CN101384865B - Refrigerating system - Google Patents

Refrigerating system Download PDF

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Publication number
CN101384865B
CN101384865B CN2007800058509A CN200780005850A CN101384865B CN 101384865 B CN101384865 B CN 101384865B CN 2007800058509 A CN2007800058509 A CN 2007800058509A CN 200780005850 A CN200780005850 A CN 200780005850A CN 101384865 B CN101384865 B CN 101384865B
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CN
China
Prior art keywords
pressure
cold
producing medium
gas
make
Prior art date
Application number
CN2007800058509A
Other languages
Chinese (zh)
Other versions
CN101384865A (en
Inventor
冈本昌和
Original Assignee
大金工业株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to JP053431/2006 priority Critical
Priority to JP2006053431A priority patent/JP2007232263A/en
Application filed by 大金工业株式会社 filed Critical 大金工业株式会社
Priority to PCT/JP2007/053255 priority patent/WO2007105440A1/en
Publication of CN101384865A publication Critical patent/CN101384865A/en
Application granted granted Critical
Publication of CN101384865B publication Critical patent/CN101384865B/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B9/00Compression machines, plant, or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002Compression machines, plant, or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008Compression machines, plant, or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B1/00Compression machines, plant, or systems with non-reversible cycle
    • F25B1/10Compression machines, plant, or systems with non-reversible cycle with multi-stage compression
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B13/00Compression machines, plant or systems with reversible cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2309/00Gas cycle refrigeration machines
    • F25B2309/06Compression machines, plant or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061Compression machines, plant or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2313/00Compression machines, plant, or systems with reversible cycle not otherwise provided for
    • F25B2313/027Compression machines, plant, or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272Compression machines, plant, or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2313/00Compression machines, plant, or systems with reversible cycle not otherwise provided for
    • F25B2313/027Compression machines, plant, or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741Compression machines, plant, or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13Economisers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23Separators

Abstract

A refrigerant circuit (10) has a compressor (30) where a low- stage side compression mechanism (34) and a high-stage side compression mechanism (35) are connected by a drive shaft (33) and also has a gas-liquid separator (15). The refrigerant circuit (10) performs a two-stage compression/two-stage expansion refrigeration cycle with a CO2 refrigerant set to a critical pressure. In the compressor (30), the volumetric ratio V2/V1 that is the ratio of the displacement volume V2 of the high-stage side compression mechanism (35) to the displacement volume V1 of the low-stage side compression mechanism (34) is set to a range that is higher than 0.8 and lower than 1.3.

Description

Air conditioner
Technical field
The present invention relates to a kind of air conditioner, it has possessed refrigerant loop that gas-liquid separator is arranged and CO 2Cold-producing medium carries out the kind of refrigeration cycle of two stages of compression double expansion as the critical pressure of high pressure.
Background technology
Always, the air conditioner that has possessed refrigerant loop is widely used air conditioner etc.
For example patent documentation 1 discloses a kind of air conditioner, and this air conditioner has the refrigerant loop that has possessed gas-liquid separator and the kind of refrigeration cycle of carrying out the two stages of compression double expansion.
Refrigerant loop at this air conditioner is provided with compressor, first heat exchanger, first expansion valve, gas-liquid separator, second expansion valve and second heat exchanger.Above-mentioned compressor is constituting rudimentary side pressure mechanism and the senior side pressure two stages of compression formula compressor that mechanism connects by driving shaft that contracts that contracts.And the gas-liquid two-phase cold-producing medium of pressing in the middle of above-mentioned gas-liquid separator structurally can make is separated into liquid refrigerant and gaseous refrigerant.
In the cold air operation of this air conditioner, the ejection cold-producing medium of compressor flows through first heat exchanger.At first heat exchanger, cold-producing medium dispels the heat to air.Press in the middle of cold-producing medium through first heat exchanger is depressurized to through first expansion valve time and flow in the gas-liquid separator.At gas-liquid separator, middle gas-liquid two-phase cold-producing medium of pressing is separated into gaseous refrigerant and liquid refrigerant.By the liquid refrigerant of gas-liquid separator separates, through second expansion valve time, be depressurized to low pressure and flow through second heat exchanger afterwards.At second heat exchanger, cold-producing medium is by air heat absorption evaporation.As a result, make indoor nice and cool.
