CN101963161A - Turbocompressor and refrigerating machine - Google Patents

Turbocompressor and refrigerating machine Download PDF

Info

Publication number
CN101963161A
CN101963161A CN2010102333909A CN201010233390A CN101963161A CN 101963161 A CN101963161 A CN 101963161A CN 2010102333909 A CN2010102333909 A CN 2010102333909A CN 201010233390 A CN201010233390 A CN 201010233390A CN 101963161 A CN101963161 A CN 101963161A
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.)
Granted
Application number
CN2010102333909A
Other languages
Chinese (zh)
Other versions
CN101963161B (en
Inventor
塚本稔
小田兼太郎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
IHI Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by IHI Corp filed Critical IHI Corp
Publication of CN101963161A publication Critical patent/CN101963161A/en
Application granted granted Critical
Publication of CN101963161B publication Critical patent/CN101963161B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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

Abstract

The invention provides a kind of turbocompressor and refrigerating machine.This turbocompressor possesses: impeller; The compressing section has and refrigerant is imported to impeller or will export to outside vortex chamber by the refrigerant that the rotation of impeller is compressed; Fuel tank is equipped with heater, stores lubricant oil; Near fuel tank, dispose at least a portion of vortex chamber.

Description

Turbocompressor and refrigerating machine
The application advocates preference 2009-170191 number to the Japanese patent application of filing an application on July 21st, 2009, quotes its content here.
Technical field
The present invention relates to turbocompressor and refrigerating machine.More particularly, relate to can with fluid by the compression of a plurality of impellers turbocompressor and possess the refrigerating machine of this turbocompressor.
Background technique
As with cooling such as water object cooling or freezing refrigerating machine, known have the compressing mechanism that possesses by possessing impeller etc. with the turbo refrigerating machine of the refrigerant compression and the turbocompressor of discharging etc.In compressor, big if compression ratio becomes, then the temperature that spues of compressor uprises, and volumetric efficiency descends.So, in possessing the turbocompressor of turbo refrigerating machine as described above etc., a plurality of sections situations (for example, with reference to special table 2008-506885 communique) of carrying out the compression of refrigerant that are divided into are arranged.
In such turbocompressor, dispose the spiral helicine vortex chamber outside or that be used for refrigerant is imported to for compression the inside of compressor that the refrigerant that is used for compressing exports to compressor.In addition, for being used for the sliding positions such as bearing of swivel bearing impeller etc. from the fuel tank supplying lubricating oil.
In above-mentioned turbocompressor and refrigerating machine in the past, when long-term operation stopped, refrigerant was condensate in below in the vortex chamber.Therefore, before the running that begins compressor again, the cooling medium liquid of condensation need be discharged to outside operation from the liquid port of the below that is provided in vortex chamber etc., trouble becomes.
Summary of the invention
The present invention In view of the foregoing makes, even purpose provides and a kind ofly stops refrigerant condensation in vortex chamber, also it automatically can be got rid of promptly the turbocompressor of entry into service and refrigerating machine again in the vortex chamber because of long-term operation.
According to the 1st technological scheme of the present invention, relevant turbocompressor of the present invention possesses: casing has sliding position; Impeller is connected and rotates around axis with axial region on being bearing in above-mentioned sliding position; A plurality of compressing sections have and fluid are imported to this impeller or will export to outside vortex chamber by the fluid that the rotation of above-mentioned impeller is compressed; Fuel tank is equipped with heating source, stores the lubricant oil that above-mentioned sliding position is supplied with; Near this fuel tank, dispose at least a portion of above-mentioned vortex chamber.
This turbocompressor disposes at least a portion of vortex chamber near the fuel tank that is equipped with heating source.Therefore, the heat by heating source lubricant oil of heating before running begins again suitably can be transferred heat to the vortex chamber wall from the fuel tank wall.And, can by this heat will the compression of condensation in vortex chamber the fluid heating.
Thereby, no longer need the cooling medium liquid of condensation is discharged to outside operation from the liquid port of the below that is provided in vortex chamber etc., can not carry out special operation and entry into service again.
