JP2017096116A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve compression efficiency of a compressor by reducing suction pressure loss of refrigerant sucked from an accumulator into a compressor body.SOLUTION: A compressor 1 includes: a compressor casing 10; a compression part 12 arranged in the compressor casing and compressing a refrigerant sucked from a suction part 30 of the compressor casing and discharging the compressed refrigerant from a discharging part 106; and an accumulator 25 attached to a side part of the compressor casing and connected to the suction part. The accumulator includes: a closed vessel of which upper part is connected to an evaporator in a refrigerant circuit; a partition plate 254 for defining an inside of the closed vessel into an upper chamber 259 and a lower chamber 256; and a communication pipe 260 passing through the partition plate and extended up to an upper part of the upper chamber so as to communicate the upper chamber with the lower chamber. The suction part is constituted by a straight pipe and is connected to the lower chamber.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor used in an air conditioner, a refrigerator, or the like.

  For example, Patent Document 1 includes a compressor body including an electric motor and a rotary type compression unit inside a hermetic shell, and an accumulator on the side of the compressor body, and a refrigerant circuit is connected to an upper portion of the accumulator. In the rotary compressor in which the refrigerant return pipe and a single L-shaped refrigerant suction pipe connected to the compression section are connected to the lower part, the inner diameter of the refrigerant return pipe is D1, and the inner diameter of the refrigerant suction pipe Describes a rotary compressor in which D2> D1, where D2 is D2.

JP 2008-240666 A

  In the rotary compressor described in Patent Document 1, the inner diameter D2 of the refrigerant suction pipe on the outlet side is larger than the inner diameter D1 of the refrigerant return pipe on the inlet side of the accumulator (D2> D1). The pressure loss is reduced by suppressing the flow velocity fluctuation in the refrigerant suction pipe connecting the.

  In such a compressor, in the case of a two-cylinder type compressor having two compression parts inside a hermetic shell, it is considered to reduce the number of refrigerant suction pipes from two to one for the purpose of cost reduction. It is done. However, in the rotary compressor described in Patent Document 1, since the refrigerant suction pipe is an L-shaped curved pipe, when the refrigerant flows in the L-shaped curved pipe, a pressure difference occurs between the inside and the outside of the bend, and this pressure Due to the difference, a vortex is generated in the pipe, resulting in a large suction pressure loss. Further, when the number of the refrigerant suction pipes is changed from two to one, the flow path cross-sectional area is reduced by half, so that the flow rate of the refrigerant increases and the suction pressure loss increases.

  An object of the present invention is to reduce the suction pressure loss of the refrigerant sucked from the accumulator into the compressor body and improve the compression efficiency of the compressor.

  The present invention includes a vertically mounted compressor housing that is provided with a refrigerant discharge portion at an upper portion and a refrigerant suction portion at a lower portion and is sealed, and is disposed in the compressor housing and sucked from the suction portion. Two upper and lower compression parts that compress the refrigerant and discharge it from the discharge part, a motor that is arranged in the compressor casing and drives the compression part via a rotating shaft, and a side part of the compressor casing An accumulator attached to and connected to the refrigerant suction section, wherein the accumulator is divided into an upper chamber and a lower chamber in a sealed container having a connection pipe connected to an upper portion thereof; A partition plate that communicates with the upper chamber and the lower chamber through the partition plate, and the two upper and lower compression portions each have a working chamber that sucks and compresses the refrigerant. A suction hole for supplying a refrigerant to the working chamber, An intermediate partition plate is disposed between the compression portions, and the intermediate partition plate includes a branch hole that connects the suction hole of the lower compression portion and the suction hole of the upper compression portion, and The section is composed of a straight pipe provided so as to connect either one of the suction holes provided in each of the two upper and lower compression parts and the accumulator, and the straight pipe is connected to the lower chamber. It is characterized by that.

  The present invention can reduce the suction pressure loss of the refrigerant sucked from the accumulator into the compressor body, and can improve the compression efficiency of the compressor.

