CN104075476B - Turborefrigerator - Google Patents
Turborefrigerator Download PDFInfo
- Publication number
- CN104075476B CN104075476B CN201410085652.XA CN201410085652A CN104075476B CN 104075476 B CN104075476 B CN 104075476B CN 201410085652 A CN201410085652 A CN 201410085652A CN 104075476 B CN104075476 B CN 104075476B
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- China
- Prior art keywords
- refrigerant
- injector
- pressure
- compressor
- turbo
- 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.)
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- 239000003507 refrigerant Substances 0.000 claims abstract description 89
- 238000005057 refrigeration Methods 0.000 claims abstract description 18
- 239000002828 fuel tank Substances 0.000 claims abstract description 17
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 9
- 239000000498 cooling water Substances 0.000 claims abstract description 7
- 238000001704 evaporation Methods 0.000 claims description 3
- 230000008020 evaporation Effects 0.000 claims description 2
- 238000002347 injection Methods 0.000 claims 1
- 239000007924 injection Substances 0.000 claims 1
- 238000011084 recovery Methods 0.000 abstract description 9
- 230000006641 stabilisation Effects 0.000 abstract description 5
- 238000011105 stabilization Methods 0.000 abstract description 5
- 230000002045 lasting effect Effects 0.000 abstract description 2
- 230000006835 compression Effects 0.000 description 9
- 238000007906 compression Methods 0.000 description 9
- 239000003795 chemical substances by application Substances 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 239000012809 cooling fluid Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000003252 repetitive effect Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000010025 steaming Methods 0.000 description 1
Classifications
-
- 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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0016—Ejectors for creating an oil recirculation
Abstract
The present invention provides a kind of Stress control by carrying out the driving gas of injector, to ensure the sufficient oil recovery function of injector, so as to the turborefrigerator of the operating of the stabilization of lasting refrigeration machine.Capture heat possessing from cold water so as to which refrigerant evaporates and plays the evaporator of refrigeration（3）, pass through the turbo-compressor of wheel compresses refrigerant（1）And the refrigerant gas compressed is cooled down condensing condensed device using cooling water（2）Turborefrigerator in, possess：Injector（20）, it will be from turbo-compressor（1）The refrigerant gas of discharge includes as driving gas, attraction and is stranded in evaporator（3）Oily refrigerant be recycled to compressor（1）Fuel tank；Valve is controlled, it is arranged at refrigerant gas from turbo-compressor（1）Supply to injector（20）Refrigerant supplying tubing（5BP）, and control in refrigerant supplying tubing（5BP）The pressure of the refrigerant gas of flowing；And control device（10）, it is to control valve（21）Aperture be controlled.
Description
Technical field
Gas is discharged as the spray of driving gas the present invention relates to turborefrigerator, more particularly to by the use of using compressor
Emitter is by comprising being stranded in the turborefrigerator of the oily refrigerant-recovery of evaporator to the mode of fuel tank.
Background technology
In the past, the turborefrigerator for being used in refrigerating air conditioning device etc. is made up of the closed system for enclosing refrigerant, and
And linked by refrigerant piping from cold water（Cooled fluid）Capture heat so as to which refrigerant evaporates and plays refrigeration
Evaporator, compression are turned into the compressor of higher pressure refrigerant gas by the refrigerant gas of the evaporator evaporation, utilize cooling
Water（Cooling fluid）Make the condensing condensed device of higher pressure refrigerant gas cooling and the condensing refrigerant progress decompression is made
Its expansion valve expanded（Expansion mechanism）To constitute.Moreover, multistage using being carried out by multistage impeller to refrigerant gas
In the case that the compound compressor of compression is as compressor, enters and be about to as the refrigeration being arranged between condensed device and evaporator
The refrigerant gas that the energy-saving appliance of intercooler in agent pipe arrangement is produced imports the intergrade of compressor（The centre of multi-stage impeller
Part）.
