CN104583688B - Freezing cycle device - Google Patents
Freezing cycle device Download PDFInfo
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- CN104583688B CN104583688B CN201380044192.XA CN201380044192A CN104583688B CN 104583688 B CN104583688 B CN 104583688B CN 201380044192 A CN201380044192 A CN 201380044192A CN 104583688 B CN104583688 B CN 104583688B
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- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
- C09K5/02—Materials undergoing a change of physical state when used
- C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
- C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
- C09K5/044—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds
- C09K5/045—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds containing only fluorine as halogen
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
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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
-
- 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
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/40—Properties
- F04C2210/44—Viscosity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Combustion & Propulsion (AREA)
- Materials Engineering (AREA)
- Organic Chemistry (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Lubricants (AREA)
Abstract
The freeze cycle (2) of the low temperature side of the freeze cycle (1) possessing the high temperature side of the compressor (4) with high temperature side and the compressor (11) with low temperature side, the most chloride cold-producing medium is used as cold-producing medium, lubricating oil and the lubricating oil of low temperature side used in the compressor (11) of low temperature side of the high temperature side used in the compressor (4) of high temperature side have the compatibility relative to cold-producing medium, and the lubricating oil of high temperature side viscosity pressure coefficient at 40 DEG C is higher than the lubricating oil of low temperature side viscosity pressure coefficient at 40 DEG C.
Description
Quoting of related application: the application is with Japan patent application 2012-181188 filed in 17 days Augusts in 2012
Number priority interests based on, and require the interests of this priority, in this application by quote comprise its all in
Hold.
Technical field
Embodiment described herein relates generally to possess high temperature side freeze cycle and the low temperature constituting binary refrigeration circulation
The freezing cycle device of side freeze cycle.
Background technology
As the freeze cycle dress possessing the high temperature side freeze cycle constituting binary refrigeration circulation and low temperature side freeze cycle
Put, the most known device having described in Japanese Laid-Open flat 8-189714 publication.
In dualistic formula freezing cycle device described in this patent gazette, at compressor and the low temperature of high temperature side freeze cycle
In the compressor of side freeze cycle, using relative to cold-producing medium (coolant) is the lubricating oil of non-compatibility.If making within the compressor
With being the lubricating oil of non-compatibility relative to cold-producing medium, then the lubricating oil flowed out from compressor together with cold-producing medium returns to compressor
The return returned can reduce.Then, in the freezing cycle device described in above-mentioned patent gazette, shorten in each freeze cycle
The length of refrigerant piping improves the return of lubricating oil, and, it is additionally provided with being used at height with refrigerant piping
Carry out, between temperature side freeze cycle and low temperature side freeze cycle, the heat transfer medium circuit road that the thermophore (heating agent) of heat exchange circulates.
Prior art literature
Patent documentation
Patent documentation 1: Unexamined Patent 8-189714 publication
Summary of the invention
The problem that invention is to be solved
As above-mentioned patent gazette is recorded, using relative to the lubricating oil that cold-producing medium is non-compatibility and arranging
In the case of heat transfer medium circuit road, system can be caused, complicate, maximize, thus cost increases.
On the other hand, in the case of employing the lubricating oil relative to cold-producing medium with the compatibility, freezing at high temperature side
Circulation compressor in, lubricating oil because of high temperature viscosity reduce and because of high pressure the cold-producing medium amount of dissolving in increase and be diluted from
And viscosity reduces significantly, the abrasion performance of sliding part is caused to reduce.
In recent years, from the viewpoint of Ozonosphere protection, it is desirable to use the most chloride cold-producing medium, but use and do not contain tool
If having the cold-producing medium of chlorine of function as the EP agent for giving load resistance, the abrasion performance of sliding part can be caused
Property and then reduction.
Embodiments of the present invention provide a kind of freezing cycle device, high temperature side freeze cycle high temperature side compressor and
The low temperature side compressor of low temperature side freeze cycle use the most chloride cold-producing medium and employing have relative to cold-producing medium compatible
Property lubricating oil in the case of, it is possible to increase the abrasion performance of the sliding part of high temperature side compressor, further, it is possible to reduce low temperature side
The resistance to sliding of the sliding part of compressor and reduce slippage loss.
For solving the means of problem
The freezing cycle device of embodiment possesses the freeze cycle of high temperature side and the freeze cycle of low temperature side, and by high temperature
The freeze cycle of side and the freeze cycle of low temperature side are equipped in same housing, in the freeze cycle of above-mentioned high temperature side, and high temperature side
Compressor, condenser to the high temperature side that heated fluid heats, the expansion gear of high temperature side, intermediate heat exchanger
The stream of high temperature side is connected via the refrigerant piping of high temperature side, along the refrigerant piping circulating refrigerant of high temperature side；
In the freeze cycle of above-mentioned low temperature side, the compressor of low temperature side, the stream of low temperature side of intermediate heat exchanger, the expansion of low temperature side
Device, the vaporizer of low temperature side are connected via the refrigerant piping of low temperature side, and the refrigerant piping along low temperature side circulates
Cold-producing medium, wherein, as cold-producing medium, uses the most chloride cold-producing medium, the profit of the high temperature side used in the compressor of high temperature side
Lubricating oil and the lubricating oil of low temperature side used in the compressor of low temperature side have the compatibility relative to cold-producing medium, the profit of high temperature side
Lubricating oil viscosity pressure coefficient at 40 DEG C is higher than the lubricating oil of low temperature side viscosity pressure coefficient at 40 DEG C.
Accompanying drawing explanation
Fig. 1 is the integrally-built explanatory diagram of the freezing cycle device representing the first embodiment.
Fig. 2 is the vertical view that the compression mechanical part of the high temperature side compressor to above-mentioned freezing cycle device is amplified representing
Explanatory diagram.
