JP2010209855A - Rotary compressor - Google Patents

Abstract

To obtain a compressor having a large balance weight that has a good yield, does not block a refrigerant gas hole of a rotor, and can be provided with a rivet hole.
A refrigerant casing is installed at a lower portion of the compressor casing and sucks refrigerant gas from a low-pressure side of the refrigeration cycle through the suction section, and passes through the compressor casing from the discharge section to the refrigeration cycle. A compression unit that discharges refrigerant gas to the high-pressure side, a motor that is installed at the top of the compressor housing and drives the compression unit via a rotating shaft, and an annular ring that is intermittently connected to an inner peripheral portion of the rotor of the motor In the rotary compressor, the arc-shaped balance weight is provided with a plurality of gas holes that pass through the refrigerant gas below the motor and the arc-shaped balance weight installed on the outer periphery of the upper and lower ends of the rotor. The inner edge is located outside the outer edge of the gas hole, and the outer edge of the arc-shaped balance weight is located inside the outer edge of the rotor.
[Selection] Figure 3-1

Description

  The present invention relates to a rotary compressor used in a refrigeration apparatus and the like, and more particularly to a balance weight installed at a rotor end portion of a motor.

  Conventionally, in a container, a compression unit, an electric motor unit, a rotary shaft having an eccentric part that transmits the rotational force of the electric motor unit to the compression unit, a rotor of the electric motor unit, and / or the rotary shaft are the same. A compressor comprising an arc-shaped balance weight that removes an unbalanced load generated during rotational movement of a rotating shaft, wherein the outer circumferential arc surface and the inner circumferential arc surface of the arc-shaped balance weight have the same curvature. A compressor is disclosed (for example, see Patent Document 1).

  The balance weight is obtained by punching a steel plate with a press. The balance weight is provided with a hole through which a rivet for fixing the balance weight to the rotor of the electric motor unit is passed. In addition, the balance weight is formed in an arc shape having the same curvature as the rotor outer peripheral surface or a slightly smaller curvature so as not to protrude outward from the outer peripheral surface of the rotor (so as not to interfere with the stator). Yes.

  The rotor is fixed to the rotation shaft and rotationally drives an eccentric portion provided at the other end of the rotation shaft. The rotor is provided with a through hole serving as a refrigerant gas passage. The rivet is for fixing the laminated rotor steel plates together, but together, the balance weight is also fixed to the rotor end face.

  The refrigerant gas compressed by the compression unit disposed at the lower part of the compressor moves up the motor unit and is discharged out of the compressor from a discharge pipe provided above the motor unit. Part of the oil that lubricates the compression part rises through the through hole of the rotor together with the refrigerant gas, collides with the oil separation plate, is centrifuged from the refrigerant gas, and returns to the oil sump at the bottom of the compressor by gravity.

JP 2006-152838 A

  However, as in the prior art, in order to improve the yield of the balance weight, if the outer peripheral arc surface and the inner peripheral arc surface are configured with the same curvature, the central portion of the inner peripheral surface protrudes toward the inner diameter side. Become. Therefore, as shown in FIG. 6, the balance weight 514 blocks a part of the through hole 512 </ b> A of the rotor 512, lowers the oil separation efficiency in the compressor, and increases the amount of oil flowing out of the compressor. There is a problem.

  If the inner peripheral portion of the balance weight has a curvature of the inner peripheral circular arc surface that does not block the through hole that becomes the refrigerant gas passage of the rotor, there is a problem that the balance weight becomes small. In addition, when there are three rivets, there is a problem that the rivet interval becomes large, the rivet through hole cannot be provided in the balance weight, and the balance weight cannot be fixed to the rotor.

  The present invention has been made in view of the above, and it is an object of the present invention to obtain a rotary compressor having a large balance weight capable of providing a rivet hole without blocking the refrigerant gas hole of the rotor with good yield. Objective.

