JP2014145318A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- JP2014145318A JP2014145318A JP2013014873A JP2013014873A JP2014145318A JP 2014145318 A JP2014145318 A JP 2014145318A JP 2013014873 A JP2013014873 A JP 2013014873A JP 2013014873 A JP2013014873 A JP 2013014873A JP 2014145318 A JP2014145318 A JP 2014145318A
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- discharge valve
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- muffler
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- 239000003507 refrigerant Substances 0.000 claims abstract description 86
- 238000007906 compression Methods 0.000 claims abstract description 48
- 230000002093 peripheral Effects 0.000 claims description 20
- 238000005192 partition Methods 0.000 claims description 11
- 238000005057 refrigeration Methods 0.000 claims description 8
- 238000000638 solvent extraction Methods 0.000 claims description 3
- 238000010438 heat treatment Methods 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 3
- 235000014676 Phragmites communis Nutrition 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 230000001629 suppression Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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Abstract
To obtain a rotary compressor that suppresses heating of refrigerant sucked by refrigerant gas passing through a refrigerant passage and refrigerant gas in the middle of compression and improves compressor efficiency.
In a rotary compressor, a refrigerant passage 336 provided in first and second cylinders 121S and 121T is disposed in a range of a phase angle of 270 ° or more and 360 ° or less from a position of vane grooves 128S and 128T in a revolving direction of an annular piston. Inside, it is arranged on the lower and upper end plates and radially outward from the discharge valve grooves 163S and 163T that accommodate the discharge valve portion.
[Selection] Figure 3
Description
The present invention relates to a rotary compressor used for an air conditioner, for example.
FIG. 7 is a longitudinal sectional view showing a refrigerant passage of a compression portion of a conventional rotary compressor, and FIG. 8 is a plan view showing a refrigerant passage of conventional first and second cylinders. As shown in FIGS. 7 and 8, in the conventional rotary compressor, the high-temperature refrigerant gas compressed by the first compressor 12S is discharged into the lower muffler chamber 180S, and the lower end plate 160S and the first cylinder 121S. Then, the refrigerant is discharged into the upper muffler chamber 180T through the refrigerant passage 136 provided so as to pass through the intermediate partition plate 140, the second cylinder 121T, and the upper end plate 160T, and is compressed by the second compression unit 12T to be compressed in the upper muffler chamber 180T. The refrigerant gas discharged into the interior merges and is discharged into the compressor housing 10.
The refrigerant passage 136 has first and second discharge valve grooves 163S and 163T, first and second vane grooves 128S and 128T, and first and second suction holes 135S and 135T provided in the lower and upper end plates 160S and 160T. The first and second compression portions 12S and 12T cannot be arranged at the arrangement positions such as screw holes (or bolt through holes) 121a for fixing. Further, since the refrigerant passage 136 must be opened in the lower and upper muffler chambers 180S and 180T, it is necessary to provide the refrigerant passage 136 inside the lower and upper muffler covers 170S and 170T. Therefore, the arrangement | positioning position of the refrigerant path 136 is limited, and as shown in FIG. 8, it arrange | positions in the place where the space is vacant on the opposite side of the 1st, 2nd vane grooves 128S and 128T.
Conventionally, for example, Patent Documents 1 and 2 are disclosed as rotary compressors having the same refrigerant passage as described above.
The temperatures of the first and second cylinder inner peripheral surfaces 123S and 123T of the first and second cylinders 121S and 121T are in the vicinity of the first and second suction holes 135S and 135T where the low-temperature refrigerant gas before the start of compression is sucked. Although the temperature is relatively low, the refrigerant temperature rises as the compression proceeds, and becomes high in the vicinity of the first and second discharge holes 190S and 190T after the compression. Opposite sides of the first and second vane grooves 128S and 128T are intermediate positions of the first and second suction holes 135S and 135T and the first and second discharge holes 190S and 190T. The temperatures of the two cylinder inner peripheral surfaces 123S and 123T are intermediate between temperatures near the first and second suction holes 135S and 135T and temperatures near the first and second discharge holes 190S and 190T.
