WO2004053335A1 - ロータリー圧縮機 - Google Patents
ロータリー圧縮機 Download PDFInfo
- Publication number
- WO2004053335A1 WO2004053335A1 PCT/JP2003/014555 JP0314555W WO2004053335A1 WO 2004053335 A1 WO2004053335 A1 WO 2004053335A1 JP 0314555 W JP0314555 W JP 0314555W WO 2004053335 A1 WO2004053335 A1 WO 2004053335A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- vane
- rotary compressor
- panel
- roller
- cylinder
- Prior art date
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/261—Carbon dioxide (CO2)
Definitions
- the present invention relates to a rotary compressor used for a refrigerator or an air conditioner.
- FIG. 4 is a longitudinal sectional view of a conventional rotary compressor
- Fig. 5 is a cross-sectional view of a compression mechanism of a conventional rotary compressor
- Fig. 6 is a dimension of a compression mechanism of a conventional rotary compressor.
- FIG. 7 and FIG. 8 are perspective views of vanes of a conventional rotary compressor.
- the rotary compressor includes an airtight container 1, a compression mechanism part 2 disposed therein, and an electric motor 3.
- the compression mechanism 2 is fitted to a cylinder 4 having a cylindrical portion, a shaft 5 rotatable about a center axis L1, and an eccentric portion 5a of the shaft 5, and is adapted to rotate the shaft 5.
- the roller 6 that makes an eccentric rotational motion inside the cylinder of the cylinder 4, and the vane 7 that reciprocates inside the vane groove 4 a provided in the cylinder 4 due to the eccentric rotational motion of the roller 6,
- a panel mechanism 8 such as a coil panel that presses the tip 7 b of the vane 7 on the back 7 a against the roller 6, and a first journal bearing on the motor 3 side that sandwiches both ends of the cylinder 4 and rotatably supports the shaft 5 9 and a second journal bearing 10 on the opposite side of the electric motor 3.
- the compression mechanism 2 is fixed to the closed casing 1 by a support 4 b formed around the cylinder 4.
- the electric motor 3 includes a cylindrical stator 11 welded inside the closed casing 1 and a cylindrical rotor 12 shrink-fitted to the shaft 5.
- the working fluid flows from the suction pipe 13 through the suction hole 4c of the cylinder 4 to the compression chamber 14 composed of the cylinder 4, the roller 6, the vane 7, the first jar nano-bearing 9, and the second jar nano-bearing 10. Is led to.
- the rotating motion generated by the electric motor 3 causes the roller 6 fitted to the eccentric portion 5a of the shaft 5 to eccentrically rotate, whereby the volume of the compression chamber 14 changes and the working fluid is compressed.
- a panel mechanism 8 such as a coil panel has one end in contact with the back surface 7 a of the vane 7 and the other end in contact with the cylindrical inner wall 1 a of the closed casing 1.
- the contact height of the spring mechanism 8 is 1 cvm
- the inner diameter of the cylindrical inner wall 1 a of the closed container 1 is dmi
- the inner diameter of the cylindrical inner wall 4 d of the cylinder 4 is dci. If the length from the tip 7b of the vane 7 to the back 7a is 1 vn, the inequality of Equation 1 must be satisfied.
- An object of the present invention is to solve the above-mentioned conventional problems, and by storing a part of a spring mechanism 8 such as a coil panel inside a vane 7, the vane 7 can be constructed with a simple and inexpensive structure. It is an object of the present invention to provide a rotary compressor that can be downsized while securing the contact area with the groove 4a and suppressing leakage of working fluid.
- a first aspect of the present invention provides a closed container, a cylinder disposed inside the closed container and having a vane groove, a shaft having an eccentric part, A roller rotatably fitted to the eccentric portion and eccentrically rotating within the cylinder; and a roller disposed in the vane groove of the cylinder and reciprocating in the vane groove while contacting the tip with the roller.
- a vane, and a panel mechanism for pressing the vane against the roller wherein the vane is provided with a panel hole on a side opposite to a side of the vane in contact with the roller,
- the panel hole is a rotary compressor that fits in a cross section of the vane perpendicular to the reciprocating direction of the vane and accommodates at least a part of the spring mechanism.
- the plurality of panel mechanisms includes the plurality of panel holes, and each of the panel mechanisms has at least a respective one of the spring mechanisms.
