US20010043877A1 - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
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- US20010043877A1 US20010043877A1 US09/849,253 US84925301A US2001043877A1 US 20010043877 A1 US20010043877 A1 US 20010043877A1 US 84925301 A US84925301 A US 84925301A US 2001043877 A1 US2001043877 A1 US 2001043877A1
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- scroll
- scrolls
- movable
- fixed
- movable scrolls
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/023—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving
- F04C18/0238—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving with symmetrical double wraps
Definitions
- the present invention relates to a scroll compressor.
- Scroll compressors are known in the art.
- Japanese Patent Laid-Open Publication No.59-65586 discloses a scroll compressor comprising paired fixed and movable scrolls, the fixed scroll of each pair having an end plate provided with a scroll body projecting from the end plate and the movable scroll of each pair having an end plate provided with a scroll body projecting from the end plate, wherein the movable scroll meshes with the fixed scroll to form a plurality of operation chambers between them and revolves relative to the fixed scroll to compress gas in the operation chambers, characterized in that two pairs of fixed and movable scrolls are disposed with back faces of the end plates of the fixed scrolls opposite each other, a main shaft for revolving the movable scrolls passes through the two pairs of fixed and movable scrolls to operatively engage the movable scrolls, and an outlet chamber is disposed between the end plates of the fixed scrolls.
- the main shaft is supported at opposite ends by a housing accommodating the two pairs of fixed and movable scrolls.
- the main shaft is supported at its the other end by a housing accommodating the fixed scroll, the movable scroll and the main shaft. Therefore, the scroll compressor of Japanese Patent Laid-Open Publication No.59-65586 has advantages over the ordinary conventional scroll compressor, including that swirling of the main shaft is restrained, and vibration and noise due to such swirling of the main shaft are restrained.
- the main shaft operatively engages the movable scrolls at the central portions of the scroll bodies. Therefore, heat generated by bearings disposed at the operative engagement points is hard to disperse. As a result, the bearings are liable to heat and the service lives of the bearings are liable to become short.
- the object of the present invention is to overcome the foregoing problems by providing a scroll compressor comprising paired fixed and movable scrolls, the fixed scroll of each pair having an end plate provided with a scroll body projecting from the end plate and the movable scroll of each pair having an end plate provided with a scroll body projecting from the end plate, wherein the movable scroll meshes with the fixed scroll to form a plurality of operation chambers between them and revolves relative to the fixed scroll to compress gas in the operation chambers, characterized in that two pairs of fixed and movable scrolls are disposed with back faces of the end plates of the fixed scrolls opposite each other, a main shaft for revolving the movable scrolls passes through the two pairs of fixed and movable scrolls to operatively engage the movable scrolls, and an outlet chamber is disposed between the end plates of the fixed scrolls.
- a scroll compressor comprising paired fixed and movable scrolls, the fixed scroll of each pair having an end plate provided with a scroll body projecting from the end plate and the movable scroll of each pair having an end plate provided with a scroll body projecting from the end plate, wherein the movable scroll meshes with the fixed scroll to form a plurality of operation chambers between them and revolves relative to the fixed scroll to compress gas in the operation chambers, characterized in that two pairs of fixed and movable scrolls are disposed with back faces of the end plates of the fixed scrolls opposite each other, the movable scrolls are integrally connected with each other, a main shaft for revolving the movable scrolls passes through the two pairs of fixed and movable scrolls to operatively engage the movable scrolls, and an outlet chamber is disposed between the end plates of the fixed scrolls.
- the two movable scrolls integrally connected with each other bear the thrust load accompanying the compression of gas in the operation chambers. Therefore, anti-rotation mechanisms disposed between the end plates of the movable scrolls and a housing accommodating the scrolls and the main shaft do not bear the thrust load. As a result, wear of the anti-rotation mechanisms is minimized and the shortening of the service life of the compressor is minimized. Being free from the thrust load, the anti-rotation mechanisms can be downsized. As a result, the compressor can be downsized.
- the two movable scrolls are integrally connected with each other. Therefore, axial spaces between the fixed scrolls and the movable scrolls of the two pairs of fixed and movable scrolls can be adjusted by a single operation.
- the main shaft operatively engages the movable scrolls at the back faces of the end plates of the movable scrolls.
- the operative engagement points are close to the housing accommodating the two pairs of fixed and movable scrolls. Therefore, heat generated by the bearings at the operative engagement points is able to disperse to outside the compressor. As a result, heating of the bearings at the operative engagement points is suppressed and shortening of the service lives of the bearings is minimized.
- the movable scrolls abut against a housing accommodating the two pairs of fixed and movable scrolls through seal members at peripheral portions of the back faces of the end plates.
- Anti-rotation mechanisms and bearings of the main shaft are disposed between the back faces of the end plates of the movable scrolls and the portions of a housing opposite the back faces of the end plates.
- partitions are formed between the inlet paths of the compressor formed at the side of the scroll bodies of the movable scrolls and the anti-rotation mechanisms, the bearings of the main shaft and the bearings at the operative engagement points. Therefore, powder of abraded materials of the anti-rotation mechanisms and bearings, grease, etc.
- the scroll compressor in accordance with the present invention can be used for compression of clean gas.
- Partitions are formed between the inlet paths of the compressor formed at the side of the scroll bodies of the movable scrolls and the anti-rotation mechanisms, the bearings of the main shaft and the bearings at the operative engagement points. Therefore, gas heated by the anti-rotation mechanisms and bearings to be increased in specific volume is prevented from entering into the operation chambers. As a result, the flow rate of discharged gas from the compressor is prevented from substantial decrease.
- difference in phase angles of 180 degrees is present between scroll bodies of the fixed scrolls.
- the relation r 0 >r>(r 0 ⁇ 0.3 mm) is present between a revolution radius r of the movable scrolls determined by the anti-rotation mechanisms and a revolution radius r 0 of the movable scrolls determined by the scroll bodies of the fixed scrolls and the scroll bodies of the movable scrolls.
- the housing is provided with air holes opposite the back faces of the end plates of the movable scrolls.
- the end plates of the movable scrolls are provided with cooling fins at their back faces.
- the main shaft is provided with balancing weights and axial fans connected to the balancing weights at its portions extending between the back faces of the end plates of the movable scrolls and the portions of the housing opposite the back faces of the end plates.
- the main shaft is provided with balancing weights and centrifugal fans connected to the balancing weights at its portions extending between the back faces of the end plates of the movable scrolls and the portions of the housing opposite the back faces of the end plates.
- the centrifugal fans are provided with deflectors for directing the discharged air parallel to the main shaft.
- centrifugal fans are provided with deflectors for directing the discharged air parallel to the main shaft, the flow rate of air colliding against the end plates of the movable scrolls increases and cooling efficiency of the movable scrolls is enhanced.
- a cooling chamber communicating with the space outside the housing is disposed between the end plates of the fixed scrolls.