According to the 2nd technological scheme of the present invention, relevant turbocompressor of the present invention is above-mentioned turbocompressor, and at least a portion of above-mentioned vortex chamber is configured in than the pasta that is stored in the lubricant oil in the above-mentioned fuel tank by the below.According to this turbocompressor, the heat of lubricant oil of heating more suitably can be transmitted to vortex chamber.
According to the 3rd technological scheme of the present invention, relevant refrigerating machine of the present invention possesses: condenser, with the refrigerant cooling liquid of compression; Vaporizer seizes heat of vaporization and with the cooling of above-mentioned cooling object by the above-mentioned refrigerant evaporation that makes liquefaction from the cooling object; Turbocompressor will be supplied in the above-mentioned condenser by the above-mentioned refrigerant compression of above-mentioned evaporator evaporation; As above-mentioned turbocompressor, use above-mentioned turbocompressor.
This refrigerating machine plays effect, the effect same with above-mentioned turbocompressor.
According to the present invention, even refrigerant condensation in vortex chamber when long-term operation stops also can automatically to be got rid of it and entry into service more promptly in vortex chamber.
Description of drawings
Fig. 1 is the block diagram of schematic configuration of the turbo refrigerating machine of the relevant one embodiment of the present invention of expression.
Fig. 2 is the vertical sectional view of the turbocompressor that possesses of the turbo refrigerating machine of relevant one embodiment of the present invention.
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 relevant turbocompressor of the present invention and refrigerating machine is described.
The turbo refrigerating machine of relevant present embodiment (refrigerating machine) 1 is arranged in mansion or the factory for the cooling water that generates for example idle call, as shown in Figure 1, possesses condenser 2, economizer 3, vaporizer 5 and turbocompressor 6.
Condenser 2 for example is supplied to the compression refrigerant gas X1 as the refrigerants such as R134a (fluid) that compress with gaseous state, by this compression refrigerant gas X1 cooling liquid is become cooling medium liquid X2.This condenser 2 as shown in Figure 1, the stream R1 that flows through via compression refrigerant gas X1 is connected with turbocompressor 6.In addition, condenser 2 is connected with economizer 3 via the stream R2 that cooling medium liquid X2 flows through.In stream R2, the expansion valve 7 that is used for cooling medium liquid X2 decompression is set.
Economizer 3 will be stored by expansion valve 7 post-decompression cooling medium liquid X2 temporarily.This economizer 3 is connected with vaporizer 5 via the stream R3 that cooling medium liquid X2 flows through.In addition, economizer 3 is connected with turbocompressor 6 via the stream R4 that the gaseous component X3 of the refrigerant that is produced by economizer 3 flows through.Stream R3 is provided with the expansion valve 8 that is used for the further decompression of cooling medium liquid X2.Stream R4 is connected with turbocompressor 6, so that it supplies with gaseous component X3 to second compressing section 23 described later that turbocompressor 6 possesses.
Vaporizer 5 is by making cooling medium liquid X2 evaporation, seizing heat of vaporization and will cool off the object cooling from cooling objects such as water.The stream R5 that the cold media air X4 that this vaporizer 5 produces via the evaporation by cooling medium liquid X2 flows through is connected with turbocompressor 6.Stream R5 is connected with first compressing section 22 described later that turbocompressor 6 possesses.
Turbocompressor 6 becomes above-mentioned compression refrigerant gas X1 with cold media air X4 compression.This turbocompressor 6 is connected with condenser 2 via the stream R1 that compression refrigerant gas X1 flows through as described above.In addition, turbocompressor 6 is connected with vaporizer 5 via the stream R5 that cold media air X4 flows through.
To shown in Figure 4, this turbocompressor 6 possesses casing 11, a plurality of compressing section 12 with a plurality of sliding positions 10 and the fuel tank 13 that stores lubricant oil LO as Fig. 2.
Casing 11 is divided into motor casing 15, compressor housing 16 and gear housing 17, connects separably respectively.In motor casing 15, dispose the output shaft 18 that rotates around axes O with being connected output shaft 18 motor 20 of drive compression section 12.The clutch shaft bearing 21 that output shaft 18 is fixed on the motor casing 15 is rotatably mounted.Here, sliding position 10 not only comprises clutch shaft bearing 21, also comprises second bearing 26 described later, the 3rd bearing 27, gear unit 28 etc.
Compressing section 12 possesses and cold media air X4 (with reference to Fig. 1) is sucked and first compressing section 22 of compression and will be by the cold media air X4 after 22 compressions of first compressing section further compression and second compressing section 23 of discharging as compression refrigerant gas X1 (with reference to Fig. 1).First compressing section 22 is configured in the compressor housing 16, and second compressing section 23 is configured in the gear housing 17.