Cold-producing medium through second heat exchanger is inhaled into compressor, presses in the middle of being compressed in the rudimentary side pressure mechanism of contracting.The contract ejection cold-producing medium of mechanism of rudimentary side pressure, mixed at gaseous refrigerant that above-mentioned gas-liquid separator separated.In other words, the gaseous refrigerant that has carried out pressing the centre at this air conditioner and rudimentary side pressure contract mechanism the ejection refrigerant mixed, be intermediate pressure gas body injection (gas injection).Thereafter, this cold-producing medium is compressed to high pressure and is ejected again from compressor in the senior side pressure mechanism of contracting.
As above-mentioned ground, at the air conditioner of patent documentation 1, inject owing to carry out the intermediate pressure gas body, make the ejection refrigerant temperature decline of compressor make the power of compressor descend simultaneously.And this air conditioner seeks to improve COP (the coefficient of performance coefficient of performance).
And, a kind of air conditioner is disclosed in the patent documentation 2, the refrigerant loop of this air conditioner is filled CO 2Cold-producing medium and carry out above-mentioned intermediate pressure gas body and inject.And, make the ejection cold-producing medium of compressor be more than the critical pressure, be overcritical circulation at this air conditioner.[patent documentation 1] japanese kokai publication hei 7-110167 communique [patent documentation 2] TOHKEMY 2001-241797 communique summary of the invention solves problem
Disclosed air conditioner in patent documentation 1, the capacity (discharging capacity displacement) that is designed to each compressing mechanism of two stages of compression formula compressor carries out two stages of compression efficiently.On the other hand, if use CO 2The cold-producing medium that is used as this type air conditioner carries out overcritical circulation time, is compressed to critical pressure and cold-producing medium after heat exchanger heat radiation, sometimes the still state of critical pressure in gas-liquid separator.When if the cold-producing medium in the gas-liquid separator is the situation of critical pressure (critical condition) like this, will be difficult to separate into gaseous refrigerant and liquid refrigerant to the cold-producing medium in the gas-liquid separator.As a result, have only gaseous refrigerant can't be sent to the middle compacting cryogen of compressor, inject and can't carry out above-mentioned intermediate pressure gas body.Therefore, the effect that can't obtain desired intermediate pressure gas body injection is arranged and this type problem that causes the COP reduction of air conditioner.
The present invention is that purpose is because the problems referred to above are thought deeply: using CO 2Cold-producing medium carries out turning round with only COP in the air conditioner of kind of refrigeration cycle of two stages of compression double expansion.Solution
First invention is to be prerequisite with the air conditioner that possesses following refrigerant loop 10, and this refrigerant loop 10 has rudimentary side pressure contract the compressors 30 that mechanism 35 connects mutually by driving shaft 33 and the gas-liquid separator 15 of centre compacting cryogen gas-liquid separation and with CO of mechanism 34 and senior side pressure that contract 2The high pressure of cold-producing medium is the kind of refrigeration cycle that critical pressure is carried out the two stages of compression double expansion.And this air conditioner is characterised in that: make senior side pressure contract mechanism 35 the discharge capacity to above-mentioned rudimentary side pressure contract mechanism 34 the discharge capacity Capacity Ratio for greater than 0.8 less than 1.3 scope.
Refrigerant loop 10 in first invention is filled with CO 2Cold-producing medium.And, have rudimentary side pressure the contract compressor 30 of mechanism 35 of mechanism 34 and senior side pressure that contracts refrigerant loop 10 setting.And, carry out the kind of refrigeration cycle of following two stages of compression double expansion at refrigerant loop 10.
Be compressed to the cold-producing medium of critical pressure in the senior side pressure mechanism 35 of contracting, for example after the indoor heat converter heat radiation, press in the middle of being depressurized to, flow in the gas-liquid separator 15.At gas-liquid separator 15, middle cold-producing medium of pressing is separated into gaseous refrigerant and liquid refrigerant.Liquid refrigerant is depressurized to after the low pressure, for example in the outdoor heat converter evaporation, is inhaled into the rudimentary side pressure mechanism 34 of contracting.This cold-producing medium is pressed in the middle of being compressed in the rudimentary side pressure mechanism 34 of contracting.And, import the gaseous refrigerant that has with gas-liquid separator 15 separation at this cold-producing medium.As a result, carry out injecting like above-mentioned intermediate pressure gas body.Thereafter, cold-producing medium is compressed to the high pressure critical pressure in the senior side pressure mechanism 35 of contracting.
