WO2005088079A1 - ロータリ式膨張機 - Google Patents
ロータリ式膨張機 Download PDFInfo
- Publication number
- WO2005088079A1 WO2005088079A1 PCT/JP2005/004502 JP2005004502W WO2005088079A1 WO 2005088079 A1 WO2005088079 A1 WO 2005088079A1 JP 2005004502 W JP2005004502 W JP 2005004502W WO 2005088079 A1 WO2005088079 A1 WO 2005088079A1
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- WO
- WIPO (PCT)
- Prior art keywords
- seal
- rotary
- rotary piston
- cylinder
- lubricating oil
- Prior art date
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Classifications
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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
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 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
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/324—Arrangements for lubrication or cooling of the sealing itself
-
- 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
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
-
- 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
- F01C19/00—Sealing arrangements in rotary-piston machines or engines
- F01C19/08—Axially-movable sealings for working fluids
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
-
- 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
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F01C1/3562—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 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 surface substantially parallel to the axis of rotation
- F01C1/3564—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 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 surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
Definitions
- the present invention relates to a rotary expander, and more particularly, to a measure for preventing oil rise.
- a positive displacement expander such as a rotary expander is disclosed in, for example, JP-A-2003-172244.
- the rotary expander includes an expansion mechanism having a cylinder whose both ends are closed by a front head and a rear head, and a piston housed in the cylinder.
- a shaft having an eccentric portion rotatably fitted to the piston is penetrated through the expansion mechanism.
- lubricating oil pumped by an oil pump provided on the shaft is supplied to the expansion mechanism to lubricate the expansion mechanism.
- the present invention has been made in view of the above point, and an object of the present invention is to prevent the lubricating oil in the expansion mechanism from excessively flowing into the expansion chamber and to solve the problem of insufficient lubrication oil. And to improve reliability.
- a first solution is to provide a cylinder (63) whose both ends are closed by closing members (61, 62) and a rotary piston (67) housed in the cylinder (63).
- Expansion mechanism with 60) It is assumed that the rotary expander is equipped with: A seal mechanism (90) for sealing between the rotary piston (67) and the closing members (61, 62) is provided on at least one of both end faces.
- a second solution is the first solution, wherein one rotating shaft (40) having an eccentric portion (41) rotatably fitted to the rotary piston (67) is provided. Be prepared.
- the rotating shaft (40) is lubricated at least to a sliding part between the eccentric part (41) and the closing member (61, 62) and a sliding part between the rotary piston (67) and the eccentric part (41).
- An oil supply groove (49) is formed for filling.
- the oil supply groove (49) of the rotating shaft (40) has at least the sliding portion between the eccentric portion (41) and the closing member (61, 62) and the rotary piston (67) and the eccentric portion ( The leakage of the lubricating oil supplied to the sliding part with (41) is suppressed.
- the expansion mechanism (60) has a plurality of pallet pistons (75, 85).
- the rotary pistons (75, 85) are connected by one rotating shaft (40) and are arranged side by side, and the end faces of the adjacent rotary pistons (75, 85) form an intermediate partition plate (64). They are arranged so as to face each other with the interposition therebetween.
- the seal mechanism (90) is provided on the end face of the plurality of rotary pistons (75, 85) facing the closing member (61, 62).
- a fourth solution is the solution according to any one of the first to thirteenth means, wherein the seal mechanism (90) is provided with a seal groove (91) formed on an end face of a rotary piston (67). ) And a seal member (92) fitted in the seal groove (91).
- the sealing member (92) is in close contact with the closing member (61, 62) and the sealing groove (91), so that the end face of the rotary piston (67) and the closing member (61, 62) The gap is sealed.
- the seal member (92) is a lip seal or a tip seal.
- the seal mechanism (90) is a labyrinth seal.
- the seal between the end face of the rotary piston (67) and the closing member (61, 62) is generated by a labyrinth effect such as a friction effect due to the viscosity of the lubricating oil and a contraction effect at the throttle port.
- the sealing member is provided.
- (92) is made of a tetrafluoroplastic styrene-based (PTFE-based) resin material.
- the resin material of the four-component chemical modified titanium is excellent in wear resistance and heat resistance, so that the end face of the rotary piston (67) and the closing members (61, 62) The gap between them is securely sealed.
- an eighth solution of the present invention is the device according to any one of the first to seventh aspects, wherein
- the rotary piston (67) fits in the axial direction of the shaft (40), and the tolerance is set to the dimension of 1Z5000-1Z1000 of the inner diameter D of the cylinder (63).
- a sealing mechanism (90) for sealing between the rotary piston (67) and the closing member (61, 62) is provided on at least one end face of the rotary piston (67). It is possible to suppress the lubricating oil supplied to the sliding portion of the expansion mechanism (60) from leaking into the expansion space. Thereby, since the lubricating oil hardly flows out with the expansion mechanism (60) together with the expanded fluid, it is possible to prevent the oil from rising and prevent the lubricating oil shortage. As a result, the reliability of the device can be improved.
- the lubricating oil is formed by a high-temperature and high-pressure gas refrigerant. While the refrigerant is heated to a high temperature, the refrigerant flowing into the expansion mechanism (60) is relatively low in temperature.However, as described above, by suppressing the leakage of the lubricating oil into the expansion space, the low-temperature refrigerant is It can be prevented from being heated by mixing with oil, and heat loss during the expansion process can be prevented. As a result, operation efficiency can be improved.
