JP6477137B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor used for an air conditioner, a refrigerator, and the like.

  In the rotary compressor, when compression distortion occurs in the stator of the motor disposed in the compressor casing, the magnetization characteristics of the stator deteriorate, the iron loss increases, and the efficiency of the motor decreases.

  For example, Patent Document 1 includes an airtight container, a motor that is disposed in the airtight container and includes at least a stator and a rotor, and a compression mechanism that includes at least a shaft driven by the rotor. A diameter larger than the outer diameter of the stator, inserted between the sealed container and the outer diameter of the stator, fixed to the outer periphery of the stator with an interference fit, and welded to the sealed container at three locations A compressor further comprising a fixing member is described.

  Patent Document 1 includes a sealed container, a motor disposed in the sealed container and including at least a stator and a rotor, and a compression mechanism including at least a shaft driven by the rotor. The diameter is larger than the outer diameter of the stator, a part of the hermetic container is drawn, and the drawn part further includes a drawn part that contacts the stator, and the drawn part and the stator are joined by laser welding. A fixed compressor is described.

  Further, Patent Document 2 discloses an annular stator, a rotor rotatably disposed in the internal space of the stator, a sealed container including a cylindrical portion that houses the stator and the rotor, and an outer peripheral surface of the stator. The compressor which fixed the said stator and the said cylindrical part by the spot welding of three or more places in the circumferential direction in the state which ensured the clearance of 0.01-0.30 mm between the internal peripheral surfaces of the said cylindrical part. Is described. The compression mechanism of this compressor is screwed to the mounting plate, and the mounting plate is spot welded to the cylindrical portion of the sealed container.

JP 2010-255623 A JP 2008-248889 A

  However, the ring-shaped fixing described in Patent Document 1 is inserted between the sealed container and the outer diameter of the stator, is fixed to the outer periphery of the stator with an interference fit, and is welded to the sealed container at three locations. The compressor including the members has a problem in that since the ring-shaped fixing member is fixed to the outer periphery of the stator by an interference fit, compression distortion occurs in the stator, and the efficiency of the motor decreases. Further, there is a problem that the cost is increased by using the fixing member.

  Further, a part of the sealed container described in Patent Document 1 is drawn, and the drawn part includes a drawn part that comes into contact with the stator, and the drawn part and the stator are fixed by laser welding. Since the compressor draws a part of the sealed container, there is a problem that the cost increases accordingly.

  Moreover, the compressor described in patent document 2 is the state which ensured the radial gap of 0.01-0.30 mm between the stator and the cylindrical part, and made the said stator and the said cylindrical part into the circumferential direction. It is fixed by spot welding at three or more locations, the compression mechanism is screwed to the mounting plate, and the mounting plate is spot welded to the cylindrical portion of the sealed container. Therefore, when a 0.30 mm radial gap is provided between the stator and the cylindrical part, the radial gap is too large, and it is necessary to center the stator with respect to the cylindrical part, which increases the number of assembly steps. There's a problem. In addition, since the compression mechanism is fixed to the cylindrical portion via the mounting plate, there is a problem that the cost is increased by the amount of the mounting plate.

  An object of the present invention is to obtain a rotary compressor in which compression distortion does not occur in a stator of a motor disposed in a compressor housing, the motor efficiency is high, and cost increase is suppressed.