FIG. 1 is a longitudinal sectional view showing a rotary compressor according to an embodiment. FIG. 2 is a cross-sectional view seen from above the first compression section. FIG. 3 is a cross-sectional view seen from above the second compression section. FIG. 4 is a plan view showing the accumulator retainer.

  DESCRIPTION OF EMBODIMENTS Modes (examples) for carrying out the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a longitudinal sectional view showing a rotary compressor according to this embodiment. FIG. 2 is a cross-sectional view seen from the top of the first and second compression portions. FIG. 3 is a plan view showing the accumulator retainer.

  As shown in FIG. 1, the rotary compressor 1 includes a compression unit 12 disposed at a lower portion of a hermetically sealed cylindrical compressor housing 10 and an upper portion of the compressor housing 10. And a motor 11 that drives the compression unit 12 via 15.

  The stator 111 of the motor 11 is formed in a cylindrical shape, and 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 inside the cylindrical 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. A terminal block 115 having a terminal 116 to which a stator winding of the motor 11 is connected is fixed to the upper portion of the compressor housing 10.

  The compressing unit 12 includes a first compressing unit 12S and a second compressing unit 12T stacked on the upper side of the first compressing unit 12S. As shown in FIG. 2, the first compression portion 12S includes a tubular first cylinder 121S in which first suction holes 135S and first vane grooves 128S are radially provided in the first laterally extending portion 122S. As shown in FIG. 3, the second compression portion 12T includes an annular second cylinder 121T in which a second suction hole 135T and a second vane groove 128T are radially provided in the second laterally extending portion 122T. It has.

  As shown in FIG. 2, the first cylinder 121 </ b> S is formed with a circular first cylinder inner wall 123 </ b> S concentric with the rotation shaft 15 of the motor 11. A first annular piston 125S having an outer diameter smaller than the cylinder inner diameter is disposed in each first cylinder inner wall 123S. The refrigerant gas is sucked and compressed between the first cylinder inner wall 123S and the first annular piston 125S. Thus, the first working chamber 130S for discharging is formed. As shown in FIG. 3, a circular second cylinder inner wall 123 </ b> T is formed in the second cylinder 121 </ b> T concentrically with the rotating shaft 15 of the motor 11. A second annular piston 125T having an outer diameter smaller than the cylinder inner diameter is disposed in the second cylinder inner wall 123T. The refrigerant gas is sucked and compressed between the second cylinder inner wall 123T and the second annular piston 125T. Thus, the second working chamber 130T for discharging is formed.

  The first cylinder 121S is formed with a first vane groove 128S extending in the radial direction from the first cylinder inner wall 123S over the entire cylinder height, and the first vane 127S having a flat plate shape is formed in the first vane groove 128S. It is slidably fitted. The second cylinder 121T is formed with a second vane groove 128T extending in the radial direction from the second cylinder inner wall 123T over the entire cylinder height, and each of the plate-like second vanes 127T is formed in the second vane groove 128T. Are slidably fitted.

As shown in FIG. 2, a first spring hole 124S is formed in the back of the first vane groove 128S so as to communicate with the first vane groove 128S from the outer peripheral portion of the first cylinder 121S. A first vane spring (not shown) that presses the back surface of the first vane 127S is inserted into the first spring hole 124S.
As shown in FIG. 3, a second spring hole 124T is formed in the inner portion of the second vane groove 128T so as to communicate with the second vane groove 128T from the outer peripheral portion of the second cylinder 121T. A second vane spring (not shown) that presses the back surface of the second vane 127T is inserted into the second spring hole 124T.

  When the rotary compressor 1 is started, the first vane 127S protrudes from the first vane groove 128S into the first working chamber 130S by the repulsive force of the first vane spring, and the tip thereof is the first annular piston 125S. The first working chamber 130S is partitioned into a first suction chamber 131S and a first compression chamber 133S by the first vane 127S. Further, due to the repulsive force of the second vane spring, the second vane 127T protrudes from the second vane groove 128T into the second working chamber 130T, and the tip thereof abuts on the outer peripheral surface of the second annular piston 125T. The second working chamber 130T is partitioned into a second suction chamber 131T and a second compression chamber 133T by the two vanes 127T.