  In order to solve the above-described problems and achieve the object, the present invention provides a vertically-placed cylindrical compressor housing that is provided with a refrigerant gas discharge part at the top and a refrigerant gas suction part at the bottom and is sealed. Installed in the lower part of the compressor housing, sucks refrigerant gas from the low pressure side of the refrigeration cycle through the suction portion, and discharges refrigerant gas from the discharge portion to the high pressure side of the refrigeration cycle through the compressor housing. A compression unit, a motor installed on an upper portion of the compressor housing and driving the compression unit via a rotation shaft; and an annular ring intermittently connected to an inner periphery of a rotor of the motor; In a rotary compressor comprising a plurality of gas holes for allowing refrigerant gas to pass upward, and arc-shaped balance weights installed on the outer peripheral portions of the upper and lower ends of the rotor, the inner edge of the arc-shaped balance weight is the gas hole Outer edge Located in remote outside edge of the arcuate balance weight, characterized in that located inside the outer edge of said rotor.

  According to the present invention, there is an effect that a rotary compressor having a large balance weight that can provide a rivet hole without blocking the refrigerant gas hole of the rotor is obtained.

FIG. 1 is a longitudinal sectional view showing an 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 a bottom view illustrating a state where the balance weight according to the first embodiment is installed on the rotor. 3-2 is an enlarged cross-sectional view of the rotor portion of FIG. FIG. 3-3 is a plan view of the balance weight according to the first embodiment. FIG. 4-1 is a plan view illustrating a state in which the balance weight according to the second embodiment is installed on the rotor. FIG. 4-2 is a plan view of the balance weight according to the second embodiment. FIG. 5A is a plan view illustrating a state in which the balance weight according to the third embodiment is installed on the rotor. FIG. 5-2 is a plan view of the balance weight according to the third embodiment. FIG. 6 is a bottom view showing a state in which a conventional balance weight is installed on a rotor.

  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.

  FIG. 1 is a longitudinal sectional view showing an 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. 3B is an enlarged cross-sectional view of the rotor portion of FIG. 1, and FIG. 3C is a plan view of the balance weight according to the first embodiment. is there.

  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 compression unit 12 includes a first compression unit 12S and a second compression unit 12T that is installed in parallel with the first compression unit 12S and stacked on the upper side of the first compression 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. In addition, six outer peripheral through holes 160TA having an arc long hole shape are provided on the outer peripheral portion of the upper end plate 160T. The outer peripheral through hole 160TA is a hole through which the lubricating oil mixed with the refrigerant gas in the compression unit 12 and blown to the upper portion of the compressor housing 10 is separated from the refrigerant gas and returned to the lower portion of the compressor housing 10. is there.

  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 first discharge hole 190S and the first discharge valve 200S constitute a first discharge valve portion.

  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 a communication path that communicates with the inside of the upper muffler chamber 180T through a refrigerant path (not shown) that passes through the center. 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. The second discharge hole 190T and the second discharge valve 200T constitute a second discharge valve portion. A gap (muffler discharge hole) 170TS is provided between the upper muffler cover 170T and the upper bearing portion 161T, and the refrigerant gas discharged from the second discharge valve portion flows out into the compressor housing 10.

  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.

  Although not shown, first and second through holes 101 and 102 are provided in the outer peripheral wall of the cylindrical compressor casing 10 in the axial direction and in order from the lower part, and the first and second suction pipes 104 and 105. It is provided to pass through. Further, an accumulator 25 </ b> T made of an independent cylindrical sealed container is held by an accumulator holder and an accumulator band 253 on the outer side of the compressor housing 10.

  A system connection pipe 255 connected to the low pressure side of the refrigeration cycle is connected to the center of the top of the accumulator 25T, and one end of the bottom through-hole 257 provided at the bottom of the accumulator 25T extends to the upper inside of the accumulator 25T. The other ends of the first and second suction pipes 104 and 105 are connected to the first and second low-pressure communication pipes 31S and 31T.

  The first and second low-pressure connecting pipes 31S and 31T for guiding the low-pressure refrigerant of the refrigeration cycle to the first and second compression parts 12S and 12T through the accumulator 25T are the first and second suction pipes 104, The first and second cylinders 121S and 121T are connected to the first and second suction holes 135S and 135T (see FIG. 2) via the 105. That is, the first and second suction holes 135S and 135T communicate in parallel with the low pressure side of the refrigeration cycle.