Turborefrigerator have as high-speed rotary body compressor, compressor be provided with rotating body for supporting bearing and
The booster engine of defined rotation number is obtained for carrying out speedup to rotary body.Freon class refrigeration is provided to bearing and booster engine
The oil of agent and intermiscibility come maintain lubrication and refrigerating function.The fuel tank portion of oil is kept to prevent from letting out to the oily of refrigerant system
Leakage utilizes balance pipe（Fuel tank balance pipe）It is pressed into the low-pressure section of refrigeration machine.
However, axle envelope part or the balance pipe of a part of oil via rotary body can not be avoided completely（Fuel tank is pressed
Pipe）Leak to refrigerant system.If to refrigerant system oily leakage continue, fuel tank possessed oil reduction, from without
Can be to bearing and booster engine fuel feeding, and the operating of turborefrigerator can not be continued.Therefore, in turborefrigerator, from refrigeration
The oil of agent system reclaims the very important effect of Function.
Existing oil recovery method is using making the discharge gas of compressor turn into the injector of driving gas, from oil most
The evaporator or compressor air suction blade secondary side being detained eventually are by comprising oily refrigerant-recovery to fuel tank.
Patent document 1：Japanese Unexamined Patent Publication 55-20049 publications
In above-mentioned existing oil recovery method, the driving pressure of injector is cooled down by the most important condition of compressor
Coolant-temperature gage condition determines, so the operating under the performance peak point that there is a situation where can not to carry out injector, it is impossible to effectively living
Function is reclaimed with the oil of injector.Accordingly, there exist can not by oil is fully recycled to fuel tank, fuel tank is possessed oil reduces so as to
Can not to bearing and booster engine fuel feeding, can not continue turborefrigerator operating it is such the problem of.
The content of the invention
The present invention be in view of above-mentioned thing and complete, its object is to used there is provided the driving by carrying out injector
The Stress control of gas, to ensure the sufficient oil recovery function of injector, so as to the operating of the stabilization of lasting refrigeration machine
Turborefrigerator.
In order to reach above-mentioned purpose, a mode of the invention is characterised by, possess from cold water capture heat so as to
Refrigerant is evaporated and plays the evaporator of refrigeration, the turbo-compressor by wheel compresses refrigerant and utilization are cooled down
Water makes the refrigerant gas compressed cool down in the turborefrigerator of condensing condensed device, possesses injector, it will be from turbine pressure
The refrigerant gas of contracting machine discharge attracts to include the oily refrigerant-recovery for being stranded in evaporator to turbine as driving gas
The fuel tank of compressor；Valve is controlled, its refrigerant supply for being arranged at the supply refrigerant gas from turbo-compressor to injector is matched somebody with somebody
Pipe, and control the pressure of refrigerant gas flowed in the refrigerant supplying tubing；And control device, it is to the control valve
Aperture be controlled.
According to the present invention, the refrigerant piping branch from connection turbo-compressor and condensed device is provided with, by refrigerant
The refrigerant supplying tubing of injector is imported from turbo-compressor, and in refrigerant supplying tubing, is set in the upstream side of injector
It is equipped with control valve.Control device to the aperture for controlling valve by being controlled, so as to control supply to the refrigerant of injector
Pressure.Thereby, it is possible to control the suction pressure in injector suction unit.Under performance peak point therefore, it is possible to carry out injector
Operating, so can substantially ensure that injector oil reclaim function, the operating of the stabilization of refrigerator can be carried out.
The preferred embodiment of the present invention is characterised by, sets multiple injectors, and connect injector and above-mentioned whirlpool with pipe arrangement
The suction vane secondary side of wheel compression machine.
In accordance with the invention it is possible to the oily refrigerant-recovery that the suction vane secondary side for being stranded in turbine refrigerator will be included
To fuel tank.
The preferred embodiment of the present invention is characterised by that the control device is controlled such that to the aperture of the control valve
Obtain the pressure of the refrigerant gas supplied from the turbo-compressor to the injector（Pd）It is attracted with from the evaporator
To the pressure of the refrigerant of the injector（Pe）Pressure ratio（Pd/Pe）For setting.