When the high-temperature refrigerant gas discharged from the first discharge hole 190S of the lower end plate 160S enters the lower muffler chamber 180S, it is radiated to the oil sump at the outer periphery of the lower muffler cover 170S through the wall surface of the lower muffler cover 170S, and the temperature slightly decreases. However, it flows in the refrigerant passage 136 in a high temperature state. Therefore, the wall surface temperature of the refrigerant passage 136 is higher than the temperatures of the first and second cylinder inner peripheral surfaces 123S and 123T on the opposite side of the first and second vane grooves 128S and 128T of the first and second cylinders 121S and 121T. Get higher.
Therefore, when the refrigerant passage 136 is disposed on the opposite side of the first and second vane grooves 128S and 128T of the first and second cylinders 121S and 121T, the refrigerant gas flowing through the refrigerant passage is changed into the first and second The temperature of the first and second cylinder inner peripheral surfaces 123S and 123T on the opposite side of the two vane grooves 128S and 128T is raised, the suction refrigerant and the refrigerant gas being compressed are heated, the volume efficiency is lowered, and the compression power is increased. There is a problem of reducing the compressor efficiency.
The present invention has been made in view of the above, and an object of the present invention is to obtain a rotary compressor that suppresses heating of refrigerant sucked by refrigerant gas flowing in a refrigerant passage and refrigerant gas during compression and improves compressor efficiency. And
In order to solve the above-described problems and achieve the object, the present invention includes a vertically-placed cylindrical compressor housing that is provided with a refrigerant discharge portion at the top and a refrigerant suction portion at the bottom and is sealed, A lower upper end plate disposed at a lower portion of the compressor housing, having annular first and second cylinders, a bearing portion and a discharge valve portion, and closing the end portions of the first and second cylinders; An intermediate partition plate arranged between the first and second cylinders and partitioning between the two and the eccentric part of the rotating shaft supported by the bearing part is fitted along the inner peripheral surface of the first and second cylinders. The first and second annular pistons that revolve inside the cylinder and form a working chamber between the inner circumferential surface of the cylinder, and the first and second cylinders protrude from the vane grooves into the working chamber and the first 1. First and second abutting against the second annular piston and dividing the working chamber into a suction chamber and a compression chamber An upper muffler cover having a muffler discharge hole communicating with the interior of the compressor housing and covering a discharge valve portion of the upper end plate to form an upper muffler chamber between the upper end plate and the lower end A lower muffler cover that covers the discharge valve portion of the plate and forms a lower muffler chamber with the lower end plate; and an upper and lower muffler chamber that penetrates the lower, upper end plate, the first and second cylinders, and the intermediate partition plate A refrigerant passage that communicates with each other, a compressor that sucks refrigerant from the low-pressure side of the refrigeration cycle through the suction portion, and discharges the refrigerant from the discharge portion through the compressor housing, and a compressor housing A rotary compressor having a motor installed at an upper portion and driving the compression unit via the rotary shaft, wherein the refrigerant passage provided in the first and second cylinders is moved from the vane groove position to the revolving direction of the annular piston. The phase Placed in degrees 270 ° or 360 ° in the following range.
According to the present invention, there is an effect that it is possible to improve the efficiency of the compressor by suppressing the heating of the refrigerant sucked by the refrigerant gas passing through the refrigerant passage and the refrigerant gas being compressed.
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, and FIG. 2 is a plan view showing first and second compression portions of the embodiment 1. FIG.
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 arranged on the first and second side projecting parts 122S and 122T in a radial manner with the first and second suction holes 135S and 135T, , Annular first and second cylinders 121S and 121T provided with second vane grooves 128S and 128T are provided.
As shown in FIG. 2, circular first and second cylinder inner peripheral surfaces 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 peripheral surfaces 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 peripheral surfaces 123S, Between the 123T and the first and second annular pistons 125S and 125T, there are formed first and second working chambers 130S and 130T for sucking, compressing and discharging the refrigerant gas.