Fig. 3 is the vertical view that the compression mechanical part of the low temperature side compressor to above-mentioned freezing cycle device is amplified representing
Explanatory diagram.
Fig. 4 A is the longitudinal section of the high temperature side compressor of the freezing cycle device representing the second embodiment.
Fig. 4 B is the longitudinal section of the low temperature side compressor of the freezing cycle device representing the second embodiment.
Detailed description of the invention
Hereinafter, referring to the drawings multiple embodiments are illustrated.In the accompanying drawings, identical reference represent identical or
Person's similar portions.According to Fig. 1 to Fig. 6, the freezing cycle device of the first embodiment is illustrated.Fig. 1 shows to generate
Hot water and the overall structure of freezing cycle device that uses.This freezing cycle device has the high temperature side constituting binary refrigeration circulation
Freeze cycle 1 and low temperature side freeze cycle 2.These high temperature side freeze cycle 1 and low temperature side freeze cycle 2 are equipped on same housing
3。
High temperature side freeze cycle 1 includes: the compressor 4 of the revolving high temperature side being compressed cold-producing medium, make refrigeration
The condenser 5 of the high temperature side of agent condensation, the expansion gear 6 of high temperature side that cold-producing medium is reduced pressure and carry out heat exchange
Intermediate heat exchanger 7.The stream of the high temperature side in these compressors 4, condenser 5, expansion gear 6 and intermediate heat exchanger 7
7a is connected, along this refrigerant piping 8 circulating refrigerant via the refrigerant piping 8 of high temperature side.Intermediate heat exchanger 7 exists
In high temperature side freeze cycle 1, as the vaporizer function of the cold-producing medium evaporation making flowing in the stream 7a of high temperature side.Cold
In condenser 5, being equipped with flowing has the fluid flowing path 9 of the water as heated fluid, in the midway of this fluid flowing path 9, is provided with stream
The pump 10 of dynamic water.
Low temperature side freeze cycle 2 includes: the compressor 11 of the revolving low temperature side that cold-producing medium is compressed, above-mentioned in
Between heat exchanger 7, the expansion gear 12 of low temperature side that cold-producing medium is reduced pressure and the steaming of the low temperature side that makes cold-producing medium evaporate
Send out device 13.Low temperature side stream 7b, expansion gear 12 and low temperature side vaporizer in these compressors 11, intermediate heat exchanger 7
13 are connected, along this refrigerant piping 14 circulating refrigerant via the refrigerant piping 14 of low temperature side.Intermediate heat exchanger 7
In low temperature side freeze cycle 2, as the condenser function of the cold-producing medium condensation making flowing in the stream 7b of low temperature side.
In the position opposed with vaporizer 13, the Air Blast fan 15 blowing this vaporizer 13 is set.
Fig. 2 is the explanatory diagram of the vertical view of the compression mechanical part 16 of the compressor 4 representing high temperature side.Compression mechanical part 16 possesses
The cylinder 18 of high temperature side, rotary shaft 19, eccentric part 20, the roller 21 of high temperature side, the blade (blade) 23 of high temperature side and bullet
Spring 24.Cylinder 18 is being internally formed cylinder chamber 17.Rotary shaft 19 is inserted through cylinder chamber 17, is arranged to revolve around axle center
Turn.Eccentric part 20 is arranged at rotary shaft 19, is arranged in cylinder chamber 17.Roller 21 is chimeric with the periphery of eccentric part 20, along with
The rotation of rotary shaft 19 and in cylinder chamber 17, carry out eccentric rotary.Blade 23 in the blade groove 22 being formed at cylinder 18 with can
The mode slided is received.The leading section of blade 23 abuts with the outer peripheral face of roller 21.Spring 24 is housed in blade groove 22
In portion, by blade 23 to roller 21 side push.
By the blade 23 making leading section abut with the outer peripheral face of roller 21 in cylinder chamber 17, it is divided into suction chamber 17a
With discharge chambe 17b.In high temperature-side cylinder 18, it is formed with the suction sucked by cold-producing medium when the driving of compressor 4 to suction chamber 17a
Enter path 25.And, rotary shaft 19 is being carried out the not shown bearing components of axle support, is being formed and will be pressed by discharge chambe 17b
The ejection path of the cold-producing medium ejection after contracting.
Fig. 3 is the explanatory diagram of the vertical view of the compression mechanical part 27 of the compressor 11 representing low temperature side.This compression mechanical part 27
Basic structure identical with the compression mechanical part 16 of the compressor 4 of the high temperature side shown in Fig. 2.Compression mechanical part 27 possesses low temperature side
Cylinder 29, rotary shaft 30, eccentric part 31, the roller 32 of low temperature side, the blade 34 of low temperature side, spring 35.Cylinder 29 is in inside
It is formed with cylinder chamber 28.Rotary shaft 30 is inserted through cylinder chamber 28, is arranged to rotate around axle center.Eccentric part 31 is arranged at
Rotary shaft 30, is arranged in cylinder chamber 28.Roller 32 is chimeric with the periphery of eccentric part 31, along with rotary shaft 30 rotation and
Eccentric rotary is carried out in cylinder chamber 28.Blade 34 is slidably housed in the blade groove 33 being formed at cylinder 29.Leaf
The leading section of sheet 34 abuts with the outer peripheral face of roller 32.Spring 35 is housed in portion in blade groove 33, by blade 34 to roller
32 sides push.
By the low temperature side blade 34 making leading section abut with the outer peripheral face of roller 32 in cylinder chamber 28, it is divided into suction
Room 28a and discharge chambe 28b.Cylinder 29 is formed and when the driving of low temperature side compressor 11, cold-producing medium is inhaled to suction chamber 28a
The suction passage 36 entered.And, rotary shaft 30 is being carried out the not shown bearing components of axle support, is being formed by discharge chambe
The ejection path of the cold-producing medium ejection after 28b compression.