  In addition, the first cylinder 121S communicates with the inner portion of the first vane groove 128S and the inside of the compressor casing 10 through the opening R shown in FIG. The first pressure introduction path 129S is formed in which the back pressure is applied to the first vane 127S by the pressure of the refrigerant gas. In addition, the second cylinder 121T communicates with the inner portion of the second vane groove 128T and the inside of the compressor casing 10 through the opening R shown in FIG. 1, and the compressed refrigerant gas in the compressor casing 10 is compressed. And a second pressure introduction path 129T is formed in the second vane 127T to apply a back pressure by the pressure of the refrigerant gas.

The first cylinder 121S is provided with a first suction hole 135S that allows the first suction chamber 131S to communicate with the outside in order to suck the refrigerant from the outside into the first suction chamber 131S.
A second cylinder 121T and an intermediate partition plate 140, which will be described later, are connected to the second suction chamber 131T and the first suction hole 135S in order to suck the refrigerant from the first suction hole 135S into the second suction chamber 131T. A suction hole 135T and a branch hole 141 are provided. The refrigerant that has flowed into the first suction hole 135S from the outside passes through the branch hole 141, and is then sucked into the second suction chamber 131T through the second suction hole 135T.

  Further, as shown in FIG. 1, an intermediate partition plate 140 is disposed between the first cylinder 121S and the second cylinder 121T, and the first working chamber 130S (see FIG. 2) of the first cylinder 121S and the second cylinder. The second working chamber 130T (see FIG. 2) of 121T is partitioned and closed. The intermediate partition plate 140 closes the upper end portion of the first cylinder 121S and the lower end portion of the second cylinder 121T. A lower end plate 160S is disposed 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 disposed at the upper end portion of the second cylinder 121T, and closes the second working chamber 130T of the second cylinder 121T. The intermediate partition plate 140 is provided with a branch hole 141 that connects the first suction hole 135S of the first cylinder 121S and the second suction hole 135T of the second cylinder 121T.

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

  The rotating shaft 15 includes a first eccentric portion 152S and a second eccentric portion 152T that are eccentric with a phase difference of 180 ° from each other. The first eccentric portion 152S is connected to the first annular piston 125S of the first compression portion 12S. The second eccentric portion 152T is rotatably fitted to the second annular piston 125T of the second compression portion 12T.

  When the rotary shaft 15 rotates, the first annular piston 125S revolves in the first cylinder 121S in the clockwise direction in FIG. 2 along the first cylinder inner wall 123S, and the first vane 127S reciprocates following this. . Due to the movement of the first annular piston 125S and the first vane 127S, the volumes of the first suction chamber 131S and the first compression chamber 133S change continuously, and the compression unit 12 continuously sucks and compresses the refrigerant gas. To discharge. Further, the second annular piston 125T revolves in the second cylinder 121T in the clockwise direction in FIG. 2 along the second cylinder inner wall 123T, and the second vane 127T reciprocates following this. Due to the movement of the second annular piston 125T and the second vane 127T, the volumes of the second suction chamber 131T and the second compression chamber 133T change continuously, and the compression unit 12 continuously sucks and compresses the refrigerant gas. To discharge.

  As shown in FIG. 1, a lower muffler cover 170S is arranged below the lower end plate 160S, and a lower muffler chamber 180S is formed between the lower end plate 160S and the lower muffler cover 170S. 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 reed valve type first discharge valve 200S for preventing the backflow of the compressed refrigerant gas is disposed.

  The lower muffler chamber 180S is one chamber formed 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 path that communicates with the upper muffler chamber 180T through the refrigerant path 136 (see FIG. 2) that passes through. 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 deflection opening of the first discharge valve 200S is fixed to the first discharge valve 200S by a rivet together with the first discharge valve 200S. The first discharge hole 190S, the first discharge valve 200S, and the first discharge valve presser 201S constitute a first discharge valve portion of the lower end plate 160S.