The first and second cylinders 121S and 121T are formed with first and second vane grooves 128S and 128T extending from the first and second cylinder inner circumferential surfaces 123S and 123T in the radial direction over the entire cylinder height. In the first and second vane grooves 128S and 128T, flat plate-like first and second vanes 127S and 127T are slidably fitted.
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 first working chamber 130S of the first cylinder 121S and the second of the second cylinder 121T. The working 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 move in the first and second cylinders 121S and 121T along the first and second cylinder inner peripheral surfaces 123S and 123T in the counterclockwise direction of FIG. Revolving around, the first and second vanes 127S and 127T reciprocate following this. 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. 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. Is a part of the communication path that communicates with the upper muffler chamber 180T through the refrigerant path 336 (see FIG. 2). 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 valve 200S and the first discharge valve presser 201S constitute a first discharge valve portion 202S of the lower end plate 160S. The first discharge valve portion 202S is accommodated in a first discharge valve groove 163S formed in the lower end plate 160S. The first discharge hole 190S is provided at the bottom of the first discharge valve groove 163S. Details of the refrigerant passage 336 will be described later.
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 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 valve 200T and the second discharge valve presser 201T constitute a second discharge valve portion 202T of the upper end plate 160T. The second discharge valve portion 202T is accommodated in a second discharge valve groove 163T formed in the upper end plate 160T. The second discharge hole 190T is provided at the bottom of the second discharge valve groove 163T. A gap is provided between the main bearing portion 161T of the upper end plate 160T and the upper end portion of the upper muffler cover 170T, and this gap serves as a muffler discharge hole 171.
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. .
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 evaporator of 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 other ends of the first and second suction pipes 104 and 105 are connected to the first and second low-pressure communication pipes 31S and 31T.
The first and second low-pressure connecting pipes 31S and 31T 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 are connected in parallel to the evaporator of the refrigeration cycle.
Connected to the top of the compressor housing 10 is a discharge pipe 107 that is connected to the refrigeration cycle and discharges high-pressure refrigerant gas to the condenser side of the refrigeration cycle. That is, the first and second discharge holes 190S and 190T are connected to the condenser of the refrigeration cycle.
Lubricating oil is sealed in the compressor housing 10 up to the height of the second cylinder 121T. Further, the lubricating oil is sucked up from the oil supply pipe 16 attached to the lower end portion of the rotating shaft 15 by a blade pump (not shown) inserted in the lower portion of the rotating shaft 15, circulates through the compressing portion 12, and slides. The moving parts 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 first embodiment will be described with reference to FIG. FIG. 3 is a plan view illustrating the refrigerant passages of the first and second cylinders of the first embodiment.
As shown in FIG. 3, the refrigerant passage 336 of the first embodiment is provided in the first and second cylinders 121S and 121T, the intermediate partition plate 140, and the upper and lower end plates 160S and 160T, and the first and second vane grooves 128S. , A phase angle of 270 ° to 360 ° in the revolving direction of the first and second annular pistons 125S and 125T (the counterclockwise direction of the first and second annular pistons 125S and 125T shown in FIG. 2) from the 128T position. It is arranged inside (that is, within a range of 90 ° in the clockwise direction from the position of the first and second vane grooves 128S and 128T).
The refrigerant passage 336 is radially outward of the first and second discharge valve grooves 163S and 163T that house the first and second discharge valve portions 202S and 202T (see FIG. 1), and the first and second The two muffler chambers 180S and 180T are disposed within the range. Note that the first and second compression portions 12S and 12T fixing screw holes (or bolt through holes) 321a arranged at the position where the refrigerant passage 336 is arranged include the first and second laterally extending portions 122S, 122T.
Since the refrigerant passage 336 according to the first embodiment is disposed within a range of 90 ° in the clockwise direction from the first and second vane grooves 128S and 128T, the refrigerant passage 336 is more than the temperature of the refrigerant gas passing through the refrigerant passage 336. 1. The temperature of the first and second cylinder inner peripheral surfaces 123S and 123T of the first and second compression chambers 133S and 133T in the vicinity of the first and second discharge holes 190S and 190T is high. Therefore, the refrigerant gas passing through the refrigerant passage 336 does not increase the temperature of the first and second cylinder inner peripheral surfaces 123S and 123T, and the compressor efficiency does not decrease.
