CN101963161B - Turbo compressor and refrigerator - Google Patents
Turbo compressor and refrigerator Download PDFInfo
- Publication number
- CN101963161B CN101963161B CN201010233390.9A CN201010233390A CN101963161B CN 101963161 B CN101963161 B CN 101963161B CN 201010233390 A CN201010233390 A CN 201010233390A CN 101963161 B CN101963161 B CN 101963161B
- Authority
- CN
- China
- Prior art keywords
- mentioned
- turbocompressor
- vortex chamber
- impeller
- compressing section
- 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.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/06—Lubrication
- F04D29/063—Lubrication specially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/01—Heaters
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention provides a turbo compressor and a refrigerator. The turbo compressor includes an impeller; compression stages having scroll chambers which introduce the refrigerant to the impeller or lead the refrigerant compressed by the rotation of the impeller to the outside; and an oil tank in which a heater is disposed and an lubricant oil is stored, and at least a part of the scroll chambers is disposed in the vicinity of the oil tank.
Description
The Japanese patent application 2009-170191 CLAIM OF PRIORITY that the application filed an application on July 21st, 2009, quotes its content here.
Technical field
The present invention relates to turbocompressor and refrigerating machine.More particularly, relating to can by fluid by the turbocompressor of multiple wheel compresses and the refrigerating machine possessing this turbocompressor.
Background technique
As by the cooling of cooling object or freezing refrigerating machines such as water, there will be a known the compressing mechanism possessed by possessing impeller etc. and refrigerant is compressed and the turbo refrigerating machine etc. of the turbocompressor of discharging.Within the compressor, if compression ratio becomes large, then the temperature that spues of compressor uprises, and volumetric efficiency declines.So, in the turbocompressor possessing turbo refrigerating machine as described above etc., have and be divided into multiple sections of situations (showing 2008-506885 publication for example, referring to spy) of carrying out the compression of refrigerant.
In such turbocompressor, spiral helicine vortex chamber that is that be configured with the outside for the refrigerant of compression being exported to compressor or that be used for inside refrigerant being imported to compressor in order to compress.In addition, lubricant oil is supplied for being used for the sliding position such as bearing of swivel bearing impeller etc. from fuel tank.
In above-mentioned turbocompressor in the past and refrigerating machine, when long-term running stops, refrigerant is condensate in below in vortex chamber.Therefore, before the running starting compressor again, need the operation cooling medium liquid of condensation be discharged to the outside from the liquid port etc. of the below being disposed in vortex chamber, become trouble.
Summary of the invention
The present invention makes in view of the foregoing, even if object being to provide a kind of refrigerant condensation in vortex chamber because operating stopping for a long time, also it automatically can being got rid of and the turbocompressor of promptly entry into service again and refrigerating machine in vortex chamber.
According to the 1st technological scheme of the present invention, turbocompressor for the present invention possesses: casing, has sliding position; Impeller, is connected with the axle portion be bearing on above-mentioned sliding position and rotates about the axis; Multiple compressing section, has and fluid is imported to this impeller or the fluid that the rotation by above-mentioned impeller compressed exports to outside vortex chamber; Fuel tank, is equipped with heating source, stores the lubricant oil supplied above-mentioned sliding position; Near this fuel tank, be configured with above-mentioned vortex chamber at least partially.
This turbocompressor is configured with vortex chamber at least partially being equipped with near the fuel tank of heating source.Therefore, it is possible to suitably transfer heat to vortex chamber wall by by the heat of lubricant oil of heating before heating source is running again from fuel tank wall.Further, can by this heat by the fluid heating of the compression of condensation in vortex chamber.
Thus, no longer need the operation cooling medium liquid of condensation be discharged to the outside from the liquid port etc. of the below being disposed in vortex chamber, special operation can not be carried out and entry into service again.
According to the 2nd technological scheme of the present invention, turbocompressor for the present invention is above-mentioned turbocompressor, above-mentioned vortex chamber be configured at least partially than the lubricant oil be stored in above-mentioned fuel tank pasta on the lower.According to this turbocompressor, the heat of the lubricant oil of heating more suitably can be transmitted to vortex chamber.
