CN101151465A - Scroll fluid machine - Google Patents
Scroll fluid machine Download PDFInfo
- Publication number
- CN101151465A CN101151465A CNA200680010110XA CN200680010110A CN101151465A CN 101151465 A CN101151465 A CN 101151465A CN A200680010110X A CNA200680010110X A CN A200680010110XA CN 200680010110 A CN200680010110 A CN 200680010110A CN 101151465 A CN101151465 A CN 101151465A
- Authority
- CN
- China
- Prior art keywords
- rotor
- armature
- vortex element
- convolute
- fluid flowing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
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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
- F04C18/0215—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 only one member is moving
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0085—Prime movers
-
- 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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/803—Electric connectors or cables; Fittings therefor
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
An electric scroll compressor as a fluid machine, comprising a housing (10) storing both a scroll unit (20) and an armature (38) driving the scroll unit (20) and a refrigerant flow passage disposed in the housing (10) and leading a refrigerant to the scroll unit (20). The refrigerant flow passage partly comprises a spiral groove (64), and the spiral groove (64) is formed in the outer peripheral surface of a rotor (54) of the armature (38) and comprises both ends opened to both end faces of the rotor (54).
Description
Technical field
The present invention relates to convolute-hydrodynamic mechanics, relate in particular to the convolute-hydrodynamic mechanics of the scroll compressor that is suitable in the refrigerating circuit of vehicle air-conditioning systems, being used for the refrigeration agent compression.
Background technique
This scroll compressor is by the motor or the motoring of vehicle.DYN dynamic compressor is compared with utilizing engine-driven compressor, and the load that can not be subjected to motor influences and easily adjusts the discharge capacity of refrigeration agent, and extremely fine controls the room temperature of vehicle, is preferable.
In addition, because the lift-launch of this scroll compressor is on vehicle, so require compact compressor as far as possible.Therefore, the electrodynamic type scroll compressor that TOHKEMY 2003-129983 communique is disclosed comprises and vortex element and 1 shared housing of motor both sides, accommodates the armature of vortex element and motor in this common housing respectively.
When motor rotates, the armature heating.The temperature of armature is if too rise, and then motor performance descends.Therefore, the compressor of above-mentioned communique comprises the cooling path that armature is used.This cooling path returns this to refrigeration agent at refrigeration agent and is directed to armature in the process that vortex element returns.The temperature of returning refrigeration agent is compared enough low with environment temperature, therefore return refrigeration agent and can cool off armature effectively.
Specifically, cooling path comprises the gap between the inner circle wall of the rotor of armature and the air gap between stator, stator and shared housing, the gap of stator coil.But these gaps are all narrow and small, and therefore, cooling path increases the pressure loss of refrigeration agent to become bigger resistance towards the flow of refrigerant of vortex element.Therefore, vortex element can not suck effectively and return refrigeration agent, and the suction efficiency of vortex element descends.
For eliminating above-mentioned unfavorable condition, the armature of the motor that TOHKEMY 2002-165406 communique discloses comprises the fan that is installed in respectively on the both ends of the surface that connect interior axial passageway of rotor and rotor.When these fan rotations, refrigeration agent to a direction forced flow, cools off armature in axial passageway.
But, being applied to the occasion of scroll compressor at armature with above-mentioned communique, armature is because of having the corresponding maximization of axial passageway, so the external diameter of the common housing of scroll compressor and weight also increase.In addition, fan increases the part number of armature, and the cost of scroll compressor is risen.
Summary of the invention
The object of the invention is, provides a kind of and do not cause maximizing and the part number increases, can improve the convolute-hydrodynamic mechanics of the suction efficiency of vortex element.