But, using CO in this wise 2When cold-producing medium carries out the situation of kind of refrigeration cycle of two stages of compression double expansion, if air conditioner always, sometimes in the gas-liquid separator in the middle of the cold-producing medium of pressing become the state of critical pressure.When this situation, in gas-liquid separator, can't separate into gaseous refrigerant and liquid refrigerant to cold-producing medium, inject and can't carry out desired intermediate pressure gas body.Here, among the present invention, make senior side pressure contract 35 pairs of rudimentary side pressures of mechanism contract mechanism 34 Capacity Ratio greater than 0.8.In other words, if make this Capacity Ratio less than 0.8, for the contract discharge capacity of mechanism 34 of rudimentary side pressure, the contract discharge capacity of mechanism 35 of senior side pressure will diminish relatively.As a result, the pressure of middle compacting cryogen uprises, and the cold-producing medium in the gas-liquid separator 15 will surpass critical pressure sometimes.On the other hand, owing to make Capacity Ratio greater than 0.8 among the present invention, can make that therefore the refrigerant pressure in the gas-liquid separator 15 is subcritical pressure boiler (subcritical pressure).Therefore, among the present invention, can positively be separated into gaseous refrigerant and liquid refrigerant to the cold-producing medium in the gas-liquid separator 15, obtain the effect that desired intermediate pressure gas body injects.
And if suppose to make that above-mentioned Capacity Ratio is more than 1.3, for the contract discharge capacity of mechanism 34 of rudimentary side pressure, the contract discharge capacity of mechanism 35 of senior side pressure will relatively become big.As a result, can't fully guarantee the contract suction refrigerant amount of mechanism 35 of senior side pressure, and cause the compression efficiency of compressor 30 to descend.On the other hand and since among the present invention Capacity Ratio less than 1.3, therefore can fully guarantee the contract suction refrigerant amount of mechanism 35 of senior side pressure, the effective forthright two stages of compression of cold-producing medium.
Second invention is characterised in that: in first invention, make that above-mentioned Capacity Ratio is greater than more than 0.9, less than the scope below 1.1.
Second the invention in make senior side pressure contract mechanism 35 the discharge capacity to rudimentary side pressure contract mechanism 34 the discharge capacity Capacity Ratio be the scope more than 0.9, below 1.1.In other words, owing to make that above-mentioned Capacity Ratio is more than 0.9, can make that the refrigerant pressure in the gas-liquid separator 15 positively becomes critical pressure.And, owing to make that above-mentioned Capacity Ratio is below 1.1, can be cold-producing medium two stages of compression more efficiently.
The 3rd invention is characterised in that: make that above-mentioned Capacity Ratio is 1.0 in second invention.
In the 3rd invention, make rudimentary side pressure the contract capacity of mechanism 35 of capacity and the senior side pressure of mechanism 34 that contracts be set at same capacity.
The 4th invention is characterised in that: in arbitrary invention of first to the 3rd invention, rudimentary side pressure mechanism 34 and the senior side pressure mechanism 35 of contracting of contracting is made up of the Rotary Compressor structure.
In the 4th invention, the rudimentary side pressure that is made up of Rotary Compressor structure mechanism 34 and the senior side pressure mechanism 35 of contracting of contracting is connect mutually by driving shaft 33 and constitutes compressor 30.The invention effect
Contract that the Capacity Ratio of mechanism 35 is set in greater than 0.8, scope less than 1.3 to contract mechanism 34 and senior side pressure of rudimentary side pressure among the present invention.Here, if make Capacity Ratio, can make the pressure of the cold-producing medium in the gas-liquid separator 15 less than critical pressure greater than 0.8.Therefore,, can carry out desired intermediate pressure gas body at refrigerant loop 10 and inject, improve the COP of air conditioner according to the present invention.And, if make this Capacity Ratio less than 1.3, with the decline of the compression efficiency that the deficiency of suction refrigerant amount of mechanism 35 causes that can not cause senior side pressure to be contracted, and can be the cold-producing medium two stages of compression.Therefore, can further improve the COP of air conditioner according to the present invention.