According to the 3rd technological scheme of the present invention, refrigerating machine for the present invention possesses: condenser, by the refrigerant cooling liquid of compression; Vaporizer, seizes heat of vaporization from cooling object by making the above-mentioned refrigerant evaporation of liquefaction and is cooled by above-mentioned cooling object; Turbocompressor, compresses the above-mentioned refrigerant by above-mentioned evaporator evaporation and is supplied in above-mentioned condenser; As above-mentioned turbocompressor, use above-mentioned turbocompressor.
This refrigerating machine plays the effect same with above-mentioned turbocompressor, effect.
According to the present invention, even if refrigerant condensation in vortex chamber when long-term running stops, also it automatically can being got rid of and promptly entry into service again in vortex chamber.
Accompanying drawing explanation
Fig. 1 is the block diagram of the schematic configuration of the turbo refrigerating machine representing a mode of execution for the present invention.
Fig. 2 is the vertical sectional view of the turbocompressor that the turbo refrigerating machine of a mode of execution for the present invention possesses.
Fig. 3 is the III-III sectional view of Fig. 2.
Fig. 4 is the IV-IV sectional view of Fig. 2.
Embodiment
Referring to figs. 1 through Fig. 4, one mode of execution of turbocompressor for the present invention and refrigerating machine is described.
About the turbo refrigerating machine (refrigerating machine) 1 of present embodiment is arranged in mansion or factory to generate the cooling water of such as idle call, as shown in Figure 1, possess condenser 2, economizer 3, vaporizer 5 and turbocompressor 6.
Condenser 2 is such as supplied to the compression refrigerant gas X1 as refrigerants (fluid) such as the R134a compressed with gaseous state, by this compression refrigerant gas X1 cooling liquid is become cooling medium liquid X2.As shown in Figure 1, the stream R1 flow through via compression refrigerant gas X1 is connected with turbocompressor 6 this condenser 2.In addition, the stream R2 that condenser 2 flows through via cooling medium liquid X2 is connected with economizer 3.In stream R2, the expansion valve 7 being used for cooling medium liquid X2 to reduce pressure is set.
Economizer 3 will by the post-decompression cooling medium liquid X2 temporary reservoir of expansion valve 7.The stream R3 that this economizer 3 flows through via cooling medium liquid X2 is connected with vaporizer 5.In addition, the stream R4 that economizer 3 flows through via the gaseous component X3 of the refrigerant produced by economizer 3 is connected with turbocompressor 6.Stream R3 is provided with the expansion valve 8 for being reduced pressure further by cooling medium liquid X2.Stream R4 is connected with turbocompressor 6, supplies gaseous component X3 to make it to the second compressing section 23 described later that turbocompressor 6 possesses.
Vaporizer 5 cools object by making cooling medium liquid X2 evaporate, from water etc. and seizes heat of vaporization and will cool object cooling.The stream R5 that the cold media air X4 that this vaporizer 5 produces through the evaporation of cooling medium liquid X2 flows through is connected with turbocompressor 6.The first compressing section 22 described later that stream R5 and turbocompressor 6 possess is connected.
Cold media air X4 compresses and becomes above-mentioned compression refrigerant gas X1 by turbocompressor 6.The stream R1 that this turbocompressor 6 flows through via compression refrigerant gas X1 is as described above connected with condenser 2.In addition, the stream R5 that turbocompressor 6 flows through via cold media air X4 is connected with vaporizer 5.
As shown in Figures 2 to 4, this turbocompressor 6 possesses casing 11, multiple compressing section 12 with multiple sliding position 10 and stores the fuel tank 13 of lubricant oil LO.
Casing 11 is divided into motor casing 15, compressor housing 16 and gear housing 17, detachably connects.In motor casing 15, be configured with the output shaft 18 that rotates around axes O and be connected output shaft 18 and drive the motor 20 of compressing section 12.Output shaft 18 rotatably supports by the clutch shaft bearing 21 be fixed on motor casing 15.Here, sliding position 10 not only comprises clutch shaft bearing 21, also comprises the second bearing 26 described later, the 3rd bearing 27, gear unit 28 etc.