For achieving the above object, convolute-hydrodynamic mechanics of the present invention has: housing; Vortex element, this vortex element are housed in this housing, and this vortex element has static vortex disk and the movable orbiting scroll that cooperates with each other the compressed action fluid to use; Armature, this armature and vortex element are housed in the housing in abutting connection with ground, and armature comprises the rotor that makes movable orbiting scroll rotation usefulness, and this rotor has side face and both ends of the surface; Fluid flowing path, this fluid flowing path is configured in the housing, is that fluid flowing path comprises the spiral chute on the side face that is formed on rotor with the fluid flowing path of action fluid by guiding to vortex element in the armature, and this spiral chute has the two ends at the both ends of the surface opening of rotor.
Adopt above-mentioned convolute-hydrodynamic mechanics, when vortex element was driven by armature, vortex element sucked the action fluid by the fluid flowing path guiding.The pressure of the action fluid that sucks changes in by the process in the vortex element, and then, the action fluid is discharged from vortex element.
Because fluid flowing path comprises and is formed on epitrochanterian spiral chute, mainly flow by spiral chute so be directed to the action fluid of vortex element.Spiral chute increases the sectional area of fluid flowing path, and fluid flowing path is not concerning becoming bigger resistance towards the flowing of the action fluid of vortex element.Its result, the pressure loss of action fluid reduces, and the suction efficiency of the action fluid in the vortex element improves.
Best, spiral chute has the Hand of spiral of when rotor rotates the action fluid in the spiral chute being extruded to vortex element.In this occasion, in the rotor rotation process, the action fluid in the spiral chute flows to vortex element so the action fluid passes through interior pressure of spiral chute owing to extrude to vortex element, not only further reduce the pressure loss of action fluid, and can further improve the suction efficiency of vortex element.
Specifically, vortex element is the compression unit that refrigerating circuit is used, and fluid flowing path leads to the refrigeration agent that returns compression unit.In this occasion, the side face with spiral fluted rotor is the outer circumferential face of rotor preferably.
Because it is enough lower than environment temperature to turn back to the temperature of refrigeration agent of compression unit, thus refrigeration agent in the spiral chute of rotor when mobile, refrigeration agent cools off armature effectively.Therefore, can prevent that armature is overheated, keep the performance of armature.
Have the occasion of the stepped construction that stacked ring-type electromagnetic steel plate forms on the rotor axis direction at rotor, each electromagnetic steel plate can have the spiral fluted of being used to form recess on the periphery that forms rotor flank.In this occasion, can be easily form spiral chute at the side face of rotor.
Description of drawings
Fig. 1 is the sectional view of the scroll compressor of expression fluid machinery.
Fig. 2 is the stereogram of the rotor of presentation graphs 1.
Fig. 3 is the plan view of electromagnetic steel plate of the rotor of expression pie graph 2.
Embodiment
The scroll compressor of Fig. 1 promptly is used as the compressor that refrigerating circuit is used as vehicle air-conditioning systems.Compressor has housing 10 cylindraceous.From Fig. 1, from left in order, housing 10 has cell enclosure 12, motor casing 14 and loop shell 16.Cell enclosure 12 and motor casing 14 utilize a plurality of connecting bolts 18 and mutually combine, and motor casing 14 and loop shell 16 utilize a plurality of connecting bolts 19 and mutually combine.
Cell enclosure 12 is accommodated vortex element 20, and this vortex element 20 has static vortex disk 22 and movable orbiting scroll 24.Static vortex disk 22 is fixed on the end wall 12a by a plurality of fixing bolts 26 with the state with the end wall 12a butt of cell enclosure 12.On the other hand, movable orbiting scroll 24 is positioned at motor casing 14 sides.
Static vortex disk and movable orbiting scroll 22,24 have vortex wall 22f, 24m, and these vortex walls 22f, 24m are assembled into and intermesh.The engagement of vortex wall 22f, 24m forms a plurality of pressing chambers 28.Movable orbiting scroll 24 is during with respect to static vortex disk 22 rotation, and pressing chamber 28 moves along the circumferential helical of static vortex disk 22, and in this moving process of the central authorities of static vortex disk 22, the volume of pressing chamber 28 dwindles.