- the oil supply groove (49) formed in the rotating shaft (40) also has a lubricating oil expansion mechanism (60) provided with an oil supply system for supplying lubricating oil. Leakage to the expansion space can be suppressed.
- the seal mechanism (90) is attached to the end face of the rotary piston (75, 85) on the side of the intermediate partition (64).
- the seal mechanism (90) is installed on the end surface on the side of the closing member (61, 62) instead of being provided. The leakage of the lubricating oil, which is not liable to be damaged by being wrapped in the through hole, can be suppressed.
- the seal mechanism (90) is constituted by the seal groove (91) and the seal member (92) fitted in the seal groove (91). Sealing members (92) The close contact between the closing member (61, 62) and the seal groove (91) allows a seal between the end face of the rotary piston (67) and the closing member (61, 62).
- the seal member (92) is a lip seal or a chip seal
- the lip seal or the chip seal is brought into contact with the closing member (61, 62) by the pressure action of the lubricating oil.
- the seal groove (91) can be securely brought into close contact with the seal groove (91). This makes it possible to reliably seal the gap between the end face of the rotary biston (67) and the closing member (61, 62).
- the seal mechanism (90) is a labyrinth seal
- the labyrinth effect ensures the clearance between the end face of the rotary piston (67) and the closing member (61, 62). Can be sealed.
- the seal member (92) is formed of a four-component styrene-based resin material having excellent wear resistance and heat resistance. High sealing performance can be ensured even in sliding with the closing members (61, 62) due to the rotation of ()).
- FIG. 1 is a piping diagram showing an air conditioner.
- FIG. 2 is a longitudinal sectional view showing a compression / expansion unit according to Embodiment 1.
- FIG. 3 is a cross-sectional view schematically showing a main part of the expansion mechanism according to the first embodiment.
- FIG. 4 is a longitudinal sectional view schematically showing a main part of the expansion mechanism according to the first embodiment.
- FIG. 5 is a cross-sectional view showing a state of the expansion mechanism for each rotation angle of the rotation shaft of 90 ° according to the first embodiment, omitting a sealing mechanism.
- FIG. 6 is a cross-sectional view schematically showing a main part of an expansion mechanism according to Embodiment 2.
- FIG. 7 is a longitudinal sectional view schematically showing a main part of an expansion mechanism according to Embodiment 2.
- FIG. 8 is a cross-sectional view schematically showing a main part of an expansion mechanism according to Embodiment 3.
- FIG. 9 is a cross-sectional view schematically showing a main part of an expansion mechanism according to Embodiment 4.
- FIG. 10 is a cross-sectional view schematically showing a main part of an expansion mechanism according to Embodiment 5.
- FIG. 11 is a longitudinal sectional view schematically showing a main part of an expansion mechanism according to Embodiment 5.
- FIG. 12 is a longitudinal sectional view showing a compression / expansion unit according to Embodiment 6.
- FIG. 13 is a longitudinal sectional view schematically showing a main part of an expansion mechanism according to another embodiment. It is.
- Embodiment 1 of the present invention will be described.
- the air conditioner (10) of the present embodiment includes a rotary expander according to the present invention.
- the air conditioner (10) is a so-called separate type, and includes an outdoor unit (11) and an indoor unit (13).
- the outdoor unit (11) includes an outdoor fan (12), outdoor heat exchange (23), a first four-way switching valve (21), a second four-way switching valve (22), and a compression / expansion unit (30). It is stored.
- the indoor unit (13) contains an indoor fan (14) and an indoor heat exchanger (24).
- the outdoor unit (11) is installed outdoors, and the indoor unit (13) is installed indoors.
- the outdoor unit (11) and the indoor unit (13) are connected by a pair of communication pipes (15, 16). The details of the compression / expansion unit (30) will be described later.
- the air conditioner (10) is provided with a refrigerant circuit (20).
- the refrigerant circuit (20) is a closed circuit to which a compression expansion unit (30), indoor heat exchange (24), and the like are connected.
- the refrigerant circuit (20) is filled with diacid carbon (CO 2) as a refrigerant.
- the outdoor heat exchange (23) and the indoor heat exchange (24) are both constituted by cross-fin type fin-and-tube heat exchangers.
- the refrigerant circulating in the refrigerant circuit (20) exchanges heat with outdoor air.
- the indoor heat exchanger (24) the refrigerant circulating in the refrigerant circuit (20) exchanges heat with indoor air.
- the first four-way switching valve (21) has four ports.
- the first four-way switching valve (21) has a first port connected to the discharge pipe (36) of the compression / expansion unit (30), and a second port connected to the indoor heat exchanger (24) via the communication pipe (15).
- the third port is connected to one end of the outdoor heat exchanger (23), and the fourth port is connected to the suction port (32) of the compression / expansion unit (30).
- the first four-way switching valve (21) has a state in which the first port and the second port are in communication and the third port and the fourth port are in communication (a state shown by a solid line in FIG. 1).
- a state where the first port and the third port communicate with each other and the second port and the fourth port communicate with each other (a state shown by a broken line in FIG. 1). Switch.
- the second four-way switching valve (22) has four ports.
- the second four-way switching valve (22) has a first port at the outlet port (35) of the compression / expansion unit (30), a second port at the other end of the outdoor heat exchanger (23), and a third port. Is connected to the other end of the indoor heat exchanger (24) via the communication pipe (16), and the fourth port is connected to the inflow port (34) of the compression / expansion unit (30).
