CN102007297A - Inverter type scroll compressor - Google Patents
Inverter type scroll compressor Download PDFInfo
- Publication number
- CN102007297A CN102007297A CN2009801065481A CN200980106548A CN102007297A CN 102007297 A CN102007297 A CN 102007297A CN 2009801065481 A CN2009801065481 A CN 2009801065481A CN 200980106548 A CN200980106548 A CN 200980106548A CN 102007297 A CN102007297 A CN 102007297A
- Authority
- CN
- China
- Prior art keywords
- scroll compressor
- variable
- type scroll
- frequency type
- freezing mixture
- 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
- 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
-
- 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
- F04C29/047—Cooling of electronic devices installed inside the pump housing, e.g. inverters
-
- 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
-
- 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
- F04C2240/808—Electronic circuits (e.g. inverters) installed inside the machine
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention relates to an inverter type scroll compressor and comprises a housing, a fixed scroll which is set up inside the housing, a swivel scroll which swivels around the fixed scroll, a driving unit which turns the swivel scroll, an intake port and a discharge port which are in the housing, and an inverter which faces the front surface of the fixed scroll. An intake hole penetrating to the compression chamber and a discharge hole are respectively formed in the fixed scroll and the swivel scroll. Accordingly, the present invention is configured so that coolant is discharged through the discharge hole after the coolant passes through the inverter and the fixed scroll and then flows into the compression chamber. Therefore, this prevents overheating of the compressor caused by the inverter and increases remarkably the efficiency of the compressor by cooling the inverter and a compressed coolant with additional coolant at the same time. Additionally, the power required for compression up to a certain pressure is saved.
Description
Technical field
The present invention relates to a kind of variable-frequency type scroll compressor, particularly a kind of freezing mixture that utilizes suction cools off frequency variator and compresses refrigerant simultaneously to reduce energy consumption and significantly to promote the variable-frequency type scroll compressor of efficient.
Background technique
Generally speaking, even scroll compressor comprises that one has the fixed scroll that vortex crustiform scrollwork and drive shaft turns still can be kept its stationary state, and a vortex matter revolution that has the vortex crustiform scrollwork and when drive shaft turns, revolve round the sun.In this scroll compressor, vortex matter revolution is along fixed scroll revolution and freezing mixture is sucked into a pressing chamber that is formed between fixed scroll and the vortex matter revolution, thus compresses refrigerant.
Fig. 1 shows the example (calling " traditional scroll compressor " in the following text) of this scroll compressor.It below is the graphical illustration of this scroll compressor being made with reference to Fig. 1.
There is shown a kind of electric scroll compressor, it comprises a shell 10, be located at a suction port 60 and an exhaust port 70 in the shell 10, be located in the shell 10 and intermeshing fixed scroll 81 and a vortex matter revolution 82, a live axle 83, a motor 84, are installed between live axle 83 ends and the vortex matter revolution 82 ordering about the sliding sleeve 85 that vortex matter revolution 82 produces revolution motions (revolution operation), and an anti-rotation mechanism 86 that is used to prevent vortex matter revolution 82 rotations.
A frequency variator 20 is installed on the side seal ground of main shell 10.
Freezing mixture is through suction chamber 13, an inlet hole 16 and a space 17 that is positioned at frequency variator 20 belows, be introduced into pressing chamber 88 (space between fixed scroll and the vortex matter revolution) by a passage 15 then, and flow to a condenser through tap hole 811, discharge chamber 73 and the exhaust port 70 of being located at fixed scroll 81.
Yet according to traditional scroll compressor, because freezing mixture is introduced into pressing chamber 88 immediately behind cooling frequency variator 20, the compresses refrigerant in the pressing chamber 88 is heated.
Therefore, the efficient of compressor reduces, and energy consumption increases.Promptly be that because the temperature in the process of squeeze operation increases, isentropic efficiency descends and energy consumption increases.
In addition, discharge chamber 73 every the neighbour because the gas that sucks is positioned at, the efficient of compressor reduces because of heating.
In addition,,, break away from liquid suction freezing mixture and be compressed and Wet Compression, finally make compressor impaired when the degree of superheat of compressor is lowered to improve the heat exchange efficiency of vaporizer (not shown) according to traditional scroll compressor.
