CN101960235B - Refrigeration device - Google Patents
Refrigeration device Download PDFInfo
- Publication number
- CN101960235B CN101960235B CN2009801070403A CN200980107040A CN101960235B CN 101960235 B CN101960235 B CN 101960235B CN 2009801070403 A CN2009801070403 A CN 2009801070403A CN 200980107040 A CN200980107040 A CN 200980107040A CN 101960235 B CN101960235 B CN 101960235B
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- Prior art keywords
- heat exchanger
- cold
- producing medium
- compression member
- refrigerant
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- 238000005057 refrigeration Methods 0.000 title description 31
- 230000007246 mechanism Effects 0.000 claims abstract description 547
- 230000006835 compression Effects 0.000 claims abstract description 304
- 238000007906 compression Methods 0.000 claims abstract description 304
- 239000003507 refrigerant Substances 0.000 claims abstract description 277
- 238000001816 cooling Methods 0.000 claims description 173
- 238000010438 heat treatment Methods 0.000 claims description 142
- 230000000306 recurrent effect Effects 0.000 claims description 113
- 239000007788 liquid Substances 0.000 claims description 75
- 238000007599 discharging Methods 0.000 claims description 59
- 230000005855 radiation Effects 0.000 claims description 18
- 238000000926 separation method Methods 0.000 claims description 8
- 230000004087 circulation Effects 0.000 claims description 7
- 230000006870 function Effects 0.000 description 60
- 239000003921 oil Substances 0.000 description 60
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 30
- 238000002347 injection Methods 0.000 description 28
- 239000007924 injection Substances 0.000 description 28
- 238000004781 supercooling Methods 0.000 description 28
- 238000012546 transfer Methods 0.000 description 26
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 22
- 238000001704 evaporation Methods 0.000 description 19
- 238000003825 pressing Methods 0.000 description 19
- 239000007921 spray Substances 0.000 description 19
- 230000006837 decompression Effects 0.000 description 17
- 230000008020 evaporation Effects 0.000 description 16
- 230000001143 conditioned effect Effects 0.000 description 13
- 230000009471 action Effects 0.000 description 11
- 229910002092 carbon dioxide Inorganic materials 0.000 description 11
- 239000001569 carbon dioxide Substances 0.000 description 11
- 230000000694 effects Effects 0.000 description 11
- 230000033228 biological regulation Effects 0.000 description 10
- 239000013256 coordination polymer Substances 0.000 description 8
- 230000007423 decrease Effects 0.000 description 7
- 239000007789 gas Substances 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 238000005507 spraying Methods 0.000 description 6
- 230000008014 freezing Effects 0.000 description 5
- 238000007710 freezing Methods 0.000 description 5
- 230000001052 transient effect Effects 0.000 description 5
- 230000002349 favourable effect Effects 0.000 description 4
- MWUXSHHQAYIFBG-UHFFFAOYSA-N Nitric oxide Chemical compound O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 3
- 230000007812 deficiency Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000000704 physical effect Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 239000012266 salt solution Substances 0.000 description 2
- 230000005144 thermotropism Effects 0.000 description 2
- OTMSDBZUPAUEDD-UHFFFAOYSA-N Ethane Chemical compound CC OTMSDBZUPAUEDD-UHFFFAOYSA-N 0.000 description 1
- VGGSQFUCUMXWEO-UHFFFAOYSA-N Ethene Chemical compound C=C VGGSQFUCUMXWEO-UHFFFAOYSA-N 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000012217 deletion Methods 0.000 description 1
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- 238000013461 design Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 239000010721 machine oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
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- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/072—Intercoolers therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/17—Control issues by controlling the pressure of the condenser
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
An air conditioner (1) has a two-stage compression type compression mechanism (2), a heat source heat exchanger (4), a utilization heat exchanger (6), a switching mechanism (3), and an intermediate heat exchanger (7). The switching mechanism (3) is a mechanism for switching between a cooling-operation state in which refrigerant is circulated in order from the compression mechanism (2) through the heat source heat exchanger (4) to the utilization heat exchanger (6) and a heating-operation state in which the refrigerant is circulated in order from the compression mechanism (2) through the utilization heat exchanger (6) to the heat source heat exchanger (4). The intermediate heat exchanger (7) is a heat exchanger which, when the switching mechanism (3) is set to the cooling-operation state, can be made to function as a cooler for the refrigerant discharged from a front stage compression element (2c) and sucked into a rear stage compression element (2d) and which, when the switching mechanism (3) is set to the heating-operation state, can be made to function as an evaporator for the refrigerant having released heat in the utilization heat exchanger (6).