Compressing section 12 possesses and to be sucked by cold media air X4 (with reference to Fig. 1) and the first compressing section 22 compressed and the second compressing section 23 compressed further by the cold media air X4 after being compressed by the first compressing section 22 and discharge as compression refrigerant gas X1 (reference Fig. 1).First compressing section 22 is configured in compressor housing 16, and the second compressing section 23 is configured in gear housing 17.
First compressing section 22 possesses and is fixed on running shaft (axle portion) 25, by motor 20 around axes O rotary actuation, multiple first impeller (impeller) 22a that the cold media air X4 imparting velocity energy supplied from thrust direction is got rid of to radial direction, the the first diffuser 22b compressed is carried out by the velocity energy being given to cold media air X4 by the first impeller 22a is transformed to pressure energy, the cold media air X4 compressed by the first diffuser 22b is exported to the first vortex chamber (vortex chamber) 22c of the outside of the first compressing section 22, with the suction port 22d supplied by cold media air X4 suction and to the first impeller 22a.A part of first diffuser 22b, the first vortex chamber 22c and suction port 22d is formed by the first housing 22e surrounding the first impeller 22a.
On the suction port 22d of the first compressing section 22, be provided with the inlet guide vane 22g of multiple inlet capacity being used for adjustment first compressing section 22.Each inlet guide vane 22g can rotate under driving mechanism 22i effect, changes from the area the flow direction of cold media air X4 is apparent to enable it.
The first impeller 22a in the first compressing section 22 and be in its upstream side suction port 22d peripheral part the first housing 22e in, divide the relaying space 22h be formed with in arc-shaped centered by axes O.In the 22h of this relaying space, be accommodated with the driving mechanism 22i driving above-mentioned inlet guide vane 22g in inside.
The back side of the inlet guide vane 22g of this relaying space 22h and suction port 22d becomes connected state via less gap 22j.Thus, be configured to, make relaying space 22h always equal with the pressure of suction port 22d.
Second compressing section 23 possesses being compressed by the first compressing section 22 and the second impeller (impeller) 23a giving velocity energy from the cold media air X4 of thrust direction supply and discharge to radial direction, by compressing being transformed to pressure energy by the second impeller 23a to the velocity energy that cold media air X4 gives, as the second diffuser 23b that compression refrigerant gas X1 discharges, the compression refrigerant gas X1 discharged from the second diffuser 23b is exported to the second vortex chamber (vortex chamber) 23c of the outside of the second compressing section 23, with importing vortex chamber (vortex chamber) 23d cold media air X4 compressed by the first compressing section 22 being directed into the second impeller 23a.Here, a part of the second diffuser 23b, the second vortex chamber 23c and importing vortex chamber 23d is formed by the second housing 23e surrounding the second impeller 23a.
Second impeller 23a is fixed on above-mentioned running shaft 25, to make it align with the first impeller 22a back side, from output shaft 18 transmitting rotary power of motor 20, running shaft 25 is rotated around axes O, thus carries out rotary actuation.Second diffuser 23b is configured in around the second impeller 23a with ring-type.
Second vortex chamber 23c is connected with the stream R1 be used for compression refrigerant gas X1 is supplied in condenser 2, the compression refrigerant gas X1 derived is supplied in stream R1 from the second compressing section 23.
In addition, first vortex chamber 22c of the first compressing section 22 is connected via with the outside pipe arrangement (not shown) that the first compressing section 22 and the second compressing section 23 split are arranged with the importing vortex chamber 23d of the second compressing section 23, is supplied in the second compressing section 23 by the cold media air X4 compressed via this outside pipe arrangement by the first compressing section 22.This outside pipe arrangement is connected to above-mentioned stream R4 (with reference to Fig. 1), the gaseous component X3 of the refrigerant produced by economizer 3 is supplied in the second compressing section 23 via outside pipe arrangement.
Running shaft 25 be can be rotated to support on casing 11 with the 3rd bearing 27 be fixed on compressor housing 16 by the second bearing 26 be fixed in gear housing 17.
In gear housing 17, be formed with collecting and be used for the containing space S1 of the gear unit 28 driving force of output shaft 18 being passed to running shaft 25.
Fuel tank 13 extends to the below in compressor housing 16 from the below of containing space S1 and forms configuration.Be configured to, the lower side making the first vortex chamber 22c, the second vortex chamber 23c and import vortex chamber 23d than the lubricant oil LO be stored in fuel tank 13 pasta L on the lower.
