CN100400887C - Screw compressor - Google Patents
Screw compressor Download PDFInfo
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- CN100400887C CN100400887C CNB2004101048733A CN200410104873A CN100400887C CN 100400887 C CN100400887 C CN 100400887C CN B2004101048733 A CNB2004101048733 A CN B2004101048733A CN 200410104873 A CN200410104873 A CN 200410104873A CN 100400887 C CN100400887 C CN 100400887C
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- clinch
- revolving spiral
- spiral spare
- screw compressor
- fuel feeding
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Abstract
The invetion relates to improve sealing of a compression space, to secure lubricity and cooling of a sliding part and to improve high performance and high reliability in simple constitution. This scroll compressor is constituted by providing a plurality of oil feeding fine pores 120a, b communicating with an oil reservoir in a high pressure space on a lap head end surface without providing a chip seal groove on the lap head end surface of a revolving scroll part 104. Consequently, it is possible to improve the sealing of the compression spaces and to promote lubricity and cooling of the sliding part by pressure-differentially feeding oil to the compression spaces 105a, b in the middle of compression by the plurality of oil feeding fine pores 120a, b.
Description
Technical field
The present invention relates to the screw compressor of use in air conditioner, refrigerating machine etc.
Background technique
Below, with reference to accompanying drawing, the mode to the compression mechanical part fuel feeding (for example, referring to patent documentation 1) in the screw compressor in the past is described.
Figure 14 has shown the longitudinal sectional drawing of the screw compressor in the past of record in patent documentation 1.
As shown in figure 14, the lubricant oil 8 behind the lubricated floating bearing 18 spreads all over the back 5 of revolving spiral spare 2.On the other hand, on the front end of the spiral clinch 2b of revolving spiral spare 2, end of blade seal groove 2c is set, and end of blade Sealing 22 is housed therein.In addition, at the fixing front end of the helical member clinch 1b of helical member 1 end of blade Sealing 21 is housed also.On revolving spiral spare 2, form the intercommunicating pore 2d at the back 5 that is communicated with described end of blade seal groove 2c and revolving spiral spare 2.Because the sectional area by dwindling intercommunicating pore 2d remains on roughly certain degree with the pressure at the back 5 of described revolving spiral spare 2, therefore, lubricants capacity can be remained at desirable state.The lubricant oil 8 that spreads all over the back 5 of revolving spiral spare 2 is supplied to end of blade seal groove 2c by intercommunicating pore 2d, and the 2f of back side portion of end of blade Sealing 22 is self-evident, and until the gap of spiral clinch 2b front end, whole surface is covered by lubricant oil 8.The lubricant oil 8 that overflows around the end of blade Sealing 22 further covered the end of blade Sealing 21 that is arranged on the fixing helical member 1 around.
As a result, owing to the whole surface that has covered end of blade Sealing 21,22 by lubricant oil 8, therefore, can improve sealing, and can also further improve the sliding properties of end of blade Sealing front-end face.In addition, because therefore normal phase supplying lubricating oil 8, can not produce under the situation of frictional heat at end of blade Sealing front end, the normal phase keeps lower temperature, can improve sliding properties.In addition, as shown in the figure,, end of blade Sealing 22 is pressed in the fixedly tooth bottom surface of helical member 1, therefore, can be reduced in the radial leakage of helical member clinch 2b front end with the power of stipulating owing to pass through the pressure of lubricant oil 8.
[patent documentation 1] spy opens flat 6-288361 communique
Summary of the invention
But, there is following problem in above-mentioned structure in the past, that is: owing to being opened in, the intercommunicating pore 2d that is communicated with the head pressure space is communicated with on the end of blade seal groove 2c that sucks the space, therefore, through intercommunicating pore 2d, the result can continuously the fuel delivery corresponding to described pressure difference be supplied in the suction chamber, suck gas owing to the heat loss who produces by high temperature high pressure oil, can reduce volumetric efficiency.
As the countermeasure that it is improved, though reduce the aperture of intercommunicating pore 2d or end of blade seal groove 2c shoaled to reduce fuel delivery by flow path resistance, perhaps shorten end of blade seal groove 2c length so that the end separate with suction chamber, reduce the heat loss, but, in the previous case, can produce the so-called problem that can not fully be sealed in the slit that produces between end of blade seal groove 2c and the end of blade Sealing 22, under latter event, can produce the so-called problem that sucks the reliability aspect of space and Sealing lack of lubrication.