The present invention includes a vertically disposed compressor housing in which a refrigerant discharge portion is provided at an upper portion, a refrigerant suction portion is provided in a lower portion and lubricating oil is stored, and the compressor housing is disposed in the compressor housing. A compressor having an annular cylinder and an upper end plate and a lower end plate for closing the end of the cylinder, and compressing the refrigerant sucked from the suction portion by the cylinder and discharging the refrigerant from the discharge portion; and the compressor In a rotary compressor comprising: a cylindrical stator, a cylindrical stator and a rotor that is fixed to a rotation shaft and rotates within the stator; and a motor that drives the compression unit via the rotation shaft. When the inner diameter of the body of the compressor housing is φDm, the outer diameter of the upper end plate of the compressor is φDb, and the outer diameter of the stator of the motor is φDs, −0.05 mm ≦ φDm−φDb ≦ 0.05 mm And 0.1 mm ≦ φDm The φDm, φDb, and φDs are set so as to satisfy two formulas of φDs ≦ 0.2 mm, and the outer peripheral portion of the upper end plate and the outer peripheral portion of the stator are spaced apart from each other in the circumferential direction. A plurality of welded portions are provided by spot welding the outer peripheral portion of the upper end plate and the outer peripheral portion of the stator to the body portion of the compressor casing. As the plurality of welded portions, the compressor portion side of the outer peripheral portion of the stator is welded to the barrel portion and arranged at intervals in the circumferential direction of the stator. a plurality of first weld the plurality of second weld the opposite side are arranged at intervals in the circumferential direction of the weld has been said stator to said barrel and said compression portion of the outer peripheral portion of the stator When, with the upper and third weld the outer peripheral portion is welded to the body portion of the plurality disposed at intervals in the circumferential direction of the stator of the plate, but respectively provided, the first weld wherein said third weld and the second weld portion, the has a circumferential position of the stator are arranged offset from one another, characterized in that.

  In the present invention, when the inner diameter of the body of the compressor housing is φDm, the outer diameter of the upper end plate of the compression section is φDb, and the outer diameter of the stator of the motor is φDs, −0.05 mm ≦ φDm−φDb ≦ 0. ΦDm, φDb, and φDs are set so as to satisfy two formulas of 05 mm and 0.1 mm ≦ φDm−φDs ≦ 0.2 mm, and in the circumferential direction of the outer peripheral portion of the upper end plate and the outer peripheral portion of the stator. Since the plurality of spaced apart spots are spot welded to the body of the compressor casing, the stator of the motor disposed in the compressor casing does not undergo compressive strain, and the magnetizing characteristics of the stator do not deteriorate. The cost can be suppressed.

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 rotary compressor of the embodiment as viewed from above the first compression unit and the second compression unit. FIG. 3 is a longitudinal sectional view showing the stator and the rotor before assembly of the rotary compressor of the embodiment. FIG. 4 is a longitudinal sectional view showing a state after assembly of the stator and the rotor of the rotary compressor of the embodiment. FIG. 5 is a longitudinal cross-sectional view showing a state before the compression portion of the rotary compressor and the stator and the body portion of the compressor housing of the embodiment are fitted. FIG. 6 is a longitudinal cross-sectional view showing the compression portion of the rotary compressor and the stator after the fitting of the body portion of the compressor housing of the embodiment. FIG. 7 is a cross-sectional view taken along line AA in FIG. FIG. 8 is a cross-sectional view taken along line BB in FIG.

  EMBODIMENT OF THE INVENTION Below, the form (Example) for implementing this invention is demonstrated in detail, referring drawings.

  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 rotary compressor of the embodiment as viewed from above the first compression unit and the second compression unit.

  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 spot welding to the inner peripheral surface of the body portion 10 </ b> A of the compressor housing 10. A dimensional relationship between the body portion 10A of the compressor housing 10 and the stator 111, which is a characteristic configuration of the rotary compressor 1 of the present invention, and an assembling method will be described later. The rotor 112 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.

  The compression unit 12 includes a first compression unit 12S and a second compression unit 12T, and the second compression unit 12T is disposed on the upper side of the first compression unit 12S. As shown in FIG. 2, the first compression unit 12S includes an annular first cylinder 121S. The first cylinder 121S includes a first lateral projecting portion 122S projecting from an annular outer periphery, and the first lateral projecting portion 122S is provided with first suction holes 135S and first vane grooves 128S radially. ing. The second compression unit 12T includes an annular second cylinder 121T. The second cylinder 121T includes a second lateral projecting portion 122T projecting from an annular outer periphery, and the second lateral projecting portion 122T is provided with second suction holes 135T and second vane grooves 128T radially. ing.

