CN106196674B - Oil injection type split-compressor and heat pump - Google Patents
Oil injection type split-compressor and heat pump Download PDFInfo
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- CN106196674B CN106196674B CN201610562464.0A CN201610562464A CN106196674B CN 106196674 B CN106196674 B CN 106196674B CN 201610562464 A CN201610562464 A CN 201610562464A CN 106196674 B CN106196674 B CN 106196674B
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Classifications
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- 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
- F25B31/004—Lubrication oil recirculating arrangements
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- 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
- F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2519—On-off valves
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1932—Oil pressures
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Even if the present invention is that one kind suction pressure and discharge pressure change the oil injection type split-compressor and heat pump that can also ensure that the circulation of oil and performance will not reduce.Oil injection type split-compressor of the invention is with the first order compression unit for compressing from suction passage sucking gas and with oil and being discharged together to intermediate pressure space, the second level compression unit for compressing from intermediate pressure space sucking gas and with oil and being discharged to discharge duct together, to second level compression unit discharge side bearing for oil supply oily supply line, it is oily to the oil ring flow path of the enclosed space circulation for compressing space on the way as first order compression unit with enabling the bearing from the discharge side of second level compression unit flow out.
Description
Technical field
The present invention relates to a kind of oil injection type split-compressor and heat pumps.
Background technique
In oil-cooled type screw compressor, the indoor space of Xiang Zuowei rotor and by rotor and from suction passage and discharge stream
In the enclosed space that road keeps apart, in order to the cooling of rotor, lubrication, sealing and for oil supply, additionally to shaft sealing and bearing
Portion is for oil supply.Therefore, not only from the gas that compressor is discharged comprising oil, from shaft sealing and bearing portion also effluent oil.It needs
Oil more than both having been quantified to supplies such as shaft sealings, so recording following technologies in such as Japanese Patent Publication 6-22587:
Enable the space circulation from the oil that shaft sealing flows out into the compressor with the pressure roughly equal with the pressure of the oil.Specifically
For, in the oil-cooled type screw compressor, order is flowed out oily to above-mentioned enclosed space circulation from the shaft sealing of discharge side.
But according to the purposes of compressor, suction pressure and discharge pressure independently change sometimes, it not necessarily can be specific
Pressure with the oil of shaft sealing and bearing portion outflow from discharge side is the part of equal pressure.At this point, being configured to from discharge
The shaft sealing and bearing portion of side flow out oily to suction passage circulation.
In the heat pump (comprising refrigeration machine) for enabling cooling medium recycle using compressor, the suction pressure of compressor is interdependent
The evaporating temperature of cooling medium in evaporator, the discharge pressure of compressor depend on the condensation of the cooling medium in condenser
Temperature.In general, being flowed out when using split-compressor in heat pump from the shaft sealing and bearing portion of the discharge side of the second level
Oil to intermediate pressure space, i.e. to the suction passage ring of the compressor of the discharge duct and second level of the compressor of the first order
Stream.
In general, the pressure (intermediate pressure) in intermediate pressure space is in heat pump etc., by the compression of suction pressure and the first order
The compression ratio of machine determines.Thus, according to the condition of temperature-heat-source (either cooling load) and Cooling and Heat Source (or heating load), have
When the first order suction pressure rise and intermediate pressure becomes to be above the discharge pressure of the second level.Then, in previous second level pressure
In contracting machine, via the circulatory stasis of the oil of the shaft sealing and bearing portion of the discharge side of the second level, asking for the damages such as bearing is generated
Topic.
If enabled from the oil that the shaft sealing and bearing portion of the discharge side of the second level flow out to the suction passage ring of the first order
Stream can then ensure the circulation of oil, but when the difference of the pressure of oil and suction pressure is big, in the moment oil of supply to suction passage
Pressure decline, dissolve in oil gas ionization (degassing).The free of the gas can enable tooth socket pressure rise and lead to compressor
Reduced performance.In general, the cooling medium for heat pump is readily soluble in oil, so while property caused by the degassing of cooling medium
The problem of capable of reducing being readily apparent.
