JP2012036775A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor capable of reducing the noise level of the resonance noise produced from the lower part of an accumulator at the operational frequency from the low-speed operation to the high-speed operation.SOLUTION: The rotary compressor includes: a compressor casing having first and second intake parts in a side lower part in the vertical direction; an accumulator having first and second bottom through-holes disposed outside and inside a bottom part, and mounted on the side upper part of the compressor casing; a first compression unit for sucking refrigerant gas via an L-shaped first low-pressure communication pipe for connecting the first bottom part through-hole to the first intake part; and a second compression unit which is arranged above the first compression unit to suck refrigerant gas via an L-shaped second low-pressure communication pipe which connects the second bottom part through-hole to the second intake part, and is arranged on the inner side of the first low-pressure communication pipe. The radius of curvature R1 of a bent part of the first low-pressure communication pipe is set to be ≥1.5 times and ≤2.5 times the radius of curvature R2 of a bent part of the second low-pressure communication pipe.

Description

  The present invention relates to a rotary compressor used in a refrigeration cycle such as an air conditioner.

  Conventionally, as shown in FIGS. 6 and 7, the first bottom through-hole 257S of the accumulator 25 attached to the upper side of the rotary compressor casing (not shown) and the lower side of the rotary compressor casing. The first suction portion (not shown) of the first compression portion provided in the first compression portion is connected by an L-shaped first low-pressure communication pipe 31S, and the second bottom through hole 257T and the second compression portion are connected to each other. The second suction part (not shown) is connected by an L-shaped second low pressure communication pipe 31T.

  The radius of curvature R1 of the bent portion of the first low-pressure connecting pipe 31S and the radius of curvature R2 of the bent portion of the second low-pressure connecting pipe 31T are set to the same relatively small radius (see FIG. 6) or shown in FIG. As described above, the curvature centers of both are positioned at the same position, and the curvature radius R1 of the first low-pressure communication pipe 31S is set to about three times the curvature radius R2 of the second low-pressure communication pipe 31T.

  However, in the structure of the conventional first and second low-pressure connecting pipes 31S and 31T shown in FIG. 6, during the high-speed operation of the rotary compressor, the vibration of the compressor housing causes the first and second low-pressure connecting pipes 31S and 31T. The sound propagates to the lower part of the accumulator 25 through the sound and the resonance sound is generated from the lower part of the accumulator 25. In addition, the conventional first and second low-pressure connecting pipes 31S and 31T shown in FIG. 7 have a problem in that resonance noise is similarly generated during medium speed operation of the rotary compressor.

  This is because, in the structure of the conventional first and second low-pressure connecting pipes 31S and 31T shown in FIG. 6, the curvature radius R1 of the first low-pressure connecting pipe 31S is small, so the entire length of the first low-pressure connecting pipe 31S is long. Thus, the rigidity of the first low-pressure connecting pipe 31S is reduced. This is because if the rigidity of the first low-pressure connecting pipe 31S is too small, the first low-pressure connecting pipe 31S resonates at a high-speed rotation frequency.

  Further, in the structure of the conventional first and second low-pressure connecting pipes 31S and 31T shown in FIG. 7, since the curvature radius R1 of the first low-pressure connecting pipe 31S is large, the entire length of the first low-pressure connecting pipe 31S is shortened. The rigidity of the first low-pressure connecting pipe 31S is increased. This is because if the rigidity of the first low-pressure connecting pipe 31S is too large, the first low-pressure connecting pipe 31S resonates at a medium-speed rotation frequency.

  The present invention has been made in view of the above, and it is decided to obtain a rotary compressor in which the noise level of the resonance sound generated from the lower part of the accumulator is reduced at the operating frequency from low speed operation to high speed operation. To do.

  In order to solve the above-described problems and achieve the object, the present invention is a sealed vertical installation in which a refrigerant discharge part is provided at the upper part and second and first suction parts are provided at the upper and lower sides. A cylindrical compressor housing and a refrigerant suction portion are provided at the top, and first and second bottom through holes are provided on the outer and inner sides of the bottom, and are attached to the upper side portion of the compressor housing. The refrigerant gas is sucked in through the L-shaped first low-pressure connecting pipe that is installed in the lower part of the compressor housing and connects between the first bottom through hole and the first suction part. A first compression section that discharges refrigerant gas from the discharge section through the compressor housing, and the first compression section, and is disposed on the first compression section, between the second bottom through-hole and the second suction section. Refrigerant gas is sucked through an L-shaped second low-pressure connecting pipe connected and arranged inside the first low-pressure connecting pipe And a second compression section that discharges refrigerant gas from the discharge section through the compressor housing, wherein a curvature radius R1 of a bent portion of the first low-pressure connecting pipe is set to the second low-pressure connection pipe. It is characterized by being 1.5 times or more and 2.5 times or less of the radius of curvature R2 of the bent portion of the connecting pipe.