Summary of the invention
In order to address the above problem, one of purpose of the present invention provides a kind of variable-frequency type scroll compressor, and it can avoid overheat of compressor, and utilizes the freezing mixture that sucks that frequency variator and compresses refrigerant are cooled off simultaneously, thereby significantly promotes the efficient of compressor.
Another object of the present invention provides a kind of variable-frequency type scroll compressor, and it saves energy consumption by the efficient that increases compressor.
Further aim of the present invention is when originally freezing mixture is inhaled into, the degree of superheat of compressor reduced, thus the heat exchange efficiency of raising vaporizer.
For achieving the above object, the invention provides a kind of variable-frequency type scroll compressor, it comprises: a shell; One is fixedly installed in the stationary vortex part in the described shell; One is set to along the vortex matter revolution of described stationary vortex part revolution; One is set to drive the actuator of described vortex matter revolution revolution; Be arranged at a suction port and an exhaust port in the described shell; One frequency variator that is arranged at described stationary vortex part front surface and is oppositely arranged with described stationary vortex part; Wherein, described stationary vortex part is established one and is passed the inlet hole that described stationary vortex part enters a pressing chamber; Described vortex matter revolution is established a tap hole.Freezing mixture is introduced into described pressing chamber by the space between described frequency variator and the described stationary vortex part through described inlet hole, discharges by described tap hole then.
The position relative with described frequency variator at the antetheca of described stationary vortex part can be provided with a guiding element, and the freezing mixture that sucks from described suction port is guided to described inlet hole.
Described guiding element can be provided with an introduction mouth that communicates with the described inlet hole of described stationary vortex part.
Observe from the direction of described live axle, many guide channels can extend around described guiding element.
One end of a minimum described guide channel is arranged at the position near described suction port, and its other end then is arranged at the position of introducing mouth near described.
Described guide channel can be arc for the rarest one section.
A minimum described guide channel is provided with straight line introduction section in a side of described suction port.
Described guide channel can be made of many guiding raised lines or guide recess.
Described exhaust port can be arranged at the rear side of described vortex matter revolution.
One discharge route can pass described live axle along the longitudinal direction of described live axle.
Be arranged at described live axle discharge route minimum one section along its rear side forward side tilt laterally from the axle center of live axle gradually.
According to the present invention, by frequency variator produce the overheat of compressor problem can freezing mixture cools off frequency variator simultaneously and compresses refrigerant is avoided by sucking, and the efficient of compressor is promoted greatly.
In addition, because the efficiengy-increasing of compressor, the energy consumption of compression can significantly reduce.
Moreover, when originally freezing mixture is inhaled into, reduce degree of superheat, also can promote the heat exchange efficiency of vaporizer.
In addition, by discharging the chamber away from sucking the gas setting, it is overheated and compression efficiency is reduced just can to avoid discharging the chamber.
Description of drawings
Fig. 1 is the longitdinal cross-section diagram of traditional frequency conversion formula scroll compressor.
Fig. 2 is the longitdinal cross-section diagram of variable-frequency type scroll compressor of the present invention.
Fig. 3 is the longitdinal cross-section diagram of variable-frequency type scroll compressor of the present invention, has shown the circulation that sucks freezing mixture.
Fig. 4 is the exploded perspective view of variable-frequency type scroll compressor of the present invention.
Fig. 5 is the front perspective view of variable-frequency type scroll compressor of the present invention after frequency variator shown in Figure 2 is removed.
Fig. 6 is the pressure-enthalpy chart of the suction freezing mixture of process variable-frequency type scroll compressor of the present invention.
Fig. 7 is the pressure-enthalpy chart of the suction freezing mixture of a process traditional frequency conversion formula scroll compressor.
Embodiment
Below with reference to Fig. 2 to Fig. 5 a preferred implementation of the present invention is described in more detail.
