JP5998522B2 - Rotary compressor - Google Patents

Description

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

  Conventionally, a sealed vertical compressor housing in which oil is stored in the lower portion, a motor that is arranged on the upper portion of the compressor housing and drives a rotating shaft having a first eccentric portion and a second eccentric portion, An annular first cylinder disposed at a lower portion of the compressor housing and radially provided with a first suction hole and a first vane groove on a side portion thereof is fitted into a first eccentric portion of the rotating shaft, and the first A first annular piston that revolves in the first cylinder along the inner wall of one cylinder, and a first vane that protrudes from the first vane groove into the first cylinder and contacts the first annular piston. A first compression section that discharges the compressed refrigerant gas into the compressor housing; and a second suction hole and a second vane groove that are disposed on the first compression section and are radially formed on the side portion. The annular second cylinder provided and the second eccentric portion of the rotary shaft are fitted to the A second annular piston that revolves in the second cylinder along the inner wall of the two cylinders, and a second vane that protrudes from the second vane groove into the second cylinder and contacts the second annular piston. A second compression section that discharges compressed refrigerant gas into the compressor casing, and the lubricating oil that is disposed in the oil supply vertical hole of the rotary shaft and is stored in the lower portion of the compressor casing. A rotary compressor is disclosed that includes an oil supply mechanism that supplies oil to a sliding portion of the first and second compression parts through an oil supply horizontal hole that communicates with a vertical hole (see, for example, Patent Document 1).

  The oil supply lateral hole is provided in the upper part of the auxiliary shaft part of the rotating shaft, the first and second eccentric parts, and the lower part of the main shaft part. An annular groove is formed in the upper part of the auxiliary shaft part and the lower part of the main shaft part in order to make it easy to supply the lubricating oil from the oil supply lateral hole.

JP 2009-127507 A (FIGS. 1, 4, 5, paragraphs 0032 to 0034)

  However, since the annular groove is formed in the upper part of the sub-shaft part and the lower part of the main shaft part, the shaft diameter of the rotating shaft is reduced at the annular groove part, and from the corner of the annular groove of the sub-shaft part. The span to the corner of the annular groove of the main shaft portion is large, the rotating shaft is easily bent by the load applied to the first and second eccentric portions, and the corner portion of the annular groove is the auxiliary bearing portion of the lower end plate and the main bearing portion of the upper end plate There is a problem that galling is likely to occur on the sliding surface.

  The present invention has been made in view of the above, and makes it difficult for the rotating shaft to be bent, and makes it difficult for the auxiliary shaft portion and the main shaft portion of the rotating shaft to bite the auxiliary bearing portion of the lower end plate and the main bearing portion of the upper end plate. The object is to obtain a rotary compressor.