Summary of the invention
In view of the above problems, even if the issue of the present invention is to provide one kind suction pressures and discharge pressure variation also can
Enough ensure the circulation of oil and oil injection type split-compressor and heat pump that performance will not reduce.
In order to solve the above problems, oil injection type split-compressor of the invention includes first order compression unit, from suction passage
It sucks gas and the gas is compressed together with oil and is discharged to intermediate pressure space；Second level compression unit, from above-mentioned intermediate pressure
Power space sucks gas and compresses the gas together with oil and be discharged to discharge duct；Oily supply line, the second level Xiang Shangshu
The shaft sealing structure of the discharge side of compression unit and bearing at least some for oil supply；Oily the circulation path is enabled from the above-mentioned second level
The oil of at least some outflow of the shaft sealing structure and bearing of the discharge side of compression unit is to as above-mentioned first order compression unit
Compression space on the way enclosed space circulation.
According to this constitution, even as discharge pressure reduce and from the shaft sealing structure of the discharge side of second level compression unit and
The pressure reduction of the oil of bearing outflow, due to enabling oil to the enclosed space circulation also lower than intermediate pressure space pressure, so
The circulation that can ensure oil, can prevent the damage etc. of bearing.In addition, the pressure in enclosed space is higher than suction pressure, so phase
It is not too big for the pressure difference of the pressure of oil, it is able to suppress the gas ionization caused by property that oil is dissolved in when discharge pressure is high
It can reduce.
In addition, in oil injection type split-compressor of the invention, can also with above-mentioned oil ring flow path branch and with above-mentioned centre
Pressure space also connects, and above-mentioned oil ring flow path has the low pressure open and close valve and energy that can cut off the flow path to above-mentioned enclosed space
The high pressure open and close valve of the flow path to above-mentioned intermediate pressure space is enough cut off, and then there is flow path control device, the flow path control
Device is closed above-mentioned low pressure open and close valve when the pressure of the above-mentioned oil ring flow path of pressure ratio of above-mentioned oily supply line is high and is opened
State high pressure open and close valve, above-mentioned oily supply line pressure be above-mentioned oil ring flow path pressure below when open above-mentioned low pressure opening and closing
Valve and close above-mentioned high pressure open and close valve.
According to this constitution, the pressure of the oil flowed out from the shaft sealing structure and bearing of the discharge side of second level compression unit is high
When, intermediate pressure space circulation of the oil to more high pressure is enabled, so being able to suppress the free caused performance for the gas for dissolving in oil
It reduces.In addition, when the pressure of the oil of outflow is low, by enabling it to enclosed space circulation, it can be ensured that oily circulation.
In addition, heat pump of the invention has above-mentioned oil injection type split-compressor.
In addition, of the invention to the heat pump application for being used to manufacture cold water and warm water using R245fa as cooling medium
If it is considered that the condition of anticipation, then it is above-mentioned suction passage that preferably above-mentioned enclosed space, which is pressure, when oil injection type split-compressor
1.1 times of space of pressure.
Detailed description of the invention
Fig. 1 is the composition figure of the heat pump of the 1st embodiment of the invention.
Fig. 2 is the composition figure of the heat pump of the 2nd embodiment of the invention.
Specific embodiment
It is described with reference to embodiments of the present invention herein.Firstly, indicating to implement as the of the invention the 1st in Fig. 1
The composition of the heat pump of mode.The heat pump assembly of present embodiment is to constitute closed cooling medium circulation stream 6, is folded with
Its own is also the oil injection type second level helical-lobe compressor 1, oil eliminator 2, condenser 3, expansion of an embodiment of the invention
Valve 4, evaporator 5 have enclosed cooling medium (such as R245fa).
Oil injection type second level helical-lobe compressor 1 is collapsed into the cooling medium of gas, at this point, for cooling, lubrication and close
It seals and is mixed with oil to compress cooling medium.The cooling medium that oil injection type second level helical-lobe compressor 1 is discharged is imported into oil eliminator
2, separate cooling medium and oil.Separated in oil eliminator 2 oil by oil injection type second level helical-lobe compressor 1 discharge pressure and
To 1 circulation of oil injection type second level helical-lobe compressor.