As shown in the figure, variable-frequency type scroll compressor 1000 of the present invention comprises a shell 100, be arranged at a suction port 600 and an exhaust port 700 in the described shell 100, be contained in the described shell 100 and an intermeshing stationary vortex part 810 and a vortex matter revolution 820; One live axle 830; One motor 840; One is installed between described live axle 830 ends and the described vortex matter revolution 820 to order about the sliding sleeve 850 of vortex matter revolution 820 revolution motions (revolution operation); And an anti-rotation mechanism 860 that is used to prevent vortex matter revolution 820 rotations, as a partition ring (Oldham ring).Described live axle 830, described motor 840, described sliding sleeve 850 and described anti-rotation mechanism 860 have been formed the revolution motion actuator of described vortex matter revolution 820.
As Fig. 2 and shown in Figure 4, described shell 100 comprises that a front side frequency variator shell 110, one rear side main shells 130 and are arranged at the master bracket 120 between described frequency variator shell 110 and the described main shell 130.But, other different known example also can be used as described shell 100.
Described suction port 600 and described exhaust port 700 are located in the described shell 100, freezing mixture is sucked by described suction port 600 from a vaporizer, after the pressing chamber 880 between described stationary vortex part 810 and the described vortex matter revolution 820 compresses, just can be expelled to a condenser by described exhaust port 700.
Particularly, according to content of the present invention, a frequency variator 200 is arranged at the front surface of described stationary vortex part 810, and is oppositely arranged with described stationary vortex part 810; One inlet hole 815 passes described stationary vortex part 810 and enters described pressing chamber 880.Described inlet hole 815 is arranged at the outer perimeter of described stationary vortex part 810, and the freezing mixture of suction is discharged when its center is compressed from the outer rim of described stationary vortex part 810.
Therefore, the freezing mixture of described suction flows between described frequency variator 200 and described guiding element 900, to cool off described frequency variator 200 and described pressing chamber 880 simultaneously.
Meanwhile, described guiding element 900 can not be provided with, and the freezing mixture of described suction process between described frequency variator 200 and described stationary vortex part 810, and make freezing mixture be sucked into described pressing chamber 880 by the inlet hole 815 of described stationary vortex part 810.
Freezing mixture is through after the described pressing chamber 880, through a tap hole 821 that is arranged at described vortex matter revolution 820, discharges by described exhaust port 700 then.
As shown in the figure, the freezing mixture of described suction is to discharge through the rear end of described shell 100 by a discharge route 835, and described discharge route passes described live axle 830 along the longitudinal direction of described live axle 830; But, described discharge route 835 might not be set to pass described live axle 830.
Meanwhile, as shown in the figure, described guiding element 900 can be provided with an introduction mouth 910 that communicates with the inlet hole 815 of described stationary vortex part 810.This structure makes the freezing mixture of described suction be flowed into described pressing chamber 880 by described guiding element 900 guiding backs.
Observe from the direction of described live axle, many guide channels 920 extend around described guiding element 900.In the case, an end of a minimum guide channel 920 is arranged at the position near described suction port 600, and its other end then is arranged at the position of introducing mouth 910 near described.
Therefore, when freezing mixture when described suction port 600 guides to described introduction mouthfuls 910, freezing mixture cools off described frequency variator 200 and described pressing chamber 880 equably.
Particularly, be arranged at a sidewall of described shell 100 when described suction port 600, the some of described guide channel 920 can be provided with a straight line in a side of described suction port 600 and introduce section 921, and all the other parts of described guide channel 920 can form arc guiding element 922, to cool off described pressing chamber 880 equably.Therefore, when freezing mixture is inhaled into, and after introducing section 921 and introduced rapidly by described straight line, just can be through described arc guiding element 922 to cool off the front surface of described pressing chamber 880 equably.The suction freezing mixture of finishing behind the cooling down operation can be introduced into described pressing chamber 880 by described introduction mouthfuls 910 and described inlet hole 815.
As shown in the figure, according to content of the present invention, because described exhaust port 700 is located at the rear side of described vortex matter revolution 820, one side of described suction freezing mixture and exhaust port, the one section suitable distance of being separated by, therefore, described suction freezing mixture can avoid being subjected to a silhouette of exhaust port to ring, thereby can bring into play its cooling effect comprehensively.
As shown in the figure, described guide channel 920 is made of many guiding raised line 923, but also can be made of guide recess.