In order to solve the above-described problems and achieve the object, the present invention provides a sealed vertical installation in which a refrigerant discharge part is provided in the upper part, a refrigerant suction part is provided in the lower part, and lubricating oil is stored in the lower part. A compressor housing, an annular first and second cylinders disposed at a lower portion of the compressor housing, an upper end plate having a main bearing portion and a discharge valve portion and closing an upper end portion of the second cylinder; A lower end plate having a sub-bearing portion and a discharge valve portion for closing the lower end portion of the first cylinder, an intermediate partition plate for closing the space between the first and second cylinders, and the main bearing portion and the sub-bearing portion. The first and second cylinders are fitted along the inner walls of the first and second cylinders of the first and second cylinders, which are fitted to the first and second eccentric parts of the rotating shaft on which the main shaft part and the sub shaft part are supported. First and second annular pistons that revolve inside to form first and second working chambers between the first and second cylinder inner walls. When the first, the first of the second cylinder, wherein the second vane groove first, said projecting second working chamber first, abuts the the second annular piston first, the second working chamber First and second suction chambers, and first and second vanes that are divided into first and second compression chambers. The refrigerant is sucked through the suction portion, and the refrigerant is discharged from the discharge portion through the compressor housing. A rotary compressor comprising: first and second compressors that discharge the gas; and a motor that is disposed on an upper portion of the compressor housing and drives the first and second compressors via the rotation shaft. The main shaft portion of the rotating shaft is axially supported on the second cylinder side end portion of the main bearing portion of the upper end plate, and the sub shaft portion of the rotating shaft is supported on the first cylinder side end portion of the sub bearing portion of the lower end plate. Is provided with an oil supply vertical hole penetrating the rotary shaft in the axial direction, and a lower portion of the oil supply vertical hole. A vane pump is disposed, and first and second eccentric part oil grooves are provided in the longitudinal direction on the outer peripheral surfaces of the first and second eccentric parts, and in the first and second eccentric part oil grooves, the oil supply longitudinal hole and the first, first to the second eccentric oil groove communicate each communication, provided a second eccentric portion refueling transverse bore, rotation between the first eccentric portion and the second eccentric portion The intermediate shaft portion of the shaft is provided with an intermediate oil supply lateral hole that communicates the oil supply vertical hole and the first and second eccentric portion oil grooves via the outer peripheral surface of the intermediate shaft portion, and the auxiliary bearing portion and the main shaft The auxiliary shaft oil groove and the main shaft oil groove communicated with the first and second eccentric oil grooves respectively on the inner peripheral portion of the bearing portion, or the outer peripheral portions of the corresponding auxiliary shaft portion and main shaft portion. The second eccentric portion oil supply horizontal hole is located on the upper side of the compressor housing relative to the first eccentric portion oil supply horizontal hole, and the diameter of the second eccentric portion oil supply horizontal hole is the first. 1 It is larger than the diameter of the eccentric oil supply horizontal hole, Lubricating oil stored in the lower part of the compressor casing is supplied to the oil supply vertical hole, the first and second eccentric part oil supply horizontal holes, the intermediate oil supply horizontal hole, and the intermediate shaft part by the blade pump disposed in the hole. And supplying the first and second compression portions, the main shaft portion, and the sub shaft portion through the outer peripheral surface, the first and second eccentric portion oil grooves, the sub shaft oil groove, and the main shaft oil groove. To do.

  According to the present invention, there is no portion with a small shaft diameter in the auxiliary shaft portion and the main shaft portion of the rotary shaft, and the span between the auxiliary shaft portion and the main shaft portion that supports the load applied to the first and second eccentric portions is supported. Therefore, the rotating shaft is not easily bent, and galling is unlikely to occur between the auxiliary shaft portion and the main shaft portion and the auxiliary bearing portion of the lower end plate and the main bearing portion of the upper end plate.

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 seen from below the first and second compression portions. FIG. 3 is an enlarged longitudinal sectional view showing a compression portion of the embodiment of the rotary compressor according to the present invention.

  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 seen from below the first and second compression sections, and FIG. It is an expanded vertical sectional view which shows the compression part of the Example of the rotary compressor which concerns on invention.

  As shown in FIG. 1, the rotary compressor 1 according to the embodiment is disposed 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 rotary shaft 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.

  The compression unit 12 includes a first compression unit 12S and a second compression unit 12T that is arranged in parallel with the first compression unit 12S and stacked on the upper side of the first compression unit 12S. As shown in FIG. 2, the first and second compression parts 12S and 12T are provided with first and second suction holes 135S and 135T, and first and second vane grooves 128S and 128T radially on the side parts. Annular first and second cylinders 121S and 121T are provided.

  As shown in FIG. 2, circular first and second cylinder inner walls 123 </ b> S and 123 </ b> T are formed in the first and second cylinders 121 </ b> S and 121 </ b> T concentrically with the rotating shaft 15 of the motor 11. In the first and second cylinder inner walls 123S and 123T, 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, The first and second working chambers 130S and 130T 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 slidably fitted into the second vane grooves 128S and 128T, respectively.

  As shown in FIG. 2, the first and second vane grooves 128S and 128T are communicated with the first and second vane grooves 128S and 128T from the outer periphery of the first and second cylinders 121S and 121T at the back of the first and second vane grooves 128S and 128T. First and second spring holes 124S and 124T are formed. Vane springs (not shown) that press the back surfaces of the first and second vanes 127S and 127T are inserted into the first and second spring holes 124S and 124T. When the rotary compressor 1 is started, the first and second vanes 127S and 127T are moved from the first and second vane grooves 128S and 128T to the first and second working chambers 130S and 130T by the repulsive force of the vane springs. The first and second working chambers 130S and 130T are moved to the first and second working chambers 130S and 130T by the first and second vanes 127S and 127T, respectively. The second suction chambers 131S and 131T and the first and second compression chambers 133S and 133T are partitioned.