  As shown in FIG. 1, an upper muffler cover 170T is arranged 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. 3) for communicating the second compression chamber 133T and the upper muffler chamber 180T of the second cylinder 121T is provided, and the second discharge hole 190T. Is provided with a reed valve type 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 second discharge hole 190T, the second discharge valve 200T, and the second discharge valve presser 201T constitute a second discharge valve portion of the upper end plate 160T.

  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 a plurality of through bolts 175 and the like. Out of the compression portion 12 that is integrally fastened by a through bolt 175 or the like, 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. .

  Lubricating oil is sealed in the compressor housing 10 up to the height of the second cylinder 121T. Further, the lubricating oil is sucked up from an oil supply pipe 16 attached to the lower end portion of the rotating shaft 15 by a pump blade (not shown) inserted in the lower portion of the rotating shaft 15, circulates through the compressing portion 12, and slide parts Lubrication is performed and a small gap in the compression portion 12 is sealed.

  Connected to the top of the compressor housing 10 is a discharge pipe 107 as a discharge unit 106 that is connected to the refrigerant circuit constituting the refrigeration cycle together with the rotary compressor 1 and discharges high-pressure refrigerant gas to the condenser side of the refrigerant circuit. ing. That is, the first discharge hole 190S and the second discharge hole 190T are connected to the condenser of the refrigerant circuit.

  Next, an accumulator 25 that is a characteristic configuration of the rotary compressor 1 of the present embodiment will be described with reference to FIGS. 1 and 4.

  A through hole 101 is provided in the outer peripheral wall of the cylindrical compressor housing 10 so as to allow the suction pipe 104 to pass therethrough. In addition, an accumulator 25 having an independent cylindrical sealed container 251 is held by an accumulator holder 252 and an accumulator band 253 on the side portion of the compressor housing 10.

  A system connection pipe 255 connected to the evaporator of the refrigerant circuit is connected to the upper part of the sealed container 251. The sealed container 251 is partitioned into an upper chamber 259 and a lower chamber 256 by a partition plate 254. The upper chamber 259 and the lower chamber 256 communicate with each other through a communication pipe 260 that extends through the partition plate 254 and extends from the lower chamber 256 to the upper portion of the upper chamber 259. The communication pipe 260 is preferably a straight pipe without bending.

  On the upper chamber 259 side of the communication pipe 260, there are a plurality of oil return holes 261 that return the lubricating oil discharged together with the refrigerant from the rotary compressor 1 and returned from the refrigerant circuit to the upper chamber 259 of the accumulator 25 to the lower chamber 256. Is provided. The bottom 258 of the lower chamber 256 of the accumulator 25 is flat.

  An accumulator retainer 263 (see FIG. 4) is disposed above the communication pipe 260 in the upper chamber 259. The accumulator retainer 263 is provided with a refrigerant passage hole 264 in the outer peripheral portion, and causes the liquid refrigerant falling from the system connection pipe 255 to fall into the upper chamber 259 from the refrigerant passage hole 264 in the outer peripheral portion. Therefore, the liquid refrigerant is prevented from falling into the communication pipe 260 and being sent directly to the lower chamber 256.

  The other end of the low-pressure connecting pipe 31S, one end of which is connected to the suction pipe 104, is fixed (brazed or welded) to the side through hole 257 provided at the lower part of the side of the lower chamber 256 of the accumulator 25. . The suction pipe 104 and the low-pressure communication pipe 31S are short straight pipes without bending.

  The suction pipe 104 and the low pressure communication pipe 31 </ b> S constitute the suction part 30 of the compressor housing 10. Note that the low-pressure communication pipe 31S may be eliminated, and the suction pipe 104 may be directly connected to the side through hole 257.

  The straight pipes (the low-pressure communication pipe 31S and the suction pipe 104) constituting the suction part are preferably prevented from protruding into the lower chamber 256 of the accumulator 25 in order not to increase the suction pressure loss of the refrigerant. In addition, the cross-sectional area of the communication pipe 260 is made larger than the cross-sectional area of the straight pipe (the low-pressure communication pipe 31S and the suction pipe 104), so that the flow rate of the refrigerant in the communication pipe 260 is lowered and the suction pressure loss is not increased. Good.