Particularly, in second invention, make rudimentary side pressure the contract Capacity Ratio of mechanism 35 of mechanism 34 and senior side pressure that contracts be set in the scope more than 0.9, below 1.1.In other words, among the present invention, make rudimentary side pressure the contract Capacity Ratio of mechanism 35 of mechanism 34 and senior side pressure that contracts be set in only scope.Therefore, can further improve the COP of air conditioner according to the present invention.
And the 3rd invention first is set rudimentary side pressure the contract capacity of mechanism 35 of capacity and the senior side pressure of mechanism 34 that contracts for same capacity.Therefore,, can make rudimentary side pressure mechanism 34 and the senior side pressure mechanism 35 of contracting of contracting be identical compressor structure (mechanism) specification, seek the cost degradation and the simplification of compressor 30 according to the present invention.
And,, in air conditioner, can carry out desired intermediate pressure gas body injection and seek to improve COP with compressor 30 of forming by two Rotary Compressor structures according to the 4th invention.
Description of drawings
Fig. 1 is the piping diagram of the refrigerant loop of the related air conditioner of embodiment.Fig. 2 is the piping diagram of heating installation when running flow of refrigerant of explanation air conditioner.Fig. 3 be the explanation air conditioner cold air operation the time flow of refrigerant piping diagram.Fig. 4 be the senior side pressure of expression contract mechanism to rudimentary side pressure contract mechanism Capacity Ratio and with the graph of a relation of COP.Symbol description
1 air conditioner, 10 refrigerant loops, 30 compressors, 34 first compressing mechanisms (rudimentary side pressure contract mechanism), 35 second compressing mechanisms (senior side pressure contract mechanism)
The specific embodiment
The related air conditioner of embodiment constitutes the air conditioner 1 that carries out room conditioning.This air conditioner 1 can constitute indoor heating installation and cold air.
Air conditioner 1 has and is arranged on indoor indoor set 11 and is arranged on outdoor off-premises station 12.Indoor set 11 is connected mutually through two contact pipe arrangements with off-premises station 12.As a result, at air conditioner 1, refrigerant loop 10 12 is configured from indoor set 11 to off-premises station.Be filled with CO at this refrigerant loop 10 2Cold-producing medium.And, in the refrigerant loop 10, with CO 2The high pressure of cold-producing medium is the kind of refrigeration cycle that critical pressure is carried out the two stages of compression double expansion.
Be provided with indoor heat converter 13 at indoor set 11.Indoor heat converter 13 constitutes finned tube (fintube) heat exchanger.At this indoor heat converter 13, room air that indoor fan is blown and cold-producing medium carry out heat exchange.
Be provided with compressor 30, outdoor heat converter 14 and the gas-liquid separator 15 that the back is detailed at off-premises station 12.
Outdoor heat converter 14 constitutes fin-tube heat exchanger.At this outdoor heat converter 14, the outdoor air and the cold-producing medium of outdoor fan air-supply carry out heat exchange.
Gas-liquid separator 15 constitutes with columnar closed container.At this gas-liquid separator 15, be connected with inflow pipe 15a and gas injection pipe arrangement 15b with the mode that connects the top.Gas injects pipe arrangement 15b and constitutes the stream that the gaseous refrigerant of pressing the centre imports compressor 30.Be connected with the effuser 15c that connects its underpart at gas-liquid separator 15.At gas-liquid separator 15, the cold-producing medium of middle gas-liquid two-phase state of pressing is separated into gaseous refrigerant and liquid refrigerant.
And, be provided with cross valve 16, bridge circuit 17, first expansion valve 18 and second expansion valve 19 at off-premises station 12.