Meanwhile, the discharge route 835 that is arranged at described live axle 830 along its rear side forward side tilt laterally partly from the axle center of described live axle 830 gradually.By this structure, the freezing mixture of oily sub can be resolved into gas and fluid oil by centrifugal force during by described pressing chamber 880, can be back to described discharge route 835 after the oil that is decomposed out, is supplied to main bearing 870.
Circulation/the cooling down operation of oil content of the suction of variable-frequency type scroll compressor of the present invention is described below in conjunction with Fig. 2 and Fig. 3:
At first, the freezing mixture of described suction is inhaled into from a vaporizer (not shown) by the described suction port 600 that is arranged at described shell 100.
Then, freezing mixture keeps utmost point low temperature, and contains small amount of liquid.
When the freezing mixture of described suction during, just can cool off described frequency variator 200 and described pressing chamber 800 simultaneously, and be heated to suitable degree of superheat simultaneously through the described guiding element 900 between described frequency variator 200 and the described stationary vortex part 810.
After the freezing mixture of described suction passes through described guiding element 900 fully, be introduced into described pressing chamber 880 by the described introduction mouth 910 of described guiding element 900 and the described inlet hole 815 of described stationary vortex part 810.
When described pressing chamber 880 carried out squeeze operation, the freezing mixture of the described suction of the thing followed can carry out cooling down operation.Carry out cooling down operation simultaneously in squeeze operation, can lower and make squeeze operation reach an energy that preset pressure is required.
The freezing mixture of finishing the compression processing is discharged by described exhaust port 700 then through being arranged at the described tap hole 821 of described vortex matter revolution 820.
Particularly, as shown in the figure, because described discharge route 835 passes described live axle 830 along the longitudinal direction of described live axle 830, freezing mixture is through behind the described tap hole 821, rear end through described shell 100 is expelled to described exhaust port 700 by the passage of being located between drive motor and the described shell 100 then.
For reaching this purpose, the radial extending groove 170 for described freezing mixture process can be set in the rear end of described shell 100.
Fig. 6 is a pressure-enthalpy chart, represents the cooling cycle of variable-frequency type scroll compressor of the present invention.Below be the explanation of in conjunction with the accompanying drawings a cooling cycle being done:
A-B-C-D-E-F segment table among the figure has shown the cyclic process of freezing mixture.Particularly, the A-D section is with respect to a compressor, and the D-E section is with respect to a condenser, and the E-F section is with respect to an expansion valve, and the F-A section is with respect to a vaporizer.
As shown in the figure, according to content of the present invention, the freezing mixture of described suction contains liquid when the introduction section A of described compressor.That is exactly that when the liquid volume in the described vaporizer was increasing, heat exchange efficiency just can improve thereupon.
The temperature of freezing mixture of showing A shown in the figure → B segment table rises and state that described frequency variator 200 is cooled simultaneously; The temperature of described freezing mixture of showing B → C segment table rises and compressed freezing mixture is cooled simultaneously in described pressing chamber 880 state.Two sections cooling programs are gasified totally the freezing mixture of described suction, and make the freezing mixture of described suction remain on suitable degree of superheat.
C afterwards → D segment table shows the compression process of the freezing mixture that in fact is inhaled into.But, because the coolant cools that compressed freezing mixture is inhaled into during compression process, it reaches to a preset pressure with trend very rapidly.That is be just can finish compression process as long as consume less energy.
As shown in the figure, dotted line is represented a constant entropy process, and represents a theory relation.
As shown in the figure, according to content of the present invention, isentropic efficiency surpasses 100%, and isentropic efficiency is defined as the energy of isentropic process (PAs) with respect to the energy (active force) in the real process (PAr).
As reference, Fig. 7 shows the cooling cycle of traditional scroll compressor, and the freezing mixture of wherein said suction only cools off frequency variator.
As shown in the figure, when freezing mixture passes through A ' → B ' section cooling frequency variator and after being heated simultaneously, freezing mixture enters a pressing chamber immediately, the energy consumption that reaches a predetermined pressure is significantly risen.That is that therefore, with respect to the present invention, the efficient of traditional scroll compressor is seriously undermined because do not had cooling action by described suction freezing mixture at the freezing mixture of described pressing chamber compression.