  As shown in FIG. 2, a circular first cylinder inner wall 123 </ b> S is formed in the first cylinder 121 </ b> S concentrically with the rotating shaft 15 of the motor 11. A first annular piston 125S having an outer diameter smaller than the inner diameter of the first cylinder 121S is disposed in the first cylinder inner wall 123S, and the refrigerant is sucked between the first cylinder inner wall 123S and the first annular piston 125S. A first cylinder chamber 130S for compressing and discharging is formed. In the second cylinder 121T, a circular second cylinder inner wall 123T is formed concentrically with the rotating shaft 15 of the motor 11. A second annular piston 125T having an outer diameter smaller than the inner diameter of the second cylinder 121T is disposed in the second cylinder inner wall 123T, and the refrigerant is sucked between the second cylinder inner wall 123T and the second annular piston 125T. A second cylinder chamber 130T that discharges after compression 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. A flat plate-like first vane 127S is slid in the first vane groove 128S. It is movably 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 a flat plate-like second vane 127T is slid in the second vane groove 128T. It is movably fitted.

  As shown in FIG. 2, a first spring hole 124S is formed on the outer side in the radial direction of the first vane groove 128S so as to communicate with the first vane groove 128S from the outer peripheral portion of the first laterally extending portion 122S. Yes. A first vane spring 126S (see FIG. 1) that presses the back surface of the first vane 127S is inserted into the first spring hole 124S. A second spring hole 124T is formed on the radially outer side of the second vane groove 128T so as to communicate with the second vane groove 128T from the outer peripheral portion of the second laterally extending portion 122T. A second vane spring 126T (see FIG. 1) 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 cylinder chamber 130S by the repulsive force of the first vane spring 126S, and the tip thereof is the first annular piston. The first cylinder chamber 130S is partitioned into a first suction chamber 131S and a first compression chamber 133S by the first vane 127S in contact with the outer peripheral surface of 125S. Similarly, due to the repulsive force of the second vane spring 126T, the second vane 127T protrudes from the second vane groove 128T into the second cylinder chamber 130T, and the tip of the second vane 127T extends to the outer peripheral surface of the second annular piston 125T. The second cylinder chamber 130T is partitioned into a second suction chamber 131T and a second compression chamber 133T by the second vane 127T.

  In addition, the first cylinder 121S communicates the radially outer side of the first vane groove 128S with the inside of the compressor casing 10 through the opening R (see FIG. 1), and the compressed refrigerant in the compressor casing 10 is compressed. And a first pressure introduction path 129S is formed in which back pressure is applied to the first vane 127S by the refrigerant pressure. The compressed refrigerant in the compressor housing 10 is also introduced from the first spring hole 124S. In addition, the second cylinder 121T communicates the radially outer side of the second vane groove 128T with the inside of the compressor casing 10 through an opening R (see FIG. 1), and the compressed refrigerant in the compressor casing 10 is compressed. , And a second pressure introduction path 129T is formed in which back pressure is applied to the second vane 127T by the refrigerant pressure. The compressed refrigerant in the compressor housing 10 is also introduced from the second spring hole 124T.

  The first side overhanging portion 122S of 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. ing. The second side overhanging portion 122T of the second cylinder 121T is provided with a second suction hole 135T that allows the second suction chamber 131T to communicate with the outside in order to suck the refrigerant from the outside into the second suction chamber 131T. ing. The cross section of the first suction hole 135S and the second suction hole 135T is circular.