- End plates of the fixed scrolls are cooled by airflow induced in the cooling chamber. As a result, thermal deformation of fixed scrolls is restrained and decrease of compression efficiency due to such thermal deformation of fixed scrolls is suppressed.
- the end plates of the fixed scrolls and movable scrolls are disks with their peripheral portions partially cut off arcuately.
- the end plates of fixed scrolls and movable scrolls are usually disks. Portions of the disks radially outside the scroll bodies serve no function. Partial cutting off of the functionless portions of the disks enables downsizing of the compressor.
- FIG. 1 is a side sectional view of a scroll compressor in accordance with a preferred embodiment of the present invention.
- FIG. 2 is a perspective view of a half of a scroll compressor in accordance with a preferred embodiment of the present invention.
- FIG. 3 is a perspective view of a half of a scroll compressor in accordance with a preferred embodiment of the present invention.
- FIGS. 1 to 3 A scroll compressor in accordance with a preferred embodiment of the present invention will be described referring to FIGS. 1 to 3 .
- a scroll compressor in accordance with the present embodiment is provided with a scroll assembly 4 comprising a fixed scroll 1 having an end plate 1 a and a scroll body 1 b projecting from the end plate 1 a and a movable scroll 2 having an end plate 2 a and a scroll body 2 b projecting from the end plate 2 a .
- the movable scroll 2 meshes with the fixed scroll 1 to form a plurality of operation chambers 3 between them.
- the scroll compressor is also provided with a scroll assembly 24 comprising a fixed scroll 21 having an end plate 21 a and a scroll body 21 b projecting from the end plate 21 a and a movable scroll 22 having an end plate 22 a and a scroll body 22 b projecting from the end plate 22 a .
- the movable scroll 22 meshes with the fixed scroll 21 to form a plurality of operation chambers 23 between them.
- the back face of the end plate 1 a of the fixed scroll 1 faces the back face of the end plate 21 a of the fixed scroll 21 .
- the end plate 1 a of the fixed scroll 1 is provided with a discharge hole 1 c at its center and the end plate 21 a of the fixed scroll 21 is provided with a discharge hole 21 c at its center.
- the end plates 1 a , 21 a of the fixed scrolls 1 , 21 and the end plates 2 a , 22 a of the movable scrolls 2 , 22 are disks with their peripheral portions radially outside the scroll bodies 1 b , 21 b , 2 b and 22 b partially cut off arcuately.
- a center block 5 is disposed between the end plate 1 a of the fixed scroll 1 and the end plate 21 a of the fixed scroll 21 .
- the fixed scroll 1 , the center block 5 and the fixed scroll 21 are integrally connected with each other by a plurality of bolts 6 . Difference in phase angles of 180 degrees is present between the scroll body 1 b of the fixed scroll 1 and the scroll body 21 b of the fixed scroll 21 .
- the center block 5 is provided with a pair of arcuate holes 5 a .
- the movable scroll 2 and the movable scroll 22 are integrally connected with each other by a plurality of connecting rods 7 movably passing through the arcuate holes 5 a and a plurality of bolts 8 passing through the connecting rods 7 .
- Difference in phase angles of 180 degrees is present between the scroll body 2 b of the movable scroll 2 and the scroll body 1 b of the fixed scroll 1 .
- Difference in phase angles of 180 degrees is present between the scroll body 22 b of the movable scroll 22 and the scroll body 21 b of the fixed scroll 21 .
- a front housing 9 abuts against the center block 5 .
- the front housing 9 cooperates with the center block 5 to form a housing for accommodating the scroll assembly 4 .
- a rear housing 29 also abuts against the center block 5 .
- the rear housing 29 cooperates with the center block 5 to form a housing for accommodating the scroll assembly 24 .
- the front housing 9 , the center block 5 and the rear housing 29 are integrally connected with each other by a plurality of bolts 10 .
- An annular seal member 11 a is embedded in a peripheral portion 2 a 1 of the end plate 2 a of the movable scroll 2 .
- the seal member 11 a projects from the peripheral portion 2 a 1 and abuts against the front housing 9 to be able to slide.
- An annular seal member 31 a is embedded in a peripheral portion 22 a 1 of the end plate 22 a of the movable scroll 22 .
- the seal member 31 a projects from the peripheral portion 22 a 1 and abuts against the rear housing 29 to be able to slide.
- the front housing 9 is provided with air holes 9 a and 9 b at its portion opposite the back face of the end plate 2 a of the movable scroll 2 .
- the rear housing 29 is provided with air holes 29 a and 29 b at its portion opposite the back face of the end plate 22 a of the movable scroll 22 .
- the end plates 2 a and 22 a of the movable scrolls 2 and 22 are provided with a plurality of radially extending cooling fins 2 c and 22 c at their back faces.
- a shaft 12 passes into and extends through the front housing 9 .
- the shaft 12 has a large diameter portion 12 a extending in the front housing 9 .
- the large diameter portion 12 a is supported to be rotatable by the front housing 9 through a bearing 13 a.
- a shaft 32 passes into and extends through the rear housing 29 .
- the shaft 32 has a large diameter portion 32 a extending in the rear housing 29 .
- the large diameter portion 32 a is supported to be rotatable by the rear housing 29 through a bearing 33 a.
- the large diameter portion 12 a is integrally connected to the large diameter portion 32 a by an offset shaft 14 .
- the offset shaft 14 passes through the fixed scrolls 1 and 21 and the movable scrolls 2 and 22 .
- the shaft 12 , the offset shaft 14 and the shaft 32 cooperate to form a main shaft.
- a bush 15 fits on the offset shaft 14 to be able to slide around the offset shaft 14 .
- the bush 15 is accommodated in a boss 2 d formed in the back face of the end plate 2 a of the movable scroll 2 through a bearing 13 b .
- the offset shaft 14 operatively engages the movable scroll 2 through the bush 15 , the bearing 13 b and the boss 2 d.
- a bush 35 fits on the offset shaft 14 to be able to slide around the offset shaft 14 .
- the bush 35 is accommodated in a boss 22 d formed in the back face of the end plate 22 a of the movable scroll 22 through a bearing 33 b .
- the offset shaft 14 operatively engages the movable scroll 22 through the bush 35 , the bearing 33 b and the boss 22 d.
- An anti-rotation mechanism 16 is disposed between the movable scroll 2 and the front housing 9 opposite the movable scroll 2 .
- the anti-rotation mechanism 16 comprises a plurality of bearings and an auxiliary crank.
- An anti-rotation mechanism 36 is disposed between the movable scroll 22 and the rear housing 29 opposite the movable scroll 22 .
- the anti-rotation mechanism 36 comprises a plurality of bearings and an auxiliary crank.
- the anti-rotation mechanism 16 is offset circumferentially by about 90 degrees from the anti-rotation mechanism 36
- a balancing weight 17 is fixed to the large diameter portion 12 a of the shaft 12 .