According to the present invention, control device turns into controlling the aperture of valve to be controlled such that from the usual characteristic of injector
It is that the optimal injector driving pressure of performance peak point compares Pd/Pe.
The present invention preferred embodiment be characterised by, the pressure ratio（Pd/Pe）Setting according to the species of refrigerant
And change.
The preferred embodiment of the present invention is characterised by, in the case that refrigerant is R134a, the pressure ratio（Pd/Pe）'s
Setting is about 1.7.
The preferred embodiment of the present invention is characterised by, is supplied from the turbo-compressor to the refrigerant gas of the injector
The pressure of body is determined by being arranged at the pressure sensor in the downstream for controlling valve in the refrigerant supplying tubing.
The preferred embodiment of the present invention is characterised by, the pressure of the refrigerant of the injector is attracted to from the evaporator
Power（Pe）Determined by being arranged at the pressure sensor of the evaporator.
The preferred embodiment of the present invention is characterised by, the pressure of the refrigerant of the injector is attracted to from the evaporator
Power（Pe）Determined by being arranged at the pressure sensor for the pipe arrangement for connecting the evaporator and the injector.
According to the present invention, by being operated with the injector pressure ratio of the performance peak point as injector, it can be ensured that
Sufficiently oil reclaims function, possess fuel tank the oil that must and sufficiently measure, the operating of the stabilization of refrigeration machine can be continued.
Brief description of the drawings
Fig. 1 is the schematic diagram for the embodiment for representing the turborefrigerator of the present invention.
Fig. 2 is the schematic sectional view for the detailed construction for representing injector.
Fig. 3 is represented by injector driving pressure than injector that Pd/Pe and injector suction unit suction pressure are represented
The chart of performance.
Embodiment
Hereinafter, 1~Fig. 3 of reference picture is illustrated to the embodiment of the turborefrigerator of the present invention.In Fig. 1~Fig. 3,
To the attached identical mark of inscape identically or comparably, simultaneously the repetitive description thereof will be omitted.
Fig. 1 is the schematic diagram for the embodiment for representing the turborefrigerator of the present invention.As shown in figure 1, turborefrigerator has
Standby turbo-compressor 1, its compression refrigerant；Condensed device 2, it utilizes cooling water（Cooling fluid）Make the refrigerant gas compressed
Cooling is condensing；Evaporator 3, it is from cold water（Cooled fluid）Capture heat so as to which refrigerant evaporates and plays refrigeration；Section
Energy device 4, it is arranged in the intercooler between condensed device 2 and evaporator 3, wherein, pass through the refrigerant of refrigerant circulation
Pipe arrangement 5 connects these each equipment to constitute.
In the embodiment shown in Fig. 1, turbo-compressor 1 is made up of multistage turbocompressor, multistage turbocompressor
By two-stage turbine compression mechanism into by first order impeller 11, second level impeller 12 and the pressure for rotating these impellers 11,12
Contracting machine motor 13 is constituted.Adjustment suck stream of the refrigerant gas to impeller 11,12 is provided with the suction side of first order impeller 11
The suction vane 14 of amount.Turbo-compressor 1 possesses collecting bearing, the gear-box 15 of booster engine, is set in the bottom of gear-box 15
Have for the fuel tank 16 to bearing and booster engine fuel feeding.Gear-box 15 is pressed into turbo-compressor 1 by fuel tank balance pipe 16
Low-pressure section.Turbo-compressor 1 is connected by stream 8 with energy-saving appliance 4, leads the refrigerant gas being separated in energy-saving appliance 4
Enter the multistage compression stage of turbo-compressor 1（It is two grades in the example）Center section（It is first order impeller 11 and the in the example
Part between sencond stage impeller 12）.