  Connected to the top of the compressor housing 10 is a discharge pipe 107 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. 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. The rotary shaft 15 is provided with an oil supply vertical hole (not shown) penetrating through the center portion and an oil supply horizontal hole (not shown) communicating with the oil supply vertical hole. A plurality of oil supply lateral holes are provided corresponding to the lower bearing portion 161S, the first and second annular pistons 125S and 125T, and the upper bearing portion 161T, respectively. In addition, an oil groove (not shown) that communicates with the oil supply lateral hole is provided in the lower bearing portion 161S and the upper bearing portion 161T, or a portion of the rotary shaft 15 corresponding thereto.

  A blade (not shown) is inserted into the oil supply vertical hole, and centrifugal force is applied to the lubricating oil by the blade rotating with the rotation of the rotary shaft 15 to improve the oil supply performance, particularly at a position higher than the lubricating oil surface. Thus, the upper bearing portion 161T is reliably lubricated.

  The lubricating oil stored in the lower portion of the compressor housing 10 is pumped up from the lower end of the rotating shaft 15 by the oil supply mechanism 155A described above, and the lower bearing portion 161S, the first and second annular pistons 125S and 125T, and the upper bearing. Lubricate the part 161T. Lubricating oil after lubricating each part enters the first and second working chambers 130S and 130T from the minute gaps between the parts that define the first and second compression parts 12S and 12T, and the first and second working chambers. The sliding portions 130S and 130T are lubricated and a minute gap pressure seal is performed, but most of the lubricating oil is discharged from the upper end of the oil groove of the upper bearing portion 161T and the lower end of the oil groove of the lower bearing portion 161S.

  As shown in FIGS. 3A and 3B, the rotor 112 formed by stacking steel plates into a columnar shape is provided with an axial hole 112B at the center, and axial rivet holes 112C at three outer peripheral portions. Is provided. In addition, elongated gas holes 112 </ b> A through which refrigerant gas discharged from the compressor 11 and below the motor 11 passes to the discharge pipe 107 side above the motor 11 are provided at six locations on the inner periphery. The long hole-shaped gas holes 112 </ b> A are arranged in an annular shape that is intermittently provided on the inner peripheral portion of the rotor 112.

  A rotor lower end plate 113A is fixed to the lower end of the rotor 112, and a rotor upper end plate 113B is fixed to the upper end. The arc-shaped lower balance weight 114A of the first embodiment is arranged on the outer peripheral portion of the rotor lower end plate 113A, and the arc-shaped lower balance weight 114A of the first embodiment is arranged on the outer peripheral portion of the rotor upper end plate 113B that is 180 ° out of phase with the lower balance weight 114A. The upper balance weight 114B is arranged to balance the rotation of the compression unit 12.

  An oil separation plate 119 having a central cylindrical portion 119B, a curved portion 119C continuously curved in the radial direction following the central cylindrical portion 119B, and an outer peripheral disc portion 119A continuous to the curved portion 119C, and a lower end portion of the central cylindrical portion 119B is a rotor The upper end of 112 and the inner periphery of the central hole of the rotor upper end plate 113B are fixed on the rotor 112 so as to be in close contact with each other.

  The inner diameter of the central cylindrical portion 119 </ b> B of the oil separation plate 119 is formed larger than the outer diameter of the rotating shaft 15 so as not to contact the rotating shaft 15. Further, the outer diameter of the outer peripheral disc portion 119A is formed to be substantially the same as the outer diameter of the rotor 112. A rivet hole is provided in a position facing the rivet hole 112 </ b> C of the rotor 112 in the outer peripheral disk portion 119 </ b> A of the oil separation plate 119.

  Three cylindrical spacers 116 are arranged at the positions of three rivet holes 112C between the outer peripheral disc portion 119A and the rotor upper end plate 113B, and the lower balance weight 114A or the upper balance weight 114B, the rotor lower end plate 113A, The oil separation plate 119 is fixed to the rotor 112 by passing through the three rivets 115 through the rotor 112, the rotor upper end plate 113B, the cylindrical spacer 116, and the outer peripheral disc portion 119A.

  Next, the shape of the balance weight according to the first embodiment will be described in detail with reference to FIGS. 3-1 and 3-3. The lower balance weight 114A and the upper balance weight 114B are obtained by stacking arc-shaped steel plates. In the two-cylinder rotary compressor 1 of the first embodiment, between the lower balance weight 114A and the upper balance weight 114B, There is no difference between the planar shape and the number of laminated steel plates (weight). In a two-stage compression type rotary compressor, a difference is provided in the number of stacked steel plates (weight) in order to balance, but there is no difference in the planar shape. In the following description, both the lower balance weight 114A and the upper balance weight 114B are collectively referred to as the balance weight 114.