First compressing section 22 possesses on the running shaft of being fixed on (axial region) 25, rotated driving by motor 20 around axes O, give the speed energy and a plurality of first impellers (impeller) 22a of getting rid of to direction radially to the cold media air X4 that supplies with from thrust direction, by the speed power conversion that will be given to cold media air X4 by the first impeller 22a is the first diffuser 22b that pressure energy compresses, to export to first vortex chamber (vortex chamber) 22c of the outside of first compressing section 22 by the cold media air X4 of first diffuser 22b compression, with the suction port 22d that cold media air X4 is sucked and supply with to the first impeller 22a.The part of the first diffuser 22b, the first vortex chamber 22c and suction port 22d is formed by the first housing 22e that surrounds the first impeller 22a.
On the suction port 22d of first compressing section 22, be provided with a plurality of inlet guide blade 22g that are used for regulating the inlet capacity of first compressing section 22.Each guide blade 22g that enters the mouth can rotate under driving mechanism 22i effect, so that the area of its flow direction from cold media air X4 on apparent can change.
At the first impeller 22a of first compressing section 22 and be among the first housing 22e of peripheral part of suction port 22d of its upstream side, divide and be formed with that to be with the axes O be the circular-arc relaying space 22h at center.In the 22h of this relaying space, take in the driving mechanism 22i that drives above-mentioned inlet guide blade 22g in inside.
The back side of the inlet guide blade 22g of this relaying space 22h and suction port 22d becomes connected state via less clearance 22j.Thus, constitute, relaying space 22h is always equated with the pressure of suction port 22d.
Second compressing section 23 possesses giving the speed energy and second impeller (impeller) 23a that discharges to direction radially by the compression of first compressing section 22 and from the cold media air X4 that thrust direction is supplied with, by the speed power conversion that will be given cold media air X4 by the second impeller 23a is that pressure energy compresses, the second diffuser 23b as compression refrigerant gas X1 discharge, to export to second vortex chamber (vortex chamber) 23c of the outside of second compressing section 23 from the compression refrigerant gas X1 that the second diffuser 23b discharges, with will direct into importing vortex chamber (vortex chamber) 23d of the second impeller 23a by the cold media air X4 of first compressing section 22 compression.Here, the part of the second diffuser 23b, the second vortex chamber 23c and importing vortex chamber 23d is formed by the second housing 23e that surrounds the second impeller 23a.
The second impeller 23a is fixed on the above-mentioned running shaft 25, so that it aligns 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, thereby is rotated driving.The second diffuser 23b with ring-type be configured in the second impeller 23a around.
The second vortex chamber 23c is connected with the stream R1 that is used for compression refrigerant gas X1 supplies in the condenser 2, will supply to the stream R1 from the compression refrigerant gas X1 that derive second compressing section 23.
In addition, the first vortex chamber 22c of first compressing section 22 is connected via the outside pipe arrangement (not shown) with first compressing section 22 and second compressing section, 23 splits setting with the importing vortex chamber 23d of second compressing section 23, will be supplied in second compressing section 23 by the cold media air X4 of first compressing section, 22 compressions via this outside pipe arrangement.Connecting above-mentioned stream R4 (with reference to Fig. 1) on this outside pipe arrangement, the gaseous component X3 of the refrigerant that will be produced by economizer 3 supplies in second compressing section 23 via outside pipe arrangement.
Running shaft 25 can be rotated to support on the casing 11 by being fixed on second bearing 26 on the gear housing 17 and the 3rd bearing 27 that is fixed on the compressor housing 16.
In gear housing 17, be formed with to accommodate and be used for the driving force of output shaft 18 is passed to the containing space S1 of the gear unit 28 of running shaft 25.
Fuel tank 13 extends to the below in the compressor housing 16 and forms configuration from the below of containing space S1.Be configured to, make the lower side of the first vortex chamber 22c, the second vortex chamber 23c and importing vortex chamber 23d lean on the below than the pasta L that is stored in the lubricant oil LO in the fuel tank 13.
In fuel tank 13, dispose and be used for lubricant oil LO is heated to the heater (heating source) 30 of set point of temperature.
Gear unit 28 possess the large diameter gear 31 on the output shaft 18 that is fixed on motor 20 and be fixed on the running shaft 25 and with the small-diameter gear 32 of large diameter gear 31 engagements.And, the rotating power of the output shaft 18 of motor 20 is passed to running shaft 25, so that the rotating speed of running shaft 25 increases with respect to the rotating speed of output shaft 18.