- the second four-way switching valve (22) is in a state where the first port and the second port are in communication and the third port and the fourth port are in communication (the state shown by the solid line in FIG. 1). The state is switched to a state in which the first port and the third port communicate with each other and the second port and the fourth port communicate with each other (a state shown by a broken line in FIG. 1).
- the compression / expansion unit (30) includes a casing (31) which is a vertically-long cylindrical closed container. Inside the casing (31), a compression mechanism (50), an electric motor (45), and an expansion mechanism (60) are arranged in order from bottom to top.
- a discharge pipe (36) is attached to the casing (31).
- the discharge pipe (36) is arranged between the electric motor (45) and the expansion mechanism (60), and communicates with the internal space of the casing (31).
- the electric motor (45) is arranged at the longitudinal center of the casing (31).
- the electric motor (45) includes a stator (46) and a rotor (47).
- the stator (46) is fixed to the casing (31).
- the rotor (47) is arranged inside the stator (46), and the main shaft (44) of the shaft (40) penetrates coaxially.
- the shaft (40) constitutes a rotating shaft, and has two lower eccentric portions (58, 59) formed at the lower end and one large-diameter eccentric portion (41) formed at the upper end. .
- the two lower eccentric portions (58, 59) are formed to have a larger diameter than the main shaft portion (44) and to be eccentric than the axis of the main shaft portion (44).
- the first lower eccentric portion (58) and the upper one constitute a second lower eccentric portion (59), respectively.
- the eccentric directions of the main shaft portion (44) with respect to the axis are reversed.
- the large-diameter eccentric portion (41) has a larger diameter than the main shaft portion (44) and is more eccentric than the axis of the main shaft portion (44). It is formed with heart.
- the compression mechanism (50) constitutes an oscillating piston type rotary compressor.
- the compression mechanism (50) includes two cylinders (51, 52) and two rotary pistons (57).
- the rear head (55), the first cylinder (51), the intermediate plate (56), the second cylinder (52), and the front head ( 54) are stacked.
- first cylinder (51) and the second cylinder (52) Inside the first cylinder (51) and the second cylinder (52), one cylindrical rotary piston (57) is arranged.
- the rotary piston (57) has a flat blade protruding from a side surface thereof, and this blade is supported by the cylinders (51, 52) via a swinging bush.
- the rotary piston (57) in the first cylinder (51) is engaged with the first lower eccentric part (58) of the shaft (40).
- the rotary piston (57) in the second cylinder (52) engages with the second lower eccentric part (59) of the shaft (40).
- each of the rotary pistons (57, 57) the inner peripheral surface is in sliding contact with the outer peripheral surface of the lower eccentric portion (58, 59), and the outer peripheral surface is in sliding contact with the inner peripheral surface of the cylinder (51, 52). Then, a compression chamber (53) is formed between the outer peripheral surface of each rotary piston (57, 57) and the inner peripheral surface of the cylinder (51, 52).
- Each of the first cylinder (51) and the second cylinder (52) has one suction port (32).
- Each of the suction ports (32) penetrates through the cylinder (51, 52) in the radial direction, and the terminal end opens into the cylinder (51, 52).
- Each suction port (32) is extended to the outside of the casing (31) by a pipe.
- Each of the front head (54) and the rear head (55) has one discharge port.
- the discharge port of the front head (54) communicates the compression chamber (53) in the second cylinder (52) with the internal space of the casing (31).
- the discharge port of the rear head (55) communicates the compression chamber (53) in the first cylinder (51) with the internal space of the casing (31).
- Each of the discharge ports is provided with a discharge valve having a reed valve force at the end, and is opened and closed by the discharge valve. In FIG. 2, the illustration of the discharge port and the discharge valve is omitted.
- the gas refrigerant discharged into the internal space of the casing (31) with the force of the compression mechanism (50) is sent out of the compression / expansion unit (30) through the discharge pipe (36).
- An oil reservoir for storing lubricating oil is formed at the bottom of the casing (31). At the lower end of the shaft (40), a centrifugal oil pump (48) immersed in an oil sump is provided.
- the oil pump (48) is configured to pump lubricating oil in an oil sump by rotation of a shaft (40).
- An oil supply groove (49) is formed inside the shaft (40) from the lower end to the upper end. The oil supply groove (49) is formed so that the lubricating oil pumped up by the oil pump (48) is supplied to each sliding portion of the compression mechanism (50) and the expansion mechanism (60).
- the expansion mechanism (60) is of a so-called swing piston type, and constitutes a rotary expander of the present invention.
- the expansion mechanism (60) includes a front head (61), a rear head (62), a cylinder (63), and a rotary piston (67). Further, the expansion mechanism (60) is provided with an inflow port (34) and an outflow port (35).
- the front head (61), the cylinder (63), and the rear head (62) are stacked in order from bottom to top.
- the cylinder (63) has a lower end face closed by a front head (61), and an upper end face closed by a rear head (62). That is, the front head (61) and the rear head (62) each constitute a closing member of the cylinder (63).
- the shaft (40) passes through the stacked front head (61), cylinder (63), and rear head (62), and the large-diameter eccentric portion (41) is positioned inside the cylinder (63). are doing.
- the rotary piston (67) is housed in a cylinder (63) whose upper and lower ends are closed.
- the rotary piston (67) is formed in an annular or cylindrical shape, and has an inner diameter substantially equal to the outer diameter of the large-diameter eccentric portion (41).