  The low-pressure communication pipe 31S for guiding the low-pressure refrigerant in the refrigerant circuit to the first compression section 12S and the second compression section 12T through the accumulator 25 is connected to the first suction hole 135S of the first cylinder 121S through the suction pipe 104. (See FIG. 2), and is connected from the first suction hole 135S to the second suction hole 135T (see FIG. 3) of the second cylinder 121T through the branch hole 141. Of the refrigerant flowing into the first suction hole 135S from the low pressure communication pipe 31S, half flows into the second suction hole 135T via the branch hole 141. The refrigerant that has flowed into the first suction hole 135S and the second suction hole 135T is sucked into the first suction chamber 131S and the second suction chamber 131T, respectively. That is, the suction portion 30 is connected to the first working chamber 130S and the second working chamber 130T through the first suction hole 135S and the second suction hole 135T.

  When the rotary compressor 1 of the present embodiment is operated, part of the gas refrigerant and lubricating oil compressed by the compression unit 12 is discharged from the discharge unit 106 (discharge pipe 107), and circulates through the refrigerant circuit to accumulator 25. Is returned to the system connection pipe 255 as a gas-liquid two-phase refrigerant and lubricating oil.

  The liquid refrigerant and lubricating oil in the gas-liquid two-phase refrigerant fall from the system connection pipe 255 onto the accumulator retainer 263 and fall into the upper chamber 259 through the refrigerant passage hole 264 on the outer peripheral portion. The liquid refrigerant is decompressed in the upper chamber 259 by the suction of the compression unit 12 to become a gas refrigerant, rises in the upper chamber 259, is sucked from the upper end opening of the communication pipe 260, passes through the communication pipe 260, and the lower chamber 256. Sent in. The lubricating oil accumulated in the upper chamber 259 falls to the bottom 258 of the lower chamber 256 through the oil return hole 261 of the communication pipe 260. The gas refrigerant in the gas-liquid two-phase refrigerant passes through the refrigerant passage hole 264 from the system connection pipe 255 and flows into the upper chamber 259. Thereafter, the air is sucked from the upper end opening of the communication pipe 260 and is sent through the communication pipe 260 into the lower chamber 256.

  The gas refrigerant and the lubricating oil in the lower chamber 256 are sucked into the compression section 12 through the suction section 30 including the short straight pipe without bending and the low pressure communication pipe 31S.

  Conventionally, since the refrigerant suction pipe is a long L-shaped curved pipe, when the refrigerant flows through the L-shaped curved pipe, a large suction pressure loss occurs and the suction pressure is reduced. When the suction pressure decreases, the volumetric efficiency of the compressor decreases, and consequently, the refrigerant circulation amount in the refrigerant circuit decreases and the refrigeration capacity decreases. On the other hand, in the rotary compressor 1 of the present embodiment, since the short straight pipe (the suction pipe 104 and the low pressure communication pipe 31S) without bending is used in the suction portion 30, the suction pressure loss of the refrigerant is further reduced. The compression efficiency of the rotary compressor 1 can be improved.

  Further, the other end of the low-pressure communication pipe 31S that is a straight pipe constituting the suction portion 30 is brazed (or welded) to the side through-hole 257 of the accumulator 25 and does not protrude into the lower chamber 256. Does not increase suction pressure loss. In addition, the cross-sectional area of the communication pipe 260 is made larger than the cross-sectional area of the straight pipe (the low-pressure communication pipe 31S and the suction pipe 104), so that the flow rate of the refrigerant in the communication pipe 260 is lowered and the suction pressure loss is not increased. ing.

  As mentioned above, although the Example which concerns on this invention was described, this Example is not limited by the content mentioned above. In addition, the above-described constituent elements include those that can be easily assumed by those skilled in the art, those that are substantially the same, and those in a so-called equivalent range. Furthermore, the above-described components can be appropriately combined. Furthermore, at least one of various omissions, substitutions, and changes of the components can be made without departing from the scope of the present embodiment.