In the kind of refrigeration cycle for the turborefrigerator being configured as shown in Figure 1, refrigerant is in turbo-compressor 1, condensing
Circulated in device 2, evaporator 3 and energy-saving appliance 4, cold water manufactured come corresponding with load using the Cooling and Heat Source obtained by evaporator 3,
The power of turbo-compressor 1 into the heat for carrying out flash-pot 3 in kind of refrigeration cycle and with being supplied from motor 13 is suitable
Heat is released into the cooling water for being supplied to condensed device 2.On the other hand, the refrigerant gas being separated in energy-saving appliance 4 is imported into
The center section of the multi-stage compression level of turbo-compressor 1, second is passed through with the refrigerant gas interflow from first order compressor
Level compressor compresses.By two stages of compression single-stage economizer cycle, the refrigeration part that energy-saving appliance 4 is brought is attached with, so
Correspondingly refrigeration increase, compared with being not provided with the situation of energy-saving appliance 4, can realize the high efficiency of refrigeration.
As shown in figure 1, the branch of refrigerant piping 5 from connection turbo-compressor 1 and condensed device 2 is provided with, by refrigerant
The refrigerant supplying tubing 5BP of injector 20 is imported from turbo-compressor 1.In refrigerant supplying tubing 5BP, in injector 20
Upstream side is provided with electric-type control valve 21, by being controlled to the aperture for controlling valve 21, can control supply to injector
The pressure of 20 refrigerant.The discharge side of injector 20 is connected with gear-box 15.On the other hand, evaporator 3 and turbo-compressor
The suction vane secondary side of machine 1 is connected via pipe arrangement 6 with injector 20.In refrigerant supplying tubing 5BP, in electric-type control valve
The pressure for determining refrigerant is provided with 21 secondary side（Injector driving pressure）Pressure sensor S1.In addition, evaporator 3 is set
It is equipped with the pressure sensor S2 for determining the pressure in evaporator 3.Electric-type control valve 21, pressure sensor S1 and pressure are passed
Sensor S2 is connected with control device 10 respectively.
In control device 10, the pressure for having refrigerant is inputted from pressure sensor S1（Injector driving pressure）Pd, from pressure
Sensor S2 inputs the pressure Pe for having evaporator 3.Control device 10 is configured to, and computing is supplied to injector from turbo-compressor 1
The pressure of 20 refrigerant gas（Pd）With the pressure for the refrigerant that injector 20 is attracted to from evaporator 3（Pe）Pressure ratio
That is, injector driving pressure is than Pd/Pe, and it is controlled based on operation values come the aperture to electric-type control valve 21, control is supplied
Pressure to the refrigerant to injector 20 is so that injector driving pressure turns into setting than Pd/Pe.In addition, from evaporator 3
It is attracted to the pressure of the refrigerant of injector 20（Pe）The pipe arrangement of evaporator 3 and injector 20 can also be connected by being arranged on
6 determination of pressure sensor.
Fig. 2 is the schematic sectional view for the detailed construction for representing injector 20.As shown in Fig. 2 injector 20 has substantially T words
The shape of shape, the pipe arrangement extended from turbo-compressor 1 and extension are connected with injector 20 in the way of being located along the same line
To the pipe arrangement of fuel tank, the suction vane from evaporator 3 and turbo-compressor 1 is generally perpendicularly connected with for the two pipe arrangements
The pipe arrangement of secondary side extension.Injector suction unit 20s is formed between nozzle 20n and diffuser 20d in injector 20.
Control device 10 is controlled by the aperture to electric-type control valve 21, so as to control to as shown in Figure 2
The pressure for the refrigerant gas that the injector 20 of composition is supplied.That is, control device 10 is switched to DYN dynamic control valve 21
Control so that it is that the optimal injector driving pressure of performance peak point compares Pd/Pe to turn into from the usual characteristic of injector.
Fig. 3 is represented by injector driving pressure than injector that Pd/Pe and injector suction unit suction pressure are represented
The chart of performance.The minimal point of the suction pressure of injector suction unit shown in Fig. 3 is the performance peak point of injector, the performance
Peak point is experimentally injector driving pressure than Pd/Pe=1.7 or so.Concrete example is mentioned, refrigerant is being regard as R134a
In the case of, in 7 DEG C of cold water outlet temperature, the common air-conditioner temperature condition of 37 DEG C of cooling water outlet temperature, evaporating pressure
For 360kPaA, condensing pressure is that discharge pressure is 960kPaA, and injector driving pressure is superfluous than about 2.7.Should
In the case of, actual operation point deviates injector performance peak point, so the oil shown as described above reclaims insufficiency
Problem.