  According to the present invention, there is an effect that the noise level of the resonance sound generated from the lower part of the accumulator is reduced at the operation frequency from the low speed operation to the high speed operation.

1 is a longitudinal sectional view showing a first embodiment of a rotary compressor according to the present invention. FIG. 2 is a cross-sectional view of the first and second compression units. FIG. 3A is an enlarged longitudinal sectional view showing the first and second low-pressure connecting pipes of Example 1. FIG. 3-2 is an enlarged longitudinal sectional view showing another form of the first and second low-pressure connecting pipes of Example 1. FIG. FIG. 4A is a diagram illustrating a noise level when the radius of curvature R1 of the first low-pressure connecting pipe is 1.5 times the radius of curvature R2 of the second low-pressure connecting pipe. FIG. 4B is a diagram illustrating a noise level when the radius of curvature R1 of the first low-pressure connecting pipe is twice the radius of curvature R2 of the second low-pressure connecting pipe. FIG. 4-3 is a diagram illustrating a noise level when the curvature radius R1 of the first low-pressure communication pipe is 2.5 times the curvature radius R2 of the second low-pressure communication pipe. FIG. 4-4 is a comparison diagram of the noise level of the rotary compressor of Example 1 and the noise level of the conventional rotary compressor. FIG. 5 is a longitudinal sectional view showing a second embodiment of the rotary compressor according to the present invention. FIG. 6 is an enlarged longitudinal sectional view showing first and second low-pressure connecting pipes of a conventional rotary compressor. FIG. 7 is an enlarged longitudinal sectional view showing first and second low-pressure connecting pipes of another conventional rotary compressor.

  Embodiments of a rotary compressor according to the present invention will be described below in detail with reference to the drawings. Note that the present invention is not limited to the embodiments.

  1 is a longitudinal sectional view showing a first embodiment of a rotary compressor according to the present invention, FIG. 2 is a transverse sectional view of first and second compression sections, and FIG. FIG. 3-2 is an enlarged longitudinal sectional view showing another embodiment of the first and second low pressure connecting pipes of Example 1, and FIG. FIG. 4A is a diagram illustrating a noise level when the radius of curvature R1 of the first low-pressure connecting pipe is 1.5 times the radius of curvature R2 of the second low-pressure connecting pipe, and FIG. FIG. 4C is a diagram showing a noise level when the curvature radius R1 of the low-pressure connection pipe is twice the curvature radius R2 of the second low-pressure connection pipe. FIG. It is a figure which shows a noise level when it is set to 2.5 times the curvature radius R2 of a low voltage | pressure connecting pipe, FIG. 4-4 shows the noise level of the rotary compressor of Example 1, and conventional noise. It is a comparison diagram of the noise level of Tari compressor.

  As shown in FIG. 1, the rotary compressor 1 according to the first embodiment is provided with a compression unit 12 installed at a lower portion of a sealed vertical cylindrical compressor housing 10 and an upper portion of the compressor housing 10. And a motor 11 that drives the compression unit 12 via the rotating shaft 15.

  The stator 111 of the motor 11 is fixed by being shrink-fitted on the inner peripheral surface of the compressor housing 10. The rotor 112 of the motor 11 is disposed at the center of the stator 111 and is fixed by being shrink-fitted to a rotating shaft 15 that mechanically connects the motor 11 and the compression unit 12.

  The compressing unit 12 includes a first compressing unit 12S, and a second compressing unit 12T that is installed in parallel with the first compressing unit 12S and disposed on the upper side of the first compressing unit 12S. The first and second compression sections 12S and 12T include short cylindrical first and second cylinders 121S and 121T.

  As shown in FIG. 2, circular first and second cylinder inner walls 123 </ b> S and 123 </ b> T are formed concentrically with the motor 11 in the first and second cylinders 121 </ b> S and 121 </ b> T. In the first and second cylinder inner walls 123S and 123T, annular first and second annular pistons 125S and 125T having an outer diameter smaller than the cylinder inner diameter are arranged, respectively, and the first and second cylinder inner walls 123S and 123T and The first and second working chambers 130S and 130T (compression spaces) are formed between the first and second annular pistons 125S and 125T for sucking, compressing and discharging the refrigerant gas.