FIG. 4 is a plan view showing refrigerant passages of the first and second cylinders of Example 2, FIG. 5 is a longitudinal sectional view showing a discharge valve portion of Example 2, and FIG. 6 is a conventional discharge. It is a longitudinal cross-sectional view which shows a valve part. As shown in FIG. 4, the refrigerant passage 436 of the second embodiment is provided in the first and second cylinders 121S and 121T, the intermediate partition plate 140, and the upper and lower end plates 160S and 160T, and the first and second vane grooves 128S. , A phase angle of 270 ° to 360 ° in the revolving direction of the first and second annular pistons 125S and 125T (the counterclockwise direction of the first and second annular pistons 125S and 125T shown in FIG. 2) from the 128T position. It is arranged inside (that is, within a range of 90 ° in the clockwise direction from the position of the first and second vane grooves 128S and 128T).
The refrigerant passage 436 according to the second embodiment includes first and second discharge valve grooves 163S and 163T that house the first and second discharge valve portions 202S and 202T. From the range of 90 ° in the clockwise direction from the 128T position, the first and second suction holes 135S and 135T of the first and second cylinders 121S and 121T shown in FIG. The discharge valve grooves 163S and 163T are arranged in empty spaces where the arrangement is changed.
However, if the first and second discharge valve grooves 163S and 163T are rearranged on the first and second suction holes 135S and 135T side, as shown in FIG. 6, the first and second discharge valve grooves 163S and 163T bottom, since the thickness t 1 is thin, bottom, upper muffler chamber 180S, the first from the 180T, the second suction chamber 131S, the amount of heat transferred to the 131T side increases, the first and second suction chamber 131S, the 131T There is a problem that the refrigerant gas is heated. Further, when the thickness t 1 is thin, under high pressure, the upper muffler chamber 180S, the first 180T and the low pressure, the second suction chamber 131S, the pressure difference between the 131T, first, second discharge valve groove 163S, the 163T The amount of elastic deformation at the bottom increases, the sliding gap between the first and second annular pistons 125S and 125T decreases, and the first and second annular pistons 125S and 125T may be seized.
As a countermeasure for the above problem, as shown in FIG. 5, the thickness t 2 of the bottom portions of the first and second discharge valve grooves 163S and 163T (the bottom portions on the fixed side of the first and second discharge valve portions 202S and 202T) is set. It should be thick. At this time, the height of the first and second discharge valve portions 202S and 202T on the fixed side is different from the height of the valve seats of the first and second discharge holes 190S and 190T, so the first and second discharge valves 400S and 400T. And the 1st, 2nd discharge valve holding | suppressing 401S, 401T (1st, 2nd discharge valve part 402S, 402T) is formed in step shape.
Since the refrigerant passage 436 according to the second embodiment is disposed in a range of 90 ° in the clockwise direction from the first and second vane grooves 128S and 128T, the refrigerant passage 436 has a refrigerant temperature higher than that of the refrigerant gas passing through the refrigerant passage 436. The temperatures of the first and second cylinder inner peripheral surfaces 123S and 123T of the first and second compression chambers 133S and 133T in the vicinity of the passage 436 are high. Therefore, the refrigerant gas passing through the refrigerant passage 436 does not increase the temperature of the first and second cylinder inner peripheral surfaces 123S and 123T, and the compressor efficiency does not decrease.