  The arc-shaped balance weight 114 according to the first embodiment has an inner edge 114n located outside the outer edge 112f of the gas hole 112A, and an outer edge 114g located inside the outer edge 112g of the rotor 112. The balance weight 114 has an inner edge 114n located outside the outer edge 112g of the gas hole 112A and does not hinder the flow of the refrigerant gas through the gas hole 112A, so that the oil separation efficiency in the rotary compressor 1 is reduced. I will not let you.

  Further, the inner edge 114tn and the outer edge 114tg of both end portions 114t provided with the rivet holes of the arc-shaped balance weight 114 of the first embodiment are formed in an arc shape with substantially the same radius of curvature R1, and the inner edge 114n and the outer edge 114g in the central portion are formed. The inner edge 114tn and the outer edge 114tg of the both ends 114t have substantially the same radius of curvature R2 that is smaller than the radius of curvature R1 of the arc, and the respective centers of curvature On and Og are shifted outward to form an arc. Since the inner edge and the outer edge of the balance weight 114 have substantially the same radius of curvature, as shown in FIG. 3C, when a plurality of balance weights 114 are punched by a press, the material yield is good and can be manufactured at low cost. it can.

  FIG. 4-1 is a plan view illustrating a state in which the balance weight of the second embodiment of the rotary compressor according to the present invention is installed on the rotor, and FIG. 4-2 is a plan view of the balance weight of the second embodiment. . As shown in FIGS. 4A and 4B, the arc-shaped balance weight 114 according to the second embodiment has an inner edge 114n positioned outside the outer edge 112f of the gas hole 112A, and an outer edge 114g of the rotor 112. It is located inside the outer edge 112g. In the balance weight 114 of the second embodiment, the inner edge 114n is located outside the outer edge 112g of the gas hole 112A and does not hinder the flow of the refrigerant gas through the gas hole 112A. There is no reduction in separation efficiency.

  In addition, the inner edge 114n and the outer edge 114g of the central portion of the arc-shaped balance weight 114 of the second embodiment are formed in an arc shape with substantially the same radius of curvature R2, and the inner edges 114tn of both end portions 114t provided with rivet holes are formed at the central portion. The outer edge 114tg of both end portions 114t is formed at a tangent line at the end of the inner edge 114n, and is formed substantially parallel to the inner edge 114tn at the tangent line of the end of the outer edge 114g at the center portion.

  Since the arc-shaped balance weight 114 of Example 2 is formed as described above, as shown in FIG. 4B, when a plurality of balance weights 114 are punched out by a press, the material yield is good and it is manufactured at low cost. be able to. Moreover, since the outer edge 114tg of the both ends 114t of the balance weight 114 and the outer edge 114g of the center part are smoothly connected, the fluid resistance of the balance weight 114 is small, and the efficiency of the rotary compressor 1 can be improved.

  FIG. 5-1 is a plan view showing a state in which the balance weight of the third embodiment of the rotary compressor according to the present invention is installed on the rotor, and FIG. 5-2 is a plan view of the balance weight of the third embodiment. . As shown in FIGS. 5A and 5B, the arc-shaped balance weight 114 according to the third embodiment has an inner edge 114n located outside the outer edge 112f of the gas hole 112A, and an outer edge 114g of the rotor 112. It is located inside the outer edge 112g. In the balance weight 114 of the third embodiment, the inner edge 114n is located outside the outer edge 112g of the gas hole 112A and does not hinder the flow of the refrigerant gas through the gas hole 112A. There is no reduction in separation efficiency.

  In addition, the inner edge 114n and the outer edge 114g at the center of the arc-shaped balance weight 114 according to the third embodiment are formed in parallel straight lines, and the inner edge 114tn and the outer edge 114tg at both ends 114t are formed at the inner edge 114n and the outer edge 114g at the center. Are formed in a parallel straight line having an obtuse angle. Since the arc-shaped balance weight 114 of the third embodiment is formed as described above, as shown in FIG. 5B, when a plurality of balance weights 114 are punched out by a press, the material yield is good and the manufacturing is performed at low cost. be able to. Further, the center of gravity position 114W of the balance weight 114 can be further away from the center of rotation than the other embodiments, and the weight of the balance weight 114 can be reduced.