  For example, in the present embodiment, the straight pipe (the low pressure communication pipe 31 and the suction pipe 104) is connected to the first suction hole 135S (see FIG. 2) of the first cylinder 121S, and is branched from the first suction hole 135S. In the above description, an example in which the second cylinder 121T is connected to the second suction hole 135T (see FIG. 3) via the 141 has been described. However, the straight pipe (the low pressure communication pipe 31 and the suction pipe 104) is the second cylinder 121T. The second suction hole 135T may be connected to the first suction hole 135S of the first cylinder 121S through the branch hole 141 from the second suction hole 135T.

  That is, the effect of the present invention of reducing the suction pressure loss can be exerted regardless of which of the upper and lower cylinders the straight pipe is connected to. However, as in this embodiment, the straight pipe (low pressure communication pipe 31 and suction pipe 104) is connected to the first suction hole 135S of the first cylinder 121S (connected to the suction hole from the lower cylinder height). By doing so, the mounting position of the accumulator 25 can be lowered compared to the case of connecting to the second suction hole 135T of the second cylinder 121T (connecting to the suction hole from the height of the upper cylinder). As a result, the height of the mounting position of the accumulator 25 can be lowered, which not only contributes to lowering the vibration by lowering the center of gravity of the compressor 1, but also lowers the height of the upper end of the accumulator. The mountability of is improved.

DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 16 Oil supply pipe 25 Accumulator 30 Suction part 31S Low-pressure connection pipe (suction part)
101 Through hole 104 Suction pipe (suction part)
106 Discharge part 107 Discharge pipe (discharge part)
111 Stator 112 Rotor 115 Terminal Block 116 Terminal 12S First Compression Unit 12T Second Compression Unit 121S First Cylinder (Cylinder)
121T 2nd cylinder (cylinder)
122S 1st side overhang part 122T 2nd side overhang part 123S 1st cylinder inner wall (cylinder inner wall)
123T 2nd cylinder inner wall (cylinder inner wall)
130S 1st working chamber (working chamber)
130T second working chamber (working chamber)
131S First suction chamber (suction chamber)
131T Second suction chamber (suction chamber)
133S 1st compression chamber (compression chamber)
133T Second compression chamber (compression chamber)
135S 1st suction hole (suction hole)
135T 2nd suction hole (suction hole)
136 Refrigerant passage 140 Intermediate partition plate 141 Branch hole 251 Airtight container 252 Accum holder 254 Partition plate 256 Lower chamber 259 Upper chamber 260 Communication tube 264 Refrigerant passage hole

Claims (2)

A vertically disposed compressor housing that is provided with a refrigerant discharge portion at the top and a refrigerant suction portion at the bottom and is sealed, and that is disposed in the compressor housing and compresses the refrigerant sucked from the suction portion. Two upper and lower compression sections that discharge from the discharge section, a motor that is disposed in the compressor casing and drives the compression section via a rotating shaft, and is attached to a side portion of the compressor casing, In a compressor comprising an accumulator connected to a refrigerant suction section,
The accumulator includes a sealed container having a connection pipe connected to an upper part thereof, a partition plate that divides the inside of the sealed container into an upper chamber and a lower chamber, and communicates the upper chamber and the lower chamber through the partition plate. A communication pipe, and
The upper and lower two compression parts each include a working chamber that sucks and compresses the refrigerant, and a suction hole that supplies the refrigerant to the working chamber,
An intermediate partition plate is disposed between the upper and lower compression parts, and a branch hole that connects the suction hole of the lower compression part and the suction hole of the upper compression part is formed in the intermediate partition plate. Prepared,
The suction part includes a straight pipe provided so as to connect either one of the suction holes provided in each of the upper and lower two compression parts and the accumulator, and the straight pipe is connected to the lower chamber. The compressor characterized by having.   The compressor according to claim 1, wherein the straight pipe is connected to the suction hole from a height of the lower compression portion.

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