Cross valve 16 has possessed first to the 4th valve port.Be connected with the bleed pipe 41 of compressor 30 at cross valve 16, the first valve ports, second valve port is connected with outdoor heat converter 14, and the 3rd valve port is connected with indoor heat converter 13, and the 4th valve port is connected with the suction line 42 of compressor 30.This cross valve 16 structurally can convert into and first valve port and second valve port is communicated with make simultaneously the state (state shown in Fig. 1 solid line) that the 3rd valve port and the 4th valve port be communicated with and make first valve port and the 3rd valve port is communicated with the state (state shown in Fig. 1 dotted line) that second valve port and the 4th valve port are communicated with.
Bridge circuit 17 is made up of four pipe arrangements that are combined into the bridge shape and four non-return valves that in each pipe arrangement, are provided with separately.Each non-return valve of this bridge circuit 17 only allows that cold-producing medium circulates with direction shown in Fig. 1 flechette-type symbol.
The electric expansion valve that first expansion valve 18 and second expansion valve, 19 each freedom can be regulated aperture constitutes.First expansion valve 18 is located at the pipe arrangement of the inflow side of gas-liquid separator 15, and second expansion valve 19 is located at the pipe arrangement of the outflow side of gas-liquid separator 15.
As shown in Figure 2, compressor 30 be formed in two compressing mechanisms the cold-producing medium two stages of compression, be two stages of compression formula compressor.Compressor 30 has the casing (casing) 31 of cylindrical shape hermetic type.Motor 32, driving shaft 33, first compressing mechanism 34 and second compressing mechanism 35 in casing 31, have been taken in.
Motor 32 is made up of with the rotor that is fixed on driving shaft 33 outer peripheral faces the stator of the inner peripheral surface that is fixed on casing 31.The state that driving shaft 33 extends with above-below direction is by bearings.This driving shaft 33 can rotate through the driving of motor 32.
First compressing mechanism 34 is configured near the bottom of casing 31, constitutes the compressing mechanism of rudimentary side.On the other hand, second compressing mechanism 35 is configured near the motor, constitutes the compressing mechanism of senior side.
First compressing mechanism 34 and second compressing mechanism, 35 each free swinging (rotary) rotary-type (swing) compressing mechanisms constitute.At the indoor piston of having taken in separately of each compressing mechanism 34,35 cylindrical cylinders (cylinder).And, each piston, with eccentric this driving shaft 33 of each self join of mode in the axle center of driving shaft 33.Therefore, in case driving shaft 33 rotations, each piston of two compressing mechanisms 34,35 will rotate with driving shaft 33 prejudicially.And each piston of each compressing mechanism 34,35 comes to connect with driving shaft 33 to depart from 180 ° of phase places mutually.Therefore, centrifugal force is cancelled each other when the driving of each piston, and suppresses the generation of vibration and the change of torque load.
Be connected with above-mentioned suction line 42 in the suction side of first compressing mechanism 34, an end of liaison tube 43 in the middle of its ejection side is connected with.Be connected with the other end of middle liaison tube 32 in the suction side of second compressing mechanism 35, its ejection side is connected with above-mentioned bleed pipe 41.
Liaison tube 43 is configured to import the cold-producing medium after 34 compressions of first compressing mechanism stream of the suction side of second compressing mechanism 35 in the middle of above-mentioned.Liaison tube 43 in the middle of this is connected with the outflow end that above-mentioned gas injects pipe arrangement 15b at the position that bends to the U font.
In the air conditioner 1 of this embodiment, the ratio (Capacity Ratio V2/V1) of discharge capacity V2 of discharge capacity V1 and second compressing mechanism 35 of the compressing mechanism 34 of winning is set in greater than 0.8 less than 1.3 scope.Its result is with the COP coefficient of performance that improves air conditioner 1.About the relation of this Capacity Ratio V2/V1 and COP will detail in the back.
The running action of the air conditioner 1 that-running action-following this embodiment of explanation is related.At air conditioner 1, can carry out heating installation running and the cold air operation shown in following.
Cross valve 16 becomes state shown in Figure 2 in the running of < heating installation running>heating installation.And, the aperture of suitably regulating first expansion valve 18 and second expansion valve 19.