To in the cold-producing medium used in the freeze cycle 1 of high temperature side and the freeze cycle 2 of low temperature side and compressor 4,11
The lubricating oil used illustrates.
About above-mentioned cold-producing medium, freeze cycle 1 and freeze cycle 2 all use the most chloride HFC (hydrogen fluorohydrocarbon (hydro
Fluorocarbon) cold-producing medium) being.Cold-producing medium as HFC system, it is possible to use HFC-134a, HFC-32, HFC-152a,
HFC-125, HFC-143a such unitary system cryogen or the R410A being obtained by mixing by HFC-32 and HFC-125 are such
Mix refrigerant.
About above-mentioned lubricating oil, in the compressor 4 of high temperature side, use the PVE (polyvinylether) as lubricating oil.Low
In the compressor 11 of temperature side, use the POE (polyol ester (polyolester)) as lubricating oil.These PVE and POE are homogeneous
Cold-producing medium for HFC system has the compatibility.PVE viscosity pressure coefficient " α " at 40 DEG C is than POE viscosity pressure at 40 DEG C
Force coefficient " α " is high.
About oil body, there is " η=η0Exp (α p) " character shown in formula (with reference to ASME
Pressure-viscosity Report, ASME, 1953)." η " is the oil body under arbitrary pressure " p ", " η0”
For the oil body under atmospheric pressure, " α " is oil body pressure coefficient.
Oil body " η " increases relative to pressure " p " exponentially function ground, therefore, is becoming mixed lubricating state
Or boundary lubrication condition and by the sliding part of relatively high surface pressure, oil body local uprises.
As the method improving abrasion performance in the sliding part of mixed lubricating state or boundary lubrication condition, in day the machine
Tool association collection of thesis C compiles .64-624. paper No.97-1425) in recorded the effect of the high lubricating oil of viscosity pressure coefficient " α "
Really.As its effect, the high lubricating oil of viscosity pressure coefficient " α " in sliding part partly viscosity extremely large, easily form institute
The cured film of meaning, protects rubbing surface by this cured film.In the above-mentioned paper that above-mentioned Japan mechanical society collection of thesis C compiles also
Describe oil body pressure coefficient " α " the highest, then the coefficient of friction of sliding part is the highest, and slippage loss becomes big.
Above-mentioned patent gazette is recorded, has in the middle of the lubricating oil of the compatibility relative to the cold-producing medium of HFC system,
The viscosity pressure coefficient " α " of PVE is higher, and coefficient of friction is the highest.
Above-mentioned patent gazette and Japan mechanical society collection of thesis C compile, and record: POE exists in 63-612, No.96-1427
Having in the middle of the lubricating oil of the compatibility relative to HFC series coolant, the particularly coefficient of friction in low temperature territory is relatively low, and passes through
Firm adsorbed film is formed and abrasion performance is excellent at rubbing surface.But, if this paper having also stated that, above-mentioned adsorbed film turns
More than temperature (transition temperature) (near 150 DEG C) then disappearing, the abrasion performance of above-mentioned rubbing surface is drastically
Ground deteriorates.
Table 1 be represent use viscosity pressure coefficient " α " different 2 kinds of lubricating oil and carry out, high temperature side freeze cycle 1
The long duration test result of the compressor under operating condition, low temperature side freeze cycle 2 operating condition under the durable examination of compressor
Test result and the explanatory diagram of performance (COP) result of the test.Above-mentioned lubricating oil is respectively the viscosity pressure coefficient at 40 DEG C
15.1GPa-1The lubricating oil (PVE) of high temperature side and 40 DEG C at viscosity pressure coefficient be 10.3GPa-1The profit of low temperature side
Lubricating oil (POE).
[table 1]
As the operating condition of the freeze cycle 1 of high temperature side, condensation temperature is set to 95 DEG C, evaporating temperature has been set
Become 35 DEG C, the operating frequency of compressor has been set to 60rps.As the operating condition of the freeze cycle 2 of low temperature side, by cold
Solidifying temperature has been set to 45 DEG C, and evaporating temperature has been set to 5 DEG C, and the operating frequency of compressor has been set to 60rps.
According to table 1, when making compressor carry out operating under the above-mentioned operating condition of the freeze cycle 1 of high temperature side,
In the case of the lubricating oil (PVE) employing the higher above-mentioned high temperature side of viscosity pressure coefficient " α ", the long duration test of compressor
Result is good (OK).On the other hand, at the lubricating oil (POE) employing the relatively low above-mentioned low temperature side of viscosity pressure coefficient " α "
In the case of, producing abrasion at compressor, long duration test result is non-good (NG).
On the other hand, when making above-mentioned compressor carry out operating under the above-mentioned operating condition of low temperature side freeze cycle 2, no
Pipe uses the lubricating oil (PVE) of the above-mentioned high temperature side that viscosity pressure coefficient " α " is higher or uses viscosity pressure coefficient " α " relatively low
Which of lubricating oil (POE) of above-mentioned low temperature side, the long duration test result of compressor is all good (OK).As performance
(COP) result of the test understands, and the situation ratio of the lubricating oil (POE) of the above-mentioned low temperature side that use viscosity pressure coefficient " α " is relatively low makes
Situation with the lubricating oil (PVE) of the higher above-mentioned high temperature side of viscosity pressure coefficient " α " is better.
Illustrate adding resistance to load carrying additive to the lubricating oil of high temperature side and the lubricating oil of low temperature side.By to lubrication
Oil adds resistance to load carrying additive, it is possible to increase the abrasion performance of the sliding part under mixed lubricating state or boundary lubrication condition.But
It is, conversely, because add resistance to load carrying additive, to cause easily producing low temperature precipitate, in the situation creating low temperature precipitate
Under, the internal diameter stenosis of the stream of cold-producing medium or lubricating oil flow is narrow, according to circumstances sometimes results in stream inaccessible.