- 1 is a rotary compressor according to a first aspect of the present invention in which a part is housed. '
- a third invention is the rotary compressor according to the first invention, wherein the panel mechanism is a coil panel.
- a fourth aspect of the present invention is the rotary invention according to the third aspect of the invention, wherein one end of the coil panel is accommodated in the spring hole of the vane, and a pedestal to which the other end of the coil panel contacts is provided with a coil panel guide mechanism.
- One compressor is the rotary compressor according to the fourth invention, wherein the coil panel guide mechanism is provided on an inner side surface of the hermetic container.
- the vane has a width of 3.0 mm or more and 3.5 mm or less, a stroke of the vane of 3.0 mm or more and 5.0 mm or less, and a diameter of the coil panel.
- a seventh invention is the rotary compressor according to the first invention, wherein the working fluid is carbon dioxide.
- a rotary compressor of the present invention it is possible to provide a rotary compressor capable of ensuring a contact area between a vane and a vane groove with a simple and inexpensive structure and suppressing leakage of a working fluid while reducing the size. Can be done.
- FIG. 1 is a perspective view of a vane of a rotary compressor according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view of the vicinity of a vane groove of a compression mechanism of the rotary compressor according to the first embodiment of the present invention.
- FIG. 3 is a cross-sectional view of the vicinity of a vane groove of a compression mechanism of a rotary compressor according to a second embodiment of the present invention.
- FIG. 4 is a longitudinal sectional view of a conventional rotary compressor.
- FIG. 5 is a cross-sectional view of a compression mechanism of a conventional rotary compressor.
- FIG. 6 is a cross-sectional view showing dimensions of a compression mechanism of a conventional rotary compressor.
- FIG. 7 is a perspective view of a vane of a conventional rotary compressor.
- FIG. 8 is a perspective view of a vane of a conventional rotary compressor. (Explanation of code)
- FIG. 1 It should be noted that the following description describes specific examples of the present invention, and does not limit the description of the claims.
- the rotary compressor according to some embodiments of the present invention is different from the conventional rotary compressor shown in FIGS. 4 to 8 in the configuration of the rotary compressor other than the cylinder 4, the vane 7, and the spring mechanism 8. It has the same structure. The same numbers are used for the same components. The description of the same configuration and operation as in the conventional example is omitted.
- FIG. 1 is a perspective view of a vane of a rotary compressor according to Embodiment 1 of the present invention.
- FIG. 2 is a cross-sectional view of the vicinity of a vane groove of a compression mechanism of the rotary compressor according to Embodiment 1 of the present invention.
- FIG. 2 shows a state in which the tip 7 b of the vane 7 is pushed down to the inner wall 4 d of the cylinder 4.
- a coil panel 20 having an outer diameter smaller than the width and height of the back 7a of the vane 7 is provided as the panel mechanism 8, and the back 7a of the vane 7 is provided.
- two panel holes 7 d having a depth of 1 V na and having a diameter larger than the outer diameter of the coil spring 20 and smaller than the width and height of the vane 7 are provided in the reciprocating direction of the vane 7. Place one end of the coil panel 20 in each of the two panel holes 7 d and close the end of the coil panel 20 on the anti-vane side. It is brought into contact with the cylindrical inner wall 1 a of the closed container 1.
- the length 1 v'n of the vane 7 is set such that the tip 7 of the vane 7] D is pushed into the cylinder inner wall 4 d surface of the cylinder 4 with the eccentric rotation of the roller 6, and the The length shall be such that a minimum clearance of 1 cr occurs between 7 a and the inner cylindrical wall 1 a of the sealed container 1.
- the coil panel 20 is not allowed to have a contact height of 1 cvm or less even in the most compressed state, and even when the vane 7 projects most from the cylindrical inner wall 4 d of the cylinder 4, the coil spring 20 is in a closed state.
- the coil spring '20 must have a free length of less than 1 cVf (not shown) in order to press the shaft 7 against the roller 6. Therefore, assuming that the stroke of the reciprocating motion of the vane 7 accompanying the eccentric rotation of the roller 6 is 1 st, the panel hole 7 d is formed with a depth 1 Vna at which the inequality expression 2 holds.
- Equation 1 is represented by Equation 3.
- dmi is the inner diameter of the cylindrical inner wall 1 a of the sealed container 1
- dci is the inner diameter of the cylindrical inner wall 4 d of the cylinder 4
- V n is the tip 7 of the vane 7 Length from b to back 7a.