  In addition, the first and second cylinders 121S and 121T communicate with the inner portions of the first and second vane grooves 128S and 128T and the interior of the compressor housing 10 through the opening R shown in FIG. First and second pressure introducing passages 129S and 129T are formed in which the compressed refrigerant gas in the housing 10 is introduced and back pressure is applied to the first and second vanes 127S and 127T by the pressure of the refrigerant gas. .

  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 disposed 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 chamber 130T is partitioned and closed. 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.

  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 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 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. A first discharge valve 200S that prevents the backflow of the compressed refrigerant gas 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 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. The first discharge hole 190S, the first discharge valve 200S, and the first discharge valve presser 201S constitute a 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. 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 that prevents 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 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 through bolts 175 or 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. .

  The first and second through holes 101 and 102 are passed through the outer peripheral wall of the cylindrical compressor housing 10 in order from the lower part in the axial direction so as to pass the first and second suction pipes 104 and 105. Is provided. In addition, an accumulator 25 formed of an independent cylindrical sealed container is held by an accumulator holder 252 and an accumulator band 253 on the outer side of the compressor housing 10.

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

  The first and second low-pressure connecting pipes 31S and 31T that guide the low-pressure refrigerant of the refrigeration cycle to the first and second compression parts 12S and 12T through the accumulator 25 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 with the refrigeration cycle in parallel.

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

  Next, a characteristic configuration of the rotary compressor of the embodiment will be described with reference to FIG. In the conventional rotary compressor, an annular groove is provided in the upper part of the sub-shaft part 151 and the lower part of the main shaft part 153 of the rotary shaft 15, and an oil supply horizontal hole communicating with the oil supply vertical hole is provided in the annular groove. In the rotary compressor 1 of the embodiment, the auxiliary shaft portion 151 and the main shaft portion 153 are not provided with an annular groove and an oil supply lateral hole in the annular groove.

  Therefore, the auxiliary shaft portion 151 is supported by the end of the auxiliary bearing portion 161S of the lower end plate 160S on the first cylinder 121S side, and the main shaft portion 153 is the end of the upper end plate 160T of the main bearing portion 161T on the second cylinder 121T side. (Conventionally, the annular groove is located at the end of the secondary bearing portion 161S on the first cylinder 121S side and the end of the main bearing portion 161T on the second cylinder 121T side. The first cylinder 121S side end portion of 161S and the second cylinder 121T side end portion of the main bearing portion 161T did not contribute to the shaft support of the rotating shaft 15.

  In the rotary compressor 1 of the embodiment, since the annular groove is not formed in the upper part of the auxiliary shaft part 151 and the lower part of the main shaft part 153, the rotary shaft 15 does not have a portion with a small shaft diameter. Further, the auxiliary shaft portion 151 is axially supported by the first cylinder 121S side end portion of the auxiliary bearing portion 161S of the lower end plate 160S, and the main shaft portion 153 is the second cylinder 121T side end portion of the main bearing portion 161T of the upper end plate 160T. Therefore, even if a load is applied to the first and second eccentric portions 152S and 152T, the rotating shaft 15 is not easily bent, and the auxiliary bearing portion 151 and the main shaft of the rotating shaft 15 are not bent. It is difficult for galling to occur between the portion 153 and the auxiliary bearing portion 161S of the lower end plate 160S and the main bearing portion 161T of the upper end plate 160T.

  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 155 penetrating the center portion. The oil supply vertical hole 155 has a large inner diameter in the range from the sub-shaft portion 151 to the second eccentric portion 152T, and a blade pump 155B described later is housed therein, and the inner diameter is narrow in the range above the main shaft portion 153. A first eccentric portion oil groove 157S is provided in the longitudinal direction on the outer peripheral surface of the first eccentric portion 152S, and an oil supply vertical hole 155 and a first eccentric portion oil are provided in the first eccentric portion oil groove 157S. A first eccentric portion oil supply lateral hole 156S that communicates with the groove 157S is provided. Further, a second eccentric portion oil groove 157T is provided in the longitudinal direction on the outer peripheral surface of the second eccentric portion 152T, and the oil supply vertical hole 155 and the second eccentric portion are provided in the second eccentric portion oil groove 157T. A second eccentric portion oil supply lateral hole 156T that communicates with the partial oil groove 157T is provided.