Be compressed to the cold-producing medium of critical pressure from compressor 30 ejections.This cold-producing medium is through flowing through indoor heat converter 13 after the cross valve 16.At indoor heat converter 13, cold-producing medium dispels the heat to room air.As a result, make indoor warm.Flow out the cold-producing medium of indoor heat converter 13, baric flow is gone in the gas-liquid separator 15 in the middle of being depressurized to through first expansion valve 18.
In gas-liquid separator 15, accumulated the gas-liquid two-phase cold-producing medium of middle pressure.And at gas-liquid separator 15, this cold-producing medium is separated into gaseous refrigerant and liquid refrigerant.The gaseous refrigerant inflow gas that accumulates in the top in the gas-liquid separator 15 injects pipe arrangement 15b.On the other hand, the cold-producing medium that accumulate the bottom in gas-liquid separator 15 is depressurized to low pressure through second expansion valve 19 and flows through outdoor heat converter 14 afterwards.At outdoor heat converter 14, cold-producing medium is by outdoor air heat absorption evaporation.The cold-producing medium of delivery chamber's outer heat-exchanger 14 is inhaled into compressor 30.
At compressor 30, at first cold-producing medium is inhaled into first compressing mechanism 34 from suction line 42.At first compressing mechanism 34, in the middle of being compressed to, cold-producing medium presses.Liaison tube 43 in the middle of the ejection cold-producing medium of first compressing mechanism 34 flows through.This sprays cold-producing medium, mixes with the gaseous refrigerant that flows out above-mentioned gas injection pipe arrangement 15b.As a result, the temperature of the ejection cold-producing medium of first compressing mechanism 34 descends.The cold-producing medium of liaison tube 43 is inhaled into second compressing mechanism 35 in the middle of flowing out.At second compressing mechanism 35, cold-producing medium is compressed to critical pressure.
In < cold air operation>cold air operation, cross valve 16 becomes state shown in Figure 3.And, the aperture of suitably regulating first expansion valve 18 and second expansion valve 19.
Be compressed to the cold-producing medium of critical pressure from compressor 30 ejections.This cold-producing medium is through flowing through outdoor heat converter 14 after the cross valve 16.At outdoor heat converter 14, cold-producing medium dispels the heat to outdoor air.The cold-producing medium of delivery chamber's outer heat-exchanger 14 is depressurized to middle baric flow through first expansion valve 18 and goes in the gas-liquid separator 15.
In gas-liquid separator 15, accumulating has middle gas-liquid two-phase cold-producing medium of pressing.And at gas-liquid separator 15, this cold-producing medium is separated into gaseous refrigerant and liquid refrigerant.The gaseous refrigerant that accumulate on top in gas-liquid separator 15, inflow gas injects pipe arrangement 15b.On the other hand, the cold-producing medium that accumulate the bottom in gas-liquid separator 15 is depressurized to low pressure through second expansion valve 19 and flows through indoor heat converter 13 afterwards.At indoor heat converter 13, cold-producing medium is by room air heat absorption evaporation.As a result, make indoor nice and cool.The cold-producing medium that flows out indoor heat converter 13 is inhaled into compressor 30.
At compressor 30, at first cold-producing medium is inhaled into first compressing mechanism 34 from suction line 42.At first compressing mechanism 34, in the middle of being compressed to, cold-producing medium presses.Liaison tube 43 in the middle of the ejection cold-producing medium of first compressing mechanism 34 flows through.This sprays cold-producing medium, mixes with the gaseous refrigerant that flows out above-mentioned gas injection pipe arrangement 15b.As a result, the temperature of the ejection cold-producing medium of first compressing mechanism 34 descends.The cold-producing medium of liaison tube 43 is inhaled into second compressing mechanism 35 in the middle of flowing out.At second compressing mechanism 35, be compressed to critical pressure to cold-producing medium.
The Capacity Ratio of-two compressing mechanisms and the relation of COP-as above-mentioned; In the heating installation running and cold air operation of the air conditioner 1 that embodiment is related, inject owing to carry out so-called intermediate pressure gas body to the gaseous refrigerant that separates at gas-liquid separator 15 with the middle compacting cryogen of compressor 30 with mixing.As a result, at this air conditioner 1, except the ejection refrigerant temperature that makes the compressing mechanism 34 of winning descends, can also cut down the power of compressor 30 and seek to improve COP.