  First and second vane grooves 128S and 128T are formed in the first and second cylinders 121S and 121T in the radial direction from the first and second cylinder inner walls 123S and 123T over the entire cylinder height. Flat plate-like first and second vanes 127S and 127T are fitted in the second vane grooves 128S and 128T, respectively.

  Although not shown, first and second springs are disposed in the inner part of the first and second vane grooves 128S and 128T. Normally, due to the repulsive force of the first and second springs, the first and second vanes 127S and 127T are moved from the first and second vane grooves 128S and 128T into the first and second working chambers 130S and 130T. The first and second working chambers 130S and 130T (compression spaces) are projected by the first and second vanes 127S and 127T. The chamber is partitioned into first and second suction chambers 131S and 131T and first and second compression chambers 133S and 133T.

  In addition, the first and second cylinders 121S and 121T communicate with the inner portions of the compressor housing 10 through the inner portions of the first and second vane grooves 128S and 128T, and the first and second vanes 127S and 127T communicate with each other. Further, back pressure introduction passages 129S and 129T for applying a back pressure by the pressure of the compressed refrigerant gas are formed.

  In the first and second cylinders 121S and 121T, the first and second suction chambers 131S and 131T communicate with the outside in order to suck the refrigerant from the outside into the first and second suction chambers 131S and 131T. Second suction holes 135S and 135T are provided.

  Further, as shown in FIG. 1, an intermediate partition plate 140 is installed between the first cylinder 121S and the second cylinder 121T, and the second operation of the first working chamber 130S of the first cylinder 121S and the second cylinder 121T. The room 130T is partitioned. A lower end plate 160S is installed at the lower end of the first cylinder 121S, and closes the first working chamber 130S of the first cylinder 121S. An upper end plate 160T is installed at the upper end of the second cylinder 121T, and closes the second working chamber 130T of the second cylinder 121T.

  A lower bearing portion 161S is formed on the lower end plate 160S, and the lower bearing support portion 151 of the rotary shaft 15 is rotatably supported by the lower bearing portion 161S. An upper bearing portion 161T is formed on the upper end plate 160T, and an upper bearing support portion 153 of the rotary shaft 15 is rotatably supported by the upper bearing portion 161T.

  The rotating shaft 15 includes a first eccentric portion 152S and a second eccentric portion 152T that are offset by 180 ° from each other. The first eccentric portion 152S is a first annular portion of the first compression portion 12S. The piston 125S is rotatably held, and the second eccentric portion 152T rotatably holds the second annular piston 125T of the second compression portion 12T.

  When the rotary shaft 15 rotates, the first and second annular pistons 125S and 125T revolve in the first and second cylinders 121S and 121T in the clockwise direction of FIG. 2 along the first and second cylinder inner walls 123S and 123T. Then, following this, the first and second vanes 127S and 127T reciprocate. Due to the movement of the first and second annular pistons 125S and 125T and the first and second vanes 127S and 127T, the volumes of the first and second suction chambers 131S and 131T and the first and second compression chambers 133S and 133T are continuous. The compressor 12 continuously sucks, compresses and discharges the refrigerant gas.

  As shown in FIG. 1, a lower muffler cover 170S is installed below the lower end plate 160S, and a lower muffler chamber 180S is formed between the lower end plate 160S. And the 1st compression part 12S is opened to lower muffler room 180S. That is, a first discharge hole 190S (see FIG. 2) that connects the first compression chamber 133S of the first cylinder 121S and the lower muffler chamber 180S is provided in the vicinity of the first vane 127S of the lower end plate 160S. In the hole 190S, a first discharge valve 200S that prevents the backflow of the compressed refrigerant gas is installed.

  The lower muffler chamber 180S is one chamber communicated in an annular shape, and the lower end plate 160S, the first cylinder 121S, the intermediate partition plate 140, the second cylinder 121T, and the upper end plate 160T are arranged on the discharge side of the first compression unit 12S. This is a part of the communication passage that communicates with the upper muffler chamber 180T through the refrigerant passage 136 (see FIG. 2) that passes through the upper muffler chamber. The lower muffler chamber 180S reduces the pressure pulsation of the discharged refrigerant gas. In addition, a first discharge valve presser 201S for limiting the amount of flexure opening of the first discharge valve 200S is fixed to the first discharge valve 200S together with the first discharge valve 200S by a rivet.

  As shown in FIG. 1, an upper muffler cover 170T is installed above the upper end plate 160T, and an upper muffler chamber 180T is formed between the upper end plate 160T and the upper muffler cover 170T. In the vicinity of the second vane 127T of the upper end plate 160T, a second discharge hole 190T (see FIG. 2) that communicates the second compression chamber 133T of the second cylinder 121T and the upper muffler chamber 180T is provided, and the second discharge hole 190T. Is provided with a second discharge valve 200T for preventing the backflow of the compressed refrigerant gas.