  In addition, the inner peripheral portions of the lower bearing portion 161S and the upper bearing portion 161T, or the corresponding outer peripheral portions of the auxiliary shaft portion 151 and the main shaft portion 153, are provided with a first eccentric portion oil groove 157S via a first eccentric portion oil groove 157S. A sub-shaft oil groove 158S (in FIG. 3, disposed on the back side of the sub-shaft portion 151 is inclined with respect to the axis) and a second eccentric oil groove 157T communicating with the core portion oil supply lateral hole 156S. A main shaft oil groove 158T communicating with the second eccentric portion oil supply horizontal hole 156T via the shaft (in FIG. 3, disposed on the back side of the main shaft portion 153 is inclined with respect to the axis). The main shaft portion 153 is located above the second eccentric portion oil supply horizontal hole 156T and is less likely to be supplied with lubricating oil than the auxiliary shaft portion 151. Therefore, the diameter of the second eccentric portion oil supply horizontal hole 156T is reduced to the first eccentric portion oil supply horizontal hole 156T. It is preferable to make the diameter larger than the diameter of the core oil supply lateral hole 156S so that the lubricating oil can be easily supplied to the main shaft part 153.

  Further, in order to increase the amount of oil supplied to the first and second compression portions 12S and 12T, the countershaft portion 151, and the main shaft portion 153, an intermediate portion between the first eccentric portion 152S and the second eccentric portion 152T of the rotating shaft 15 is provided. An intermediate oil supply lateral hole 159 is provided in the shaft portion 154. The intermediate oil supply horizontal hole 159 connects the oil supply vertical hole 155 and the first and second eccentric part oil grooves 157 </ b> S and 157 </ b> T via the outer peripheral surface of the intermediate shaft part 154. A plurality of intermediate oil supply lateral holes 159 may be provided in the intermediate shaft portion 154 while being shifted in the axial direction or the circumferential direction. Since the second compression portion 12T and the main shaft portion 153 are located above the intermediate oil supply horizontal hole 159 and are difficult to be supplied with lubricating oil, the intermediate oil supply horizontal hole 159 may be provided at the upper portion of the intermediate shaft portion 154.

  A blade pump 155B is disposed in the oil supply vertical hole 155, and centrifugal force is applied to the lubricating oil by the blade pump 155B that rotates along with the rotation of the rotary shaft 15 to improve the oil supply performance, especially at a position higher than the lubricating oil surface. The main shaft portion 153 positioned is reliably lubricated.

  The oil supply vertical hole 155, the blade pump 155B, the first and second eccentric part oil supply horizontal holes 156S and 156T, the auxiliary shaft oil groove 158S, the main shaft oil groove 158T, the intermediate oil supply horizontal hole 159, and the intermediate shaft part described above. The lubricating oil stored in the lower portion of the compressor housing 10 is pumped up from the oil supply pipe 16 by the oil supply mechanism 155A including the outer peripheral surface, the first and second eccentric portion oil grooves 157S, 157T, and the like. The portion 151, the first and second compression portions 12S and 12T, and the main shaft portion 153 are lubricated.

DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 16 Oil supply pipe 25 Accumulator 31S 1st low pressure connection pipe 31T 2nd low pressure connection pipe 101 1st through-hole 102 2nd through-hole 104 1st suction pipe 105 Second suction pipe 107 Discharge pipe (discharge part)
111 Stator 112 Rotor 12S First Compression Unit 12T Second Compression Unit 121S First Cylinder (Cylinder)
121T 2nd cylinder (cylinder)
123S 1st cylinder inner wall (cylinder inner wall)
123T 2nd cylinder inner wall (cylinder inner wall)
124S first spring hole 124T second spring hole 125S first annular piston (annular piston)
125T second annular piston (annular piston)
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 129T second pressure introduction path 130S first 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 151 Secondary shaft portion 152S First eccentric portion (eccentric portion)
152T second eccentric part (eccentric part)
153 Main shaft portion 154 Intermediate shaft portion 155 Oil supply vertical hole 155A Oil supply mechanism 155B Blade pump 156S First eccentric portion oil supply horizontal hole 156T Second eccentric portion oil supply horizontal hole 157S First eccentric portion oil groove 157T Second eccentric portion oil Groove 158S Secondary shaft oil groove 158T Main shaft oil groove 159 Intermediate oil supply lateral hole 160S Lower end plate (end plate)
160T Top plate (end plate)
161S Sub bearing portion 161T Main bearing portion 170S Lower muffler cover 170T Upper muffler cover 175 Through bolt 180S Lower muffler chamber 180T Upper muffler chamber 190S First discharge hole (discharge hole)
190T Second discharge hole (discharge hole)
200S 1st discharge valve 200T 2nd discharge valve 201S 1st discharge valve holder 201T 2nd discharge valve holder 252 Accum holder 253 Accum band 255 System connection pipe R Opening part of 1st, 2nd pressure introduction path

Claims (2)

A hermetically sealed compressor housing in which a refrigerant discharge part is provided in the upper part, a refrigerant suction part is provided in the lower part, and lubricating oil is stored in the lower part;
An annular first and second cylinder, an upper end plate having a main bearing portion and a discharge valve portion and closing an upper end portion of the second cylinder, a sub-bearing portion and discharge A lower end plate that has a valve portion and closes a lower end portion of the first cylinder, an intermediate partition plate that closes between the first and second cylinders, a main shaft portion and a sub shaft portion in the main bearing portion and the sub bearing portion Is fitted into the first and second eccentric portions of the rotating shaft supported by the first and second cylinders and revolves along the inner walls of the first and second cylinders to revolve the first and second cylinders. 1, first and second annular pistons forming first and second working chambers between the inner wall of the second cylinder and the first and second vane grooves of the first and second cylinders. said protruding second working chamber first, abuts the the second annular piston first, the second working chamber first, second suction chamber and the first, First and second vanes that are divided into two compression chambers, sucking refrigerant through the suction section, and discharging refrigerant from the discharge section through the compressor housing; ,
A motor that is disposed at an upper portion of the compressor housing and drives the first and second compression units via the rotation shaft;
A rotary compressor comprising:
The main shaft portion of the rotating shaft is axially supported on the second cylinder side end portion of the main bearing portion of the upper end plate, and the sub shaft portion of the rotating shaft is pivoted on the first cylinder side end portion of the sub bearing portion of the lower end plate. Support,
The rotary shaft is provided with an oil supply vertical hole penetrating the rotary shaft in the axial direction, a blade pump is disposed at a lower portion of the oil supply vertical hole, and the first and second eccentric portions are vertically arranged on the outer peripheral surfaces. 1, a first eccentric portion oil groove is provided, and in the first and second eccentric portion oil grooves, the first and second eccentric portion oil grooves communicate with the first and second eccentric portion oil grooves, respectively. the second eccentric portion refueling transverse bore provided, said first eccentric part and the oil supply longitudinal hole and the first and second eccentric oil groove in the intermediate shaft portion of the rotary shaft between the second eccentric portion Is provided in the inner peripheral portion of the auxiliary bearing portion and the main bearing portion, or the corresponding auxiliary shaft portion and the outer peripheral portion of the main shaft portion. Are provided with a countershaft oil groove and a main shaft oil groove communicating with the first and second eccentric oil grooves, respectively.
The second eccentric portion oil supply horizontal hole is located on the upper side of the compressor housing relative to the first eccentric portion oil supply horizontal hole, and the diameter of the second eccentric portion oil supply horizontal hole is the first eccentricity. Is larger than the diameter of
Lubricating oil stored in the lower part of the compressor casing is supplied to the oil supply vertical hole, the first and second eccentric part oil supply horizontal holes, the intermediate oil supply horizontal holes by a blade pump arranged in the oil supply vertical hole, Supplying the first and second compression parts, the main shaft part and the sub-shaft part through the outer peripheral surface of the intermediate shaft part, the first and second eccentric oil grooves, the sub-shaft oil groove and the main shaft oil groove. Rotary compressor characterized by this. The rotary compressor according to claim 1, wherein the intermediate oil supply lateral hole is provided in an upper portion of the intermediate shaft portion .

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