- the balancing weight 17 is provided with a centrifugal fan 18 .
- the centrifugal fan 18 is provided with a deflector 18 a for directing discharged air parallel to the main shaft and to the end plate 2 a of the movable scroll 2 .
- a balancing weight 37 is fixed to the large diameter portion 32 a of the shaft 32 .
- the balancing weight 37 is provided with a centrifugal fan 38 .
- the centrifugal fan 38 is provided with a deflector 38 a for directing discharged air parallel to the main shaft and to the end plate 22 a of the movable scroll 22 .
- the end plate 1 a of the fixed scroll 1 is provided with a boss 1 d surrounding the offset shaft 14 .
- An annular seal member 11 b is embedded in the end face of the boss 1 d .
- the seal member 11 b projects from the end face of the boss 1 d and abuts against the end plate 2 a of the movable scroll 2 to be able to slide.
- the end plate 21 a of the fixed scroll 21 is provided with a boss 21 d surrounding the offset shaft 14 .
- An annular seal member 31 b is embedded in the end face of the boss 21 d .
- the seal member 31 b projects from the end face of the boss 21 d and abuts against the end plate 22 a of the movable scroll 22 to be able to slide.
- the center block 5 is provided with an inlet port 5 b communicating with the arcuate hole 5 a .
- the center block 5 is provided with a boss 5 c surrounding the offset shaft 14 .
- the center block 5 is provided with a cylindrical portion 5 d radially outside the boss 5 c .
- the cylindrical portion 5 d is made integral with the boss 5 c and extends coaxially with the boss 5 c .
- the center block 5 is provided with an outlet chamber 5 e between the boss 5 c and the cylindrical portion 5 d .
- the outlet chamber 5 e communicates with the discharge hole 1 c of the fixed scroll 1 and the discharge hole 21 c of the fixed scroll 21 .
- the center block 5 is provided with an outlet port 5 f .
- the outlet chamber 5 e communicates with the outlet port 5 f through a cylindrical portion 5 g .
- the center block 5 is provided with a cooling chamber 5 h radially outside the cylindrical portion 5 d and between the end plate 1 a of the fixed scroll 1 and the end plate 21 a of the fixed scroll 21 .
- the cooling chamber 5 h communicates with the space outside the center block 5 through an air hole 5 i.
- the shaft 12 is rotated around the central axis X by a driving means not shown in FIGS. 1 to 3 .
- the offset shaft 14 rotates around the axis X accompanying the shaft 12 .
- Rotation of the offset shaft 14 is transmitted to the movable scrolls 2 and 22 operatively engaging the offset shaft 14 through the bushes 15 and 35 .
- the movable scrolls 2 and 22 integrally connected with each other revolve around the axis X.
- Gas is taken into the compressor through the inlet port 5 b and then into the operation chambers 3 and 23 .
- the operation chambers 3 and 23 approach the center of the fixed scrolls 1 and 21 with their volume gradually decreasing.
- the gas in the operation chambers 3 and 23 is compressed.
- the compressed gas discharges into the outlet chamber 5 e through the discharge holes 1 c and 21 c of the end plates 1 a and 21 a of the fixed scrolls 1 and 21 and discharges from the compressor through the outlet port 5 f.
- the movable scrolls 2 and 22 are allowed to revolve but are prevented from rotation by the anti-rotation mechanisms 16 and 36 .
- the movable scrolls 2 and 22 integrally connected with each other bear the thrust load accompanying the compression of gas in the operation chambers 3 and 23 . Therefore, the anti-rotation mechanism 16 disposed between the end plate 2 a of the movable scroll 2 and the front housing 9 opposite the end plate 2 a does not bear the thrust load. Similarly, the anti-rotation mechanism 36 disposed between the end plate 22 a of the movable scroll 22 and the rear housing 29 opposite the end plate 22 a does not bear the thrust load. As a result, wear of the anti-rotation mechanisms 16 and 36 is minimized and decrease of service life of the compressor is minimized. Being free from the thrust load, the anti-rotation mechanisms 16 and 36 can be downsized. As a result, the compressor can be downsized.
- the fixed scrolls 1 and 21 are integrally connected with each other and the movable scrolls 2 and 22 are integrally connected with each other. Therefore, axial space between the fixed scroll 1 and the movable scroll 2 and the axial space between the fixed scroll 21 and the movable scroll 22 can be adjusted by a single operation of adjusting the length of the connecting rods 7 integrally connecting the movable scrolls 2 and 22 or of adjusting the thickness of shims inserted between end faces of the connecting rods 7 and the movable scrolls 2 and 22 .
- the bushes 15 and 35 , the bearings 13 b and 33 b and the bosses 2 d and 22 d constituting the operative engagement points between the offset shaft 14 and the movable scrolls 2 and 22 are disposed at the back faces of the end plates 2 a and 22 a of the movable scrolls 2 and 22 .
- these members are close to the front housing 9 and the rear housing 29 . Therefore, heat generated by the bearings 13 b and 33 b at the operative engagement points easily disperses to the outside the compressor through the front housing 9 and the rear housing 29 . As a result, heating of the bearings 13 b and 33 b is minimized and decrease of the service lives of the bearings 13 b and 33 b is minimized.
- the end plates 2 a and 22 a abut against the front housing 9 and the rear housing 29 at peripheral portions 2 a 1 and 22 a 1 of their back faces through the seal members 11 a and 31 a .
- partitions are formed between the inlet paths of the compressor formed at the side of the scroll bodies 2 b and 22 b of the movable scrolls 2 and 22 and the anti-rotation mechanisms 16 and 36 , and the bearings 13 a , 33 a , 13 b and 33 b . Therefore, powder of abraded materials of the anti-rotation mechanisms 16 and 36 , and the bearings 13 a , 33 a , 13 b and 33 b , grease, etc. are prevented from entering into the operation chambers 3 and 23 and discharged gas from the compressor is prevented from contamination by the powder of abraded materials, grease, etc.
- the scroll compressor of the present embodiment can be used for compression of clean gas.
- Partitions are formed between the inlet paths of the compressor formed at the side of the scroll bodies 2 b and 22 b of the movable scrolls 2 and 22 and the anti-rotation mechanisms 16 and 36 , and the bearings 13 a , 33 a , 13 b and 33 b . Therefore, gas heated by the anti-rotation mechanisms 16 and 36 , and the bearings 13 a , 33 a , 13 b and 33 b , to be increased in specific volume is prevented from entering into the operation chambers 3 and 23 . As a result, flow rate of discharged gas from the compressor is prevented from substantial decrease.
- difference in phase angles of 180 degrees is present between the scroll bodies 1 b and 21 b of the fixed scrolls 1 and 21 .