  In addition, a second discharge valve presser 201T for limiting the deflection opening amount of the second discharge valve 200T is fixed to the second discharge valve 200T by a rivet together with the second discharge valve 200T. The upper muffler chamber 180T reduces the pressure pulsation of the discharged refrigerant.

  The first cylinder 121S, the lower end plate 160S, the lower muffler cover 170S, the second cylinder 121T, the upper end plate 160T, the upper muffler cover 170T, and the intermediate partition plate 140 are integrally fastened by bolts 175. Out of the compression portion 12 that is integrally fastened by the bolt 175, the outer peripheral portion of the upper end plate 160T is fixed to the compressor housing 10 by spot welding, and the compression portion 12 is fixed to the compressor housing 10.

  First and second through-holes 103S and 103T pass through the first and second suction pipes 105S and 105T, respectively, in the lower side portion of the cylindrical compressor housing 10 in order from the lower part in the axial direction. It is provided for. The first through hole 103S and the first suction pipe 105S constitute a first suction part 101S, and the second through hole 103T and the second suction pipe 105T constitute a second suction part 101T. Further, an accumulator 25 made of an independent cylindrical sealed container is attached to the upper side portion of the compressor housing 10 by an accumulator holder 252 and an accumulator band 253.

  A system connection pipe 255 as a refrigerant suction portion connected to the low pressure side of the refrigeration cycle is provided at the upper portion of the accumulator 25, and the first and second bottom portions pass through the outer portion and the inner portion of the accumulator 25, respectively. Holes 257S and 257T are provided. The first bottom through hole 257S and the first suction part 101S are connected by a first low-pressure communication pipe 31S bent in an L shape. The second bottom through hole 257T and the second suction part 101T are connected by a second low-pressure communication pipe 31T bent in an L shape. One ends of the first and second low pressure communication pipes 31 </ b> S and 31 </ b> T are extended to the upper inside of the accumulator 25.

  The first and second low-pressure communication pipes 31S and 31T that guide the low-pressure refrigerant of the refrigeration cycle to the first and second compression units 12S and 12T via the accumulator 25 are connected via the first and second suction pipes 105S and 105T. The first and second cylinders 121S and 121T are connected to the first and second suction holes 135S and 135T (see FIG. 2). That is, the first and second suction holes 135S and 135T communicate in parallel with the low pressure side of the refrigeration cycle.

  A discharge pipe 107 serving as a discharge unit that is connected to the high-pressure side of the refrigeration cycle and discharges high-pressure refrigerant gas to the high-pressure side of the refrigeration cycle is provided on the upper portion of the compressor housing 10. That is, the first and second discharge holes 190S and 190T communicate with the high pressure side of the refrigeration cycle.

  Lubricating oil is sealed in the compressor housing 10 up to the height of the second cylinder 121T. Further, the lubricating oil circulates in the compression section 12 by a blade pump (not shown) inserted in the lower part of the rotating shaft 15, and the compression space of the compressed refrigerant is partitioned by lubrication of sliding parts and a minute gap Have a seal.

  Next, a characteristic configuration of the rotary compressor 1 according to the first embodiment will be described with reference to FIGS. 1 and 3-1. In the rotary compressor 1 according to the first embodiment, the curvature radius R1 of the bent portion of the first low-pressure connecting pipe 31S is set to 1.5 times the curvature radius R2 of the bent portion of the second low-pressure connecting pipe 31T. The curvature center position P1 is positioned on the center line of the second bottom through-hole 257T or inward of the center of the second bottom through-hole 257T below the curvature center position P2 of the curvature radius R2.

  3-2, the curvature radius R1 of the bent portion of the first low-pressure connecting pipe 31S is set to 2.5 times the curvature radius R2 of the bent portion of the second low-pressure connecting pipe 31T. The curvature center position P1 with the curvature radius R1 is positioned below the curvature center position P2 with the curvature radius R2.

  According to the experiment, as shown in FIGS. 4-1 to 4-3, the curvature radius R1 of the bent portion of the first low-pressure connecting pipe 31S is set to 1.. By setting it to 5 times or more and 2.5 times or less, the rigidity of the first low-pressure connecting pipe 31S is not too small and not too large, and is at an appropriate level. The noise level of the resonance sound generated from the lower part of the accumulator 25 is reduced.