Yet,, carry out so-called overcritical circulation to the high pressure compressed of cold-producing medium to critical pressure at the refrigerant loop 10 of this air conditioner 1.Therefore, if in the gas-liquid separator 15 in the middle of the cold-producing mediums of pressing when becoming critical pressure, will be difficult to make that the cold-producing mediums in the gas-liquid separator 15 are separated into gaseous refrigerant and liquid refrigerant, inject and possibly can't carry out above-mentioned intermediate pressure gas body.Here; Among the present invention; Owing to the Capacity Ratio V2/V1 of the capacity V1 of first compressing mechanism 34 is set in only scope to the capacity V2 of second compressing mechanism 35, make in the gas-liquid separator 15 in the middle of the refrigerant pressure of pressing less than critical pressure, can carry out desired intermediate pressure gas body injection.
Fig. 4 illustrates the result of the relation of above-mentioned Capacity Ratio V2/V1 of self-criticism and COP.Fig. 4 is the heating installation running and the cold air operation of the different air conditioner of relevant Capacity Ratio V2/V1, at the COP of each air conditioner acquisition.And, among Fig. 4, in each air conditioner, try to achieve the COP in heating installation when running of general outdoor temperature condition and range in winter (10 ℃ to 15 ℃), simultaneously, the OP when trying to achieve the cold air operation of general outdoor temperature condition and range in summer (25 ℃ to 35 ℃).And; Here " COP than " shown in is to be that the minimum COP of 0.65 air conditioner is benchmark when COP when the heating installation running of 15 ℃ of outdoor temperatures or the cold air operation 25 ℃ of outdoor temperatures (for example COP) with Capacity Ratio, and comes relatively to estimate the COP of air conditioner of other Capacity Ratio.
As shown in Figure 4, be 0.8 when following making Capacity Ratio, in heating installation running and cold air operation, the COP tendency is for low.This be because: if be Capacity Ratio 0.8 when following; Discharge capacity for first compressing mechanism 34; The discharge capacity of second compressing mechanism 35 will relatively become too small; Cold-producing medium in the gas-liquid separator 15 surpasses critical pressure, therefore can't isolate gaseous refrigerant and can't carry out desired intermediate pressure gas body injection from the cold-producing medium in the gas-liquid separator 15.On the contrary, if so that Capacity Ratio, can make that the cold-producing medium in the gas-liquid separator 15 is a subcritical pressure boiler greater than 0.8, and can separate gaseous refrigerant from the cold-producing medium in the gas-liquid separator 15.Therefore, Capacity Ratio is greater than 0.8 air conditioner, can carry out desired intermediate pressure gas body and inject and obtain high COP.
And if make that Capacity Ratio is 1.3, in the cold air operation under the condition that heating installation turns round and outside air temperature is low, the COP tendency is for low.Be Capacity Ratio more than 1.3, relatively will become excessive if this is, can't guarantee the suction refrigerant amount of second compressing mechanism 35 and become for the discharge capacity of first compressing mechanism 34, the discharge capacity of second compressing mechanism 35.In other words,, can't make the cold-producing medium two stages of compression efficiently, reduce along with the power of compressor 30 increases COP to Capacity Ratio if be more than 1.3.On the contrary, Capacity Ratio is less than 1.3 little air conditioners, two stages of compression cold-producing medium more efficiently, and obtain high COP.
And as shown in the figure, if make that Capacity Ratio is the scope more than 0.9, below 1.1, the COP of cold air operation and heating installation running will uprise.In other words, the capacity V2 of second compressing mechanism 35 to the Capacity Ratio V2/V1 of the capacity V1 of first compressing mechanism 34 preferably more than 0.9, below 1.1.Particularly, if be 1.0, then in the both sides of cold air operation and heating installation running, can reach high COP to this Capacity Ratio.