The internal rules of cell enclosure 12 are discharged chamber 30, and this inner end wall of discharging chamber 30 is formed by the end wall 12a of unit housings 12 and the end plate 22a of static vortex disk 22 respectively.There is tap hole 32 in the central authorities of end wall 22a, and this tap hole 32 connects end wall 22a.Tap hole 32 opens and closes by expulsion valve (not shown).Expulsion valve is configured in discharges in the chamber 30, and is fixed on the end wall 22a of static vortex disk 22.
In addition, the end wall 12a of cell enclosure 12 has exhaust port 34.The inner of this exhaust port 34 with discharge chamber 30 and be communicated with, the outer end of exhaust port 34 by the refrigerant cycle path (not shown) of aforesaid refrigerating circuit, pass through the refrigerant cycle path in detail and be connected with the condenser (not shown) of refrigerant circuit.
When movable orbiting scroll 24 rotatablely moves, stop movable orbiting scroll 24 rotations.In more detail, between an end of the end plate 24a of movable orbiting scroll 24 and motor casing 14, sandwich ball formula coupling 36.Ball formula coupling 36 stops movable orbiting scroll 24 rotations, on the other hand, will pass to motor casing 14 from the thrust load of movable orbiting scroll 24.
On the other hand, armature 38 is accommodated in the inside of motor casing 14, and armature 38 will be divided into the chamber 13 of cell enclosure 12 sides and the chamber 15 of loop shell 16 sides in the motor casing 14.Armature 38 has running shaft 40, and this running shaft 40 is positioned at the central authorities of motor casing 14, and extends to loop shell 16 from an end of motor casing 14.The two ends of running shaft 40 rotate on the end and the next door 16a in the loop shell 16 that is bearing in motor casing 14 freely by ball bearing 42 and roller bearing 44.Next door 16a will be divided in the loop shell 16 and the motor casing interior chambers 17 and the chamber, loop 19 of separating with this chamber 17 that link to each other 14.
In addition, as can be seen from Figure 1, an end of running shaft 40 forms bigger diameter end portion 46, and this bigger diameter end portion 46 has the end plate opposing end faces with movable orbiting scroll 24.Crank pin 48 is outstanding to movable orbiting scroll 24 from the end face of bigger diameter end portion 46, and eccentric adjusting sleeve 50 is installed on this crank pin 48.This eccentric adjusting sleeve 50 rotates on the protruded stigma 24a that is bearing in movable orbiting scroll 24 freely by needle bearing 52.
When running shaft 40 rotations, the rotating force of running shaft 40 passes to movable orbiting scroll 24 by crank pin 48, eccentric adjusting sleeve 50, needle bearing 52.Therefore, movable orbiting scroll 24 is rotated with respect to static vortex disk 22 by the state that ball formula coupling 36 stops with its rotation.The turning radius of movable orbiting scroll 24 is by the distance decision between the axis of the axis of running shaft 40 and crank pin 48.
Aforesaid armature 38 has rotor 54, and this rotor 54 is installed on the running shaft 40.Rotor 54 is surrounded by stator 56, and this stator 56 is fixed on the inner circle wall of motor casing 14.
On the other hand, the periphery wall of loop shell 16 has return port 58, and the inner of this return port 58 is that aforesaid chamber 15 is communicated with by the chamber 17 of loop shell 16 with the inside of motor casing 14.The other end of return port 58 is by the refrigerant cycle path of aforesaid refrigerating circuit, in more detail by refrigerant cycle path and being connected with the vaporizer of refrigerating circuit.Therefore, the refrigeration agent of sending from vaporizer that returns flows in the chamber 17 of loop shell 16 by return port 58, and, supply in the motor casing 16 from this chamber 17.
In the driving loop 59 that the chamber, loop 19 of loop shell 16 disposes armature 38 usefulness, this driving loop 59 is controlled the electric power that feeds to armature 38 and the rotation of armature 38 respectively.