Cooling medium after oil eliminator 2 removes oil is imported into condenser 3.Condenser 3 cooling medium and water it
Between carry out heat exchange, be to heat water and manufacture the heat exchanger of warm water.In condenser 3, cooling medium condenses and becomes liquid.
Condensed cooling medium is depressurized in expansion valve 4 and is supplied to evaporator 5 in condenser 3.Evaporator 5
It is the heat exchanger for carrying out heat exchange and cooling water between cooling medium and water and manufacturing cold water.It is cooling to be situated between in evaporator 5
Matter evaporates and becomes gas.In evaporator 5, the cooling medium after evaporation is supplied again to oil injection type second level helical-lobe compressor
1。
Oil injection type second level helical-lobe compressor 1 forms first order compression unit 8 and second level compression unit 9 in shell 7.
First order compression unit 8 is that the screw rotor 11 of yin-yang a pair is stored in the rotor chamber 10 for being formed in shell 7, from
Be formed as the suction passage 12 connecting with cooling medium circulation stream 6 sucking cooling medium and to compress, via discharge duct 13 to
The intermediate pressure space 14 being formed in shell 7 is discharged.Space in 11 zoning rotor chamber 10 of screw rotor and form multiple envelopes
The volume in enclosed space 15 is reduced with rotation to compress cooling medium in the enclosed space 15 closed.At this point, the first order is compressed
Portion 8 sucks oil together with cooling medium.The oil carry out between the cooling and screw rotor 11 of shell 7 and screw rotor and
Sealing and lubrication between screw rotor 11 and the inner wall of rotor chamber 10.
In addition, second level compression unit 9 is also received in the rotor chamber 16 for being formed in shell 7 in the same manner as first order compression unit 8
It receives the screw rotor 17 of yin-yang a pair, sucks cooling medium from intermediate pressure space 14 via suction passage 18 and compress, pass through
It is discharged from discharge duct 19 to cooling medium circulation stream 6.One screw rotor 11 of first order compression unit 8 and the second level
The output shaft of the axis and motor 20 of one screw rotor 17 of compression unit 9 is integrally connected.
The axis of screw rotor 11,17 is supported by bearing 21,22,23,24.Intermediate pressure space 14 is not only and first order pressure
The flow path for the cooling medium that contracting portion 8 and second level compression unit 9 connect, or with the space one of storage bearing 22,23 and be used for
Flow path to the supply of bearing 22,23 for the oil of lubrication.Similarly, it is compressed the suction side of first order compression unit 8 and the 2nd grade
The discharge side in portion 9 is formed with bearing space 25,26.Bearing space 25,26 is also the flow path for lubricating the oil of bearing 21,24.
To the discharge side of second level compression unit 9 bearing 24 in order to lubricate and from oil eliminator 2 via oily supply line 27
For oil supply.The oil for having lubricated bearing 24 is flowed out to bearing space 26.Oil injection type second level helical-lobe compressor 1 has connection second level pressure
The oil ring flow path 28 in the enclosed space 15 of the bearing space 26 and first order compression unit 5 of the discharge side in contracting portion 9.In addition, oil ring stream
The pressure of the cooling medium in the enclosed space 15 at position that road 28 is connect with enclosed space 15 is the cooling in suction passage 12
About 1.1 times of the pressure of medium.