Then, in the case of adding resistance to load carrying additive to the lubricating oil of high temperature side and the lubricating oil of low temperature side, will add
The weight rate of the resistance to load carrying additive entered is set as the relation of lubricating oil >=0 of the lubricating oil ＞ low temperature side of high temperature side.
Representative as resistance to load carrying additive, it is possible to list the additive comprising phosphoric acid ester.Specifically phosphoric acid
The phosphate ester of front three phenyl ester (TCP), triphenyl phosphate (TPP) etc；The Asia of tricresyl phosphite, triphenyl phosphite etc
Phosphate ester；Acid phosphoric acid ester；Acidic phosphite etc..And then, thiophosphate (zinc dialkyl dithiophosphate；ZnDTP), high
Level fatty acid, senior ethanol, organic molybdenum also are able to be used as resistance to load carrying additive.
The blade 23 of high temperature side and the process of the blade 34 respective blade sliding surface of low temperature side are described.To at high temperature side
The blade sliding surface of blade 23 that blade 23 abuts against with other components or contacts in the case of sliding, implement for height
The mother metal of temperature lateral lobe sheet 23 compares the scattering and permeating process improving hardness, and such as, scattering and permeating based on nitrogen treatment processes.
On the other hand, the blade abutting against with other components or contacting in the case of the blade 34 at low temperature side being slided
The blade sliding surface of 34, implement the mother metal of blade 34 with low temperature side compared with reduce the tunicle of coefficient of friction and process, such as,
DLC (diamond-like-carbon) processes.
Table 2 is to represent to use blade sliding surface implements the blade after DLC processes and implements based on nitrogen treatment
Scattering and permeating process after blade carry out, the long duration test result of blade under the operating condition of high temperature side freeze cycle 1 and
The long duration test result of the blade under the operating condition of low temperature side freeze cycle 2 and performance (COP) result of the test of compressor.
[table 2]
As the operating condition of the freeze cycle 1 of high temperature side, the test illustrated with using above-mentioned table 1 is same, will condense
Temperature has been set to 95 DEG C, and evaporating temperature has been set to 35 DEG C, and the operating frequency of compressor has been set to 60rps.Low temperature
Condensation temperature as the test that illustrates, has been set to 45 DEG C with using above-mentioned table 1 by the operating condition of the freeze cycle 2 of side,
Evaporating temperature is set to 5 DEG C, the operating frequency of compressor has been set to 60rps.
According to table 2, under the operating condition of the freeze cycle 1 of high temperature side, blade sliding surface is being implemented nitridation
In the case of process, the result of the test of the long duration test of blade is good (OK).On the other hand, the feelings that DLC processes are being implemented
Under condition, process part is peeling and long duration test is non-good (NG).
On the other hand, under the operating condition of the freeze cycle 2 of low temperature side, blade sliding surface is being implemented nitrogen treatment
Situation and implement situation that DLC processes all, the long duration test result of blade good (OK).Test according to performance (COP)
Result understands, and the situation comparison blade sliding surface implementing DLC process implements all right of nitrogen treatment.
Table 3 is to represent to make implementing blade sliding surface in the case of scattering and permeating based on nitrogen treatment processes at nitrogen
Change processes the result of the blade long duration test in the case of the thickness change of the porous layer that surface produces.This long duration test be into
Gone high temperature side freeze cycle 1 high compression ratio operating and high pressure operate in the case of long duration test.
[table 3]
The operating of above-mentioned high compression ratio refers to, compresses the highest among the use condition and range of the freeze cycle 1 of high temperature side
Under the conditions of operating.The operating of above-mentioned high pressure refers to, at the mesolow of use condition and range of freeze cycle 1 and the height of high temperature side
Pressure be all the highest under conditions of operating.
In the above-mentioned high compression ratio operating of the freeze cycle 1 of above-mentioned high temperature side, condensation temperature is set to 90 DEG C, will
Evaporating temperature has been set to 10 DEG C, and the operating frequency of compressor has been set to 60rps.
In the above-mentioned high pressure of above-mentioned high temperature side freeze cycle 1 operates, condensation temperature is set to 95 DEG C, will evaporation
Temperature has been set to 35 DEG C, and the operating frequency of compressor has been set to 60rps.
According to table 3, by the thickness of porous layer is set to below 1 μm so that above-mentioned high compression ratio operating and
The operating of above-mentioned high pressure which in the case of long duration test result all good (OK).Understand, at the thickness of porous layer more than 1 μm
In the case of, produce in porous layer and be partially stripped or peel off.
In above-mentioned above-mentioned freezing cycle device, carry out the low temperature that the compressor 11 by low temperature side is driven and carry out
The operating of the freeze cycle 2 of side and the fortune of the freeze cycle 1 of high temperature side driven and carry out by the compressor 4 of high temperature side
Turn.And then, driven by pump 10, and in fluid flowing path 9 flowing have water, this water in the condenser 5 of high temperature side by from system
The heat that cryogen is released heats and becomes hot water, and this hot water is supplied to the place needing hot water of outside.
The freeze cycle 1 of freeze cycle 2 and high temperature side by making low temperature side operates, and carries out in intermediate heat exchanger 7
Heat exchange.As its result, the cold-producing medium of the freeze cycle 1 of high temperature side is released by the cold-producing medium from the freeze cycle 2 of low temperature side
Heat heating.By such heat exchange, in the freeze cycle 1 of high temperature side, it is inhaled into the refrigeration in the compressor 4 of high temperature side
The temperature of agent uprises, the cylinder of the compressor 11 of the temperature and pressure in the cylinder chamber 17 of the compressor 4 of high temperature side and low temperature side
Temperature and pressure in room 28 is compared and is uprised.Therefore, become many from condenser 5 liberated heat of high temperature side, promote hot water
Generate.