Therefore, at above-mentioned the problems of the prior art, the object of the present invention is to provide the screw compressor that to guarantee high-performance and high reliability.
In order to solve described the problems of the prior art, the present invention is not provided with the end of blade seal groove on the clinch front-end face of revolving spiral spare, but is provided with a plurality of fuel feeding micropores that are communicated with the oily reservoir of high-pressure space on the clinch front-end face.
By described a plurality of fuel feeding micropores, in compression pressing chamber midway, can realize the pressure reduction fuel feeding, and improve the sealing of pressing chamber, simultaneously, can promote the lubricated and cooling of slide part.
In screw compressor of the present invention, the oil by from a plurality of fuel feeding micropores on the overlap joint end that is arranged on revolving spiral spare need not to use the end of blade Sealing, just can realize high-performance and high reliability.
According to the present invention in the 1st embodiment's the screw compressor, make the fixedly helical member of formation vortex clinch on backplate and the clinch interlock each other of revolving spiral spare, thereby form a plurality of pressing chambers, by on the anti-clinch side guard plate surface of described revolving spiral spare, applying certain pressure, thereby the backplate portion of two helical members and clinch front end are in contact with one another, utilization is arranged on the lip-deep rotation limiting component of anti-clinch side guard plate of revolving spiral spare, prevent the rotation of revolving spiral spare, realize rotation motion simultaneously, whereby, from outer circumferential side when volume is reduced at the center, pressing chamber is moved, thereby compress, in described screw compressor, a plurality of fuel feeding micropores that are communicated with the oil measure nonresident portion of high-pressure space are set on the clinch front-end face of revolving spiral spare.According to present embodiment, need not on the clinch front-end face of revolving spiral spare, the end of blade seal groove to be set, by a plurality of fuel feeding micropores are set, just can in compression pressing chamber midway, realize the pressure reduction fuel feeding, and the sealing that improves pressing chamber, thereby can realize high-performance, simultaneously, by promoting the lubricated and cooling of slide part, also can realize high reliability.
The 2nd embodiment of the present invention in the screw compressor according to the 1st embodiment, is communicated with in 1 oil supply gallery in the backplate that a plurality of fuel feeding micropores is collected in be arranged at revolving spiral spare and with this oil supply gallery.Adopt present embodiment,, just can realize the effect identical with the 1st embodiment by manufacturing procedure still less.
The 3rd embodiment of the present invention in the screw compressor according to the 1st embodiment, makes the aperture of a plurality of fuel feeding micropores form different sizes respectively.Adopt present embodiment, can critically control towards the fuel feeding distribution of the pressing chamber of adjacency, and can realize higher performance and the reliability of Geng Gao.
The 4th embodiment of the present invention, in the screw compressor according to the 3rd embodiment, it is more little that the aperture of a plurality of fuel feeding micropores stops side near the clinch coiling more.Adopt present embodiment, stop by the clinch coiling that increases at the pressure reduction at micropore two ends applying resistance on the fuel feeding micropore of side, can suppress to avoid crossing the reduction of thermogenetic volumetric efficiency, and can further improve performance because of refrigerant gas towards the overboost that sucks the space.
The 5th embodiment of the present invention, in the screw compressor according to the 1st embodiment, the length of a plurality of fuel feeding micropores is short more near clinch coiling origination side more.Adopt present embodiment, shortening then more, the peripheral temperature of the fuel feeding micropore of clinch coiling origination side raises more, thereby the clinch front end that can avoid the revolving spiral spare that causes because of thermal expansion is near near the flow passage resistance force of waterproof increase the fuel feeding pore openings end that floor space produced of fixing helical member, thereby can realize higher reliability.
Description of drawings
Fig. 1 is the longitudinal sectional drawing of the present invention the 1st embodiment's screw compressor.
Fig. 2 is the amplification profile of revolving spiral spare in the screw compressor of present embodiment.
Fig. 3 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
Fig. 4 is the amplification profile of revolving spiral spare in the present invention the 2nd embodiment's the screw compressor.
Fig. 5 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
Fig. 6 is the amplification profile of revolving spiral spare in the present invention the 3rd embodiment's the screw compressor.
Fig. 7 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
Fig. 8 is the amplification profile of the revolving spiral spare in the present invention the 4th embodiment's the screw compressor.