In the present invention, above-mentioned electric-type control valve 21 is carried out closing motion, make the two of DYN dynamic control valve 21
The injector driving pressure Pd reductions of the pressure of secondary side, i.e. injector 20, it is 1.7 or so than Pd/Pe to make injector driving pressure.
In the case of the low cooling water temperature condition of 7 DEG C of fixations of cold water outlet temperature and winter, transitional period etc., there is injector driving
Pressure ratio Pd/Pe is less than 1.7 situation.In this case, being also equipped with the DYN dynamic control standard-sized sheet of valve 21 avoiding injector
Driving pressure than excessive reduction control.
According to the present invention, computing supplies the pressure of the refrigerant gas to injector 20 from turbo-compressor（Pd）With from steaming
Hair device 3 is attracted to the pressure of the refrigerant of injector 20（Pe）Pressure ratio that is, injector driving pressure than Pd/Pe, and base
The aperture of electric-type control valve 21 is controlled in operation values, the pressure of control supply to the refrigerant of injector 20（Pd）With
So that injector driving pressure is setting than Pd/Pe.Accordingly, because can carry out under the performance peak point of injector 20
Operating, so can substantially ensure that the oil of injector 20 reclaims function, can carry out the operating of the stabilization of refrigeration machine.
In fig. 1 it is shown that setting the example of an injector 20, but it is also possible to set multiple injectors 20, and with matching somebody with somebody
One injector 20 is connected by pipe with evaporator 3, with pipe arrangement by the suction vane two of another injector 20 and turbo-compressor
Secondary side connection.That is, make each injector 20 separately from evaporator 3 and the suction vane secondary side of turbo-compressor everywhere
Carry out oily recovery.In this case, by the use of control valve come to as supply to injector 20 driving gas refrigerant gas
The composition that is controlled of pressure according to above-mentioned.
So far embodiments of the present invention are illustrated, but the invention is not limited in above-mentioned embodiment, when
So can in a variety of ways it implement in the range of its technological thought.
Symbol description in figure：
1 ... turbo-compressor；2 ... condensed devices；3 ... evaporators；4 ... energy-saving appliances；5 ... refrigerant pipings；5BP ... refrigerants
Supplying tubing；6 ... pipe arrangements；8 ... streams；10 ... control devices；11 ... first order impellers；12 ... second level impellers；13 ... compressions
Machine motor；14 ... suction vanes；15 ... gear-boxes；16 ... fuel tanks；17 ... balance pipes；20 ... injectors；20d ... diffusers；
20n ... nozzles；20s ... injectors suction unit；21 ... electric-type control valves；S1 ... pressure sensors；S2 ... pressure sensors.
Claims (7)
1. a kind of turborefrigerator, possess from cold water capture heat so as to refrigerant evaporates and play the evaporator of refrigeration,
The refrigerant gas compressed is set to cool down condensing coagulate by the turbo-compressor of wheel compresses refrigerant and using cooling water
Contracting device, the turborefrigerator is characterised by possessing：
Injector, the refrigerant gas discharged from turbo-compressor is attracted to include by it as driving with gas is stranded in evaporation
The oily refrigerant of device and the fuel tank for being recycled to compressor；
Valve is controlled, it, which is arranged at, supplies refrigerant gas to the refrigerant supplying tubing of injector from turbo-compressor, and controls
Make the pressure of the refrigerant gas flowed in the refrigerant supplying tubing；And
Control device, it is controlled to the aperture for controlling valve,
The control device is controlled to the aperture of the control valve so that supplied from the turbo-compressor to the injection
The pressure of the refrigerant gas of device and by the pressure ratio of the pressure for the refrigerant that the injector is attracted to from the evaporator it is
Setting.
2. turborefrigerator according to claim 1, it is characterised in that
Multiple injectors are set, and injector and the suction vane secondary side of the turbo-compressor are connected with pipe arrangement.