In the case of Gai, as the lubricating oil of the high temperature side used in the compressor 4 of high temperature side, the viscosity pressure at using 40 DEG C
Force coefficient " α " is 15.1GPa-1The PVE of high viscosity pressure coefficient.By using this PVE, even if the compressor of high temperature side 4
Temperature and pressure in cylinder chamber 17 rises, and also improves the durability of the compressor 4 of high temperature side as shown in table 1 like that.
And, as the lubricating oil of the low temperature side used in the compressor 11 of low temperature side, the viscosity pressure at using 40 DEG C
Coefficient " α " is 10.3GPa-1POE.By using this POE, as shown in table 1, it is ensured that resistance in the compressor 11 of low temperature side
Property for a long time, and, performance (COP) result of the test is better compared with during use PVE.
In the present embodiment, the resistance to load added to high temperature side lubricating oil (PVE) and low temperature side lubricating oil (POE) is added
Add the relation of lubricating oil >=0 that the weight rate of agent is set as the lubricating oil ＞ low temperature side of high temperature side.Therefore, although high temperature side
In compressor 4, slip environment is very severe, but by the lubricating oil of the high temperature side that the compressor 4 of high temperature side uses is increased resistance to load
The addition of lotus additive, it is possible to increase the abrasion performance of high temperature side compressor 4.Additionally, the compressor 4 of this high temperature side and height
The freeze cycle 1 of temperature side is difficult to become low temperature, therefore, even if increasing the addition of resistance to load carrying additive, it is also possible to suppression low temperature
The generation of precipitate.As it as a result, it is possible to the freezing of the high temperature side preventing the precipitation along with low temperature precipitate and producing follows
The reliability of ring 1 and the reduction of performance.On the other hand, in the compressor 11 of low temperature side, slip environment is not severe and easily becomes low
Temperature.Therefore, the lubricating oil of the low temperature side of the compressor 11 of low temperature side is reduced the addition of resistance to load carrying additive, or, it is not added with
Enter resistance to load carrying additive.As it as a result, it is possible to the suppression generation of low temperature precipitate that adds resistance to load carrying additive and cause, energy
Enough maintain the performance of the freeze cycle 2 of low temperature side.
In the present embodiment, as shown in table 2, by the surface of the blade 23 of the compressor 4 to high temperature side implement based on
The scattering and permeating of nitrogen treatment processes, it is possible to increase the durability of blade 23.On the other hand, by the compressor 11 to low temperature side
The surface of blade implement DLC processs, it is possible to increase the durability of blade 34, further, it is possible to raising low temperature side compressor 11
Performance (COP).
And, in the present embodiment, as shown in table 3, the sliding surface of high temperature side blade 23 will implemented base
The thickness of porous layer produced on nitrogen treatment surface in the case of the scattering and permeating of nitrogen treatment processes be set to 1 μm with
Under.Thereby, it is possible to prevent being partially stripped or peeling off of porous layer, it is possible to increase the performance of high temperature side compressor 4 and reliability.
The freezing cycle device of second embodiment of the present invention is illustrated.This freezing cycle device is except high temperature side
And outside the compressor of low temperature side, as the freezing cycle device of the first embodiment.Based on Fig. 4 A and 4B to these
The structure of compressor illustrates.
Fig. 4 A is the longitudinal section of the compressor 4A of the high temperature side of the freeze cycle of the high temperature side representing the second embodiment.
Fig. 4 B is the longitudinal section of the low temperature side compressor 11A of the freeze cycle of the low temperature side representing the second embodiment.At high temperature side
The respective indoor of cylinder chamber 17,17 of compressor 4A employ blade 23a, 23b of 2 high temperature sides.Compression at low temperature side
The respective indoor of the cylinder 28,28 of machine 11A employ 1 low temperature side blade 34.
Illustrate in detail below.The compression mechanical part 16A of high temperature side compressor 4A possesses the cylinder of a pair high temperature side
18,18, rotary shaft 19, eccentric part 20,20, the roller of high temperature side 21,21, blade 23a, 23a, 23b, 23b of high temperature side and
Spring 24.In the inside of cylinder 18,18, it is respectively formed with high temperature-side cylinder room 17,17.Rotary shaft 19 be inserted through cylinder chamber 17,
17, it is arranged to rotate around axle center.Eccentric part 20,20 is arranged at rotary shaft 19, is arranged respectively at cylinder chamber 17,17
In.Roller 21,21 is chimeric with the periphery of eccentric part 20,20 respectively, along with rotary shaft 19 rotation and in cylinder chamber 17,17
Carry out eccentric rotary.Blade 23a, 23a, 23b, 23b are arranged to slide relative to above-mentioned roller 21,21.These multiple leaves
The leading section of sheet abuts with the outer peripheral face of roller 21,21, thus, is separated into suction chamber and discharge chambe in cylinder chamber 17,17.Bullet
Blade 23a, 23a, 23b, 23b are pushed by spring 24 to roller 21,21 side.
The compression mechanical part 27A of low temperature side compressor 11A possess the cylinder 29 of a pair low temperature side, 29, rotary shaft 30, eccentric
Portion 31,31, the roller of low temperature side 32,32, low temperature side blade 34,34 and spring 35.In the inside of cylinder 29,29, shape respectively
Cheng You cylinder chamber 28,28.Rotary shaft 30 is inserted through cylinder chamber 28,28, is arranged to rotate around axle center.Eccentric part
31,31 it is arranged at rotary shaft 30, is arranged respectively in cylinder chamber 28,28.Roller 32,31 respectively with the periphery of eccentric part 31,31
Chimeric, in cylinder chamber 28,28, carry out eccentric rotary along with the rotation of rotary shaft 30.Blade 34,34 is arranged to phase
Above-mentioned roller 32,32 is slided.The respective leading section of blade 34,34 outer peripheral face with low temperature side roller 32,32 respectively abuts,
Thus in cylinder chamber 28,28, it is separated into suction chamber and discharge chambe.Blade 34,34 is pushed by spring 35 to roller 32,32 side.