Guarantee cooling path in motor casing 14, the refrigeration agent that returns that this cooling path will supply in the motor casing 14 is directed in the armature 38.In detail, cooling path is as previously mentioned the clearance G b and the gap between stator coil (not shown) except between the periphery wall of the inner circle wall of the air gap Ga of 56 of rotor 54 and stators, motor casing 14 and stator 56, the chamber 13,15 that the spiral chute that also comprises the major component that forms cooling path, these gaps and spiral chute all will be configured in the both sides of armature 38 connects.
Now spiral chute is described in detail, as can be seen from Figure 1, rotor 54 has the stepped construction that many ring-type electromagnetic steel plates 62 are overlapped on the axial direction of running shaft 40.As shown in Figure 2, spiral chute 64 is formed on the outer circumferential face of rotor 54, and the two ends of spiral chute 64 difference opening is on the both ends of the surface of rotor 54.In more detail, when rotor 54 rotation, spiral chute 64 have with right-handed thread similarly to the Hand of spiral of cell enclosure 12 lateral movements.
In the occasion of an embodiment rotor 54, the outer circumferential face of each electromagnetic steel plate 62 has the recess 66 of U font.Rotor 54 makes many electromagnetic steel plate 62 stacked and when forming, and the recess 66 of the electromagnetic steel plate 62 of adjacency to be to overlap mutually at the state that circumferentially staggers a little of rotor 54, thus, forms aforesaid spiral chute 64 at the axial direction recess 66 side by side of rotor 54.
Also can after forming rotor 54, utilize machining that spiral chute 64 is formed on the outer circumferential face of rotor 54 by many electromagnetic steel plates 62.
On the other hand, the suction chamber 60 of regulation vortex element 20 usefulness in cell enclosure 12, this suction chamber 60 surrounds the movable orbiting scroll 24 of vortex element 20, separates with aforesaid discharge chamber 30 by static vortex disk 22.The space of the inner space of suction chamber 60 by aforesaid ball formula coupling 36, movable orbiting scroll 24 and 42 on ball bearing and the inner space of ball bearing 42 and be connected with chamber 13 in the aforesaid motor casing 14.Therefore, suction chamber 60 is connected with the return port 58 of loop shell 16 by the refrigerant flow path that comprises aforesaid cooling path, its result, and the refrigeration agent that returns that flows into return port 58 supplies to suction chamber 60 through refrigerant flow path.
When the running shaft 40 of aforesaid armature 38 rotated, the rotation of this running shaft 40 passed to movable orbiting scroll 24 by crank pin 48 and eccentric adjusting sleeve 50.Therefore, the state that is prevented from its rotation of movable orbiting scroll 24 and relatively static vortex disk 22 be rotated.In the rotatablely moving of movable orbiting scroll 24,1 pressing chamber 28 is in case open to suction chamber 60, and then refrigeration agent is inhaled into pressing chamber 28 from suction chamber 60, and pressing chamber 28 separates with suction chamber 60 then.
Then, the tap hole 32 to static vortex disk 22 moves pressing chamber 28 along with rotatablely moving of movable orbiting scroll 24, the volume reducing in this process in the pressing chamber 28, and the result, the refrigeration agent that is drawn in the pressing chamber 28 is compressed.The pressure that pressing chamber 28 arrives the refrigeration agent in tap holes 32 and the pressing chamber 28 is during greater than the closing pressure of expulsion valve, and expulsion valve is opened, and the compressed refrigerants in the pressing chamber 28 are discharged to by tap hole 32 and discharge chamber 30.
The compressed refrigerant of discharging in the chamber 30 is sent the refrigerant cycle path by exhaust port 34, supplies with to the condenser of refrigerating circuit.Then, reservoir and the expansion valve and supply to vaporizer of compressed refrigerant in the refrigerant cycle path, and, carry out refrigeration agent from this vaporizer to return and turn back to return port 58, and from chamber 17 that this return port 58 flows in loop shells 16.In addition, returning refrigeration agent 17 is cooling flowing path and supply to suction chamber 60 through aforesaid refrigerant flow path from the chamber.