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 (low-pressure connection pipe)
31T Second low pressure connection pipe (low pressure connection pipe)
101 First through hole (through hole)
102 Second through hole (through hole)
104 1st suction pipe (suction pipe, suction part)
105 Second suction pipe (suction pipe, suction part)
107 Discharge pipe (discharge section)
111 Stator 112 Rotor 12S 1st compression part (compression part)
12T 2nd compression part (compression part)
121S 1st cylinder (cylinder)
121T 2nd cylinder (cylinder)
121a, 321a Screw hole 122S First lateral overhang (side overhang)
122T Second lateral overhang (side overhang)
123S 1st cylinder inner peripheral surface (cylinder inner peripheral surface)
123T 2nd cylinder inner surface (cylinder inner surface)
124S 1st spring hole (spring hole)
124T Second spring hole (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 (pressure introduction path)
129T Second pressure introduction path (pressure introduction path)
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, 336, 436 Refrigerant passage 140 Intermediate partition plate 151 Sub 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)
163S First discharge valve groove 163T Second discharge valve groove 170S Lower muffler cover (muffler cover)
170T Upper muffler cover (muffler cover)
171 Muffler discharge hole 175 Through bolt 180S Lower muffler chamber (muffler chamber)
180T Upper muffler room (muffler room)
190S 1st discharge hole (discharge hole)
190T Second discharge hole (discharge hole)
200S, 400S 1st discharge valve (discharge valve)
200T, 400T Second discharge valve (discharge valve)
201S, 401S First discharge valve presser (discharge valve presser)
201T, 401T Second discharge valve presser (discharge valve presser)
202S, 402S 1st discharge valve part 202T, 402T 2nd discharge valve part 252 Accum holder 253 Accum band 255 System connection pipe R Opening part of 1st, 2nd pressure introduction path
Claims (3)
A lower upper end plate disposed at a lower portion of the compressor housing, having annular first and second cylinders, a bearing portion and a discharge valve portion, and closing the end portions of the first and second cylinders; An intermediate partition plate arranged between the first and second cylinders and partitioning between the two and the eccentric part of the rotating shaft supported by the bearing part is fitted along the inner peripheral surface of the first and second cylinders. The first and second annular pistons that revolve inside the cylinder and form a working chamber between the cylinder inner peripheral surface and the vane groove provided in the first and second cylinders project into the working chamber. The first and second vanes contacting the first and second annular pistons and partitioning the working chamber into a suction chamber and a compression chamber, and a muffler discharge hole communicating with the interior of the compressor housing. Upper muffler that covers the discharge valve portion of the upper end plate and forms an upper muffler chamber with the upper end plate A bar, a lower muffler cover that covers the discharge valve portion of the lower end plate and forms a lower muffler chamber between the lower end plate, the lower, upper end plate, the first and second cylinders, and the intermediate partition plate. A refrigerant passage that communicates between the upper and lower muffler chambers, and a compressor that sucks refrigerant from the low-pressure side of the refrigeration cycle through the suction part and discharges the refrigerant from the discharge part through the compressor housing;
A motor that is installed in an upper part of the compressor housing and drives the compression unit via the rotating shaft;
A rotary compressor comprising:
A rotary compressor, wherein the refrigerant passages provided in the first and second cylinders are arranged within a range of a phase angle of 270 ° to 360 ° in a revolving direction of the annular piston from a vane groove position.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013014873A JP2014145318A (en) | 2013-01-29 | 2013-01-29 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013014873A JP2014145318A (en) | 2013-01-29 | 2013-01-29 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2014145318A true JP2014145318A (en) | 2014-08-14 |
Family
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|---|---|---|---|
| JP2013014873A Pending JP2014145318A (en) | 2013-01-29 | 2013-01-29 | Rotary compressor |
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| CN105114310A (en) * | 2015-08-21 | 2015-12-02 | 广东美芝制冷设备有限公司 | Rotary compressor and compression assembly thereof |
| JP2016050528A (en) * | 2014-08-29 | 2016-04-11 | 東芝キヤリア株式会社 | Rotation type compressor and refrigeration cycle device |
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| EP3321507A1 (en) | 2016-11-14 | 2018-05-16 | Fujitsu General Limited | Rotary compressor |
| EP3324051A1 (en) | 2016-11-17 | 2018-05-23 | Fujitsu General Limited | Rotary compressor |
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