In the freezing cycle device of present embodiment, the respective indoor of the cylinder chamber 28,28 of low temperature side are provided with 1
Individual blade 34.The respective indoor of the cylinder chamber 17,17 of high temperature side are provided with 2 blades 23a, 23b.The blade of high temperature side
23a, 23a, 23b, 23b are separated along axial 22 ground of rotary shaft 19.
In such a configuration, at the compressor 4A and the compressor 11A of low temperature side of high temperature side, if by the pressure of cold-producing medium
Power and make rotary shaft 19,30 produce flexure, then relative to the outer peripheral face of roller 21,21 of high temperature side, the blade 23a of high temperature side,
23a, 23b, 23b abut partly.Additionally, the outer peripheral face of the roller 32,32 relative to low temperature side, the blade 34,34 of low temperature side
Abut partly.As its result, the face of the part being in abutting of above-mentioned multiple blades presses liter.
The compressor 4A of high temperature side pressure of cold-producing medium compared with the compressor 11A of low temperature side is higher, therefore, with rotary shaft
30 compare, and the deflection of rotary shaft 19 easily becomes big.But, in the compressor 4A of high temperature side, the blade 23a of high temperature side,
23a, 23b, 23b by 22 separately and every 2 ground are arranged in cylinder 18,18, therefore, it is possible to by the blade 23a of high temperature side,
The face of the abutting part that one of roller 21,21 with high temperature side of every 1 of 23a, 23b, 23b abuts constrains prepared relatively low.Therefore,
Abrasion performance can be improved, it is possible to increase the performance of the compressor 4A of high temperature side and reliability.
On the other hand, even if the rotary shaft 30 of the compressor 11A of low temperature side produces flexure, its deflection is again smaller than high temperature side
The deflection of rotary shaft 19 of compressor 4A.Therefore, bend and the blade 34,34 of low temperature side local even if rotary shaft 30 produces
Be connected to roller 32,32, it is also possible to the face of low temperature side blade 34,34 with the abutting part of low temperature side roller 32,32 is constrained system
Obtain relatively low.In the compressor 11A of low temperature side, by 1 blade 34 of each use for cylinder 29,29, it is possible in minimizing
State the component count of freezing cycle device, it is possible to the rising of suppression cost.
In the present embodiment, in the compressor 4A of high temperature side, for cylinder 18,18 each respectively arrange 2 high
Temperature lateral lobe sheet 23a, 23b, in the compressor 11A of low temperature side, each respectively arrange 1 low temperature lateral lobe for cylinder 29,29
Sheet 34.The number of blade is not limited to this situation, it is also possible to be number and the low temperature side of the blade of the compressor 4A making high temperature side
The number of the blade of compressor 11A is the most more, makes the number ratio of the blade used in the compressor 4A of high temperature side at low temperature
The number of the blade used in the compressor 11A of side is many.
The freezing cycle device of multiple embodiment described above has the freeze cycle 1 of high temperature side and the cold of low temperature side
Freeze circulation 2.Freeze cycle 1 possesses the compressor 4 of high temperature side, 4A, condenser to the high temperature side that heated fluid heats
5, high temperature side expansion gear 6, there is the intermediate heat exchanger 7 of the stream 7a of high temperature side.These key elements are via the system of high temperature side
Cryogen pipe arrangement 8 and connected, cold-producing medium circulates along high temperature side refrigerant piping 8.The freeze cycle 2 of low temperature side possesses low temperature side
Compressor 11,11A, above-mentioned intermediate heat exchanger 7, the expansion gear 12 of low temperature side, the vaporizer 13 of low temperature side.Above-mentioned centre
Heat exchanger 7 has the stream 7b of low temperature side.These key elements are connected, cold-producing medium edge via the refrigerant piping 14 of low temperature side
The refrigerant piping 14 low temperature side circulates.The most chloride cold-producing medium is employed as above-mentioned cold-producing medium.Compress at high temperature side
The lubricating oil of the high temperature side used in machine 4 and the lubricating oil of low temperature side that uses in the compressor 11 of low temperature side are relative to above-mentioned
Cold-producing medium has the compatibility.Above-mentioned high temperature side at lubricating oil viscosity pressure coefficient at 40 DEG C than the lubricating oil of above-mentioned low temperature side
Viscosity pressure coefficient at 40 DEG C is high.Therefore, due to the dilution under high temperature and high pressure, above-mentioned oil body is easy
The high temperature side being greatly reduced, uses the above-mentioned lubricating oil that viscosity pressure coefficient is higher, thereby, it is possible to carry in compressor 4,4A
Height easily becomes the abrasion performance of the sliding part of above-mentioned multiple blades of mixed lubrication or boundary lubrication.On the other hand, low temperature side
Compressor 11,11A be relative low temperature, low pressure, the oil body of above-mentioned low temperature side is difficult to reduce.In this low temperature side pressure
In contracting machine 11, use the lubricating oil that viscosity pressure coefficient is relatively low, thereby, it is possible to maintain multiple sliding parts of above-mentioned multiple blade
Abrasion performance, further, it is possible to the slippage loss reduced in above-mentioned multiple sliding part.
It is explained above embodiments of the present invention, but these embodiments is intended only as example and points out, it is not intended to
Limit the scope of invention.These new embodiments should be implemented in other various modes, in the scope of the main idea without departing from invention
In can carry out various omission, replace and change.These embodiments and deformation thereof are comprised in scope and the main idea of invention,
And it is included in the range of the invention described in claims and equivalent thereof.