  As shown in FIG. 4-4, in the conventional first and second low-pressure connecting pipes 31S and 31T shown in FIG. 6 (R1 <1.5R2), the compressor housing is operated during high-speed operation of the rotary compressor 1. 10 vibration propagates to the lower part of the accumulator 25 through the first and second low-pressure connecting pipes 31S and 31T, and a resonance sound is generated from the lower part of the accumulator 25, and the conventional first and second low-pressures shown in FIG. In the structure of the connecting pipes 31S and 31T (2.5R2 <R1), the resonance noise is similarly generated during the medium speed operation of the rotary compressor, but the embodiment shown in FIGS. 3-1 and 3-2. In the structure of the first and second low-pressure connecting pipes 31S and 31T (1.5R2 ≦ R1 ≦ 2.5R2), resonance noise generated from the lower portion of the accumulator 25 at the operating frequency from low speed operation to high speed operation. The level is getting smaller (Fig. 4-4 Noise level indicated by the solid line is the average value of the noise level indicated by the solid line in FIG. 4-1 Figure 4-3. Also, the scale of Figure 4-1 Figure 4-4 are the same.).

  FIG. 5 is a longitudinal sectional view showing a second embodiment of the rotary compressor according to the present invention. As shown in FIG. 5, the rotary compressor 2 according to the second embodiment is provided with an annular weight 259 at the lower part in the housing of the accumulator 25. Other parts of the rotary compressor 2 of the second embodiment are not different from the rotary compressor 1 of the first embodiment.

  According to the rotary compressor 2 of the second embodiment, the weight of the lower portion of the housing of the accumulator 25 is increased, the vibration of the lower portion of the housing of the accumulator 25 can be reduced, and the noise level of the resonance sound can be further reduced. .

  As described above, the rotary compressor according to the present invention is suitable for a low-noise rotary compressor used in a refrigeration cycle such as an air conditioner.

DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 25 Accumulator 31S 1st low pressure connection pipe 31T 2nd low pressure connection pipe 101S 1st suction part 101T 2nd suction part 103S 1st through-hole 103T 2nd penetration Hole 105S First suction pipe 105T Second suction pipe 107 Discharge pipe (discharge section)
111 Stator 112 Rotor 12S 1st compression part 12T 2nd compression part 121S 1st cylinder 121T 2nd cylinder 123S 1st cylinder inner wall 123T 2nd cylinder inner wall 125S 1st annular piston 125T 2nd annular piston 127S 1st vane 127T 1st 2-vane 128S first vane groove 128T second vane groove 129S, 129T back pressure introduction path 130S first working chamber 130T second working chamber 131S first suction chamber 131T second suction chamber 133S first compression chamber 133T second compression chamber 135S First suction hole 135T Second suction hole 136 Refrigerant passage 140 Intermediate partition plate 151 Lower bearing support portion 152S First eccentric portion 152T Second eccentric portion 153 Upper bearing support portion 160S Lower end plate 160T Upper end plate 161S Lower bearing portion 161T Upper Bearing part 170S Lower muff Lur cover 170T Upper muffler cover 175 Bolt 180S Lower muffler chamber 180T Upper muffler chamber 190S First discharge hole 190T Second discharge hole 200S First discharge valve 200T Second discharge valve 201S First discharge valve press 201T Second discharge valve press 252 Accum holder 253 Accum Band 255 System connection pipe (suction part)
257S First bottom through hole 257T Second bottom through hole 259 Weight

Claims (2)

A hermetically sealed cylindrical compressor housing that is provided with a refrigerant discharge part at the top and second and first suction parts at the top and bottom of the side;
An accumulator attached to the upper side portion of the compressor housing, provided with a refrigerant suction portion at the top, and provided with first and second bottom through holes on the outside and inside of the bottom;
Refrigerant gas is sucked through an L-shaped first low-pressure connecting pipe installed at the lower part of the compressor housing and connecting the first bottom through hole and the first suction portion, and the compressor housing A first compression section for discharging refrigerant gas from the discharge section through the body;
An L-shaped second low-pressure connecting pipe disposed on the first compression section, connected between the second bottom through-hole and the second suction section and disposed inside the first low-pressure connecting pipe; A second compression unit that sucks refrigerant gas through the compressor housing and discharges the refrigerant gas from the discharge unit through the compressor housing;
In a rotary compressor with
A rotary compressor characterized in that a curvature radius R1 of a bent portion of the first low-pressure connecting pipe is 1.5 times or more and 2.5 times or less of a curvature radius R2 of the bent portion of the second low-pressure connecting pipe. .   The rotary compressor according to claim 1, wherein a weight is installed at a lower part of the housing of the accumulator.

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