- the conventional rotary compressor is dense.
- the radius of the sealed container 1 was reduced by the difference between the contact height 1 cvm of the coil spring 20 and the clearance 1 cr.
- the length 1 Vn of the vane 7 is the same as before the diameter reduction, and furthermore, since the outer diameter of the panel hole 7 d is smaller than the width of the vane 7, there is a defect on the side of the vane 7. This does not occur and does not impair the length of the fitting portion between the vane 7 and the vane groove 4a, so that it is possible to maintain the sealing performance at the fitting portion between the vane 7 and the vane groove 4a.
- a part of the coil spring 20 can be housed in the spring hole 7 d of the vane 7, so that even if the rotary compressor is reduced in diameter, the length of the vane 7 is longer than that of the conventional rotary compressor. Can be longer. Therefore, the sealing performance at the fitting portion between the vane 7 and the vane groove 4a can be more securely maintained than in the conventional rotary compressor.
- the sealed container 1 of the conventional rotary compressor is not used. Since the length 1 Vn of the vane 7 is longer than when the diameter of the vane 7 is reduced, it is needless to say that the sealing performance at the fitting portion between the vane 7 and the vane groove 4a is reduced. Nor.
- the fitting length between the vane 7 and the vane groove 4a is longer than that of the conventional rotary compressor, the angle at which the vane 7 is inclined with respect to the vane groove 4a is smaller. Therefore, the contact pressure between vane 7 and vane groove 4a is low. As a result, the oil film is easily held and the reliability of the sliding surface is improved. In addition, a decrease in the contact surface pressure between the vane 7 and the vane groove 4a reduces a loss due to friction and improves mechanical efficiency.
- two panel holes 7 d are provided on the back 7 a of the vane 7, and at least a part of the coil spring 20 is placed in each of the two panel holes 7 d, so that the vane 7 is Can be pressed, so that the spring constant of each coil panel 20 can be designed to be small. For this reason, the diameter of the coil panel 20 can be reduced, and the above effects can be obtained without increasing the thickness of the vane 7. Furthermore, the spring of the coil panel 20 can be operated at the dispersed position of the back 7 a of the vane 7, and the tip 7 b of the vane 7 can be pressed uniformly to the roller 6. 7 b no longer hits the roller 6, thereby improving the reliability of the tip 7 b of the vane 7.
- two panel holes 7 d and two coil springs 20 are used.However, the present invention is not limited to this, and two or more panel holes 7 d and two or more coil panels 20 are used. No problem. In a configuration using two or more panel holes 7d and two or more coilpanes 20, the diameter of the coil spring 8 can be further reduced, and the tip 7b of the vane 7 can be pressed uniformly against the roller 6. Needless to say.
- the assembly can be performed at low cost and easily.
- the coil spring 20 is used for the panel mechanism 8, but it is needless to say that the same effect can be obtained by using an elastic body such as resin or gas. Nor. In the present embodiment, it has been described that two panel holes 7 d and two coil panels 20 are used. However, the present invention is not limited to this, and one spring hole 7 d and one coil panel 20 may be used. .
- the present embodiment can be easily realized only by forming a panel hole 7 d having a depth of 1 V na within a range represented by the inequality of Equation 2 on the back surface 7 a of the vane 7. Therefore, the above effects can be obtained at low cost.
- FIG. 3 is a cross-sectional view of the vicinity of a vane groove of a compression mechanism of a rotary compressor according to Embodiment 2 of the present invention.
- FIG. 3 shows a state in which the tip of the vane is pushed into the inner wall surface of the cylinder of the cylinder.
- the Koirupane 2 0 cylindrical inner wall 1 a of the closed container 1 in which the end portion is in contact, and in that a Koirupanegai de mechanism 1 b.
- the coil spring guide mechanism 1 b is formed of a columnar projection having a diameter smaller than the inner diameter of the coil spring 20 provided on the cylindrical inner wall 1 a of the closed casing 1. In other words, as is clear from FIG. 3, a cylindrical projection serving as the coil panel guide mechanism 1 b penetrates into the inside of the coil spring 20.
- the length of the coil panel guide mechanism 1 b of the cylindrical inner wall 1 a of the closed casing 1 is shorter than the depth 1 Vna of the spring hole 7 d of the vane 7.
- the configuration of the second embodiment is the same as that of the first embodiment except for the configuration described above, and it goes without saying that the same effects can be obtained by those configurations. Next, effects of the above configuration will be described.