  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 cylinder chamber 130S (see FIG. 2) of the first cylinder 121S and the second cylinder. The second cylinder chamber 130T (see FIG. 2) of 121T is partitioned. 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 cylinder chamber 130S of the first cylinder 121S. An upper end plate 160T is disposed at the upper end of the second cylinder 121T, and closes the second cylinder chamber 130T of the second cylinder 121T. The lower end plate 160S closes the lower end portion of the first cylinder 121S, and the upper end plate 160T closes the upper end portion 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 continuously change, and the compression unit 12 continuously sucks and compresses the refrigerant. Discharge. When the rotary shaft 15 rotates, the second annular piston 125T revolves in the second cylinder 121T in the clockwise direction of FIG. 2 along the second cylinder inner wall 123T, and the second vane 127T reciprocates following this. Exercise. By 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 are continuously changed, and the compression unit 12 continuously sucks and compresses the refrigerant. Discharge.

  As shown in FIG. 1, a lower end plate cover 170S is disposed below the lower end plate 160S, and a lower muffler chamber 180S is formed between the lower end plate 160S and the lower end plate 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. A reed valve type first discharge valve (not shown) that prevents the backflow of the compressed refrigerant is disposed in the hole 190S.

  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 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. In addition, a first discharge valve presser (not shown) for limiting the amount of deflection opening of the first discharge valve is fixed to the first discharge valve by a rivet together with the first discharge valve. The first discharge hole 190S, the first discharge valve, and the first discharge valve presser constitute a first discharge valve portion of the lower end plate 160S.

  As shown in FIG. 1, an upper end plate 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 end plate 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 reed valve type second discharge valve (not shown) for preventing the backflow of the compressed refrigerant. In addition, a second discharge valve presser (not shown) for limiting the amount of deflection opening of the second discharge valve is fixed to the second discharge valve by a rivet together with the second discharge valve. The upper muffler chamber 180T reduces the pressure pulsation of the discharged refrigerant. The second discharge hole 190T, the second discharge valve, and the second discharge valve presser constitute a second discharge valve portion of the upper end plate 160T.

  The lower end plate cover 170S, the lower end plate 160S, the first cylinder 121S, and the intermediate partition plate 140 are inserted into the second cylinder 121T by a plurality of through bolts 175 that are inserted from below and screwed into female screws provided in the second cylinder 121T. To be concluded. The upper end plate cover 170T and the upper end plate 160T are fastened to the second cylinder 121T by through bolts 174 that are inserted from above and screwed into female screws provided in the second cylinder 121T. The lower end plate cover 170S, the lower end plate 160S, the first cylinder 121S, the intermediate partition plate 140, the second cylinder 121T, the upper end plate 160T, and the upper end plate cover 170T integrally fastened by a plurality of through bolts 174, 175, etc. 12 is constituted. The outer peripheral portion of the upper end plate 160 </ b> T is fixed to the body portion 10 </ b> A of the compressor housing 10 by spot welding 163, and the compression portion 12 is fixed to the compressor housing 10. The dimensional relationship between the upper end plate 160T and the trunk portion 10A will be described later.

  The low-pressure refrigerant in the refrigerant circuit is guided to the first compression unit 12S via an accumulator (not shown) and the first suction hole 135S (see FIG. 2) of the first cylinder 121S. Further, the low-pressure refrigerant in the refrigerant circuit is guided to the second compression portion 12T through an accumulator (not shown) and the second suction hole 135T (see FIG. 2) of the second cylinder 121T. That is, the first suction hole 135S and the second suction hole 135T are connected in parallel to the evaporator of the refrigerant circuit.

  Connected to the top of the compressor housing 10 is a discharge pipe 107 that is connected to the refrigerant circuit and discharges high-pressure refrigerant to the condenser side of the refrigerant circuit. That is, the first discharge hole 190S and the second discharge hole 190T are connected to the condenser of the refrigerant circuit.

  Lubricating oil is sealed in the compressor housing 10 up to the height of the second cylinder 121T. The lubricating oil is sucked up from an oil supply pipe 16 attached to the lower end of the rotating shaft 15 by a pump blade (not shown) inserted into the lower portion of the rotating shaft 15, circulates through the compressing portion 12, and slides ( The first annular piston 125S and the second annular piston 125T) are lubricated and a minute gap in the compression portion 12 is sealed.