3. turborefrigerator according to claim 1, it is characterised in that
The setting of the pressure ratio changes according to the species of refrigerant.
4. turborefrigerator according to claim 3, it is characterised in that
In the case where refrigerant is R134a, the setting of the pressure ratio is 1.7.
5. turborefrigerator as claimed in any of claims 1 to 4, it is characterised in that
Supplied from the turbo-compressor to the pressure of the refrigerant gas of the injector by matching somebody with somebody in refrigerant supply
The pressure sensor in the downstream for controlling valve is arranged in pipe to determine.
6. turborefrigerator as claimed in any of claims 1 to 4, it is characterised in that
The pressure that the refrigerant of the injector is attracted to from the evaporator is passed by being arranged at the pressure of the evaporator
Sensor is determined.
7. turborefrigerator as claimed in any of claims 1 to 4, it is characterised in that
The pressure of the refrigerant of the injector is attracted to from the evaporator by being arranged at the connection evaporator and institute
The pressure sensor for stating the pipe arrangement of injector is determined.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-064981 | 2013-03-26 | ||
| JP2013064981A JP6096551B2 (en) | 2013-03-26 | 2013-03-26 | Turbo refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104075476A CN104075476A (en) | 2014-10-01 |
| CN104075476B true CN104075476B (en) | 2017-07-14 |
Family
ID=51596924
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410085652.XA Active CN104075476B (en) | 2013-03-26 | 2014-03-10 | Turborefrigerator |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6096551B2 (en) |
| CN (1) | CN104075476B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110914545B (en) | 2017-07-28 | 2022-11-01 | 开利公司 | Lubrication supply system |
| RU2019103187A (en) * | 2018-02-06 | 2020-08-05 | Кэрриер Корпорейшн | Energy recovery from hot gas in the bypass line |
| CN117647033B (en) * | 2024-01-29 | 2024-04-02 | 荏原冷热系统（中国）有限公司 | Injection oil return control method |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5822064Y2 (en) * | 1978-07-25 | 1983-05-11 | 株式会社荏原製作所 | turbo refrigerator |
| JPS5579964A (en) * | 1978-12-14 | 1980-06-16 | Ebara Mfg | Oil returning device for refrigerating plant |
| JPS5738692A (en) * | 1980-08-20 | 1982-03-03 | Ebara Corp | Oil returning device of refrigerator |
| JPH0697122B2 (en) * | 1985-02-06 | 1994-11-30 | 株式会社荏原製作所 | Turbo refrigerator |
| JPH0686962B2 (en) * | 1988-11-15 | 1994-11-02 | 株式会社荏原製作所 | refrigerator |
| US5165248A (en) * | 1991-09-03 | 1992-11-24 | Carrier Corporation | Oil reclaim in a centrifugal chiller system |
| JPH06317290A (en) * | 1993-05-07 | 1994-11-15 | Mitsubishi Heavy Ind Ltd | Pressure boosting device |
| JP2002322999A (en) * | 2001-04-25 | 2002-11-08 | Mitsubishi Heavy Ind Ltd | Centrifugal compressor and refrigerator |
| JP4277597B2 (en) * | 2003-07-02 | 2009-06-10 | 株式会社日立プラントテクノロジー | Refrigeration equipment |
| JP2007232353A (en) * | 2006-01-04 | 2007-09-13 | Japan Energy Corp | Centrifugal compression refrigerator and lubricating oil used for the same |
| KR20110097367A (en) * | 2010-02-25 | 2011-08-31 | 엘지전자 주식회사 | Chiller |
| JP2011220146A (en) * | 2010-04-06 | 2011-11-04 | Ihi Corp | Turbo compressor and turbo refrigerator |
-
2013
- 2013-03-26 JP JP2013064981A patent/JP6096551B2/en active Active
-
2014
- 2014-03-10 CN CN201410085652.XA patent/CN104075476B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN104075476A (en) | 2014-10-01 |
| JP2014190578A (en) | 2014-10-06 |
| JP6096551B2 (en) | 2017-03-15 |
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