- Both ends of the coil panel 20 are moved in directions other than the direction of expansion and contraction by the panel spring holes 7 d of the vane 7 and the coil spring guide mechanism 1 b of the cylindrical inner wall 1 a of the sealed container 1.
- the coil panel 20 When the coil panel 20 repeatedly expands and contracts, the coil panel 20 is prevented from being caught between the coil panel 20 and the entrance of the panel hole 7 d on the back 7 a of the vane 7. It is possible to prevent a failure due to detachment or bending of the rotary compressor, and to secure reliability of the rotary compressor.
- An R may be added at the entrance of the spring hole 7d. In this way, by adding an R to the entrance of the panel hole 7 d, it is possible to further reduce the possibility that the coil panel 20 and the entrance of the spring hole 7 d on the back 7 a of the vane 7 will be caught. I can do it.
- the length of the coil panel guide mechanism 1 b on the inner cylindrical wall 1 a of the closed casing 1 to a depth of 1 V na of the spring hole 7 d of the vane 7 or less, the rear face 7 a of the vane 7 and the closed Even when the inner wall 1a of the cylinder 1 approaches, the bottom of the spring hole 7d does not collide with the tip of the coil panel guide mechanism 1b. Therefore, it is possible to minimize the clearance 1 cr between the back surface 7 a of the vane 7 and the cylindrical inner wall 1 a of the closed casing 1, and in the present embodiment, the effect of the first embodiment of the present invention is reduced. It can be maximized.
- the support portion for fixing the coil panel guide mechanism 1 b to the closed container 1 is combined with the coil spring 20 and the vane 7. Since it can be configured without interference, the sealing surface of the vane 7 can be made longer than in the case where a support portion for fixing to the cylinder 4 is provided.
- a small rotary compressor generally uses a vane 7 having a width of 3.0 mm or more and 3.5 mm or less, and a stroke of the vane 7 is 3.0 mm or more and 5.0 mm or less.
- a coil panel 20 having a free length of 100 mm or more is used in consideration of the close contact height of the coil panel 20.
- both ends are fixed, and the free length of the coil panel is set by the coil spring.
- the aspect ratio divided by the average diameter is less than 5, the risk of buckling is reduced. Therefore, by setting the diameter of the coil spring 20 to at least 2.0 mm and less than the width of the vane 7, the reliability of the compressor can be ensured.
- carbon dioxide as a working fluid has a higher pressure than other working fluids such as chlorofluorocarbon, alternative chlorofluorocarbons, hydrocarbons, and ammonia, and leakage of the working fluid in the gap between the vane groove 4a and the vane 7 is prevented. Although it becomes larger, the leakage of the working fluid can be reduced by using the embodiment of the present invention to make the length of the vane 7 longer than before.
- carbon dioxide as a working fluid has a high density and a smaller cylinder volume than other working fluids.
- the use of carbon dioxide as the working fluid reduces the cylinder volume, but by using the present invention, it is possible to further reduce the size of the compression mechanism 2 and to achieve a rotary-type compressor. Becomes possible.
- the present invention is realized by placing at least a part of the coil panel 20 in the panel hole 7 d on the back surface 7 a of the vane 7.
- the space between the vane 7 and the airtight container 1 which has been required between the vane 7 and the airtight container 1 is no longer necessary than the close contact height of the coil spring 20, and the seal length between the vane 7 and the vane groove 7a can be increased. It has the advantage of providing a compact, high-efficiency rotary compressor with a structure.