Fig. 9 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
Figure 10 is the amplification profile of revolving spiral spare in the present invention the 5th embodiment's the screw compressor.
Figure 11 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
Figure 12 is the amplification profile of revolving spiral spare in the present invention the 6th embodiment's the screw compressor.
Figure 13 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
Figure 14 is the longitudinal sectional drawing of screw compressor in the past.
Embodiment
Below, with reference to accompanying drawing embodiments of the invention are described.
Fig. 1 is the longitudinal sectional drawing of the screw compressor of the 1st embodiment among the present invention, and Fig. 2 be the amplification profile of revolving spiral spare in the screw compressor of present embodiment, and Fig. 3 is the view from the revolving spiral spare of clinch side observation present embodiment.
The structure that screw compressor adopted of present embodiment is: make the fixedly helical member 103 of each vortex clinch (hereinafter referred to as clinch) of formation on each piece backplate and the clinch interlock each other of revolving spiral spare 104, thereby form a plurality of pressing chamber 105a, 105b, by on the anti-clinch side guard plate surface of revolving spiral spare 104, applying certain pressure, make two helical members 103,104 backplate portion and clinch front end are in contact with one another, by being arranged on the lip-deep rotation limiting component 121 of anti-clinch side guard plate of revolving spiral spare 104, can prevent the rotation of revolving spiral spare 104 and realize rotation motion, thereby from outer circumferential side when volume is reduced at the center, make pressing chamber 105a, 105b moves, and refrigerant gas is compressed.
Below, the work of the screw compressor of present embodiment is described.
In Fig. 1～Fig. 3, the refrigerant gas that sucks from suction pipe 101 is through the fixing suction passage 102 of helical member 103, sealing go into can with the pressing chamber 105a of revolving spiral spare 104 interlocks, in the 105b, when the center reduces volume, refrigerant gas is compressed, and discharge by tap hole 106.
On the other hand, lubricant oil (below, be called oil) by trochoid pump 107 sucking-offs, by the through hole 109 of bent axle 108 inside, the capacity eccentric bearing inner space 110 of guiding revolving spiral spare 104.From described capacity eccentric bearing inner space 110 as the oil measure nonresident portion, the oil runner branches into two, flow through in the backplate of oil through being arranged on revolving spiral spare 104 of an oily runner and, be imported into by fixedly helical member 103, revolving spiral spare 104 and main bearing parts 112 surround the back pressure chamber 113 that forms in the restriction 111 of anti-clinch side opening.
Described back pressure chamber 113 forms the intermediate pressure of head pressure and suction pressure, and controls so that described intermediate pressure forms certain pressure by backpressure adjusting mechanism 114.Backpressure adjusting mechanism 114 is being communicated with back pressure chamber 113 and fixedly is being provided with valve 117 between 115 the ramp way 116 near the inlet hole of helical member 103, if the pressure of back pressure chamber 113 is higher than setting pressure, then valve 117 is opened, and to the oil that sucks space 118 supply back pressure chambers 113, thereby in back pressure chamber 113, keep roughly certain intermediate pressure.In addition, when revolving spiral spare 104 rotated, to pressing chamber 105a, 105b moved, thereby helps to prevent at pressing chamber 105a the leakage between 105b towards the oil that sucks space 118 supplies.
The flow through oil of another oily runner, the 1st fuel feeding micropore 120a oil supply to pressing chamber 105a that the 1st fuel supply path 119a guiding in the backplate that is formed at revolving spiral spare 104 is provided with along the short transverse in the clinch.Equally, the 2nd fuel feeding micropore 120b that the 2nd fuel supply path 119b guiding in the backplate that is formed at revolving spiral spare 104 is provided with along the short transverse in the clinch, and in another pressing chamber 105B oil supply.
And, by suitably setting fixedly the clinch height of helical member 103 and the clinch height of revolving spiral spare 104, even do not use end of blade Sealing sheet, by oil from the 1st fuel feeding micropore 120a and the 2nd fuel feeding micropore 120b, can guarantee pressing chamber 105a, sealing between the 105b, and can avoid compression leakage.In addition, pass through the oil supplied with, can realize the lubricated and cooling of the slide part that waits between the clinch, avoid wearing and tearing and ablate.