  As described above, the rotary compressor according to the present invention is useful for a refrigeration apparatus and the like.

DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 25T Accumulator 31S, 31T Low-pressure connection pipe 101 1st through-hole 102 2nd through-hole 104 1st suction pipe 105 2nd suction pipe 107 Discharge pipe (discharge) Part)
111 Stator 112 Rotor 112g Outer edge of rotor 112A Gas hole 112f Outer edge of gas hole 112B Shaft hole 112C Rivet hole 113A Rotor lower end plate 113B Rotor upper end plate 114 Balance weight 114n Inner edge (inner edge of central portion)
114g outer edge (outer edge of the center)
114t end portion 114tn end inner edge 114tg end outer edge 114w center of gravity position 114A lower balance weight 114B upper balance weight 115 rivet 116 cylindrical spacer 119 oil separation plate 119A outer peripheral disc portion 119B central cylindrical portion 119C bending portion 12S first Compression section 12T Second compression section 121S First cylinder 121T Second cylinder 123S First cylinder inner wall 123T Second cylinder inner wall 125S First annular piston 125T Second annular piston 127S First vane 127T Second 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 135 T second suction hole 140 intermediate partition plate 151 lower bearing support portion 152S first eccentric portion 152T second eccentric portion 153 upper bearing support portion 155A oil supply mechanism 160S lower end plate 160T upper end plate 160TA outer peripheral through hole 161S lower bearing portion 161T upper Bearing part 170S Lower muffler cover 170T Upper muffler cover 170TS Clearance (muffler discharge hole)
175 bolts 180S lower muffler chamber 180T upper muffler chamber 190S first discharge hole 190T second discharge hole (discharge valve part)
200S 1st discharge valve 200T 2nd discharge valve (discharge valve part)
201S First discharge valve holder 201T Second discharge valve holder 253 Accum band 255 System connection pipe 257 Bottom through hole

Claims (4)

A vertically-placed cylindrical compressor housing which is provided with a refrigerant gas discharge part at the top and a refrigerant gas suction part at the bottom and is sealed,
A compressor that is installed in the lower part of the compressor casing and sucks refrigerant gas from the low-pressure side of the refrigeration cycle through the suction section and discharges refrigerant gas from the discharge section to the high-pressure side of the refrigeration cycle through the compressor casing. When,
A motor that is installed in an upper portion of the compressor housing and drives the compression unit via a rotation shaft;
A plurality of gas holes arranged in an annular shape intermittently connected to the inner peripheral portion of the rotor of the motor, and allowing the refrigerant gas below the motor to pass upward;
An arc-shaped balance weight installed on the outer periphery of the upper and lower ends of the rotor;
A rotary compressor comprising:
The rotary compressor characterized in that an inner edge of the arc-shaped balance weight is located outside the outer edge of the gas hole, and an outer edge of the arc-shaped balance weight is located inside the outer edge of the rotor.   The inner edge and the outer edge of both ends of the arc-shaped balance weight are formed in an arc shape with substantially the same radius of curvature, and the inner edge and the outer edge of the central portion are substantially the same curvature smaller than the radius of curvature of the arc of the inner edge and the outer edge of the both ends. 2. The rotary compressor according to claim 1, wherein each of the rotary compressors has a radius and is formed in an arc shape by shifting each center of curvature outward.   The inner edge and the outer edge of the central portion of the arc-shaped balance weight are formed in an arc shape with substantially the same radius of curvature, the inner edges of both end portions are formed by tangent lines of the inner edge end of the central portion, and the outer edges of the both end portions are The rotary compressor according to claim 1, wherein the rotary compressor is formed by a tangent to an outer edge of the central portion.   The inner edge and the outer edge of the central part of the arc-shaped balance weight are formed in parallel straight lines, and the inner edge and the outer edge of both end parts are formed in parallel straight lines forming obtuse angles with the inner edge and the outer edge of the central part, respectively. The rotary compressor according to claim 1.

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