- a large-diameter eccentric portion (41) is rotatably fitted to the rotary piston (67), and the inner peripheral surface of the rotary piston (67) and the outer peripheral surface of the large-diameter eccentric portion (41) cover almost the entire surface. It slides over it.
- the rotary piston (67) has an outer peripheral surface in sliding contact with an inner peripheral surface of the cylinder (63), an upper end surface (67b) of the rotary head (62), and a lower end surface (67c) of the front head (61). Are in sliding contact with each other.
- a fluid chamber (65) is formed in the cylinder (63) between the inner peripheral surface and the outer peripheral surface of the rotary piston (67).
- the rotary piston (67) is provided with a blade (67a).
- the blade (67a) is formed in a plate shape extending in the radial direction of the rotary piston (67).
- the outer peripheral surface force of the piston (67) also protrudes outward.
- the fluid chamber (65) in the cylinder (63) is partitioned by a blade (67a) into a high-pressure chamber (66a) on the high-pressure side and a low-pressure chamber (66b) on the low-pressure side.
- the cylinder (63) is provided with a pair of bushes (68).
- Each bush (68) is formed in a semilunar shape with the inner surface being flat and the outer surface being arcuate, and is mounted with the blade (67a) sandwiched therebetween.
- the bush (68) slides on the inner surface with the blade (67a) and on the outer surface with the cylinder (63).
- the blade (67a) integral with the rotary piston (67) is supported by a cylinder (63) via a bush (68), and is configured to be rotatable and retractable with respect to the cylinder (63). ! RU
- the inflow port (34) is formed in the front head (61), and the terminal end opens to the inner side surface of the front head (61) and communicates with the high-pressure chamber (66a).
- the outflow port (35) is formed in the cylinder (63), and has a start end opening to the inner peripheral surface of the cylinder (63) and communicating with the low-pressure chamber (66b).
- the oil supply groove (49) of the shaft (40) is provided with a thin groove (49a) for supplying oil to each sliding portion ( ⁇ , ⁇ ) of the expansion mechanism (60).
- the narrow groove (49a) mainly includes a sliding portion (A) between the end faces of the large-diameter eccentric portion (41) and the rear head (62) and the front head (61), and a portion outside the large-diameter eccentric portion (41). It is formed to supply oil to the sliding portion (B) between the peripheral surface and the inner peripheral surface of the rotary piston (67).
- a seal mechanism (90) for sealing between the rear head (62) and the front head (61) is provided on both upper and lower end faces (67b, 67c) of the rotary piston (67). .
- the sealing mechanism (90) includes a seal groove (91) and a seal member (92) fitted in the seal groove (91).
- the seal groove (91) is provided on both surfaces of the upper end surface (67b) and the lower end surface (67c) of the rotary piston (67).
- Each of the seal grooves (91) has a concave cross section and is formed in a ring shape in plan view along the entire circumference of the end faces (67b, 67c) of the rotary piston (67).
- the seal member (92) is configured as a lip seal which is a mechanical seal.
- the lip seal (92) is formed to have a substantially C-shaped cross-section opening inward, and The vision is formed in a continuous annular shape. That is, the lip seal (92) is mounted in the seal groove (91) such that the opening side faces the shaft (40).
- the lip seal (92) is made of a tetrafluoroplastic styrene (PTFE) resin material.
- PTFE tetrafluoroplastic styrene
- This tetrafluoroplastic titanium material is obtained by adding a filler such as glass fiber or carbon fiber to pure tetrafluoroethylene resin (PTFE).
- the four-component titanium-based resin material is a material excellent in abrasion resistance and heat resistance, so that a high sealing property is ensured.
- the seal mechanism (90) when lubricating oil is excessively supplied to the sliding portions ( ⁇ , ⁇ ), the lubricating oil enters the opening of the lip seal (92), and the lip is acted on by the pressure action of the lubricating oil.
- the opening of the seal (92) is widened.
- the lip seal (92) comes into close contact with the front head (61) and the rear head (62), and adheres to the bottom surface of the seal groove (91), and the rotary piston (67) ) Is sealed between the upper and lower end faces (67b, 67c), the rear head (62) and the front head (61).
- the lubricating oil supplied to each sliding portion ( ⁇ , ⁇ ) hardly leaks into the fluid chamber (65) of the cylinder (63)! /.
- the clearance between the upper end surface (67b) of the rotary piston (67) and the rear head (62) and the clearance between the lower end surface (67c) of the rotary piston (67) and the front head (61) are: Each is set to the dimension of 1Z10000-1Z2000 of the inside diameter of the cylinder (63). In other words, the fit of the rotary piston (67) in the axial direction of the shaft (40) is set to the dimension of 1Z5000-1Z1000 of the inner diameter of the cylinder (63). This is because the seal between the upper and lower end faces (67b, 67c) of the rotary piston (67) and the front head (61) and the rear head (62) can be sealed by the seal mechanism (90).
- the first four-way switching valve (21) and the second four-way switching valve (22) are switched to the state shown by the broken line in FIG. In this state, when the electric motor (45) of the compression / expansion unit (30) is energized, the refrigerant circulates in the refrigerant circuit (20) to perform a vapor compression refrigeration cycle.
- the refrigerant compressed by the compression mechanism (50) is discharged from the compression / expansion unit (30) through the discharge pipe (36). In this state, the pressure of the refrigerant is higher than the critical pressure.
- the discharged refrigerant is sent to the outdoor heat exchanger (23) through the first four-way switching valve (21). In the outdoor heat exchanger (23), the inflow refrigerant dissipates heat to outdoor air.