As previously mentioned, the temperature of returning refrigeration agent is enough lower than environment temperature, and therefore, the refrigeration agent that returns that flows through cooling path cools off armature 38 effectively, prevents that armature 38 is overheated.
The major component of cooling path comprises spiral chute 64, and this spiral chute 64 increases effective flow path cross sectional area of cooling path integral body.Therefore, cooling path is not for becoming bigger resistance towards returning of suction chamber 60 the flowing of refrigeration agent, and the pressure loss of returning refrigeration agent is little.
In addition, because spiral chute 64 with rotor 54 rotations, so the refrigeration agent that returns in the spiral chute 64 is forced to extrude to cell enclosure 12, thus, returns chamber 15 the flowing to chamber 13 of refrigeration agent from motor casing 14 in spiral chute 64.
Its result, armature 38 not only utilizes and returns the forced flow of refrigeration agent and effectively cooled off, and, can realize returning the pressurization of refrigeration agent to suction chamber 60, therefore, can improve the suction efficiency of vortex element 20, can improve the performance of scroll compressor.
Above-mentioned spiral chute 64 can not make rotor 54 big footpathizations and increase the part number of armature 38 usefulness, can stop the maximization of scroll compressor, and the lightweight of scroll compressor is had bigger contribution.
The present invention is not subjected to an above-mentioned embodiment's constraint, can do various distortion, and for example, shown in the double dot dash line, the outer circumferential face of rotor 54 also can have a plurality of spiral chutes 64, also can replace this outer circumferential face among Fig. 3, and has spiral chute 64 more than 1 at inner peripheral surface.
In addition, the present invention can be suitable for scroll expander rather than compressor equally.
Claims (6)
1. convolute-hydrodynamic mechanics is characterized in that having:
Housing;
Vortex element, this vortex element is housed in the described housing, has the static vortex disk and the movable orbiting scroll that cooperate with each other the compressed action fluid to use;
Armature, this armature and described vortex element are housed in the described housing in abutting connection with ground, and described armature comprises the rotor that makes described movable orbiting scroll rotation usefulness, and this rotor has side face and both ends of the surface;
Fluid flowing path, this fluid flowing path is configured in the described housing, be by guiding to the fluid flowing path of described vortex element in the described armature with the action fluid, described fluid flowing path comprises the spiral chute on the described side face that is formed on described rotor, and this spiral chute has the two ends at the described both ends of the surface opening of described rotor.
2. convolute-hydrodynamic mechanics as claimed in claim 1 is characterized in that, described spiral chute has the Hand of spiral of when described rotor rotates the action fluid in the described spiral chute being extruded to described vortex element.
3. convolute-hydrodynamic mechanics as claimed in claim 2 is characterized in that, described vortex element is the compression unit that refrigerating circuit is used, and described fluid flowing path leads to the refrigeration agent that returns described compression unit.
4. convolute-hydrodynamic mechanics as claimed in claim 2 is characterized in that, the described side face of described rotor is the outer circumferential face of described rotor.
5. convolute-hydrodynamic mechanics as claimed in claim 4 is characterized in that, described vortex element is the compression unit that refrigerating circuit is used, and described fluid flowing path leads to the refrigeration agent that returns described compression unit.