As shown in the figure, dotted line is represented a constant entropy process, and isentropic efficiency can't surpass 100%.
According to the present invention, by frequency variator produce the overheat of compressor problem can freezing mixture cools off frequency variator simultaneously and compresses refrigerant is avoided by sucking, and the efficient of compressor is promoted greatly.
In addition, because the efficiengy-increasing of compressor, the energy consumption of compression can significantly reduce.
Moreover, when originally freezing mixture is inhaled into, reduce degree of superheat, also can promote the heat exchange efficiency of vaporizer.
In addition, by discharging the chamber away from sucking the gas setting, it is overheated and compression efficiency is reduced just can to avoid discharging the chamber.
Claims (11)
1. variable-frequency type scroll compressor, it comprises:
One shell;
One is fixedly installed in the stationary vortex part in the described shell;
One is set to along the vortex matter revolution of described stationary vortex part revolution;
One is set to drive the actuator of described vortex matter revolution revolution;
Be arranged at a suction port and an exhaust port in the described shell;
One frequency variator that is arranged at described stationary vortex part front surface and is oppositely arranged with described stationary vortex part;
Wherein, described stationary vortex part is established one and is passed the inlet hole that described stationary vortex part enters a pressing chamber; Described vortex matter revolution is established a tap hole; Freezing mixture is introduced into described pressing chamber by the space between described frequency variator and the described stationary vortex part through described inlet hole, discharges by described tap hole then.
2. variable-frequency type scroll compressor according to claim 1 is characterized in that: the position relative with described frequency variator at the antetheca of described stationary vortex part is provided with a guiding element, and the freezing mixture that sucks from described suction port is guided to described inlet hole.
3. variable-frequency type scroll compressor according to claim 2 is characterized in that: described guiding element is provided with an introduction mouth that communicates with the described inlet hole of described stationary vortex part.
4. variable-frequency type scroll compressor according to claim 3 is characterized in that: observe from the direction of described live axle, many guide channels extend around described guiding element.
5. variable-frequency type scroll compressor according to claim 4 is characterized in that: an end of a minimum described guide channel is arranged at the position near described suction port, and its other end then is arranged at the position of introducing mouth near described.
6. variable-frequency type scroll compressor according to claim 5 is characterized in that: described guide channel is arc for the rarest one section.
7. variable-frequency type scroll compressor according to claim 5 is characterized in that: a minimum described guide channel is provided with straight line introduction section in a side of described suction port.
8. according to any one described variable-frequency type scroll compressor of claim 4 to 7, it is characterized in that: described guide channel is made of many guiding raised lines or guide recess.
9. according to any one described variable-frequency type scroll compressor of claim 1 to 7, it is characterized in that: described exhaust port is arranged at the rear side of described vortex matter revolution.
10. according to any one described variable-frequency type scroll compressor of claim 1 to 7, it is characterized in that: a discharge route passes described live axle along the longitudinal direction of described live axle.