The explanation of reference
1 ... the freeze cycle of high temperature side, 2 ... the freeze cycle of low temperature side, 3 ... housing, 4 ... the pressure of high temperature side
Contracting machine, 4A ... the compressor of high temperature side, 5 ... the condenser of high temperature side, 6 ... the expansion gear of high temperature side, 7 ... middle
Heat exchanger, 7a ... the stream of high temperature side, 7b ... the stream of low temperature side, 8 ... the refrigerant piping of high temperature side, 11 ...
The compressor of low temperature side, 11A ... the compressor of low temperature side, 12 ... the expansion gear of low temperature side, 13 ... the steaming of low temperature side
Send out device, 14 ... the refrigerant piping of low temperature side, 17 ... the cylinder chamber of high temperature side, 17a ... suction chamber, 17b ... compression
Room, 21 ... the roller of high temperature side, 23 ... the blade of high temperature side, 23a, 23b ... the blade of high temperature side, 28 ... low temperature side
Cylinder chamber, 28a ... suction chamber, 28b ... discharge chambe, 31 ... rotary shaft, 32 ... the roller of low temperature side, 34 ... low
The blade of temperature side.
Claims (5)
1. a freezing cycle device, possesses the freeze cycle of high temperature side and the freeze cycle of low temperature side, and by above-mentioned high temperature side
Freeze cycle and the freeze cycle of above-mentioned low temperature side be equipped in same housing, in the freeze cycle of above-mentioned high temperature side, high temperature
The compressor of side, the condenser to the high temperature side that heated fluid heats, the expansion gear of high temperature side, intermediate heat exchanger
The stream of high temperature side connected via the refrigerant piping of high temperature side, the refrigerant piping along above-mentioned high temperature side circulates system
Cryogen；In the freeze cycle of above-mentioned low temperature side, the compressor of low temperature side, the stream, low of low temperature side of above-mentioned intermediate heat exchanger
The temperature expansion gear of side, the vaporizer of low temperature side are connected via the refrigerant piping of low temperature side, along above-mentioned low temperature side
Refrigerant piping circulating refrigerant, wherein,
As above-mentioned cold-producing medium, use the most chloride cold-producing medium,
The lubricating oil of the high temperature side used in the compressor of above-mentioned high temperature side and use in the compressor of above-mentioned low temperature side
The lubricating oil of low temperature side has the compatibility relative to above-mentioned cold-producing medium,
The lubricating oil of above-mentioned high temperature side viscosity pressure coefficient at 40 DEG C is than lubricating oil the gluing at 40 DEG C of above-mentioned low temperature side
Degree pressure coefficient is high,
The compressor of above-mentioned high temperature side is revolving compressor, possesses the cylinder chamber of high temperature side and by the gas of this high temperature side
The blade of the high temperature side that can slide of suction chamber and discharge chambe it is divided in cylinder chamber,
The compressor of above-mentioned low temperature side is revolving compressor, possesses the cylinder chamber of low temperature side and by the gas of this low temperature side
Cylinder chamber is divided into the blade of the low temperature side that can slide of suction chamber and discharge chambe,
The sliding surface of the blade of above-mentioned high temperature side has been carried out compared with mother metal the scattering and permeating process increasing hardness,
The sliding surface of the blade of above-mentioned low temperature side has been carried out the tunicle process reducing coefficient of friction compared with mother metal.
2. freezing cycle device as claimed in claim 1, wherein,
Above-mentioned cold-producing medium is hydrogen fluorohydrocarbon series coolant, and the lubricating oil of above-mentioned high temperature side is polyvinylether, the lubrication of above-mentioned low temperature side
Oil is polyol ester.
3. freezing cycle device as claimed in claim 1 or 2, wherein,
The weight rate of the resistance to load carrying additive that the lubricating oil of above-mentioned high temperature side and the lubricating oil of above-mentioned low temperature side add is in
The resistance to load carrying additive of the lubricating oil of the above-mentioned low temperature side of weight rate ＞ of the resistance to load carrying additive of the lubricating oil of above-mentioned high temperature side
The relation of weight rate >=0.
4. a freezing cycle device, possesses the freeze cycle of high temperature side and the freeze cycle of low temperature side, and by above-mentioned high temperature side
Freeze cycle and the freeze cycle of above-mentioned low temperature side be equipped in same housing, in the freeze cycle of above-mentioned high temperature side, high temperature
The compressor of side, the condenser to the high temperature side that heated fluid heats, the expansion gear of high temperature side, intermediate heat exchanger
The stream of high temperature side connected via the refrigerant piping of high temperature side, the refrigerant piping along above-mentioned high temperature side circulates system
Cryogen；In the freeze cycle of above-mentioned low temperature side, the compressor of low temperature side, the stream, low of low temperature side of above-mentioned intermediate heat exchanger
The temperature expansion gear of side, the vaporizer of low temperature side are connected via the refrigerant piping of low temperature side, along above-mentioned low temperature side
Refrigerant piping circulating refrigerant, wherein,
As above-mentioned cold-producing medium, use the most chloride cold-producing medium,
The lubricating oil of the high temperature side used in the compressor of above-mentioned high temperature side and use in the compressor of above-mentioned low temperature side
The lubricating oil of low temperature side has the compatibility relative to above-mentioned cold-producing medium,
The lubricating oil of above-mentioned high temperature side viscosity pressure coefficient at 40 DEG C is than lubricating oil the gluing at 40 DEG C of above-mentioned low temperature side
Degree pressure coefficient is high,
The compressor of above-mentioned high temperature side is revolving compressor, possesses: the cylinder chamber of high temperature side, insert the cylinder of this high temperature side
The rotary shaft of room chimeric with this rotary shaft and carry out in the cylinder chamber of above-mentioned high temperature side the high temperature side of eccentric rotary roller,
And make leading section abut with the outer peripheral face of the roller of above-mentioned high temperature side the cylinder chamber of above-mentioned high temperature side is divided into suction chamber
Blade with at least 2 high temperature sides that can slide of discharge chambe；
The compressor of above-mentioned low temperature side is revolving compressor, possesses: the cylinder chamber of low temperature side, insert the cylinder of this low temperature side
The rotary shaft of room chimeric with this rotary shaft and carry out in the cylinder chamber of above-mentioned low temperature side the low temperature side of eccentric rotary roller,
And make leading section abut with the outer peripheral face of the roller of this low temperature side to be divided into suction chamber in the cylinder chamber of above-mentioned low temperature side
Blade with at least 1 low temperature side that can slide of discharge chambe；
The number of the blade of the high temperature side of the compressor of above-mentioned high temperature side is than the blade of the low temperature side of the compressor of above-mentioned low temperature side
Number many.