- the refrigerant radiated in the outdoor heat exchanger (23) passes through the second four-way switching valve (22) and flows into the inflow port (34).
- the expansion mechanism of the compression / expansion unit (30) (60) Flows into In the expansion mechanism (60), the high-pressure refrigerant expands, and its internal energy is converted into rotational power of the shaft (40). Then, the expanded low-pressure refrigerant flows out of the compression / expansion unit (30) through the outflow port (35), and is sent to the indoor heat exchanger (24) through the second four-way switching valve (22).
- the refrigerant that has flowed in absorbs heat from room air and evaporates, thereby cooling the room air.
- the low-pressure gas refrigerant that has been subjected to the indoor heat exchange (24) passes through the first four-way switching valve (21) and is sucked into the compression mechanism (50) of the suction port (32) force compression / expansion unit (30). Then, the compression mechanism (50) compresses the sucked refrigerant again and discharges it.
- the first four-way switching valve (21) and the second four-way switching valve (22) are switched to the state shown by the solid line in FIG. In this state, when the electric motor (45) of the compression / expansion unit (30) is energized, the refrigerant circulates in the refrigerant circuit (20) to perform a vapor compression refrigeration cycle.
- the refrigerant compressed by the compression mechanism (50) is discharged from the compression / expansion unit (30) through the discharge pipe (36). In this state, the pressure of the refrigerant is higher than the critical pressure.
- the discharged refrigerant is sent to the indoor heat exchanger (24) through the first four-way switching valve (21). In the indoor heat exchanger (24), the inflowing refrigerant radiates heat to the indoor air, and the indoor air is heated.
- the refrigerant radiated by the indoor heat exchanger (24) passes through the second four-way switching valve (22), and flows into the inflow port (34).
- the expansion mechanism of the compression / expansion unit (30) (60) Flows into With this expansion mechanism (60)
- the high-pressure refrigerant expands, and its internal energy is converted into rotational power of the shaft (40).
- the expanded low-pressure refrigerant flows out of the compression / expansion unit (30) through the outflow port (35), and is sent to the outdoor heat exchanger (23) through the second four-way switching valve (22).
- the inflow refrigerant absorbs heat from the outdoor air and evaporates.
- the low-pressure gas refrigerant flowing out of the outdoor heat exchanger (23) passes through the first four-way switching valve (21), and flows from the suction port (32) to the compression mechanism (50) of the compression / expansion unit (30). ). Then, the compression mechanism (50) compresses the sucked refrigerant again and discharges it.
- the rotation angle of the shaft (40) When the rotation angle of the shaft (40) is 0 °, the end of the inflow port (34) is closed by the end face of the large-diameter eccentric part (41). When the shaft (40) slightly rotates from this state, the inflow port (34) communicates with the high-pressure chamber (66a), and the high-pressure refrigerant starts flowing into the high-pressure chamber (66a). Thereafter, as the rotation angle of the shaft (40) gradually increases to 90 °, 180 °, and 270 °, the volume of the high-pressure chamber (66a) gradually increases.
- the low-pressure chamber (66b) communicates with the outlet port (35), and the refrigerant in the low-pressure chamber (66b) flows out.
- the rotation angle of the shaft (40) gradually increases to 90 °, 180 °, and 270 °
- the capacity of the low-pressure chamber (66b) gradually decreases, during which the refrigerant flows out of the outflow port (35). to continue.
- the outflow port (35) is closed by the rotary piston (67), and the outflow of the refrigerant from the low-pressure chamber (66b) is shut off.
- the rotary piston (67) and the shaft (40) are driven to rotate by the pressure difference between the high-pressure chamber (66a) and the low-pressure chamber (66b).
- the lubricating oil in the oil reservoir is supplied from the oil supply groove (49) to a sliding portion such as the expansion mechanism (60) by the rotation of the shaft (40).
- the expansion mechanism (60 ) Even if excess lubricating oil is generated from the narrow groove (49a) to each sliding part ( ⁇ , ⁇ ), the lubricating oil flows into the fluid chamber (65) with a seal.
- Mechanism (90) suppresses. Thereby, the lubricating oil mixes with the refrigerant in the fluid chamber (65), and hardly flows out of the compression / expansion unit (30) through the outflow port (35) together with the refrigerant. As a result, oil rise to the refrigerant circuit (20) can be suppressed, and performance degradation of each heat exchange (23, 24) can be suppressed.
- the compression / expansion unit (30) of the present embodiment has a compression mechanism (50) and is configured in a so-called high-pressure dome shape, the lubricating oil in the oil sump is compressed by the compression mechanism (50). ) Is heated by the high-temperature and high-pressure gas refrigerant discharged from). Therefore, the lubricating oil supplied to the expansion mechanism (60) has a relatively high temperature. On the other hand, the temperature of the refrigerant flowing into the expansion mechanism (60) is relatively low because the refrigerant circuit (20) performs a refrigerant vapor compression refrigeration cycle.
- the seal mechanism (90) suppresses the inflow of the lubricating oil into the fluid chamber (65), so that the low-temperature refrigerant in the fluid chamber (65) is replaced with the high-temperature lubricating oil. Since the mixture is not heated, the heat loss in the expansion process can be suppressed.
- the lip seal (92) is formed of a four-component modified styrene-based resin material having excellent wear resistance and heat resistance, the front head (67) is rotated by the rotation of the rotary piston (67). High sealing performance can be ensured even when sliding with 61) or rear head (62).