11. variable-frequency type scroll compressor according to claim 10 is characterized in that: be arranged at described live axle discharge route minimum one section along its rear side forward side tilt laterally from the axle center of described live axle gradually.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020080018985A KR100927437B1 (en) | 2008-02-29 | 2008-02-29 | Inverter Scroll Compressor |
| KR10-2008-0018985 | 2008-02-29 | ||
| PCT/KR2009/000951 WO2009108006A2 (en) | 2008-02-29 | 2009-02-27 | Inverter type scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102007297A true CN102007297A (en) | 2011-04-06 |
Family
ID=41016600
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009801065481A Pending CN102007297A (en) | 2008-02-29 | 2009-02-27 | Inverter type scroll compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20110008197A1 (en) |
| KR (1) | KR100927437B1 (en) |
| CN (1) | CN102007297A (en) |
| DE (1) | DE112009000419T5 (en) |
| WO (1) | WO2009108006A2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6225064B2 (en) * | 2014-04-16 | 2017-11-01 | Ｋｙｂ株式会社 | Electric pump |
| JP6222012B2 (en) * | 2014-08-29 | 2017-11-01 | 株式会社デンソー | Electronic component cooling structure and electric compressor |
| US10760479B2 (en) * | 2018-06-26 | 2020-09-01 | Fca Us Llc | Turbocharger surge management control techniques to eliminate surge valve |
| KR20210012291A (en) * | 2019-07-24 | 2021-02-03 | 한온시스템 주식회사 | Scroll compressor |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06280757A (en) * | 1993-03-30 | 1994-10-04 | Toyota Autom Loom Works Ltd | Scroll type compressor |
| US20040101428A1 (en) * | 2002-03-13 | 2004-05-27 | Yoshitaka Shibamoto | Scroll type fluid machine |
| US20040109772A1 (en) * | 2002-12-06 | 2004-06-10 | Matsushita Electric Industrial Co., Ltd. | Electric compressor with inverter |
| US20040191100A1 (en) * | 2003-03-31 | 2004-09-30 | Yoshiyuki Nakane | Compressor |
| JP2007224809A (en) * | 2006-02-23 | 2007-09-06 | Matsushita Electric Ind Co Ltd | Electric compressor |
| JP2007292044A (en) * | 2006-03-28 | 2007-11-08 | Matsushita Electric Ind Co Ltd | Electric compressor |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5026262A (en) * | 1989-11-28 | 1991-06-25 | Carrier Corporation | Multipiece eccentric shaft |
| JPH07247968A (en) * | 1994-03-09 | 1995-09-26 | Daikin Ind Ltd | Scroll compressor |
| US6139295A (en) * | 1998-06-22 | 2000-10-31 | Tecumseh Products Company | Bearing lubrication system for a scroll compressor |
| KR20010002248U (en) * | 1998-12-19 | 2001-10-18 | 전주범 | Shaft Lubrication Structure of Hermetic Compressor_ |
| US6361281B1 (en) * | 2000-08-22 | 2002-03-26 | Delphi Technologies, Inc. | Electrically driven compressor with contactless control |
| JP2002180981A (en) * | 2000-12-12 | 2002-06-26 | Toyota Industries Corp | Scroll type compressor |
| JP2005171951A (en) * | 2003-12-15 | 2005-06-30 | Matsushita Electric Ind Co Ltd | Electric compressor |
| JP3744522B2 (en) * | 2004-03-11 | 2006-02-15 | 松下電器産業株式会社 | Electric compressor |
-
2008
- 2008-02-29 KR KR1020080018985A patent/KR100927437B1/en active IP Right Grant
-
2009
- 2009-02-27 DE DE112009000419T patent/DE112009000419T5/en not_active Ceased
- 2009-02-27 US US12/919,495 patent/US20110008197A1/en not_active Abandoned
- 2009-02-27 WO PCT/KR2009/000951 patent/WO2009108006A2/en active Application Filing
- 2009-02-27 CN CN2009801065481A patent/CN102007297A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06280757A (en) * | 1993-03-30 | 1994-10-04 | Toyota Autom Loom Works Ltd | Scroll type compressor |
| US20040101428A1 (en) * | 2002-03-13 | 2004-05-27 | Yoshitaka Shibamoto | Scroll type fluid machine |
| US20040109772A1 (en) * | 2002-12-06 | 2004-06-10 | Matsushita Electric Industrial Co., Ltd. | Electric compressor with inverter |
| US20040191100A1 (en) * | 2003-03-31 | 2004-09-30 | Yoshiyuki Nakane | Compressor |
| JP2007224809A (en) * | 2006-02-23 | 2007-09-06 | Matsushita Electric Ind Co Ltd | Electric compressor |
| JP2007292044A (en) * | 2006-03-28 | 2007-11-08 | Matsushita Electric Ind Co Ltd | Electric compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2009108006A2 (en) | 2009-09-03 |
| WO2009108006A9 (en) | 2010-12-23 |
| KR100927437B1 (en) | 2009-11-19 |
| KR20090093455A (en) | 2009-09-02 |
| US20110008197A1 (en) | 2011-01-13 |
| DE112009000419T5 (en) | 2011-03-03 |
| WO2009108006A3 (en) | 2009-12-10 |
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Application publication date: 20110406 |