in that the front projection is formed symmetrically in the axial direction or radial direction. The method according to claim 2 or 3, An asymmetric displacement 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. The method of claim 1, Asymmetrical capacity hermetic compressor, characterized in that the partition plate is formed in the same thickness. The method of claim 1, The partition plate is asymmetrical capacity hermetic compressor characterized in that it is formed to be symmetrical with respect to the top dead center and bottom dead center.