In the effect of-embodiment-above-mentioned embodiment, the Capacity Ratio of 35 pairs first compressing mechanisms 34 of second compressing mechanism be set in greater than 0.8, scope less than 1.3.Here, if make this Capacity Ratio, can make the pressure of the cold-producing medium in the gas-liquid separator 15 less than critical pressure greater than 0.8.Therefore,, can carry out desired intermediate pressure gas body at refrigerant loop 10 and inject, improve the COP of air conditioner 1 according to this embodiment.And, if make this Capacity Ratio less than 1.3, with not causing because the decline of the compression efficiency that the deficiency of the suction refrigerant amount of second compressing mechanism 35 causes, and can the two stages of compression cold-producing medium.Therefore, according to above-mentioned embodiment, can further hang down the COP that improves air conditioner 1.
Particularly, as shown in Figure 4 if be set in the scope more than 0.9, below 1.1 to the Capacity Ratio of 35 pairs first compressing mechanisms 34 of second compressing mechanism, can obtain high COP.
And, be same capability (Capacity Ratio=1.0) if make the capacity of the compressing mechanism 34 of winning and the capacity of second compressing mechanism 35, in the both sides of cold air operation and heating installation running, can obtain high COP.And, make the compressing mechanism 34 of winning identical in this wise with the capacity of second compressing mechanism 35, can make that two compressing mechanisms are identical compressor structure specification.Therefore, can be with than being easier to and making at low cost compressor 30.
" other embodiments " relevant above-mentioned embodiment can also be following formation.
At above-mentioned embodiment, connect rudimentary side pressure the contract suction side of mechanism 35 of ejection side and the senior side pressure of mechanism 34 of contracting with middle liaison tube 43, liaison tube 43 is connected with the outflow end that gas injects pipe arrangement 15b in the middle of this.But, also can be: the contract ejection cold-producing medium of mechanism 34 of rudimentary side pressure is full of in the inside of the casing 31 of compressor 30, makes compressor 30 be the compressor of half dome-shaped in the middle of so-called, the gaseous refrigerant of in the middle of the inside of this casing 31 imports, pressing.
And, in the above-described embodiment, constitute rudimentary side pressure mechanism 34 and the senior side pressure mechanism 35 of contracting of contracting by the compressing mechanism of rotary-type (swing).But, also can be to constitute these compressing mechanisms with helicoid rotary-piston type compressing mechanism, but or compressing mechanism (such as vortex (scroll) compressing mechanism) formation to constitute by fixed eddy plate and movable orbiting scroll.
And above-mentioned embodiment is desirable in essence illustration just, is not that attempt is used for limiting the present invention, application of the present invention or the scope of purposes of the present invention.Utilize possibility on the industry
As above explanation, the present invention is for the refrigerant loop that possesses gas-liquid separator and with CO 2Cold-producing medium is that the air conditioner of the critical pressure of the high pressure kind of refrigeration cycle of carrying out the two stages of compression double expansion is very useful.

Claims (3)

1. air conditioner that possesses refrigerant loop; This refrigerant loop have by driving shaft come to connect mutually rudimentary side pressure contract mechanism and senior side pressure contract mechanism compressor and make in the middle of gas-liquid separator, indoor heat converter, the outdoor heat converter of compacting cryogen gas-liquid separation, and make CO 2The high pressure of cold-producing medium is the kind of refrigeration cycle that critical pressure is carried out the two stages of compression double expansion; Said air conditioner carries out heating installation running and cold air operation; In the heating installation running, make refrigerant loses heat and make the cold-producing medium evaporation with indoor heat converter, in cold air operation with outdoor heat converter; Make refrigerant loses heat and make the cold-producing medium evaporation with outdoor heat converter, it is characterized in that with indoor heat converter:
Make the contract discharge capacity of mechanism of senior side pressure contract the Capacity Ratio of discharge capacity of mechanism in the scope more than 0.9, below 1.1 to above-mentioned rudimentary side pressure.
2. air conditioner according to claim 1 is characterized in that:
Above-mentioned Capacity Ratio is 1.0.
3. air conditioner according to claim 1 and 2 is characterized in that:
Rudimentary side pressure mechanism and the senior side pressure mechanism of contracting of contracting is made up of the Rotary Compressor structure.
CN2007800058509A 2006-02-28 2007-02-22 Refrigerating system CN101384865B (en)

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AU2007226005B2 (en) 2010-05-20
CN101384865A (en) 2009-03-11
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EP1990587A4 (en) 2014-11-19
US20090044564A1 (en) 2009-02-19

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