In fuel tank 13, be configured with the heater (heating source) 30 for lubricant oil LO being heated to set point of temperature.
Gear unit 28 possesses the large diameter gear 31 that is fixed on the output shaft 18 of motor 20 and is fixed on the small-diameter gear 32 engaged on running shaft 25 and with large diameter gear 31.Further, the rotating power of the output shaft 18 of motor 20 is passed to running shaft 25, increase relative to the rotating speed of output shaft 18 to make the rotating speed of running shaft 25.
Then, be described about the turbo refrigerating machine 1 of present embodiment and the effect of turbocompressor 6.
First, along with the running of turbo refrigerating machine 1 and turbocompressor 6 starts, by not shown oil pump, lubricant oil LO is supplied to sliding position 10 from fuel tank 13.Then, drive motor 20, passes to running shaft 25 by the rotating power of the output shaft 18 of motor 20 via gear unit 28.Thus, rotary actuation first compressing section 22 and the second compressing section 23.
If rotary actuation first compressing section 22, then the suction port 22d of the first compressing section 22 becomes negative pressure state, and the cold media air X4 from stream R5 flow in the first compressing section 22 via suction port 22d.Now, suitably inlet capacity is regulated by inlet guide vane 22g.
The cold media air X4 flowing into the inside of the first compressing section 22 flow into the first impeller 22a from thrust direction, is given velocity energy, radially discharge by the first impeller 22a.
The cold media air X4 discharged from the first impeller 22a is compressed by velocity energy being transformed to pressure energy with the first diffuser 22b.The cold media air X4 discharged from the first diffuser 22b is exported to the outside of the first compressing section 22 via the first vortex chamber 22c.
Then, the cold media air X4 exporting to the outside of the first compressing section 22 is supplied in the second compressing section 23 via outside pipe arrangement.
The cold media air X4 be supplied in the second compressing section 23 flow into the second impeller 23a via importing vortex chamber 23d from thrust direction, gives velocity energy, radially discharge by the second impeller 23a.
The cold media air X4 discharged from the second impeller 23a being compressed further by velocity energy being transformed to pressure energy by the second diffuser 23b, becoming compression refrigerant gas X1.
The compression refrigerant gas X1 discharged from the second diffuser 23b is exported to the outside of the second compressing section 23 via the second vortex chamber 23c.
Then, the compression refrigerant gas X1 exporting to the outside of the second compressing section 23 is supplied in condenser 2 via stream R1.
When using R134a etc. as cooling medium liquid X2, because condensing temperature is 30 DEG C ~ 40 DEG C, so when making turbo refrigerating machine 1 stop for a long time, be condensed in their below at the first vortex chamber 22c, the second vortex chamber 23c, the refrigerant imported in vortex chamber 23d as gas residue.
When operating beginning, by heater 30, the lubricant oil LO be stored in fuel tank 13 is heated to more than the condensing temperature of refrigerant.Thus, the heat of the lubricant oil LO of heating is delivered to the first vortex chamber 22c, the second vortex chamber 23c from the wall of fuel tank 13, imports each wall of vortex chamber 23d, is heated by the refrigerant in indoor condensation.Thereupon, refrigerant evaporation and again become gas.
Be configured near fuel tank 13 according to this turbo refrigerating machine 1 and turbocompressor 6, first vortex chamber 22c, the second vortex chamber 23c, the lower side that imports vortex chamber 23d.Therefore, when turbocompressor 6 is started, by the lubricant oil LO be stored in fuel tank 13 being heated by heater 30, can by the first vortex chamber 22c, the second vortex chamber 23c, import condensation in vortex chamber 23d refrigerant heating evaporation, automatically get rid of indoor.
Now, due to the first vortex chamber 22c, the second vortex chamber 23c, the lower side that imports vortex chamber 23d be configured in than the lubricant oil LO be stored in fuel tank 13 pasta L on the lower, so the heat of the lubricant oil LO of heating more suitably can be transmitted.
In addition, technical scope of the present invention is not limited to above-mentioned mode of execution, without departing from the spirit and scope of the invention can various change in addition.