Description
Technical field
The present invention relates to a kind of refrigerating plant, particularly relate to and a kind ofly have the refrigerant loop that can switch cooling operation and add heat run, and carry out the refrigerating plant of multi-stage compression formula freeze cycle.
Background technology
In the prior art, can switch cooling operation and add the refrigerant loop of heat run and carry out example of refrigerating plant of multi-stage compression formula freeze cycle as having, aircondition shown in the patent documentation 1 is arranged, it has the refrigerant loop that can switch cooling operation and heating running, and carries out two-stage compression formula freeze cycle.This aircondition mainly comprises: the compressor with two compression member that are connected in series; Be used for switching four phase transfer valves of cooling operation and heating running; Outdoor heat converter; And indoor heat converter.
Patent documentation 1: JP 2007-232263 communique
Summary of the invention
The 1st refrigerating plant that relates to of invention comprises: compressing mechanism, have heat source side heat exchanger as the radiator of cold-producing medium or evaporator function, have and utilize side heat exchanger, switching mechanism and intermediate heat exchanger as the evaporimeter of cold-producing medium or radiator function.Compressing mechanism has a plurality of compression member, and uses the rear-stage side compression member to compress successively the cold-producing medium that the preceding-stage side compression member from a plurality of compression member is discharged.Said " compressing mechanism " comprises the compressing mechanism that forms by connecting multiple compressors herein, and compressor comprises that a plurality of compression member are assembled into one and the compressor that consists of and assembling single compressed parts and the compressor that consists of and/or assemble a plurality of compression member and the compressor that consists of.In addition, " compressing successively the cold-producing medium that the preceding-stage side compression member from a plurality of compression member is discharged with the rear-stage side compression member " is not only to refer to comprise that " preceding-stage side compression member " reaches two compression member that " rear-stage side compression member " is connected in series, and refer to that a plurality of compression member are connected in series, and the relation between each compression member has above-mentioned " preceding-stage side compression member " and the relation of " rear-stage side compression member ".Switching mechanism be used for switching make cold-producing medium successively at compressing mechanism, have heat source side heat exchanger as the radiator function of cold-producing medium, have the cooling operating condition that circulates in the side heat exchanger of utilizing as the evaporator function of cold-producing medium; And make cold-producing medium successively at compressing mechanism, have utilizing the side heat exchanger, have the heating operating condition that circulates in the heat source side heat exchanger as the evaporator function of cold-producing medium as the radiator function of cold-producing medium.When intermediate heat exchanger switches to the cooling operating condition at switching mechanism, can be as discharging the cooler that then is inhaled into the cold-producing medium the rear-stage side compression member from prime side pressure contracting parts, when switching mechanism switches to the heating operating condition, can be as the evaporimeter of the cold-producing medium after the heat radiation in utilizing the side heat exchanger.
In existing aircondition, then the rear-stage side compression member that the cold-producing medium of discharging from the rudimentary compression member of compressor is inhaled into compressor is further compressed, therefore, the temperature of the cold-producing medium of discharging from the rear-stage side compression member of compressor raises, for example, in the outdoor heat converter that has as the radiator function of cold-producing medium, empty G﹠W and the temperature difference between the cold-producing medium as thermal source increase, radiation loss in the outdoor heat converter increases, therefore, existence is difficult to obtain the such problem of high running efficiency.