As mentioned above, adopt the screw compressor of present embodiment, the oil by being supplied with by a plurality of fuel feeding micropores on the clinch front end that is arranged on revolving spiral spare need not to use the end of blade Sealing, just can realize high-performance and high reliability.
In addition, by respectively the 1st fuel feeding micropore 120a and the 2nd fuel feeding micropore 120b being arranged on refrigerant is sucked into needs fuel feeding between the discharge any position, thereby can realize that fuel feeding distributes.In the present embodiment, be 2 situation although understand oil supply hole, still, also can increase its quantity as required.
Fig. 4 is the amplification profile of the revolving spiral spare in the present invention the 2nd embodiment's the screw compressor, and Fig. 5 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
The screw compressor of present embodiment and the 1st embodiment's difference only is the structure of revolving spiral spare, and other structure is then identical with the 1st embodiment, the Therefore, omited to the explanation of these structures and action.
That is, the revolving spiral spare 104b in the 2nd embodiment's the screw compressor as shown in Figure 4 and Figure 5, the structure of employing is: make along clinch inner height direction the 2nd fuel feeding micropore 120d that is provided with and 1 the fuel supply path 119c connection that is communicated with the 1st fuel feeding micropore 120c.
The structure of the screw compressor by this 2nd embodiment can economical, reasonably realize the effect identical with the 1st embodiment.
Embodiment 3
Fig. 6 is the amplification profile of the revolving spiral spare in the present invention the 3rd embodiment's the screw compressor, and Fig. 7 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
The screw compressor of present embodiment and the 1st embodiment's difference only is the structure of revolving spiral spare, and other structure is then identical with the 1st embodiment, the Therefore, omited to the explanation of these structures or action.
Promptly, revolving spiral spare 104c in the 3rd embodiment's the screw compressor as shown in Figure 6 and Figure 7, the structure that adopts is: have the 1st fuel feeding micropore 120e that the 1st fuel supply path 119e interior with being formed on its backplate is communicated with, the 2nd fuel feeding micropore 120f that is communicated with the 2nd fuel supply path 119f, and make the radial dimension of the 2nd fuel feeding micropore 120f be different from the radial dimension of the 1st fuel feeding micropore 120e.
The structure of the screw compressor by this 3rd embodiment can realize the control that distributes as the accurate fuel feeding such as aperture that selectively strengthen the fuel feeding micropore of opening when the bigger fuel delivery of needs, thereby can realize more high-performance and high reliability.
Embodiment 4
Fig. 8 is the amplification profile of the revolving spiral spare in the present invention the 4th embodiment's the screw compressor, and Fig. 9 is a view of observing the revolving spiral spare of present embodiment from the overlap joint side.
The screw compressor of present embodiment and the 2nd embodiment's difference only is the structure of revolving spiral spare, and other structure is then identical with the 2nd embodiment, the Therefore, omited to the explanation of these structures and action.
Promptly, the structure that revolving spiral spare 104d in the 4th embodiment's the screw compressor adopts is: as Fig. 8 and shown in Figure 9, have the 1st fuel feeding micropore 120g and the 2nd fuel feeding micropore 120h that the fuel supply path 119g interior with being formed on its backplate is communicated with, and make the clinch that is arranged on the clinch front-end face coil the aperture size of the aperture size of the 2nd fuel feeding micropore 120h that stops side less than the 1st fuel feeding micropore 120g that is arranged on clinch coiling origination side.
Utilize the structure of this 4th embodiment's screw compressor, by reducing aperture size to apply resistance, thereby that can suppress that pressure reduction because of two opening ends of fuel feeding micropore increases stops the fuel delivery of the 2nd fuel feeding micropore 120h of side through coiling, and can avoid reducing, thereby can realize higher performance because of the volumetric efficiency that sucks the gas superheat generation.
In addition, though the structure of present embodiment has been described according to the structure that a plurality of fuel feeding micropores are set on 1 fuel supply path of the 2nd embodiment, but, the structure of present embodiment also is applicable to the screw compressor that a plurality of fuel feeding micropores are set on the 1st embodiment's many fuel supply paths, and can realize identical effect.
Figure 10 is the amplification profile of the revolving spiral spare in the present invention the 5th embodiment's the screw compressor, and Figure 11 is a view of observing the revolving spiral spare of present embodiment from the overlap joint side.