  Next, a characteristic configuration of the rotary compressor 1 according to the embodiment will be described with reference to FIGS. FIG. 3 is a longitudinal sectional view showing the stator and the rotor before assembly of the rotary compressor of the embodiment. FIG. 4 is a longitudinal sectional view showing a state after assembly of the stator and the rotor of the rotary compressor of the embodiment. FIG. 5 is a longitudinal cross-sectional view showing a state before the compression portion of the rotary compressor and the stator and the body portion of the compressor housing of the embodiment are fitted. FIG. 6 is a longitudinal cross-sectional view showing the compression portion of the rotary compressor and the stator after the fitting of the body portion of the compressor housing of the embodiment. FIG. 7 is a cross-sectional view taken along line AA in FIG. FIG. 8 is a cross-sectional view taken along line BB in FIG.

  As shown in FIG. 3, the outer diameter φDr of the rotor 112 of the motor 11 is 1.4 mm smaller than the inner diameter φDt of the stator 111, and is between the outer peripheral surface of the rotor 112 and the inner peripheral surface of the stator 111. The gap is 0.7 mm. The thickness of the shim 201 of the gap gauge 200 that centers the rotor 112 and the stator 111 is 0.1 mm thinner than the gap 0.7 mm between the outer peripheral surface of the rotor 112 and the inner peripheral surface of the stator 111, and is 0.6 mm. It has become.

  As shown in FIG. 5, the outer diameter φDs of the stator 111 of the motor 11 is formed smaller than the outer diameter φDb of the upper end plate 160T of the compression portion 12 (φDs <φDb). Further, the inner diameter φDm of the body portion 10A of the compressor housing 10 is formed to be 0.1 mm to 0.2 mm larger than the outer diameter φDs of the stator 111 (0.1 mm ≦ φDm−φDs ≦ 0.2 mm). Further, the inner diameter φDm of the body portion 10A is formed in a range of −0.05 mm to +0.05 mm with respect to the outer diameter φDb of the upper end plate 160T (−0.05 mm ≦ φDm−φDb ≦ 0.05 mm). As shown in FIGS. 7 and 8, the body portion 10A is formed by winding a steel plate and welding the end portions by butt welding to form a cylindrical shape. The dimensional accuracy and roundness of the inner diameter φDm are as follows. It is lower than that which has been drawn or machined (a butt weld site 165 is shown in FIGS. 7 and 8).

  Next, a method for fixing the motor 11 and the compression unit 12 connected by the rotary shaft 15 in the body 10A of the compressor housing 10 will be described. As shown in FIGS. 3 and 4, when assembling the motor 11, the stator 111 is placed on the upper end of a cylindrical assembly jig 210 having a circular recess 211 at the bottom. A gap gauge 200 having a plurality of shims 201 attached to the outer periphery is set.

  The compression part 12 having the rotor 112 fixed to the rotating shaft 15 is lowered with the rotor 112 facing downward, and the end of the rotating shaft 15 is brought into contact with the upper convex part 202 of the gap gauge 200. When the compression unit 12 is further lowered, the rotor 112 is guided by the shim 201 of the gap gauge 200 and inserted into the stator 111, and pushes the gap gauge 200 downward. As shown in FIG. 4, when the lower convex portion 203 of the gap gauge 200 is fitted into the concave portion 211 of the assembly jig 210, the rotor 112 is completely inserted into the stator 111 and centered by the shim 201. Are assembled.