6. convolute-hydrodynamic mechanics as claimed in claim 2, it is characterized in that, described rotor has the stepped construction of stacked ring-type electromagnetic steel plate on described rotor axis direction, and each electromagnetic steel plate has on the periphery of the described side face that forms described rotor and is used to form described spiral fluted recess.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005106098A JP2006283694A (en) | 2005-04-01 | 2005-04-01 | Scroll type fluid machine |
| JP106098/2005 | 2005-04-01 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101151465A true CN101151465A (en) | 2008-03-26 |
Family
ID=37073316
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200680010110XA Pending CN101151465A (en) | 2005-04-01 | 2006-03-29 | Scroll fluid machine |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20090148314A1 (en) |
| EP (1) | EP1865201B1 (en) |
| JP (1) | JP2006283694A (en) |
| CN (1) | CN101151465A (en) |
| DE (1) | DE602006018117D1 (en) |
| WO (1) | WO2006106753A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101619721B (en) * | 2009-07-24 | 2010-11-17 | 南京银茂压缩机有限公司 | Integral electric scroll compressor assembly for vehicle air conditioners |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5018450B2 (en) * | 2007-12-18 | 2012-09-05 | 株式会社豊田自動織機 | Electric compressor |
| JP5109642B2 (en) * | 2007-12-18 | 2012-12-26 | 株式会社豊田自動織機 | Electric compressor |
| JP4985590B2 (en) * | 2008-09-02 | 2012-07-25 | 株式会社豊田自動織機 | Electric compressor |
| KR101682250B1 (en) * | 2010-12-06 | 2016-12-02 | 한온시스템 주식회사 | Electronic Compressor |
| KR101358602B1 (en) | 2011-08-31 | 2014-02-04 | 한라비스테온공조 주식회사 | Electric Compressor |
| JP5867313B2 (en) * | 2012-06-28 | 2016-02-24 | 株式会社豊田自動織機 | Electric compressor |
| JP6119962B2 (en) * | 2012-11-15 | 2017-04-26 | 株式会社豊田自動織機 | Electric compressor |
| JP6842385B2 (en) | 2017-08-25 | 2021-03-17 | 三菱重工サーマルシステムズ株式会社 | Scroll compressor |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2620205A1 (en) * | 1987-09-04 | 1989-03-10 | Zimmern Bernard | HERMETIC COMPRESSOR FOR REFRIGERATION WITH ENGINE COOLED BY GAS ECONOMIZER |
| JP2568915B2 (en) * | 1989-07-19 | 1997-01-08 | イビデン株式会社 | IC card |
| JPH0351196U (en) * | 1989-09-26 | 1991-05-17 | ||
| JPH05302581A (en) | 1992-04-24 | 1993-11-16 | Daikin Ind Ltd | Vertical type compressor |
| JPH0932729A (en) * | 1995-07-19 | 1997-02-04 | Mitsubishi Heavy Ind Ltd | Motor-driven compressor |
| JP3870642B2 (en) * | 1999-12-21 | 2007-01-24 | 株式会社デンソー | Electric compressor |
| JP3475174B2 (en) * | 2000-02-10 | 2003-12-08 | 東芝テック株式会社 | Electric pump |
| JP4356232B2 (en) | 2000-11-22 | 2009-11-04 | 株式会社デンソー | Rotor center of gravity eccentric type motor |
| JP2004204791A (en) * | 2002-12-26 | 2004-07-22 | Fujitsu General Ltd | Hermetic compressor |
| JP4372511B2 (en) * | 2003-10-17 | 2009-11-25 | トヨタ自動車株式会社 | Supercharger with rotating electric machine having a cylindrical member extending between bearings |
-
2005
- 2005-04-01 JP JP2005106098A patent/JP2006283694A/en active Pending
-
2006
- 2006-03-29 WO PCT/JP2006/306507 patent/WO2006106753A1/en active Application Filing
- 2006-03-29 DE DE602006018117T patent/DE602006018117D1/en active Active
- 2006-03-29 CN CNA200680010110XA patent/CN101151465A/en active Pending
- 2006-03-29 EP EP06730455A patent/EP1865201B1/en not_active Not-in-force
- 2006-03-29 US US11/887,691 patent/US20090148314A1/en not_active Abandoned
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101619721B (en) * | 2009-07-24 | 2010-11-17 | 南京银茂压缩机有限公司 | Integral electric scroll compressor assembly for vehicle air conditioners |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1865201A4 (en) | 2008-07-23 |
| EP1865201B1 (en) | 2010-11-10 |
| JP2006283694A (en) | 2006-10-19 |
| DE602006018117D1 (en) | 2010-12-23 |
| EP1865201A1 (en) | 2007-12-12 |
| US20090148314A1 (en) | 2009-06-11 |
| WO2006106753A1 (en) | 2006-10-12 |
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