- difference in phase angles of 180 degrees is generated between pulsation of discharged gas from the paired fixed scroll 1 and movable scroll 2 and pulsation of discharged gas from the paired fixed scroll 21 and movable scroll 22 . Therefore, the pulsations of the two discharged gases cancel each other and noise due to the pulsation of discharged gas is prevented from generation.
- difference in phase angles of 180 degrees is generated between pulsation of intake gas into the paired fixed scroll 1 and movable scroll 2 and pulsation of intake gas into the paired fixed scroll 21 and movable scroll 22 . Therefore, the pulsations of the two intake gases cancel each other and noise due to the pulsation of intake gas is prevented from generation.
- the relation r 0 >r is present between a revolution radius r of the movable scrolls 2 and 22 determined by the anti-rotation mechanisms 16 and 36 and a revolution radius r 0 of the movable scrolls 2 and 22 determined by the scroll bodies 1 b and 21 b of the fixed scrolls 1 and 21 and the scroll bodies 2 b and 22 b of the movable scrolls 2 and 22 .
- the relation r>(r 0 ⁇ 0.3 mm) is present between the revolution radiuses r and r 0 . As a result, decrease of compression efficiency is prevented.
- the end plates 2 a and 22 a of the movable scrolls 2 and 22 are provided with cooling fins 2 c and 22 c at their back faces.
- cooling efficiencies of the movable scrolls 2 and 22 , the anti-rotation mechanisms 16 and 36 , and the bearings 13 a , 13 b , 33 a and 33 b are enhanced.
- the balancing weights 17 and 37 are provided with centrifugal fans 18 and 38 . Therefore, external air is taken into the front housing 9 and the rear housing 29 through the air holes 9 a , 9 b , 29 a and 29 b . As a result, cooling efficiencies of the movable scrolls 2 and 22 , the anti-rotation mechanisms 16 and 36 , and the bearings 13 a , 13 b , 33 a and 33 b are enhanced.
- discharged airs from the centrifugal fans 18 and 38 are directed to the end plates 2 a and 22 a of the movable scrolls 2 and 22 by the deflectors 18 a and 38 a .
- flow rates of the airs colliding against the end plates 2 a and 22 a of the movable scrolls 2 and 22 increase and cooling efficiencies of the movable scrolls 2 and 22 are enhanced.
- the balancing weights 17 and 37 may be provided with axial fans instead of the centrifugal fans 18 and 38 .
- the cooling chamber 5 h communicating with space outside the housing of the compressor is disposed between the end plates 1 a and 21 a of the fixed scrolls 1 and 21 . Therefore, the end plates 1 a and 21 a of the fixed scrolls 1 and 21 are cooled by the airflow taken into the cooling chamber 5 h . As a result, thermal deformations of the fixed scrolls 1 and 21 are restrained and decrease of compression efficiency due to such thermal deformations of the fixed scrolls 1 and 21 is suppressed.
- the difference in phase angles between the scroll bodies 1 b and 21 b of the fixed scrolls 1 and 21 need not be strictly 180 degrees. It may be larger or smaller than 180 degrees to some extent.
- the difference in phase angles between the scroll bodies 2 b , 22 b of the movable scrolls 2 , 22 and the scroll bodies 1 b , 21 b of the fixed scrolls 1 , 21 need not be strictly 180 degrees. It may be larger or smaller than 180 degrees to some extent.
- the numeral in the relation between r and r 0 need not be strictly 0.3. It may slightly deviate from 0.3.
Abstract
Description
- The present invention relates to a scroll compressor.
- Scroll compressors are known in the art. For example, Japanese Patent Laid-Open Publication No.59-65586 discloses a scroll compressor comprising paired fixed and movable scrolls, the fixed scroll of each pair having an end plate provided with a scroll body projecting from the end plate and the movable scroll of each pair having an end plate provided with a scroll body projecting from the end plate, wherein the movable scroll meshes with the fixed scroll to form a plurality of operation chambers between them and revolves relative to the fixed scroll to compress gas in the operation chambers, characterized in that two pairs of fixed and movable scrolls are disposed with back faces of the end plates of the fixed scrolls opposite each other, a main shaft for revolving the movable scrolls passes through the two pairs of fixed and movable scrolls to operatively engage the movable scrolls, and an outlet chamber is disposed between the end plates of the fixed scrolls.
- In this known scroll compressor, the main shaft is supported at opposite ends by a housing accommodating the two pairs of fixed and movable scrolls. In the ordinary conventional scroll compressor comprising a pair of fixed and movable scrolls, and a main shaft operatively engaging the movable scroll at its one end, the main shaft is supported at its the other end by a housing accommodating the fixed scroll, the movable scroll and the main shaft. Therefore, the scroll compressor of Japanese Patent Laid-Open Publication No.59-65586 has advantages over the ordinary conventional scroll compressor, including that swirling of the main shaft is restrained, and vibration and noise due to such swirling of the main shaft are restrained.
- However, the scroll compressor of Japanese Patent Laid-Open Publication No.59-65586 has following disadvantages.
- 1. Two movable scrolls are independent of each other. Therefore, anti-rotation mechanisms disposed between the end plates of the movable scrolls and the housing accommodating the scrolls are exposed to thrust load due to the compression of gas in the compression chambers, which causes them to wear and shorten the service life of the compressor. Downsizing of the compressor is difficult because downsizing of the ant-rotation mechanisms exposed to the thrust load is difficult
- 2. Also owing to the fact that two movable scrolls are independent of each other, adjustment of axial space between the fixed scroll and the movable scroll of one of the two pairs of fixed and movable scrolls must be carried out independently from the adjustment of axial space between the fixed and movable scrolls of the other of the two pairs of fixed and movable scrolls.
- 3. The main shaft operatively engages the movable scrolls at the central portions of the scroll bodies. Therefore, heat generated by bearings disposed at the operative engagement points is hard to disperse. As a result, the bearings are liable to heat and the service lives of the bearings are liable to become short.
- 4. No partition is disposed between bearings at the opposite ends of the main shaft and inlet chambers. Moreover, no partition is disposed between bearings at the operative engagement points and the inlet chambers. Therefore, gas taken into the inlet chambers is contaminated with lubricating oil in the bearings and the discharged gas is contaminated with lubricating oil. Therefore, the scroll compressor is not suitable for the compression of clean gas.
- 5. Also owing to the fact that no partition is disposed between bearings at the opposite ends of the main shaft and inlet chambers and no partition is disposed between bearings at the operative engagement points and the inlet chambers, gas heated by the hot bearings and increased in specific volume is taken into the operation chambers. As a result, flow rate of discharged gas from the scroll compressor is really low.
- 6. The bearings at the opposite ends of the main shaft and the bearings at the operative engagement points are disposed in substantially closed spaces. Therefore, heat generated by the bearings is hard to disperse, the bearings are liable to heat, and service lives of the bearings are liable to become short.