  Next, as shown in FIGS. 5 and 6, with the motor 11 and the compression unit 12 placed on the assembly jig 210, the body 10 </ b> A of the compressor housing 10 is moved to the upper end plate 160 </ b> T of the compression unit 12. And fitted to the stator 111 of the motor 11. Since the inner diameter φDm of the trunk portion 10A is −0.05 mm to 0.05 mm with respect to the outer diameter φDb of the upper end plate 160T, fitting between the trunk portion 10A and the upper end plate 160T can be performed by general press-fitting or Compared with shrink fitting, it should be light press-fit or light shrink fitting. Since the inner diameter φDm of the trunk portion 10A is formed to be 0.1 mm to 0.2 mm larger than the outer diameter φDs of the stator 111, the fitting between the trunk portion 10A and the stator 111 is non-contact or does not require a compressive force. Can be done with one side contact. As shown in FIG. 6, the body portion 10 </ b> A is lowered until the lower end comes into contact with the step portion 212 of the assembly jig 210, and the fitting operation is completed. In this state, a gap of 0.05 mm to 0.10 mm is formed between the inner peripheral portion of the body portion 10A and the outer peripheral portion of the stator 111, and the stator 111 and the rotor 112 are centered. It is in.

  Next, a method of fixing the upper end plate 160T of the compression unit 12 and the stator 111 of the motor 11 to the body 10A of the compressor housing 10 will be described with reference to FIGS. The body portion 10A is provided with three holes 164 spaced from each other by 120 ° in the circumferential direction at the position where the upper end plate 160T is fitted and at the compression portion 12 side position and the anti-compression portion 12 side position of the stator 111. (The number of holes 164 may be three or more). A welding wire is inserted into the hole 164, and the barrel portion 10A and the upper end plate 160T are welded first by spot welding. Weld. Either the compression part 12 side position welding or the anti-compression part 12 side position welding may be performed first. FIG. 6 shows a spot weld site 163 (the hole 164 is completely filled by spot welding to withstand the pressure of the compressed refrigerant). Thereafter, the gap gauge 200 is removed.

  The body 11A and the upper end plate 160T are first welded, and the motor 11 centered by the compression unit 12 and the gap gauge 200 is positioned and fixed in the body 10A. Next, in the centered state, the body 11 Since the stator 111 is directly welded to the body portion 10A without receiving the radial compressive force from the portion 10A, the stator 111 is not subjected to compressive strain, the magnetization characteristics of the stator are deteriorated, and the iron loss is increased. In addition, the efficiency of the motor 11 is high, and the cost increase can be suppressed.

  Further, since the compression portion 12 side position and the anti-compression portion 12 side position of the stator 111 are fixed by spot welding to the body portion 10A, even if the rotary compressor 1 receives an impact such as dropping, the laminated steel plates should be caulked. The formed stator 111 is not caulked between the welding position on the compression part 12 side and the welding position on the anti-compression part 12 side and the stator 111 is not damaged. In addition, as shown in FIG. 8, the circumferential position of the spot welded part 163 of the upper end plate 160T, the circumferential position of the spot welded part 163 on the compression part 12 side of the stator 111, and the anti-compression part 12 side of the stator 111 If the circumferential position of the spot welded part 163 is shifted in the circumferential direction, the welded parts do not line up in a straight line in the axial direction, so the distance between welded parts with relatively low strength increases. The strength of the trunk portion 10A does not become weak. Further, since the maximum gap between the inner peripheral portion of the body portion 10A and the outer peripheral portion of the stator 111 is 0.10 mm, spatter due to welding does not enter the compressor housing 10.

  After the compression portion 12 and the motor 11 are welded and fixed to the barrel portion 10A, as shown in FIG. 1, the assembly of the rotary compressor 1 is completed by welding the bottom portion 10C and the top portion 10B to the barrel portion 10A. The present invention can be applied to a single cylinder type rotary compressor and a two-stage compression type rotary compressor.

  Although the embodiments have been described above, the embodiments are not limited to the above-described contents. 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 embodiments.

DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 10A Body part 10B Top part 10C Bottom part 11 Motor 12 Compression part 15 Rotating shaft 16 Oil supply pipe 107 Discharge pipe (discharge part)
111 Stator 112 Rotor 12S 1st compression part (compression part)
12T 2nd compression part (compression part)
121S 1st cylinder (cylinder)
121T 2nd cylinder (cylinder)
122S first lateral overhang (side overhang)
122T Second lateral overhang (side overhang)
123S 1st cylinder inner wall (cylinder inner wall)
123T 2nd cylinder inner wall (cylinder inner wall)
124S 1st spring hole (spring hole)
124T Second spring hole (spring hole)
125S first annular piston (annular piston)
125T second annular piston (annular piston)
126S 1st vane spring (vane spring)
126T 2nd vane spring (vane spring)
127S 1st vane (vane)
127T 2nd vane (vane)
128S 1st vane groove (vane groove)
128T 2nd vane groove (vane groove)
129S First pressure introduction path (pressure introduction path)
129T Second pressure introduction path (pressure introduction path)
130S 1st cylinder chamber (cylinder chamber)
130T Second cylinder chamber (cylinder 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 151 Secondary shaft portion 152S First eccentric portion (eccentric portion)
152T second eccentric part (eccentric part)
153 Main shaft portion 160S Lower end plate (end plate)
160T Top plate (end plate)
161S Sub bearing part (bearing part)
161T Main bearing (bearing)
163 Spot welding part 164 hole 165 Butt welding part 170S Lower end plate cover 170T Upper end plate cover 174 Through bolt 175 Through bolt 180S Lower muffler chamber 180T Upper muffler chamber 190S First discharge hole (discharge valve part)
190T 2nd discharge hole (discharge valve part)
200 Gap gauge 201 Shim 202 Upper convex part 203 Lower convex part 210 Assembly jig 211 Concave part 212 Step part

Claims (3)

A hermetic vertical compressor housing in which a refrigerant discharge part is provided at the upper part, a refrigerant suction part is provided in the lower part and lubricating oil is stored;
An annular cylinder and an upper end plate and a lower end plate that close the end of the cylinder are disposed in the compressor casing, and the refrigerant sucked from the suction portion is compressed by the cylinder and discharged from the discharge portion. A compression unit to perform,
A motor disposed in the compressor housing, having a cylindrical stator and a rotor fixed to a rotating shaft and rotating in the stator, and driving the compression unit via the rotating shaft;
A rotary compressor comprising:
When the inner diameter of the body of the compressor housing is φDm, the outer diameter of the upper end plate of the compressor is φDb, and the outer diameter of the stator of the motor is φDs, −0.05 mm ≦ φDm−φDb ≦ 0.05 mm And φDm, φDb, and φDs are set so as to satisfy the two expressions of 0.1 mm ≦ φDm−φDs ≦ 0.2 mm, and the outer periphery of the upper end plate and the outer periphery of the stator In a plurality of locations spaced apart in the direction, a plurality of welded portions are provided by spot welding the outer peripheral portion of the upper end plate and the outer peripheral portion of the stator to the body portion of the compressor housing,
As the plurality of welded portions, the compressor portion side of the outer peripheral portion of the stator is welded to the barrel portion and arranged at intervals in the circumferential direction of the stator. a plurality of first weld the plurality of second weld the opposite side are arranged at intervals in the circumferential direction of the weld has been said stator to said barrel and said compression portion of the outer peripheral portion of the stator And a plurality of third welded portions, each having an outer peripheral portion of the upper end plate welded to the body portion and arranged at intervals in the circumferential direction of the stator,
Wherein the first weld the second weld third weld portion is arranged offset from one another in the circumferential direction of the position of the stator, the rotary compressor, characterized in that. Spot welding of the body portion of the compressor housing and the stator of the motor, a rotary as claimed in claim 1, characterized in that it is performed after the spot welding of the upper end plate and the body portion of the compression unit Compressor. The spot welding of the stator and the said body portion of the compressor housing of the motor, the rotary compressor according to claim 2, characterized in that the rotor of the with the stator motor is performed in a state of being centered .

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