- the provision of (90) makes it possible to prevent the lubricating oil supplied to the sliding portions ( ⁇ , ⁇ ) of the expansion mechanism (60) from leaking into the fluid chamber (65). Thereby, the lubricating oil hardly flows out of the compression / expansion unit (30) together with the refrigerant. Therefore, it is possible to suppress oil rising to the refrigerant circuit (20), to eliminate a shortage of lubricating oil in the expansion mechanism (60), and to suppress a decrease in performance of each heat exchange (23, 24). . As a result, the reliability of the device can be improved.
- the lubricating oil in the oil reservoir is relatively high.
- the refrigerant circuit (20) where the vapor compression refrigeration cycle is performed the refrigerant flowing into the expansion mechanism (60) has a relatively low temperature, but the lubrication into the fluid chamber (65) is performed as described above.
- the lip seal (92) is used as the seal member, the opening of the lip seal (92) is expanded by the pressure action of the lubricating oil, and the lip seal (92) is connected to the front head (
- the lip seal (92) is made of a four-part modified titanium-based resin material having excellent wear resistance and heat resistance, the front head accompanying the rotational movement of the rotary piston (67) is formed. (61) or high sliding performance can be ensured in sliding with the rear head (62).
- the fitting tolerance of the rotary piston (67) in the axial direction of the shaft (40) is set to the dimension of 1Z5000—1Z1000 of the inner diameter of the cylinder (63), the processing accuracy of the rotary piston (67) is improved. ⁇ a It is not necessary to strictly control the standing accuracy, and costs can be reduced.
- the second embodiment uses a tip seal instead of the first embodiment using a lip seal as the seal member (92). That is, in the present embodiment, the seal mechanism (90) includes a seal groove (91) formed on the upper and lower end surfaces (67b, 67c) of the rotary piston (67), and a tip seal fitted into the seal groove (91). (92).
- the tip seal (92) is a type of mechanical seal, and is formed of a metal material such as copper.
- the tip seal (92) has a rectangular cross section, and is formed in an annular shape that is discontinuous in plan view. That is, the tip seal (92) One part of the circumference is cut in the radial direction (see D in Fig. 6). This cutting is performed in such a manner that the tip seal (92) is attached to the seal groove (91) with tension applied thereto, and the tip seal (92) is extended radially outward after the attachment. .
- the tip seal (92) is formed of a metal material, but may be formed of a tetrafluoroplastic styrene-based resin material as in the first embodiment. . In that case, the tip seal (92) is formed in a continuous annular shape without cutting.
- the third embodiment is different from the second embodiment in that the shapes of the seal groove (91) and the tip seal (92) are changed. That is, the seal groove (91) of the present embodiment is formed in a C shape in which one portion of the annular seal groove (91) in the second embodiment is omitted. Similarly, the tip seal (92) is formed in a C shape in plan view according to the seal groove (91). The seal groove (91) is formed so that the portion (C) corresponding to the C-shaped opening faces the high pressure chamber (66a) side of the fluid chamber (65).
- the seal groove (91) is formed in a C shape
- the tip seal (92) is displaced in the seal groove (91) in the circumferential direction due to the sliding caused by the rotation of the shaft (40). Or not.
- the portion (C) corresponding to the C-shaped opening always faces the high-pressure chamber (66a), Leakage of the lubricating oil into the fluid chamber (65) can be reliably suppressed.
- Other configurations, operations, and effects are the same as those of the second embodiment.
- Embodiment 4 is a modification of the cutting mode of the tip seal (92) in Embodiment 2 described above.
- a force that cuts one portion of the tip seal (92) in a straight line in the radial direction is used.
- one portion of the tip seal (92) is cut in a step shape (see the section D).
- a cutting margin (D) is provided with an overlap margin.
- the tip seal (92) is cut in a step shape.
- the tip seal (92) may be cut in a straight line inclining with respect to the radial direction. That is, the tip seal (92) may be cut so that the cut shape is tapered.
- any cutting form may be used so that an overlap margin is formed at the cutting portion (D).
- Embodiment 5 is different from Embodiment 1 in that the seal mechanism (90) is constituted by a seal groove (91) and a seal member (92).
- the seal mechanism (90) is constituted by only a plurality of seal grooves (93). That is, the sealing mechanism (90) of the present embodiment is configured as a labyrinth seal.
- the labyrinth seal (90) is constituted by three seal grooves (93).
- the three seal grooves (93) are formed on both upper and lower end surfaces (67b, 67c) of the rotary piston (67).
- the above-mentioned three seal grooves (93) are similar in shape to the seal groove (91) in the first embodiment, have different diameters from each other, and are formed three times in the radial direction of the rotary piston (67). I have.
- both upper and lower end faces (67b, 67c) of the rotary piston (67) and the rear head (62) are formed by a labyrinth effect such as a friction effect due to the viscosity of the lubricating oil and a contraction effect at the throttle opening.
- a labyrinth effect such as a friction effect due to the viscosity of the lubricating oil and a contraction effect at the throttle opening.
- the front head (61) are sealed.
- the omission of the seal member (92) itself and the step of assembling the seal member (92) can be omitted, so that cost reduction can be achieved.
- Other configurations, operations, and effects are the same as those of the first embodiment.
- the labyrinth seal (90) is constituted by three seal grooves (93), and the cross-sectional shape of the seal groove (93) is rectangular. Any number and cross-sectional shape may be used as long as the range can be exhibited.