Then, the turbo refrigerating machine 1 of relevant present embodiment and the effect of turbocompressor 6 are described.
At first, along with the running of turbo refrigerating machine 1 and turbocompressor 6 begins, lubricant oil LO is supplied to sliding position 10 from fuel tank 13 by not shown oil pump.Then, drive motor 20 passes to running shaft 25 with the rotating power of the output shaft 18 of motor 20 via gear unit 28.Thus, rotation drives first compressing section 22 and second compressing section 23.
If rotation drives first compressing section 22, then the suction port 22d of first compressing section 22 becomes negative pressure state, flow in first compressing section 22 via suction port 22d from the cold media air X4 of stream R5.At this moment, suitably regulate inlet capacity by inlet guide blade 22g.
The cold media air X4 that flow into the inside of first compressing section 22 flow into the first impeller 22a from thrust direction, is given the speed energy by the first impeller 22a, radially discharges.
The cold media air X4 that will discharge from the first impeller 22a is by being that pressure energy compresses with the first diffuser 22b with the speed power conversion.To export to the outside of first compressing section 22 from the cold media air X4 that the first diffuser 22b discharges via the first vortex chamber 22c.
Then, the cold media air X4 that exports to the outside of first compressing section 22 is supplied in second compressing section 23 via outside pipe arrangement.
The cold media air X4 that supplies in second compressing section 23 flow into the second impeller 23a from thrust direction via importing vortex chamber 23d, gives the speed energy by the second impeller 23a, radially discharges.
The cold media air X4 that will discharge from the second impeller 23a is by being pressure energy and further compression becomes compression refrigerant gas X1 by the second diffuser 23b with the speed power conversion.
To export to the outside of second compressing section 23 from the compression refrigerant gas X1 that the second diffuser 23b discharges via the second vortex chamber 23c.
Then, the compression refrigerant gas X1 that exports to the outside of second compressing section 23 is supplied in the condenser 2 via stream R1.
Under the situation of using R134a etc. as cooling medium liquid X2, because condensing temperature is 30 ℃～40 ℃, so when turbo refrigerating machine 1 is stopped for a long time, below them, be condensed as the refrigerant of gas residue in the first vortex chamber 22c, the second vortex chamber 23c, importing vortex chamber 23d.
When the running beginning, the lubricant oil LO that will be stored in the fuel tank 13 by heater 30 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, imports each wall of vortex chamber 23d from the wall of fuel tank 13, will be in the refrigerant heating of indoor condensation.Thereupon, refrigerant evaporation and become gas once more.
According to this turbo refrigerating machine 1 and turbocompressor 6, the first vortex chamber 22c, the second vortex chamber 23c, the lower side that imports vortex chamber 23d be configured in fuel tank 13 near.Therefore, when turbocompressor 6 is started, by will be stored in the lubricant oil LO heating in the fuel tank 13 by heater 30, can be with the refrigerant heating evaporation of condensation in the first vortex chamber 22c, the second vortex chamber 23c, importing vortex chamber 23d, automatically from indoor eliminating.
At this moment, because being configured in than the pasta L that is stored in the lubricant oil LO in the fuel tank 13, the lower side of the first vortex chamber 22c, the second vortex chamber 23c, importing vortex chamber 23d leans on the below, so can more suitably transmit the heat of the lubricant oil LO of heating.
In addition, technical scope of the present invention is not limited to above-mentioned mode of execution, various changes in addition in the scope that does not break away from purport of the present invention.
For example, in the above-described embodiment, the structure that possesses two compressing sections (first compressing section 22 and second compressing section 23) is illustrated, but is not limited thereto, also can adopt the structure that possesses the compressing section more than 3.
And then, be illustrated dividing the turbocompressor that is formed with motor casing 15, compressor housing 16 and gear housing 17 respectively as casing 11, but being not limited thereto, for example also can be the structure of motor configurations between first compressing section and second compressing section.
More than, preferred embodiment of the present invention has been described, but the present invention is not limited to these embodiments.In the scope that does not break away from purport of the present invention, can carry out adding, omit, replacing and other changes of structure.The present invention is not limited by above-mentioned explanation, and only is defined by the claims.