Such as, in the above-described embodiment, the structure possessing two compressing sections (first compressing section 22 and the second compressing section 23) is illustrated, but is not limited thereto, also can adopt the structure of the compressing section possessing more than 3.
And then, be illustrated dividing as casing 11 turbocompressor being formed with motor casing 15, compressor housing 16 and gear housing 17 respectively, such as, but being not limited thereto, also can be the structure of motor configurations between the first compressing section and the second compressing section.
Above, describe preferred embodiment of the present invention, but the present invention is not limited to these embodiments.Can carry out without departing from the spirit and scope of the invention structure additional, omit, displacement and other change.The present invention does not limit by above-mentioned explanation, and is only defined by the claims.
Claims (2)
1. a turbocompressor, is characterized in that,
Possess:
Casing, has sliding position;
Impeller, is connected with the axle portion be bearing on above-mentioned sliding position and rotates about the axis;
Multiple compressing section, has and fluid is imported to this impeller or the fluid that the rotation by above-mentioned impeller compressed exports to outside vortex chamber;
Fuel tank, is equipped with heating source, stores the lubricant oil supplied above-mentioned sliding position;
Near this fuel tank, be configured with above-mentioned vortex chamber at least partially;
Above-mentioned vortex chamber be configured at least partially than the above-mentioned lubricant oil be stored in above-mentioned fuel tank pasta on the lower.
2. a refrigerating machine, is characterized in that,
Possess:
Condenser, by the refrigerant cooling liquid of compression;
Vaporizer, seizes heat of vaporization from cooling object by making the above-mentioned refrigerant evaporation of liquefaction and is cooled by above-mentioned cooling object;
Turbocompressor, compresses the above-mentioned refrigerant by above-mentioned evaporator evaporation and is supplied in above-mentioned condenser;
As above-mentioned turbocompressor, use the turbocompressor described in claim 1.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009170191A JP5326900B2 (en) | 2009-07-21 | 2009-07-21 | Turbo compressor and refrigerator |
| JP2009-170191 | 2009-07-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101963161A CN101963161A (en) | 2011-02-02 |
| CN101963161B true CN101963161B (en) | 2014-12-31 |
Family
ID=43496105
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010233390.9A Active CN101963161B (en) | 2009-07-21 | 2010-07-19 | Turbo compressor and refrigerator |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20110016916A1 (en) |
| JP (1) | JP5326900B2 (en) |
| CN (1) | CN101963161B (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5515990B2 (en) | 2010-04-06 | 2014-06-11 | 株式会社Ｉｈｉ | Turbo compressor and turbo refrigerator |
| JP5240392B2 (en) * | 2011-09-30 | 2013-07-17 | ダイキン工業株式会社 | Refrigeration equipment |
| KR20130091009A (en) * | 2012-02-07 | 2013-08-16 | 엘지전자 주식회사 | Turbo chiller |
| JP6056270B2 (en) * | 2012-08-28 | 2017-01-11 | ダイキン工業株式会社 | Turbo compressor and turbo refrigerator |
| JP6223696B2 (en) * | 2013-03-06 | 2017-11-01 | 三菱重工サーマルシステムズ株式会社 | Oil tank for turbo refrigerator compressor and compressor for turbo refrigerator |
| JP6111912B2 (en) | 2013-07-10 | 2017-04-12 | ダイキン工業株式会社 | Turbo compressor and turbo refrigerator |
| JP6565116B2 (en) * | 2015-06-04 | 2019-08-28 | 株式会社Ｉｈｉ回転機械エンジニアリング | Turbo compressor |
| JP2018169059A (en) * | 2017-03-29 | 2018-11-01 | 三菱重工サーマルシステムズ株式会社 | refrigerator |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0446635A2 (en) * | 1990-02-13 | 1991-09-18 | Iwata Air Compressor Mfg. Co.,Ltd. | Scroll-type fluid machinery |