- Therefore, the object of the present invention is to overcome the foregoing problems by providing a scroll compressor comprising paired fixed and movable scrolls, the fixed scroll of each pair having an end plate provided with a scroll body projecting from the end plate and the movable scroll of each pair having an end plate provided with a scroll body projecting from the end plate, wherein the movable scroll meshes with the fixed scroll to form a plurality of operation chambers between them and revolves relative to the fixed scroll to compress gas in the operation chambers, characterized in that two pairs of fixed and movable scrolls are disposed with back faces of the end plates of the fixed scrolls opposite each other, a main shaft for revolving the movable scrolls passes through the two pairs of fixed and movable scrolls to operatively engage the movable scrolls, and an outlet chamber is disposed between the end plates of the fixed scrolls.
- In accordance with the present invention, there is provided a scroll compressor comprising paired fixed and movable scrolls, the fixed scroll of each pair having an end plate provided with a scroll body projecting from the end plate and the movable scroll of each pair having an end plate provided with a scroll body projecting from the end plate, wherein the movable scroll meshes with the fixed scroll to form a plurality of operation chambers between them and revolves relative to the fixed scroll to compress gas in the operation chambers, characterized in that two pairs of fixed and movable scrolls are disposed with back faces of the end plates of the fixed scrolls opposite each other, the movable scrolls are integrally connected with each other, a main shaft for revolving the movable scrolls passes through the two pairs of fixed and movable scrolls to operatively engage the movable scrolls, and an outlet chamber is disposed between the end plates of the fixed scrolls.
- In the present scroll compressor, the two movable scrolls integrally connected with each other bear the thrust load accompanying the compression of gas in the operation chambers. Therefore, anti-rotation mechanisms disposed between the end plates of the movable scrolls and a housing accommodating the scrolls and the main shaft do not bear the thrust load. As a result, wear of the anti-rotation mechanisms is minimized and the shortening of the service life of the compressor is minimized. Being free from the thrust load, the anti-rotation mechanisms can be downsized. As a result, the compressor can be downsized.
- In the present scroll compressor, the two movable scrolls are integrally connected with each other. Therefore, axial spaces between the fixed scrolls and the movable scrolls of the two pairs of fixed and movable scrolls can be adjusted by a single operation.
- According to a preferred embodiment of the present invention, the main shaft operatively engages the movable scrolls at the back faces of the end plates of the movable scrolls.
- When the main shaft operatively engages the movable scrolls at the back faces of the end plates of the movable scrolls, the operative engagement points are close to the housing accommodating the two pairs of fixed and movable scrolls. Therefore, heat generated by the bearings at the operative engagement points is able to disperse to outside the compressor. As a result, heating of the bearings at the operative engagement points is suppressed and shortening of the service lives of the bearings is minimized.
- According to another preferred embodiment of the present invention, the movable scrolls abut against a housing accommodating the two pairs of fixed and movable scrolls through seal members at peripheral portions of the back faces of the end plates.
- Anti-rotation mechanisms and bearings of the main shaft are disposed between the back faces of the end plates of the movable scrolls and the portions of a housing opposite the back faces of the end plates. When the movable scrolls abut against the portions of the housing through seal members at peripheral portions of the back faces of the end plates, partitions are formed between the inlet paths of the compressor formed at the side of the scroll bodies of the movable scrolls and the anti-rotation mechanisms, the bearings of the main shaft and the bearings at the operative engagement points. Therefore, powder of abraded materials of the anti-rotation mechanisms and bearings, grease, etc. are prevented from entering into the operation chambers and discharged gas from the compressor is prevented from contamination by powder of abraded materials of the anti-rotation mechanisms and bearings, grease, etc. As a result, the scroll compressor in accordance with the present invention can be used for compression of clean gas.
- Partitions are formed between the inlet paths of the compressor formed at the side of the scroll bodies of the movable scrolls and the anti-rotation mechanisms, the bearings of the main shaft and the bearings at the operative engagement points. Therefore, gas heated by the anti-rotation mechanisms and bearings to be increased in specific volume is prevented from entering into the operation chambers. As a result, the flow rate of discharged gas from the compressor is prevented from substantial decrease.
- According to another preferred embodiment of the present invention, difference in phase angles of 180 degrees is present between scroll bodies of the fixed scrolls.
- When difference in phase angles of 180 degrees is present between the scroll bodies of the fixed scrolls, difference in phase angles of 180 degrees is generated between pulsations of discharged gases from the two pairs of fixed and movable scrolls. Therefore, the pulsations of discharged gases cancel each other and generation of noise due to the pulsation of discharged gas is prevented. Moreover, difference in phase angles of 180 degrees is generated between pulsations of intake gases into the two pairs of fixed and movable scrolls. Therefore, the pulsations of intake gases cancel each other and generation of noise due to the pulsation of intake gas is prevented.
- According to another preferred embodiment of the present invention, the relation r0>r>(r0−0.3 mm) is present between a revolution radius r of the movable scrolls determined by the anti-rotation mechanisms and a revolution radius r0 of the movable scrolls determined by the scroll bodies of the fixed scrolls and the scroll bodies of the movable scrolls.
- When r0>r, interferences between the scroll bodies of the fixed scrolls and the scroll bodies of the movable scrolls are prevented and generation of powder of abraded members due to such interferences is prevented. When r>(r0−0.3 mm), decrease of compression efficiency is prevented.
- According to another preferred embodiment of the present invention, the housing is provided with air holes opposite the back faces of the end plates of the movable scrolls.
- When the housing is provided with air holes opposite the back faces of the end plates of the movable scrolls, spaces formed between the back faces of the end plates of the movable scrolls and the housing communicate with the atmosphere through the air holes. Therefore, heat generated by the anti-rotation mechanisms, bearings, etc. disposed in the spaces disperses to the atmosphere through the air holes. As a result, decrease of compression efficiency due to thermal deformation of movable scrolls is prevented and shortening of the service lives of the anti-rotation mechanisms, bearings, etc. due to loss of grease, thermal deformation, etc. is prevented.
- According to another preferred embodiment of the present invention, the end plates of the movable scrolls are provided with cooling fins at their back faces.
- When the end plates of the movable scrolls are provided with cooling fins at their back faces, cooling efficiency of the movable scrolls, anti-rotation mechanisms and bearings is enhanced.
- According to another preferred embodiment of the present invention, the main shaft is provided with balancing weights and axial fans connected to the balancing weights at its portions extending between the back faces of the end plates of the movable scrolls and the portions of the housing opposite the back faces of the end plates.
- According to another preferred embodiment of the present invention, the main shaft is provided with balancing weights and centrifugal fans connected to the balancing weights at its portions extending between the back faces of the end plates of the movable scrolls and the portions of the housing opposite the back faces of the end plates.
- When balancing weights are provided with axial fans or centrifugal fans, cooling efficiency of the movable scrolls, anti-rotation mechanisms and bearings is enhanced.