To bearing space 26 flow out oil pressure be from oil eliminator 2 oil supply pressure, i.e. with oil injection type second level
The second level helical-lobe compressor 1(compression unit 9) discharge pressure is roughly the same and the amount of the pressure loss in slightly low bearing 24
Pressure.The discharge pressure of oil injection type second level helical-lobe compressor 1 is determined by the condensation temperature in condenser 3.In the present embodiment
Under the operating condition of imagination, the discharge pressure of oil injection type second level helical-lobe compressor 1 is likely to decrease 0.61Mpa.In addition, oil is cold
Formula second level helical-lobe compressor 1(first order compression unit 8) suction pressure determined by the evaporating temperature in evaporator 5.In this implementation
In mode, it is contemplated that evaporating temperature is up to 66 DEG C.At this point, suction pressure is 0.54Mpa.Thus, what oil ring flow path 28 was connected
The pressure in the enclosed space 15 of first order compression unit 5 is identical as the 0.61Mpa of the minimum of discharge pressure, can just ensure through
By the circulation of the oil of oil ring flow path 28.
So, in the present embodiment, even if the condensation temperature in condenser 3 is low, evaporating temperature in evaporator 5
Height also can be discharged oil from bearing space 26 via oil ring flow path 28 and ensure the supply to the new oil of bearing 24.In addition,
Enclosed space 15 is higher than 12 pressure of suction passage, so the pressure reduction of the oil flowed into via oil ring flow path 28 tails off.Therefore,
With the pressure reduction of oil, the quantitative change of free cooling medium is few, is able to suppress the performance of oil injection type second level helical-lobe compressor 1
It reduces.
Then, the composition of the heat pump of the 2nd embodiment of the invention is indicated in Fig. 2.In addition, in the present embodiment,
Identical symbol is marked for constituent element identical with the 1st embodiment and the repetitive description thereof will be omitted.In present embodiment
In heat pump, 28 branch of oil ring flow path and also connect with intermediate pressure space 14.Moreover, oil ring flow path 28, which has, can cut off to envelope
Enter the low pressure open and close valve 29 of the flow path of the oil in space 15 and can cut off to the height of the flow path of the oil in intermediate pressure space 14 to press off
Valve closing 30.In addition, the pressure for the oil that there is the oil injection type second level helical-lobe compressor 1 of present embodiment detection to supply from oil eliminator 3
The discharge pressure sensor 31 of power Pd, detect intermediate pressure space 14 pressure Pm intermediate pressure sensor 32 and correspond to
The detected value of discharge pressure sensor 31 and intermediate pressure sensor 32 and be opened and closed low pressure open and close valve 29 and high pressure open and close valve
30 flow path control device 33.
Flow path system drives device 33 and compares the pressure Pd and the inspection of intermediate pressure sensor 32 that discharge pressure sensor 31 detects
The pressure Pm measured, if the pressure Pd that discharge pressure sensor 31 detects is higher than what intermediate pressure sensor 32 detected
Pressure Pm then closes low pressure open and close valve 29 and opens high pressure open and close valve 30, on the other hand, if discharge pressure sensor 31 detects
To pressure Pd be the pressure Pm that detects of intermediate pressure sensor 32 hereinafter, then opening low pressure open and close valve 29 and closing height and press off
Valve closing 30.
That is, in the present embodiment, when Pd high is pressed in discharge, enabling the bearing space of the discharge side to second level compression unit 9
The oil of 26 outflows intermediate pressure space 14 circulation high to 15 pressure of enclosed space than first order compression unit 8.To with oil
Pressure reduction and reduced from the amount of the free cooling medium of oil, the discharge pressure for reducing oil injection type second level helical-lobe compressor 1 is high
When reduced performance.In addition, present embodiment is, when discharge pressure Pd is low, the bearing of the discharge side to second level compression unit 9 is enabled
Oil that space 26 is flowed out is in a same manner as in the first embodiment to 15 circulation of enclosed space of first order compression unit 8, so that it is guaranteed that oil
Circulation.
In addition, in the above-described embodiment, illustrate to enable the oil flowed out from bearing 24 via oil ring flow path 28 and to envelope
Enter the example of 15 circulation of space, but there is the shaft sealing structure for carrying out sealing by the oil supplied from oily supply line 27
When, the oil flowed out from the shaft sealing structure of the discharge side of second level compression unit 9 can also be enabled via oil ring flow path 28 and to enclosed
15 circulation of space.