The screw compressor of present embodiment and the 2nd embodiment's difference only is the structure of revolving spiral spare, and other structure is then identical with the 2nd embodiment, the Therefore, omited to the explanation of these structures or action.
Promptly, revolving spiral spare 104e in the 5th embodiment's the screw compressor is shown in Figure 10 and 11, the structure that adopts is: have be formed on its backplate in fuel supply path 119e the 1st fuel feeding micropore 120i and the 2nd fuel feeding micropore 120j that are communicated with, and the shorten length of the 1st fuel feeding micropore 120i of clinch coiling origination side that will be arranged on the clinch front-end face is to than being arranged on the length weak point of bond pads around the 2nd fuel feeding micropore 120j of termination side.
The structure of the screw compressor by this 5th embodiment, the peripheral temperature of fuel feeding micropore raises, thereby can avoid near the flow passage resistance force of waterproof the 1st fuel feeding micropore 120i opening end that floor space produced of the more approaching fixedly helical member 103 of clinch front end of the revolving spiral spare 104e that causes because of thermal expansion to increase, by stably supplying with oil, thereby can realize higher reliability to pressing chamber.
In addition, present embodiment adopts aluminum alloy at revolving spiral spare, and fixedly helical member adopts under the situation such as cast iron, during less than the material of fixing helical member, is effective especially at revolving spiral spare employing thermal expansion coefficient.
In addition, though the structure of present embodiment has been described according to the structure that a plurality of fuel feeding micropores are set on 1 fuel supply path of the 2nd embodiment, but, the structure of present embodiment also is applicable to the screw compressor that a plurality of fuel feeding micropores are set on a plurality of fuel supply paths of the 1st embodiment, and can realize identical effect.
Embodiment 6
Figure 12 is the amplification profile of the revolving spiral spare in the present invention the 6th embodiment's the screw compressor, and Figure 13 is a view of observing the revolving spiral spare of present embodiment from the clinch side.
The screw compressor of present embodiment and the 5th embodiment's difference only is the structure of revolving spiral spare, and other structure is then identical with the 5th embodiment, the Therefore, omited to the explanation of these structures or action.
Promptly, the structure that revolving spiral spare 104f in the 6th embodiment's the screw compressor is adopted is: shown in Figure 12 and 13, have the 1st fuel feeding micropore 120k and the 2nd fuel feeding micropore 120m that the fuel supply path 119j interior with being formed on its backplate is communicated with, and the short measure of length as the length of the 1st fuel feeding micropore 120k that makes clinch coiling origination side is coiled the 2nd fuel feeding micropore 120m of termination side than clinch makes the open circumferential portion of the 1st fuel feeding micropore 120k recessed.By this embodiment's 6 screw compressor structure, can avoid the increase of flow passage resistance force of waterproof, and obtain the effect identical with the 5th embodiment.
Industrial applicibility
As mentioned above, because screw compressor of the present invention need not to use the end of blade seal, just High-performance and high reliability be can realize, therefore, air-conditioning, refrigerator etc. are applicable to.
Claims (3)
1. screw compressor, wherein, make the fixedly helical member of formation vortex clinch on backplate and the clinch interlock each other of revolving spiral spare, thereby form a plurality of pressing chambers, by on the anti-overlap joint side guard plate surface of described revolving spiral spare, applying certain pressure, the backplate portion and the clinch front end of two helical members are in contact with one another, by being arranged on the lip-deep rotation limiting component of anti-clinch side guard plate of described revolving spiral spare, prevent the rotation of revolving spiral spare and realize rotation motion, whereby, from outer circumferential side when volume is reduced at the center, described pressing chamber is moved, thereby compress, it is characterized in that:
The a plurality of fuel feeding micropores that are communicated with the oily reservoir of high-pressure space the setting of the clinch front-end face of described revolving spiral spare,
Make the aperture of described a plurality of oil supply holes form different sizes respectively,
It is more little that the aperture of described a plurality of oil supply holes stops side near the clinch coiling more.
2. screw compressor according to claim 1 is characterized in that: in 1 oil supply gallery in the backplate that described a plurality of fuel feeding micropore is collected in be arranged at described revolving spiral spare and they are communicated with this oil supply gallery.