- the configuration of the expansion mechanism (60) according to the first embodiment is changed, and the installation position of the seal mechanism (90) is changed.
- the present embodiment uses a two-cylinder expansion mechanism (60).
- the shaft (40) has two large-diameter eccentric portions (41, 42) formed on the upper end side.
- the lower one constitutes the first large-diameter eccentric portion (41)
- the upper one constitutes the second large-diameter eccentric portion (42)! /
- the eccentric directions of the main shaft portion (44) with respect to the axis are reversed.
- the expansion mechanism (60) includes two pairs of a pair of cylinders (71, 81) and rotary pistons (75, 85), a front head (61), an intermediate plate (64), and a rear head ( 62).
- the front head (61), the first cylinder (71), the intermediate plate (64), the second cylinder (81), and the rear head (62) are stacked in that order in the downward direction as well.
- the first cylinder (71) has a lower end face closed by a front head (61) and an upper end face closed by an intermediate plate (64).
- the second cylinder (81) has a lower end face closed by an intermediate plate (64), and an upper end face closed by a rear head (62).
- the first cylinder (71) and the second cylinder (81) have the same inner diameter.
- the shaft (40) includes a front head (61), a first cylinder (71), It passes through the plate (64), the second cylinder (81) and the rear head (62).
- the first large-diameter eccentric portion (41) of the shaft (40) is located in the first cylinder (71), and the second large-diameter eccentric portion (42) of the shaft (40) is located in the second cylinder (81). )
- a first rotary piston (75) is provided in the first cylinder (71).
- a second rotary piston (85) is provided in the second cylinder (81).
- Both the first cylinder (71) and the second cylinder (81) are formed in an annular or cylindrical shape, and have the same outer diameter.
- a first large-diameter eccentric portion (41) is rotatably fitted to the first rotary piston (75), and a second large-diameter eccentric portion (42) is fitted to the second rotary piston (85).
- the first rotary piston (75) has an outer peripheral surface slidably in contact with an inner peripheral surface of the first cylinder (71), a lower end surface (75c) of the first rotary piston (75) and the upper end surface (75b) of the front head (61). Are in sliding contact with the intermediate plate (64), respectively.
- a first fluid chamber (72) is formed between the inner peripheral surface and the outer peripheral surface of the first rotary piston (75).
- the second rotary piston (85) the outer peripheral surface is in sliding contact with the inner peripheral surface of the second cylinder (81), the upper end surface (85b) is in contact with the rear head (62), and the lower end surface (85c) is in the middle. It is in sliding contact with each plate (64).
- a second fluid chamber (82) is formed between the inner peripheral surface and the outer peripheral surface of the second rotary piston (85).
- the intermediate plate (64) forms an intermediate partition plate for separating the inside of the first cylinder (71) and the inside of the second cylinder (81). .
- Each of the one-way pistons (75, 85) is connected by one shaft (40) and arranged in order, and the end faces (75b, 85c) of the adjacent rotary pistons (75, 85) are They are arranged to face each other via the intermediate plate (64).
- the front head (61) has a first inflow port (34a) communicating with the high-pressure chamber of the first fluid chamber (72), and the rear head (62) has a second fluid chamber (82). ), A second inflow port (34b) communicating with the high-pressure chamber is formed.
- each of the cylinders (71, 81) is formed with an outflow port (35) communicating with the low pressure chamber of each of the fluid chambers (72, 82).
- Each of the lower end surface (75c) of the first rotary piston (75) and the upper end surface (85b) of the first rotary piston (75) is provided with a seal mechanism (90). That is, the sealing mechanism (90) is provided with a front head (a closing member) of the end faces of the rotary pistons (75, 85). 61) and end faces (75c, 85b) facing the rear head (62).
- the configuration of the seal mechanism (90) is the same as that of the first embodiment.
- a seal mechanism (90) is provided when excessive oil is supplied in each cylinder (71, 81), and the seal mechanism (90 ).
- the pressure higher than the pressure of the lubricating oil acting on the end face (75b, 85c) on the intermediate plate (64) side acts, and the tally pistons (75, 85) at each port
- the intermediate plate (64) is pushed toward the intermediate plate (64) and becomes almost in close contact with the intermediate plate (64). Thereby, between the front head (61), the rear head (62), and the intermediate plate (64) on the upper and lower end surfaces (75b, 75c, 85b, 85c) of each rotary piston (75, 85) are sealed.
- the seal mechanism (90) is not provided on the end surface (75b, 85c) on the intermediate plate (64) side of each rotary piston (75, 85), the shaft (40) of the intermediate plate (64) is not provided. ), The lip seal (92) can be prevented from being inserted into the through hole (64a), and the sealing property can be ensured.
- Other configurations, operations, and effects are the same as those of the first embodiment.
- the present invention may be configured as follows in each of the above embodiments.
- a pair of the seal groove (91) and the tip seal (92) are provided on both upper and lower end surfaces (67b, 67c) of the rotary piston (67). As shown in FIG. 13, two pairs may be provided and two seals may be provided. In this case, the sealing performance can be further ensured.
- a force for providing the seal mechanism (90) on both end faces (67b, 67c) of the rotary piston (67) may be provided on any one of the end faces. .
- the same sealing effect as in the sixth embodiment can be obtained. That is, in the present invention, the seal mechanism (90) may be provided on at least one of both end faces (67b, 67c) of the rotary piston (67).
- the seal member (92) may be made of a material other than the tetrafluoroethylene-based resin material.