Claims (3)
1. a kind of heat pump, there is oil injection type split-compressor, it is the oil injection type split-compressor and oil eliminator, condenser, swollen
Swollen valve is sandwiched together with the evaporator of the heat exchanger that manufactures cold water as heat exchange is carried out between cooling medium in water,
The cooling medium circulation stream for having enclosed cooling medium is constituted,
The oil injection type split-compressor includes
First order compression unit sucks gas from suction passage and compresses the gas together with oil, and arranges to intermediate pressure space
Out；
Second level compression unit compresses the gas and oil from above-mentioned intermediate pressure space sucking gas together, and to discharge stream
Road discharge；
One screw rotor of above-mentioned first order compression unit and a screw rotor of above-mentioned second level compression unit are set as axle center
It is identical,
The suction passage of above-mentioned first order compression unit, the discharge duct of above-mentioned first order compression unit, above-mentioned intermediate pressure space, on
It is suitable along above-mentioned axle center to state the suction passage of second level compression unit, the discharge duct of above-mentioned second level compression unit and bearing space
Sequence setting,
The oil injection type split-compressor is characterized in that,
It includes
Oily supply line, at least some supply of the shaft sealing structure and bearing of the discharge side of the second level Xiang Shangshu compression unit
Oil；
Oil ring flow path, enable from the shaft sealing structure of the discharge side of above-mentioned second level compression unit and bearing at least some is upwards
State the enclosed space circulation in space of the oil of bearing space outflow to the compression as above-mentioned first order compression unit on the way.
2. heat pump according to claim 1, which is characterized in that
Above-mentioned oil ring flow path branch and also connect with above-mentioned intermediate pressure space,
Above-mentioned oil ring flow path have can cut off to the flow path in above-mentioned enclosed space low pressure open and close valve and can cut off to above-mentioned
The high pressure open and close valve of the flow path in intermediate pressure space,
With flow path control device, pressure of the flow path control device in the above-mentioned oil ring flow path of pressure ratio of above-mentioned oily supply line
Above-mentioned low pressure open and close valve is closed when power is high and is opened above-mentioned high pressure open and close valve, is above-mentioned oil ring in the pressure of above-mentioned oily supply line
Above-mentioned low pressure open and close valve is opened when below the pressure of flow path and closes above-mentioned high pressure open and close valve.
3. heat pump according to claim 1, which is characterized in that
Above-mentioned enclosed space is 1.1 times of space of the pressure that pressure is above-mentioned suction passage.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011284072A JP5714479B2 (en) | 2011-12-26 | 2011-12-26 | Oil-cooled two-stage compressor and heat pump |
| JP2011-284072 | 2011-12-26 | ||
| CN201210564832.7A CN103175346B (en) | 2011-12-26 | 2012-12-24 | Oil injection type split-compressor and heat pump |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210564832.7A Division CN103175346B (en) | 2011-12-26 | 2012-12-24 | Oil injection type split-compressor and heat pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106196674A CN106196674A (en) | 2016-12-07 |
| CN106196674B true CN106196674B (en) | 2019-09-03 |
Family
ID=48635387
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210564832.7A Active CN103175346B (en) | 2011-12-26 | 2012-12-24 | Oil injection type split-compressor and heat pump |