5. a freezing cycle device, possesses the freeze cycle of high temperature side and the freeze cycle of low temperature side, and by above-mentioned high temperature side
Freeze cycle and the freeze cycle of above-mentioned low temperature side be equipped in same housing, in the freeze cycle of above-mentioned high temperature side, high temperature
The compressor of side, the condenser to the high temperature side that heated fluid heats, the expansion gear of high temperature side, intermediate heat exchanger
The stream of high temperature side connected via the refrigerant piping of high temperature side, the refrigerant piping along above-mentioned high temperature side circulates system
Cryogen；In the freeze cycle of above-mentioned low temperature side, the compressor of low temperature side, the stream, low of low temperature side of above-mentioned intermediate heat exchanger
The temperature expansion gear of side, the vaporizer of low temperature side are connected via the refrigerant piping of low temperature side, along above-mentioned low temperature side
Refrigerant piping circulating refrigerant, wherein,
As above-mentioned cold-producing medium, use the most chloride cold-producing medium,
The lubricating oil of the high temperature side used in the compressor of above-mentioned high temperature side and use in the compressor of above-mentioned low temperature side
The lubricating oil of low temperature side has the compatibility relative to above-mentioned cold-producing medium,
The lubricating oil of above-mentioned high temperature side viscosity pressure coefficient at 40 DEG C is than lubricating oil the gluing at 40 DEG C of above-mentioned low temperature side
Degree pressure coefficient is high,
The compressor of above-mentioned high temperature side is revolving compressor, possesses: the cylinder chamber of high temperature side, insert the cylinder of this high temperature side
The rotary shaft of room chimeric with this rotary shaft and carry out in the cylinder chamber of above-mentioned high temperature side the high temperature side of eccentric rotary roller,
And make leading section abut with the outer peripheral face of the roller of above-mentioned high temperature side the cylinder chamber of above-mentioned high temperature side is divided into suction chamber
Blade with at least 2 high temperature sides that can slide of discharge chambe；
The compressor of above-mentioned low temperature side is revolving compressor, possesses: the cylinder chamber of low temperature side, insert the cylinder of this low temperature side
The rotary shaft of room chimeric with this rotary shaft and carry out in the cylinder chamber of above-mentioned low temperature side the low temperature side of eccentric rotary roller,
And make leading section abut with the outer peripheral face of the roller of this low temperature side to be divided into suction chamber in the cylinder chamber of above-mentioned low temperature side
Blade with at least 1 low temperature side that can slide of discharge chambe.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012181188A JP2014037928A (en) | 2012-08-17 | 2012-08-17 | Refrigeration cycle device |
| JP2012-181188 | 2012-08-17 | ||
| PCT/JP2013/004239 WO2014027438A1 (en) | 2012-08-17 | 2013-07-09 | Refrigeration cycle device |
Publications (2)
| Publication Number | Publication Date |
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| CN104583688A CN104583688A (en) | 2015-04-29 |
| CN104583688B true CN104583688B (en) | 2016-09-21 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201380044192.XA Active CN104583688B (en) | 2012-08-17 | 2013-07-09 | Freezing cycle device |
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| JP (1) | JP2014037928A (en) |
| CN (1) | CN104583688B (en) |
| WO (1) | WO2014027438A1 (en) |
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| CN106662369A (en) * | 2014-07-18 | 2017-05-10 | 科慕埃弗西有限公司 | Use of 1,1,2,2-tetrafluoroethane in high temperature heat pumps |
| JP6522345B2 (en) * | 2015-01-13 | 2019-05-29 | 日立ジョンソンコントロールズ空調株式会社 | Refrigerating apparatus and sealed electric compressor |
| WO2016185546A1 (en) * | 2015-05-18 | 2016-11-24 | 三菱電機株式会社 | Compressor |
| JP6736019B2 (en) * | 2016-02-08 | 2020-08-05 | Ｅｎｅｏｓ株式会社 | Refrigerator, method for manufacturing refrigerator, and method for improving COP |
| JP6834389B2 (en) * | 2016-11-16 | 2021-02-24 | 株式会社富士通ゼネラル | Rotary compressor |
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| US4514154A (en) * | 1981-07-16 | 1985-04-30 | Concezio Mazzagatti | Self-sealing abutment |
| CN1210961A (en) * | 1990-11-16 | 1999-03-17 | 株式会社日立制作所 | Refrigerant compressor |
| US5733112A (en) * | 1993-12-08 | 1998-03-31 | Samsung Electronics Co., Ltd. | Rotary compressor having a roller mounted eccentrically in a cylindrical chamber of a rotatable cylinder |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN104583688A (en) | 2015-04-29 |
| WO2014027438A1 (en) | 2014-02-20 |
| JP2014037928A (en) | 2014-02-27 |
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