- the present invention provides a rotor that generates power by expansion of a high-pressure fluid. Useful as a re-expander.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Sealing With Elastic Sealing Lips (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Sealing Devices (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2005220502A AU2005220502B2 (en) | 2004-03-16 | 2005-03-15 | Rotary expander |
EP05720759A EP1726779A4 (en) | 2004-03-16 | 2005-03-15 | ROTATION EXPANSION MACHINE |
US10/592,869 US20080274001A1 (en) | 2004-03-16 | 2005-03-15 | Rotary Expander |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004074454A JP2005264748A (ja) | 2004-03-16 | 2004-03-16 | ロータリ式膨張機 |
JP2004-074454 | 2004-03-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005088079A1 true WO2005088079A1 (ja) | 2005-09-22 |
Family
ID=34975641
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/004502 WO2005088079A1 (ja) | 2004-03-16 | 2005-03-15 | ロータリ式膨張機 |
Country Status (7)
Country | Link |
---|---|
US (1) | US20080274001A1 (ja) |
EP (1) | EP1726779A4 (ja) |
JP (1) | JP2005264748A (ja) |
KR (1) | KR100810407B1 (ja) |
CN (1) | CN100434656C (ja) |
AU (1) | AU2005220502B2 (ja) |
WO (1) | WO2005088079A1 (ja) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
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AU2007218986A1 (en) | 2006-02-22 | 2007-08-30 | Peraves Ag | Sealing system for an oscillating-piston engine |
JP4830565B2 (ja) * | 2006-03-17 | 2011-12-07 | ダイキン工業株式会社 | 流体機械 |
EP2224095A4 (en) * | 2007-11-21 | 2012-11-07 | Panasonic Corp | COMPRESSOR WITH INTEGRATED REGULATOR |
JP2009186064A (ja) * | 2008-02-05 | 2009-08-20 | Daikin Ind Ltd | 膨張機及び冷凍装置 |
JP2009215985A (ja) * | 2008-03-11 | 2009-09-24 | Daikin Ind Ltd | 膨張機 |
CN102192149B (zh) * | 2010-03-10 | 2013-03-13 | 广东美芝制冷设备有限公司 | 旋转式压缩机 |
CN101864992B (zh) * | 2010-06-18 | 2012-09-19 | 江西华电电力有限责任公司 | 一种螺杆膨胀动力机的机械密封结构 |
CN102444581A (zh) * | 2010-09-30 | 2012-05-09 | 广东美芝制冷设备有限公司 | 一种旋转式压缩机 |
JP5370450B2 (ja) | 2011-09-28 | 2013-12-18 | ダイキン工業株式会社 | 圧縮機 |
JP5994596B2 (ja) * | 2012-11-21 | 2016-09-21 | ダイキン工業株式会社 | ロータリ式膨張機 |
CN104632288A (zh) * | 2014-01-09 | 2015-05-20 | 摩尔动力(北京)技术股份有限公司 | 圆形缸轴向隔离同轮控制流体机构及包括其的装置 |
CN105179234B (zh) * | 2015-09-29 | 2018-03-13 | 中国石油天然气股份有限公司 | 气液混输装置 |
EP3546699B1 (en) * | 2016-11-22 | 2021-07-21 | Eagle Industry Co., Ltd. | Sealing member |
WO2018165455A1 (en) | 2017-03-09 | 2018-09-13 | Johnson Controls Technology Company | Back to back bearing sealing systems |
CN110062859A (zh) * | 2017-08-24 | 2019-07-26 | 国立大学法人埼玉大学 | 密封装置 |
CN109372749A (zh) * | 2018-11-06 | 2019-02-22 | 西安理工大学 | 一种罗茨鼓风机转子端面密封结构 |
CN113027600B (zh) * | 2021-03-03 | 2022-04-22 | 李玉春 | 一种三圆同心偏心转子均质压燃发动机 |
WO2023283660A1 (de) * | 2021-07-14 | 2023-01-19 | Ausserer Florian Karl | Rotationskolbenverdichter |
CN113958500B (zh) * | 2021-09-30 | 2022-10-25 | 西安交通大学 | 一种微型容积式液泵 |
DE102022105004A1 (de) * | 2022-03-03 | 2023-09-07 | Carl Freudenberg Kg | Dichtungsanordnung, umfassend einen Axialdichtring |
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- 2005-03-15 US US10/592,869 patent/US20080274001A1/en not_active Abandoned
- 2005-03-15 CN CNB200580008481XA patent/CN100434656C/zh not_active Expired - Fee Related
- 2005-03-15 EP EP05720759A patent/EP1726779A4/en not_active Withdrawn
- 2005-03-15 AU AU2005220502A patent/AU2005220502B2/en not_active Ceased
- 2005-03-15 WO PCT/JP2005/004502 patent/WO2005088079A1/ja active Application Filing
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Also Published As
Publication number | Publication date |
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KR100810407B1 (ko) | 2008-03-04 |
AU2005220502B2 (en) | 2010-05-20 |
EP1726779A4 (en) | 2012-04-04 |
EP1726779A1 (en) | 2006-11-29 |
US20080274001A1 (en) | 2008-11-06 |
CN1934335A (zh) | 2007-03-21 |
AU2005220502A1 (en) | 2005-09-22 |
KR20060127258A (ko) | 2006-12-11 |
CN100434656C (zh) | 2008-11-19 |
JP2005264748A (ja) | 2005-09-29 |
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