3. screw compressor, wherein, make the fixedly helical member of formation vortex clinch on backplate and the clinch interlock each other of revolving spiral spare, thereby form a plurality of pressing chambers, by on the anti-overlap joint side guard plate surface of described revolving spiral spare, applying certain pressure, the backplate portion and the clinch front end of two helical members are in contact with one another, by being arranged on the lip-deep rotation limiting component of anti-clinch side guard plate of described revolving spiral spare, prevent the rotation of revolving spiral spare and realize rotation motion, whereby, from outer circumferential side when volume is reduced at the center, described pressing chamber is moved, thereby compress, it is characterized in that:
The a plurality of fuel feeding micropores that are communicated with the oily reservoir of high-pressure space the setting of the clinch front-end face of described revolving spiral spare,
The length of described a plurality of oil supply holes is short more near clinch coiling origination side more.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003426823 | 2003-12-24 | ||
| JP2003426823A JP4329530B2 (en) | 2003-12-24 | 2003-12-24 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1637299A CN1637299A (en) | 2005-07-13 |
| CN100400887C true CN100400887C (en) | 2008-07-09 |
Family
ID=34786250
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004101048733A Expired - Fee Related CN100400887C (en) | 2003-12-24 | 2004-12-24 | Screw compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4329530B2 (en) |
| CN (1) | CN100400887C (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5061462B2 (en) * | 2006-01-23 | 2012-10-31 | パナソニック株式会社 | Scroll compressor |
| JP2008101559A (en) * | 2006-10-20 | 2008-05-01 | Hitachi Appliances Inc | Scroll compressor and refrigeration cycle using the same |
| JP5181534B2 (en) * | 2007-05-22 | 2013-04-10 | パナソニック株式会社 | Scroll compressor |
| JP5291423B2 (en) * | 2008-10-01 | 2013-09-18 | サンデン株式会社 | Fluid machinery |
| JP5428522B2 (en) * | 2009-05-22 | 2014-02-26 | パナソニック株式会社 | Scroll compressor |
| CN102330681A (en) * | 2011-09-30 | 2012-01-25 | 安徽美芝压缩机有限公司 | Vortex compressor |
| CN103807166B (en) * | 2012-11-14 | 2017-12-26 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN104047849B (en) * | 2014-07-03 | 2017-01-18 | 湖南联力精密机械有限公司 | Vortex air compressor with built-in lubricating oil path |
| CN109538471A (en) * | 2018-12-03 | 2019-03-29 | 珠海格力节能环保制冷技术研究中心有限公司 | Screw compressor and refrigeration equipment |
| US20230258186A1 (en) * | 2020-06-23 | 2023-08-17 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Scroll compression mechanism and scroll compressor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06288361A (en) * | 1993-04-07 | 1994-10-11 | Hitachi Ltd | Scroll compressor |
| CN1111725A (en) * | 1993-11-19 | 1995-11-15 | 倪诗茂 | High compression ratio volumetric fluid displacement device |
| CN1386982A (en) * | 2001-05-18 | 2002-12-25 | 松下电器产业株式会社 | Turbocompressor and driving method thereof |
| JP2003254267A (en) * | 2002-03-06 | 2003-09-10 | Matsushita Electric Ind Co Ltd | Hermetic scroll compressor and applied device of the same |
| CN1458422A (en) * | 2002-05-15 | 2003-11-26 | 松下电器产业株式会社 | Vortex compressor |
-
2003
- 2003-12-24 JP JP2003426823A patent/JP4329530B2/en not_active Expired - Fee Related
-
2004
- 2004-12-24 CN CNB2004101048733A patent/CN100400887C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06288361A (en) * | 1993-04-07 | 1994-10-11 | Hitachi Ltd | Scroll compressor |
| CN1111725A (en) * | 1993-11-19 | 1995-11-15 | 倪诗茂 | High compression ratio volumetric fluid displacement device |
| CN1386982A (en) * | 2001-05-18 | 2002-12-25 | 松下电器产业株式会社 | Turbocompressor and driving method thereof |
| JP2003254267A (en) * | 2002-03-06 | 2003-09-10 | Matsushita Electric Ind Co Ltd | Hermetic scroll compressor and applied device of the same |
| CN1458422A (en) * | 2002-05-15 | 2003-11-26 | 松下电器产业株式会社 | Vortex compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1637299A (en) | 2005-07-13 |
| JP4329530B2 (en) | 2009-09-09 |
| JP2005188294A (en) | 2005-07-14 |
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