| CN1336527A (en) * | 2000-08-02 | 2002-02-20 | 三菱重工业株式会社 | Turbine compressor and refrigerator |
| CN1410680A (en) * | 2001-09-25 | 2003-04-16 | Lg电子株式会社 | Turbine compressor |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4066869A (en) * | 1974-12-06 | 1978-01-03 | Carrier Corporation | Compressor lubricating oil heater control |
| JPS56146095A (en) * | 1980-04-15 | 1981-11-13 | Hitachi Ltd | Centrifugal compressor for refrigeration |
| JPH0431689A (en) * | 1990-05-24 | 1992-02-03 | Hitachi Ltd | Scroll compressor and freezing cycle with scroll compressor |
| KR930008386A (en) * | 1991-10-30 | 1993-05-21 | 가나이 쯔또무 | Shallow compressors and air conditioners using it |
| JP4107492B2 (en) * | 2003-01-28 | 2008-06-25 | 株式会社日立製作所 | Scroll compressor for helium and scroll compressor for helium |
| JP2008506885A (en) * | 2004-07-13 | 2008-03-06 | タイアックス エルエルシー | Refrigeration system and refrigeration method |
| JP4947405B2 (en) * | 2005-12-28 | 2012-06-06 | 株式会社Ｉｈｉ | Turbo compressor |
-
2009
- 2009-07-21 JP JP2009170191A patent/JP5326900B2/en not_active Expired - Fee Related
-
2010
- 2010-07-19 CN CN201010233390.9A patent/CN101963161B/en active Active
- 2010-07-21 US US12/840,368 patent/US20110016916A1/en not_active Abandoned
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0446635A2 (en) * | 1990-02-13 | 1991-09-18 | Iwata Air Compressor Mfg. Co.,Ltd. | Scroll-type fluid machinery |
| CN1336527A (en) * | 2000-08-02 | 2002-02-20 | 三菱重工业株式会社 | Turbine compressor and refrigerator |
| CN1410680A (en) * | 2001-09-25 | 2003-04-16 | Lg电子株式会社 | Turbine compressor |
Non-Patent Citations (2)
| Title |
|---|
| JP昭56-146095A 1981.11.13 * |
| JP特开2004-232481A 2004.08.19 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101963161A (en) | 2011-02-02 |
| US20110016916A1 (en) | 2011-01-27 |
| JP5326900B2 (en) | 2013-10-30 |
| JP2011026958A (en) | 2011-02-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101963161B (en) | Turbo compressor and refrigerator | |
| CN101105346B (en) | Frequency conversion magnetic levitation compression expansion engine set | |
| JP5262155B2 (en) | Turbo compressor and refrigerator | |
| KR100423618B1 (en) | Turbocompressor and refrigerating machine | |
| JP5167845B2 (en) | Turbo compressor and refrigerator | |
| CN100547244C (en) | Helical-lobe compressor | |
| CN104823360B (en) | motor rotor and air gap cooling | |
| CN104454657A (en) | Turbo-compressor and refrigeration cycle apparatus | |
| CN116398452A (en) | Magnetic suspension centrifugal heat pump compressor with wide frequency conversion operation | |
| JP3728399B2 (en) | Oil / refrigerant pump for centrifugal chillers | |
| US8756954B2 (en) | Turbo compressor and turbo refrigerator | |
| CN103518106A (en) | Condensing device | |
| US9416788B2 (en) | Turbo compressor and refrigerator | |
| JP5136096B2 (en) | Turbo compressor and refrigerator | |
| CN218439808U (en) | Compressor, refrigerant circulation system and air conditioning equipment | |
| JP5272941B2 (en) | Turbo compressor and refrigerator | |
| JP6004004B2 (en) | Turbo refrigerator | |
| CN102859202B (en) | Axial flow compressor | |
| JP5545326B2 (en) | Turbo compressor and refrigerator | |
| CN219953690U (en) | Magnetic suspension centrifugal heat pump compressor with wide frequency conversion operation | |
| EP3006860B1 (en) | Turbo refrigerator | |
| CN112112824B (en) | Pump press, refrigeration cycle system and control method thereof | |
| CN115717600A (en) | Compressor, refrigerant circulation system and air conditioning equipment | |
| JP2000074506A (en) | Compression refrigerating machine with built-in motor | |
| RU2330186C1 (en) | Centrifugal steam and gas hydraulic machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20151117 Address after: Osaka City, Osaka of Japan Patentee after: Daikin Industries, Ltd. Address before: Tokyo, Japan, Japan Patentee before: IHI Corp. |