- According to another preferred embodiment of the present invention, the centrifugal fans are provided with deflectors for directing the discharged air parallel to the main shaft.
- When the centrifugal fans are provided with deflectors for directing the discharged air parallel to the main shaft, the flow rate of air colliding against the end plates of the movable scrolls increases and cooling efficiency of the movable scrolls is enhanced.
- According to another preferred embodiment of the present invention, a cooling chamber communicating with the space outside the housing is disposed between the end plates of the fixed scrolls.
- End plates of the fixed scrolls are cooled by airflow induced in the cooling chamber. As a result, thermal deformation of fixed scrolls is restrained and decrease of compression efficiency due to such thermal deformation of fixed scrolls is suppressed.
- According to another preferred embodiment of the present invention, the end plates of the fixed scrolls and movable scrolls are disks with their peripheral portions partially cut off arcuately.
- The end plates of fixed scrolls and movable scrolls are usually disks. Portions of the disks radially outside the scroll bodies serve no function. Partial cutting off of the functionless portions of the disks enables downsizing of the compressor.
- Further objects, features and advantages of the present invention will become apparent from the Detailed Description of the Preferred Embodiment when read in conjunction with the accompanying drawings.
- The present invention may be more readily understood with reference to the following drawings, in which:
- FIG. 1 is a side sectional view of a scroll compressor in accordance with a preferred embodiment of the present invention.
- FIG. 2 is a perspective view of a half of a scroll compressor in accordance with a preferred embodiment of the present invention; and
- FIG. 3 is a perspective view of a half of a scroll compressor in accordance with a preferred embodiment of the present invention.
- A scroll compressor in accordance with a preferred embodiment of the present invention will be described referring to FIGS.1 to 3.
- A scroll compressor in accordance with the present embodiment is provided with a scroll assembly4 comprising a
fixed scroll 1 having anend plate 1 a and ascroll body 1 b projecting from theend plate 1 a and amovable scroll 2 having anend plate 2 a and ascroll body 2 b projecting from theend plate 2 a. Themovable scroll 2 meshes with the fixedscroll 1 to form a plurality ofoperation chambers 3 between them. - The scroll compressor is also provided with a
scroll assembly 24 comprising a fixedscroll 21 having anend plate 21 a and ascroll body 21 b projecting from theend plate 21 a and amovable scroll 22 having anend plate 22 a and ascroll body 22 b projecting from theend plate 22 a. Themovable scroll 22 meshes with the fixedscroll 21 to form a plurality ofoperation chambers 23 between them. - The back face of the
end plate 1 a of the fixedscroll 1 faces the back face of theend plate 21 a of the fixedscroll 21. Theend plate 1 a of the fixedscroll 1 is provided with adischarge hole 1 c at its center and theend plate 21 a of the fixedscroll 21 is provided with adischarge hole 21 c at its center. - The
end plates end plates movable scrolls scroll bodies - A
center block 5 is disposed between theend plate 1 a of the fixedscroll 1 and theend plate 21 a of the fixedscroll 21. The fixedscroll 1, thecenter block 5 and the fixedscroll 21 are integrally connected with each other by a plurality ofbolts 6. Difference in phase angles of 180 degrees is present between thescroll body 1 b of the fixedscroll 1 and thescroll body 21 b of the fixedscroll 21. - The
center block 5 is provided with a pair ofarcuate holes 5 a. Themovable scroll 2 and themovable scroll 22 are integrally connected with each other by a plurality of connectingrods 7 movably passing through thearcuate holes 5 a and a plurality ofbolts 8 passing through the connectingrods 7. Difference in phase angles of 180 degrees is present between thescroll body 2 b of themovable scroll 2 and thescroll body 1 b of the fixedscroll 1. Difference in phase angles of 180 degrees is present between thescroll body 22 b of themovable scroll 22 and thescroll body 21 b of the fixedscroll 21. - A
front housing 9 abuts against thecenter block 5. Thefront housing 9 cooperates with thecenter block 5 to form a housing for accommodating the scroll assembly 4. - A
rear housing 29 also abuts against thecenter block 5. Therear housing 29 cooperates with thecenter block 5 to form a housing for accommodating thescroll assembly 24. - The
front housing 9, thecenter block 5 and therear housing 29 are integrally connected with each other by a plurality ofbolts 10. - An
annular seal member 11 a is embedded in aperipheral portion 2 a 1 of theend plate 2 a of themovable scroll 2. Theseal member 11 a projects from theperipheral portion 2 a 1 and abuts against thefront housing 9 to be able to slide. - An
annular seal member 31 a is embedded in aperipheral portion 22 a 1 of theend plate 22 a of themovable scroll 22. Theseal member 31 a projects from theperipheral portion 22 a 1 and abuts against therear housing 29 to be able to slide. - The
front housing 9 is provided withair holes end plate 2 a of themovable scroll 2. Therear housing 29 is provided withair holes end plate 22 a of themovable scroll 22. - The
end plates movable scrolls cooling fins - A
shaft 12 passes into and extends through thefront housing 9. Theshaft 12 has a large diameter portion 12 a extending in thefront housing 9. The large diameter portion 12 a is supported to be rotatable by thefront housing 9 through a bearing 13 a. - A
shaft 32 passes into and extends through therear housing 29. Theshaft 32 has alarge diameter portion 32 a extending in therear housing 29. Thelarge diameter portion 32 a is supported to be rotatable by therear housing 29 through a bearing 33 a. - The large diameter portion12 a is integrally connected to the
large diameter portion 32 a by an offsetshaft 14. The offsetshaft 14 passes through the fixedscrolls movable scrolls shaft 12, the offsetshaft 14 and theshaft 32 cooperate to form a main shaft. - A
bush 15 fits on the offsetshaft 14 to be able to slide around the offsetshaft 14. Thebush 15 is accommodated in aboss 2 d formed in the back face of theend plate 2 a of themovable scroll 2 through abearing 13 b. The offsetshaft 14 operatively engages themovable scroll 2 through thebush 15, the bearing 13 b and theboss 2 d. - A
bush 35 fits on the offsetshaft 14 to be able to slide around the offsetshaft 14. Thebush 35 is accommodated in aboss 22 d formed in the back face of theend plate 22 a of themovable scroll 22 through abearing 33 b. The offsetshaft 14 operatively engages themovable scroll 22 through thebush 35, the bearing 33 b and theboss 22 d. - An
anti-rotation mechanism 16 is disposed between themovable scroll 2 and thefront housing 9 opposite themovable scroll 2. Theanti-rotation mechanism 16 comprises a plurality of bearings and an auxiliary crank. - An
anti-rotation mechanism 36 is disposed between themovable scroll 22 and therear housing 29 opposite themovable scroll 22. Theanti-rotation mechanism 36 comprises a plurality of bearings and an auxiliary crank. - The
anti-rotation mechanism 16 is offset circumferentially by about 90 degrees from theanti-rotation mechanism 36 - The relation r0>r>(r0−0.3 mm) is present between a revolution radius r of the
movable scrolls anti-rotation mechanisms movable scrolls scroll bodies scrolls scroll bodies movable scrolls - A balancing