- the compressor according to the present invention has a function of compressing and conveying a working fluid, and is useful for a refrigerant-type heat pump such as a refrigerator and a refrigerator. It can also be applied to applications such as vacuum pumps.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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JP2004558395A JPWO2004053335A1 (ja) | 2002-12-11 | 2003-11-17 | ロータリー圧縮機 |
US10/514,691 US20050214151A1 (en) | 2002-12-11 | 2003-11-17 | Rotary compressor |
EP03772798A EP1500820A4 (en) | 2002-12-11 | 2003-11-17 | ROTARY COMPRESSOR |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002359745 | 2002-12-11 | ||
JP2002-359745 | 2002-12-11 |
Publications (1)
Publication Number | Publication Date |
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WO2004053335A1 true WO2004053335A1 (ja) | 2004-06-24 |
Family
ID=32500954
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/014555 WO2004053335A1 (ja) | 2002-12-11 | 2003-11-17 | ロータリー圧縮機 |
Country Status (6)
Country | Link |
---|---|
US (1) | US20050214151A1 (ja) |
EP (1) | EP1500820A4 (ja) |
JP (1) | JPWO2004053335A1 (ja) |
KR (1) | KR20050084781A (ja) |
CN (1) | CN1692228A (ja) |
WO (1) | WO2004053335A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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KR100939571B1 (ko) * | 2004-12-29 | 2010-01-29 | 아스펜 컴프레서 엘엘씨. | 소형 로터리 압축기 및 그 제조방법 |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015217922A1 (de) * | 2015-09-18 | 2017-03-23 | Continental Automotive Gmbh | Verfahren und zweiteilige Werkzeuganordnung zum Herstellen eines Stators für eine elektrische Maschine |
DE102015217936A1 (de) * | 2015-09-18 | 2017-03-23 | Continental Automotive Gmbh | Verfahren und einteilige Werkzeuganordnung zum Herstellen eines Stators für eine elektrische Maschine |
JP6305471B2 (ja) * | 2016-07-25 | 2018-04-04 | 本田技研工業株式会社 | ステータの製造方法及びその装置 |
CN109026699B (zh) * | 2018-08-21 | 2024-03-29 | 珠海凌达压缩机有限公司 | 一种泵体、压缩机及泵体的制造方法 |
KR20240071008A (ko) | 2022-11-15 | 2024-05-22 | 주식회사 비에이치다온 | 반도체 소자의 세정용 초순수 제조 버블러 |
Citations (6)
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JPS50124204A (ja) * | 1974-03-18 | 1975-09-30 | ||
JPS51159010U (ja) * | 1975-06-12 | 1976-12-17 | ||
JPS56157394U (ja) * | 1980-04-25 | 1981-11-24 | ||
JPS57193089U (ja) * | 1981-05-29 | 1982-12-07 | ||
JP2000170677A (ja) * | 1998-12-02 | 2000-06-20 | Matsushita Electric Ind Co Ltd | ロータリー圧縮機 |
JP2001280276A (ja) * | 2000-03-30 | 2001-10-10 | Sanyo Electric Co Ltd | 多段圧縮機 |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2111595B (en) * | 1981-12-04 | 1985-11-06 | Ken Hsu Song | A rotary gas compressor |
US4598559A (en) * | 1985-05-31 | 1986-07-08 | Carrier Corporation | Reversible fixed vane rotary compressor having a reversing disk which carries the suction port |
-
2003
- 2003-11-17 KR KR1020047016443A patent/KR20050084781A/ko not_active IP Right Cessation
- 2003-11-17 JP JP2004558395A patent/JPWO2004053335A1/ja not_active Withdrawn
- 2003-11-17 EP EP03772798A patent/EP1500820A4/en not_active Withdrawn
- 2003-11-17 US US10/514,691 patent/US20050214151A1/en not_active Abandoned
- 2003-11-17 CN CNA2003801004211A patent/CN1692228A/zh active Pending
- 2003-11-17 WO PCT/JP2003/014555 patent/WO2004053335A1/ja not_active Application Discontinuation
Patent Citations (6)
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JPS50124204A (ja) * | 1974-03-18 | 1975-09-30 | ||
JPS51159010U (ja) * | 1975-06-12 | 1976-12-17 | ||
JPS56157394U (ja) * | 1980-04-25 | 1981-11-24 | ||
JPS57193089U (ja) * | 1981-05-29 | 1982-12-07 | ||
JP2000170677A (ja) * | 1998-12-02 | 2000-06-20 | Matsushita Electric Ind Co Ltd | ロータリー圧縮機 |
JP2001280276A (ja) * | 2000-03-30 | 2001-10-10 | Sanyo Electric Co Ltd | 多段圧縮機 |
Non-Patent Citations (1)
Title |
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See also references of EP1500820A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100939571B1 (ko) * | 2004-12-29 | 2010-01-29 | 아스펜 컴프레서 엘엘씨. | 소형 로터리 압축기 및 그 제조방법 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2004053335A1 (ja) | 2006-04-13 |
CN1692228A (zh) | 2005-11-02 |
EP1500820A4 (en) | 2005-05-11 |
US20050214151A1 (en) | 2005-09-29 |
KR20050084781A (ko) | 2005-08-29 |
EP1500820A1 (en) | 2005-01-26 |
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