Claims (3)

1. a turbocompressor is characterized in that,
Possess:
Casing has sliding position;
Impeller is connected and rotates around axis with axial region on being bearing in above-mentioned sliding position;
A plurality of compressing sections have and fluid are imported to this impeller or will export to outside vortex chamber by the fluid that the rotation of above-mentioned impeller is compressed;
Fuel tank is equipped with heating source, stores the lubricant oil that above-mentioned sliding position is supplied with;
Near this fuel tank, dispose at least a portion of above-mentioned vortex chamber.
2. turbocompressor as claimed in claim 1 is characterized in that, at least a portion of above-mentioned vortex chamber is configured in than the pasta that is stored in the lubricant oil in the above-mentioned fuel tank by the below.
3. a refrigerating machine is characterized in that,
Possess:
Condenser is with the refrigerant cooling liquid of compression;
Vaporizer seizes heat of vaporization and with the cooling of above-mentioned cooling object by the above-mentioned refrigerant evaporation that makes liquefaction from the cooling object;
Turbocompressor will be supplied in the above-mentioned condenser by the above-mentioned refrigerant compression of above-mentioned evaporator evaporation;
As above-mentioned turbocompressor, use claim 1 or 2 described turbocompressor.
CN201010233390.9A 2009-07-21 2010-07-19 Turbo compressor and refrigerator Active CN101963161B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-170191 2009-07-21
JP2009170191A JP5326900B2 (en) 2009-07-21 2009-07-21 Turbo compressor and refrigerator

Publications (2)

Publication Number Publication Date
CN101963161A true CN101963161A (en) 2011-02-02
CN101963161B 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)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102213221A (en) * 2010-04-06 2011-10-12 株式会社Ihi Turbo compressor and turbo refrigerator
CN103245118A (en) * 2012-02-07 2013-08-14 Lg电子株式会社 Turbo refrigerator
CN110307176A (en) * 2013-03-06 2019-10-08 三菱重工制冷空调系统株式会社 Turborefrigerator compressor and its fuel tank and turborefrigerator
CN110476025A (en) * 2017-03-29 2019-11-19 三菱重工制冷空调系统株式会社 Refrigeration machine

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5240392B2 (en) * 2011-09-30 2013-07-17 ダイキン工業株式会社 Refrigeration equipment
JP6056270B2 (en) * 2012-08-28 2017-01-11 ダイキン工業株式会社 Turbo compressor and 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

Citations (10)

* Cited by examiner, † Cited by third party
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
EP0446635A2 (en) * 1990-02-13 1991-09-18 Iwata Air Compressor Mfg. Co.,Ltd. Scroll-type fluid machinery
US5211031A (en) * 1990-05-24 1993-05-18 Hitachi, Ltd. Scroll type compressor and refrigeration cycle using the same
US5345785A (en) * 1991-10-30 1994-09-13 Hitachi, Ltd. Scroll compressor and air conditioner using the same
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
JP2004232481A (en) * 2003-01-28 2004-08-19 Hitachi Ltd Scroll compression device for helium
US20060130495A1 (en) * 2004-07-13 2006-06-22 Dieckmann John T System and method of refrigeration
US20070147985A1 (en) * 2005-12-28 2007-06-28 Ishikawajima-Harima Heavy Industries Co., Ltd. Turbo compressor