weight 17 is fixed to the large diameter portion 12 a of theshaft 12. The balancingweight 17 is provided with acentrifugal fan 18. Thecentrifugal fan 18 is provided with adeflector 18 a for directing discharged air parallel to the main shaft and to theend plate 2 a of themovable scroll 2. - A balancing
weight 37 is fixed to thelarge diameter portion 32 a of theshaft 32. The balancingweight 37 is provided with acentrifugal fan 38. Thecentrifugal fan 38 is provided with adeflector 38 a for directing discharged air parallel to the main shaft and to theend plate 22 a of themovable scroll 22. - The
end plate 1 a of the fixedscroll 1 is provided with aboss 1 d surrounding the offsetshaft 14. Anannular seal member 11 b is embedded in the end face of theboss 1 d. Theseal member 11 b projects from the end face of theboss 1 d and abuts against theend plate 2 a of themovable scroll 2 to be able to slide. - The
end plate 21 a of the fixedscroll 21 is provided with aboss 21 d surrounding the offsetshaft 14. Anannular seal member 31 b is embedded in the end face of theboss 21 d. Theseal member 31 b projects from the end face of theboss 21 d and abuts against theend plate 22 a of themovable scroll 22 to be able to slide. - The
center block 5 is provided with aninlet port 5 b communicating with thearcuate hole 5 a. Thecenter block 5 is provided with aboss 5 c surrounding the offsetshaft 14. Thecenter block 5 is provided with acylindrical portion 5 d radially outside theboss 5 c. Thecylindrical portion 5 d is made integral with theboss 5 c and extends coaxially with theboss 5 c. Thecenter block 5 is provided with anoutlet chamber 5 e between theboss 5 c and thecylindrical portion 5 d. Theoutlet chamber 5 e communicates with thedischarge hole 1 c of the fixedscroll 1 and thedischarge hole 21 c of the fixedscroll 21. Thecenter block 5 is provided with anoutlet port 5 f. Theoutlet chamber 5 e communicates with theoutlet port 5 f through acylindrical portion 5 g. Thecenter block 5 is provided with acooling chamber 5 h radially outside thecylindrical portion 5 d and between theend plate 1 a of the fixedscroll 1 and theend plate 21 a of the fixedscroll 21. The coolingchamber 5 h communicates with the space outside thecenter block 5 through anair hole 5 i. - The abutting point between the
boss 5 c and theend plate 1 a of the fixedscroll 1 is sealed by theseal member 11 c and the abutting point between theboss 5 c and theend plate 21 a of the fixedscroll 21 is sealed by theseal member 31 c. - In operation, the
shaft 12 is rotated around the central axis X by a driving means not shown in FIGS. 1 to 3. The offsetshaft 14 rotates around the axis X accompanying theshaft 12. Rotation of the offsetshaft 14 is transmitted to themovable scrolls shaft 14 through thebushes movable scrolls inlet port 5 b and then into theoperation chambers operation chambers scrolls operation chambers outlet chamber 5 e through the discharge holes 1 c and 21 c of theend plates scrolls outlet port 5 f. - The
movable scrolls anti-rotation mechanisms - In the scroll compressor of the present embodiment, the
movable scrolls operation chambers anti-rotation mechanism 16 disposed between theend plate 2 a of themovable scroll 2 and thefront housing 9 opposite theend plate 2 a does not bear the thrust load. Similarly, theanti-rotation mechanism 36 disposed between theend plate 22 a of themovable scroll 22 and therear housing 29 opposite theend plate 22 a does not bear the thrust load. As a result, wear of theanti-rotation mechanisms anti-rotation mechanisms - In the scroll compressor of the present embodiment, the fixed
scrolls movable scrolls fixed scroll 1 and themovable scroll 2 and the axial space between the fixedscroll 21 and themovable scroll 22 can be adjusted by a single operation of adjusting the length of the connectingrods 7 integrally connecting themovable scrolls rods 7 and themovable scrolls - In the scroll compressor of the present embodiment, the
bushes bearings bosses shaft 14 and themovable scrolls end plates movable scrolls front housing 9 and therear housing 29. Therefore, heat generated by thebearings front housing 9 and therear housing 29. As a result, heating of thebearings bearings - In the scroll compressor of the preset embodiment, the
end plates front housing 9 and therear housing 29 atperipheral portions seal members scroll bodies movable scrolls anti-rotation mechanisms bearings anti-rotation mechanisms bearings operation chambers - Partitions are formed between the inlet paths of the compressor formed at the side of the
scroll bodies movable scrolls anti-rotation mechanisms bearings anti-rotation mechanisms bearings operation chambers - In the scroll compressor of the present embodiment, the
bosses scrolls end plates movable scrolls seal members bearings operation chambers shaft 14 and contaminate the discharged gas from the compressor. - The abutting points between the
boss 5 c of thecenter block 5 and theend plates scrolls seal members bearings outlet chamber 5 e along the offsetshaft 14 and contaminate the discharged gas from the compressor. - In the scroll compressor of the present embodiment, difference in phase angles of 180 degrees is present between the
scroll bodies scrolls fixed scroll 1 andmovable scroll 2 and pulsation of discharged gas from the paired fixedscroll 21 andmovable scroll 22. Therefore, the pulsations of the two discharged gases cancel each other and noise due to the pulsation of discharged gas is prevented from generation. Moreover, difference in phase angles of 180 degrees is generated between pulsation of intake gas into the pairedfixed scroll 1 andmovable scroll 2 and pulsation of intake gas into the paired fixedscroll 21 andmovable scroll 22. Therefore, the pulsations of the two intake gases cancel each other and noise due to the pulsation of intake gas is prevented from generation. - In the scroll compressor of the present embodiment, the relation r0>r is present between a revolution radius r of the
movable scrolls anti-rotation mechanisms movable scrolls scroll bodies scrolls scroll bodies movable scrolls scroll bodies scrolls scroll bodies movable scrolls - In the scroll compressor of the present embodiment, spaces formed between the back faces of the
end plates movable scrolls housing 9 and therear housing 29 communicate with the atmosphere through theair holes anti-rotation mechanisms bearings air holes movable scrolls anti-rotation mechanisms bearings - In the scroll compressor of the present embodiment, the
end plates movable scrolls cooling fins movable scrolls anti-rotation mechanisms bearings - In the scroll compressor of the present embodiment, the balancing
weights centrifugal fans front housing 9 and therear housing 29 through theair holes movable scrolls anti-rotation mechanisms bearings - In the scroll compressor of the present embodiment, discharged airs from the
centrifugal fans end plates movable scrolls deflectors end plates movable scrolls movable scrolls - The balancing
weights centrifugal fans - In the scroll compressor of the present embodiment, the cooling
chamber 5 h communicating with space outside the housing of the compressor is disposed between theend plates scrolls end plates scrolls cooling chamber 5 h. As a result, thermal deformations of the fixedscrolls scrolls - In the scroll compressor of the present embodiment, functionless portions of the disk-shaped
end plates scrolls scroll bodies end plates movable scrolls scroll bodies - In the above embodiment, the difference in phase angles between the
scroll bodies scrolls - In the above embodiment, the difference in phase angles between the
scroll bodies movable scrolls scroll bodies - In the above embodiment, the numeral in the relation between r and r0 need not be strictly 0.3. It may slightly deviate from 0.3.