In order to address this problem, as this refrigerating plant, have in setting in the situation of the intermediate heat exchanger that is used as the cooler function of discharging the cold-producing medium that then is inhaled into the rear-stage side compression member from prime side pressure contracting parts, be inhaled into the temperature step-down of the cold-producing medium of rear-stage side compression member, therefore, compare with the mode that intermediate heat exchanger is not set, can reduce finally the temperature of the cold-producing medium of discharging from compressing mechanism.Like this, in when running cooling, have as the radiation loss in the heat source side heat exchanger of the radiator function of cold-producing medium and reduce, therefore, the running efficiency in the time of can improving the cooling running.
But, when adding heat run, do not arranging in the situation with the intermediate heat exchanger that is used as the cooler function of discharging the cold-producing medium that then is inhaled into the rear-stage side compression member from prime side pressure contracting parts, when adding heat run, owing to be provided with intermediate heat exchanger, therefore, the heat that can utilize in utilizing the side heat exchanger will reject heat to the outside from middle heat exchanger, like this, utilize the heating efficiency in the side heat exchanger to reduce, the running efficiency when adding heat run will descend.
In contrast, for example, setting is used for the intermediate heat exchanger bypass pipe of bypass intermediate heat exchanger, and, when adding heat run, use this intermediate heat exchanger bypass pipe to carry out bypass, thereby make and discharge the cold-producing medium then be inhaled into the rear-stage side compression member from prime side pressure contracting parts and intermediate heat exchanger, be not cooled, thereby become the state that does not use intermediate heat exchanger, like this, under the heating operating condition, can prevent from utilizing the heating efficiency in the side heat exchanger to descend, thereby the running efficiency when adding heat run can not reduced.
But, if become the state that does not use intermediate heat exchanger when adding heat run, so, intermediate heat exchanger will only arrange in the mode of cooling off the heat exchanger that uses when turning round according to conduct, therefore, intermediate heat exchanger just becomes obsolete instrument when adding heat run.
Therefore, in this refrigerating plant, when switching mechanism switches to the cooling operating condition, make intermediate heat exchanger can be used as cooler, when switching mechanism switches to the heating operating condition, can be as the evaporimeter of the cold-producing medium after the heat radiation in utilizing the side heat exchanger.Therefore, in this refrigerating plant, when the cooling running, can reduce from the temperature of the cold-producing medium of compressing mechanism discharge, when adding heat run, can improve the evaporability of cold-producing medium, can prevent from middle heat exchanger to external cooling simultaneously.
Like this, in this refrigerating plant, when the cooling running, have as the radiation loss in the heat source side heat exchanger of the radiator function of cold-producing medium and reduce, running efficiency in the time of can improving the cooling running when adding heat run, effectively utilizes intermediate heat exchanger, and suppress to utilize the decline of the heating efficiency in the side heat exchanger, thereby the running efficiency in the time of can preventing from adding heat run reduces.
Invent the refrigerating plant that relates to for the 2nd, in the refrigerating plant that the 1st invention relates to, intermediate heat exchanger is arranged on to suck from the cold-producing medium that prime side pressure contracting parts are discharged in the intermediate refrigerant pipe the rear-stage side compression member, the intermediate refrigerant pipe is connected with the intermediate heat exchanger bypass pipe that makes the intermediate heat exchanger bypass, and it also comprises: the suction recurrent canal that is used for connecting suction one side of an end of intermediate heat exchanger and compressing mechanism; Be used for connecting the intermediate heat exchanger recurrent canal that utilizes between side heat exchanger and the heat source side heat exchanger with the other end of intermediate heat exchanger.
In this refrigerating plant, when the cooling running, utilize intermediate heat exchanger can cool stream through the middle compression refrigerant of intermediate refrigerant pipe, when adding heat run, utilize the intermediate heat exchanger bypass pipe to make the intermediate heat exchanger bypass, make the middle compression refrigerant bypass of the intermediate refrigerant pipe of flowing through, and utilize and suck recurrent canal and intermediate heat exchanger recurrent canal, the part of the cold-producing medium that will be cooled in utilizing the side heat exchanger imports and then makes its evaporation in the intermediate heat exchanger, returns suction one side of compressing mechanism.