Patent Citations (10)

* Cited by examiner, † Cited by third party
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
EP0446635A2 (en) * 1990-02-13 1991-09-18 Iwata Air Compressor Mfg. Co.,Ltd. Scroll-type fluid machinery
US5211031A (en) * 1990-05-24 1993-05-18 Hitachi, Ltd. Scroll type compressor and refrigeration cycle using the same
US5345785A (en) * 1991-10-30 1994-09-13 Hitachi, Ltd. Scroll compressor and air conditioner using the same
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
JP2004232481A (en) * 2003-01-28 2004-08-19 Hitachi Ltd Scroll compression device for helium
US20060130495A1 (en) * 2004-07-13 2006-06-22 Dieckmann John T System and method of refrigeration
US20070147985A1 (en) * 2005-12-28 2007-06-28 Ishikawajima-Harima Heavy Industries Co., Ltd. Turbo compressor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102213221A (en) * 2010-04-06 2011-10-12 株式会社Ihi Turbo compressor and turbo refrigerator
US9027362B2 (en) 2010-04-06 2015-05-12 Ihi Corporation Turbo compressor and turbo refrigerator
CN102213221B (en) * 2010-04-06 2016-01-20 大金工业株式会社 Turbocompressor and turborefrigerator
CN103245118A (en) * 2012-02-07 2013-08-14 Lg电子株式会社 Turbo refrigerator
CN103245118B (en) * 2012-02-07 2015-09-16 Lg电子株式会社 Turbo refrigerating machine
CN110307176A (en) * 2013-03-06 2019-10-08 三菱重工制冷空调系统株式会社 Turborefrigerator compressor and its fuel tank and turborefrigerator
CN110476025A (en) * 2017-03-29 2019-11-19 三菱重工制冷空调系统株式会社 Refrigeration machine

Also Published As

Publication number Publication date
JP2011026958A (en) 2011-02-10
CN101963161B (en) 2014-12-31
JP5326900B2 (en) 2013-10-30
US20110016916A1 (en) 2011-01-27

Similar Documents

Publication Publication Date Title
CN101963161A (en) Turbocompressor and refrigerating machine
US10378539B2 (en) System including high-side and low-side compressors
CN101105346B (en) Frequency conversion magnetic levitation compression expansion engine set
JP5262155B2 (en) Turbo compressor and refrigerator
CN101504009B (en) Turbo compressor and refrigerator
US20160047575A1 (en) Compressor Bearing Cooling
CN100547244C (en) Helical-lobe compressor
CN102042227B (en) Double-rotor two-stage enthalpy-increase compressor, air conditioner and heat pump water heater
WO2017215493A1 (en) Refrigerating unit
US9416788B2 (en) Turbo compressor and refrigerator
CN207647779U (en) Compressor and air-conditioning system with it
CN101504015B (en) Turbo compressor and refrigerator
US8756954B2 (en) Turbo compressor and turbo refrigerator
CN101963160B (en) Turbo compressor and refrigerator
CN218439808U (en) Compressor, refrigerant circulation system and air conditioning equipment
CN104315750B (en) The system and method for cooling gas compressor inlet gas
US20110289961A1 (en) Enhanced liquid pressure cycle having an ejector
CN201093793Y (en) Frequency conversion magnetic suspension compressing and expanding unit assembly
US2820350A (en) Refrigeration apparatus
CN213627937U (en) Rolling rotor type and centrifugal composite compressor
CN115717600A (en) Compressor, refrigerant circulation system and air conditioning equipment
JP2000074506A (en) Compression refrigerating machine with built-in motor
JP2001280740A (en) Air conditioner
CN114458583A (en) Rolling rotor type and centrifugal composite compressor

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.