| CN201610562464.0A Active CN106196674B (en) | 2011-12-26 | 2012-12-24 | Oil injection type split-compressor and heat pump |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210564832.7A Active CN103175346B (en) | 2011-12-26 | 2012-12-24 | Oil injection type split-compressor and heat pump |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5714479B2 (en) |
| KR (1) | KR101429363B1 (en) |
| CN (2) | CN103175346B (en) |
| MY (1) | MY164694A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6670645B2 (en) * | 2016-03-16 | 2020-03-25 | 株式会社日立産機システム | Multi-stage compressor |
| JP6767948B2 (en) * | 2017-08-25 | 2020-10-14 | 株式会社神戸製鋼所 | Oil-cooled two-stage screw compressor |
| JP2020007982A (en) * | 2018-07-10 | 2020-01-16 | 日立ジョンソンコントロールズ空調株式会社 | Two-stage screw fluid machine |
| CN115751772B (en) * | 2022-11-15 | 2023-09-15 | 大同云清科技有限公司 | Screw two-stage compressed air source heat pump |
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| CN1690590A (en) * | 2004-04-27 | 2005-11-02 | 株式会社神户制钢所 | Two-stage screw bolt refrigerating machine |
| CN101644501A (en) * | 2008-08-08 | 2010-02-10 | 株式会社神户制钢所 | Refrigerating device |
| CN102635551A (en) * | 2011-02-15 | 2012-08-15 | 株式会社神户制钢所 | Two-stage screw compression type freezing device |
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|---|---|---|---|---|
| JPS5145315A (en) * | 1974-10-16 | 1976-04-17 | Hokuetsu Kogyo Co | EKIREISHIKITADANKAITENATSUSHUKUKINO EKITAISHORINYORU DORYOKUSE TSUGENHOHO |
| JPS56118988U (en) * | 1981-01-21 | 1981-09-10 | ||
| JPH0636312Y2 (en) * | 1986-11-07 | 1994-09-21 | 株式会社前川製作所 | Two-stage screw compressor |
| JPS63102988U (en) * | 1986-12-22 | 1988-07-04 | ||
| JPH03185293A (en) * | 1989-12-15 | 1991-08-13 | Hitachi Ltd | Displacement compressor rotating screw |
| JPH05145315A (en) * | 1991-11-22 | 1993-06-11 | Sony Corp | Coaxial dielectric resonator and manufacture thereof |
| JPH0622587U (en) * | 1992-08-25 | 1994-03-25 | 株式会社神戸製鋼所 | Oil-cooled compressor |
| JPH09324783A (en) * | 1996-06-05 | 1997-12-16 | Hitachi Ltd | Oil feed type multistage screw compressor and intermediate cooler |
| JP2000337282A (en) | 1999-05-26 | 2000-12-05 | Kobe Steel Ltd | Two-stage type screw compressor |
| JP4559283B2 (en) * | 2004-04-27 | 2010-10-06 | 株式会社神戸製鋼所 | 2-stage screw refrigerator |
| WO2007000815A1 (en) * | 2005-06-29 | 2007-01-04 | Mayekawa Mfg. Co., Ltd | Oil supply method and device for two-stage screw compressor, and method of operating refrigeration device |
| JP5543093B2 (en) * | 2008-06-09 | 2014-07-09 | 荏原冷熱システム株式会社 | Compressive refrigerator and operation method thereof |
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2011
- 2011-12-26 JP JP2011284072A patent/JP5714479B2/en active Active
-
2012
- 2012-11-30 MY MYPI2012005174A patent/MY164694A/en unknown
- 2012-12-21 KR KR1020120150747A patent/KR101429363B1/en active IP Right Grant
- 2012-12-24 CN CN201210564832.7A patent/CN103175346B/en active Active
- 2012-12-24 CN CN201610562464.0A patent/CN106196674B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1690590A (en) * | 2004-04-27 | 2005-11-02 | 株式会社神户制钢所 | Two-stage screw bolt refrigerating machine |
| CN101644501A (en) * | 2008-08-08 | 2010-02-10 | 株式会社神户制钢所 | Refrigerating device |
| CN102635551A (en) * | 2011-02-15 | 2012-08-15 | 株式会社神户制钢所 | Two-stage screw compression type freezing device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103175346A (en) | 2013-06-26 |
| MY164694A (en) | 2018-01-30 |
| KR101429363B1 (en) | 2014-08-11 |
| KR20130079203A (en) | 2013-07-10 |
| JP2013133740A (en) | 2013-07-08 |
| CN103175346B (en) | 2016-08-17 |
| JP5714479B2 (en) | 2015-05-07 |
| CN106196674A (en) | 2016-12-07 |
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Effective date of registration: 20220221 Address after: Tokyo, Japan Patentee after: Shengang Compressor Co.,Ltd. Address before: Kobe City, Hyogo Prefecture, Japan Patentee before: Kobe Steel, Ltd. |
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