- While the present invention has been described with reference to preferred embodiments, one of ordinary skill in the art will recognize that modifications and improvements may be made while remaining within the spirit and scope of the present invention. The scope of the invention is determined solely by the appended claims.
Claims (12)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000-148654 | 2000-05-16 | ||
JP2000148654A JP4424821B2 (en) | 2000-05-16 | 2000-05-16 | Scroll compressor |
Publications (2)
Publication Number | Publication Date |
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US20010043877A1 true US20010043877A1 (en) | 2001-11-22 |
US6379134B2 US6379134B2 (en) | 2002-04-30 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US09/849,253 Expired - Lifetime US6379134B2 (en) | 2000-05-16 | 2001-05-07 | Scroll compressor having paired fixed and moveable scrolls |
Country Status (4)
Country | Link |
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US (1) | US6379134B2 (en) |
JP (1) | JP4424821B2 (en) |
DE (1) | DE10123398B4 (en) |
FR (1) | FR2809141B1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060153705A1 (en) * | 2004-11-10 | 2006-07-13 | Horton W T | Drive shaft for compressor |
Families Citing this family (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES2365399T3 (en) * | 2004-12-22 | 2011-10-03 | Mitsubishi Denki Kabushiki Kaisha | SPIRAL COMPRESSOR |
JP2007198184A (en) * | 2006-01-24 | 2007-08-09 | Sanden Corp | Fluid machine |
US7942655B2 (en) * | 2006-02-14 | 2011-05-17 | Air Squared, Inc. | Advanced scroll compressor, vacuum pump, and expander |
US10221852B2 (en) | 2006-02-14 | 2019-03-05 | Air Squared, Inc. | Multi stage scroll vacuum pumps and related scroll devices |
US10683865B2 (en) | 2006-02-14 | 2020-06-16 | Air Squared, Inc. | Scroll type device incorporating spinning or co-rotating scrolls |
US8668479B2 (en) * | 2010-01-16 | 2014-03-11 | Air Squad, Inc. | Semi-hermetic scroll compressors, vacuum pumps, and expanders |
US8523544B2 (en) | 2010-04-16 | 2013-09-03 | Air Squared, Inc. | Three stage scroll vacuum pump |
JP4973237B2 (en) * | 2006-10-27 | 2012-07-11 | ダイキン工業株式会社 | Rotary fluid machine |
CN100510414C (en) * | 2007-11-08 | 2009-07-08 | 南昌利柯即技术有限公司 | Vortex fluid machinery |
US11047389B2 (en) | 2010-04-16 | 2021-06-29 | Air Squared, Inc. | Multi-stage scroll vacuum pumps and related scroll devices |
US20130232975A1 (en) | 2011-08-09 | 2013-09-12 | Robert W. Saffer | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
US20130236344A1 (en) * | 2012-03-09 | 2013-09-12 | RichStone Limited (Korea) | Scroll fluid machine |
US10508543B2 (en) | 2015-05-07 | 2019-12-17 | Air Squared, Inc. | Scroll device having a pressure plate |
US10865793B2 (en) | 2016-12-06 | 2020-12-15 | Air Squared, Inc. | Scroll type device having liquid cooling through idler shafts |
US10400771B2 (en) | 2016-12-09 | 2019-09-03 | Air Squared, Inc. | Eccentric compensating torsional drive system |
US11454241B2 (en) | 2018-05-04 | 2022-09-27 | Air Squared, Inc. | Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump |
US20200025199A1 (en) | 2018-07-17 | 2020-01-23 | Air Squared, Inc. | Dual drive co-rotating spinning scroll compressor or expander |
US11067080B2 (en) | 2018-07-17 | 2021-07-20 | Air Squared, Inc. | Low cost scroll compressor or vacuum pump |
US11530703B2 (en) | 2018-07-18 | 2022-12-20 | Air Squared, Inc. | Orbiting scroll device lubrication |
US11473572B2 (en) | 2019-06-25 | 2022-10-18 | Air Squared, Inc. | Aftercooler for cooling compressed working fluid |
US11898557B2 (en) | 2020-11-30 | 2024-02-13 | Air Squared, Inc. | Liquid cooling of a scroll type compressor with liquid supply through the crankshaft |
US11885328B2 (en) * | 2021-07-19 | 2024-01-30 | Air Squared, Inc. | Scroll device with an integrated cooling loop |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2153129B2 (en) * | 1971-06-01 | 1974-01-04 | Vulliez Paul | |
JPS5965586A (en) | 1982-10-07 | 1984-04-13 | Nippon Soken Inc | Scroll system pump |
JP3249832B2 (en) * | 1991-11-15 | 2002-01-21 | 株式会社日立製作所 | Scroll compressor |
US5466134A (en) * | 1994-04-05 | 1995-11-14 | Puritan Bennett Corporation | Scroll compressor having idler cranks and strengthening and heat dissipating ribs |
EP0687815B1 (en) * | 1994-06-17 | 1998-11-18 | Asuka Japan Co., Ltd. | Scroll type fluid machine |
DE19528070C2 (en) * | 1995-07-31 | 1999-03-04 | Knorr Bremse Systeme | Spiral compressor with double-sided spiral arrangement |
-
2000
- 2000-05-16 JP JP2000148654A patent/JP4424821B2/en not_active Expired - Fee Related
-
2001
- 2001-05-07 US US09/849,253 patent/US6379134B2/en not_active Expired - Lifetime
- 2001-05-14 DE DE10123398A patent/DE10123398B4/en not_active Expired - Fee Related
- 2001-05-15 FR FR0106371A patent/FR2809141B1/en not_active Expired - Fee Related
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060153705A1 (en) * | 2004-11-10 | 2006-07-13 | Horton W T | Drive shaft for compressor |
Also Published As
Publication number | Publication date |
---|---|
DE10123398A1 (en) | 2001-11-29 |
US6379134B2 (en) | 2002-04-30 |
JP2001323883A (en) | 2001-11-22 |
FR2809141A1 (en) | 2001-11-23 |
DE10123398B4 (en) | 2004-08-26 |
FR2809141B1 (en) | 2006-01-13 |
JP4424821B2 (en) | 2010-03-03 |
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