Invent the refrigerating plant that relates to for the 3rd, in the refrigerating plant that the 2nd invention relates to, switch to the running of cooling operating condition when beginning at switching mechanism, make the cold-producing medium of discharging from described preceding-stage side compression member suck described rear-stage side compression member by described intermediate heat exchanger bypass pipe, and connect suction one side of intermediate heat exchanger and compressing mechanism by described suction recurrent canal.
In this refrigerating plant, switch to the running of cooling operating condition when beginning at switching mechanism, make the cold-producing medium of discharging from prime side pressure contracting parts suck the rear-stage side compression member by the intermediate heat exchanger bypass pipe, and suction one side that connects intermediate heat exchanger and compressing mechanism by sucking recurrent canal, therefore, switching mechanism switch to the cooling operating condition running begin before, even liquid refrigerant accumulates in the intermediate heat exchanger, also this liquid refrigerant can be expelled to outside the intermediate heat exchanger.Like this, switch to the running of cooling operating condition when beginning at switching mechanism, just can avoid occuring liquid refrigerant and accumulate in the interior state of intermediate heat exchanger, can not occur because liquid refrigerant accumulates in liquid compression in the rear-stage side compression member that causes in the intermediate heat exchanger, can will suck the rear-stage side compression member from the cold-producing medium that prime side pressure contracting parts are discharged by intermediate heat exchanger.
Refrigerating plant for the 4th invention relates in the refrigerating plant that the 2nd or the 3rd invention relates to, is provided with flow control valve in the intermediate heat exchanger recurrent canal.
In this refrigerating plant, can prevent that when the cooling running cold-producing medium from flowing in the intermediate heat exchanger recurrent canal, and when adding heat run, the distribution of the flow of the cold-producing medium of the flow of the cold-producing medium of the heat source side heat exchanger of can flowing through effectively and the intermediate heat exchanger of flowing through.
Refrigerating plant for the 5th invention design, in the 1st～the 4th invention in any one related refrigerating plant, at the heat source side heat exchanger with utilize between the side heat exchanger, make the heat source side heat exchanger and utilize the expansion gear of the cold-producing medium constant entropy expansion between the side heat exchanger to be connected by rectification circuit of flowing through, utilize side heat exchanger and cold-producing medium from utilizing the side heat exchanger to flow in the situation of heat source side heat exchanger in the situation that cold-producing medium flows to from the heat source side heat exchanger, thereby also it is carried out rectification cold-producing medium is flowed into from the entrance of expansion gear.
In this refrigerating plant, because in when running cooling and during any one running when adding heat run, utilize can both improve results coefficient and carry out energy and reclaim of expansion gear, therefore, in the time of can further improving the cooling running and the running efficiency when adding heat run.
Invent the aircondition that relates to for the 6th, in the refrigerating plant of the 5th invention, the gas-liquid separator that connects the gas-liquid separation of carrying out cold-producing medium in the outlet of expansion gear, connection is used for making gas refrigerant separated in gas-liquid separator to return the rear-stage side playpipe of rear-stage side compression member in gas-liquid separator.
In this refrigerating plant, because returning middle pressure of rear-stage side compression member, sprays by the cold-producing medium of pressing in the middle of can making, therefore, can further improve running efficiency.
Description of drawings
Fig. 1 is the structure sketch plan as the aircondition of an embodiment of the refrigerating plant that the present invention relates to.
The schematic diagram of the mobility status of the cold-producing medium when Fig. 2 is cooling operation in the aircondition.
The pressure of the freeze cycle when Fig. 3 is cooling operation-enthalpy line chart.
The temperature of the freeze cycle when Fig. 4 is cooling operation-entropy line chart.
The schematic diagram of the mobility status of the cold-producing medium when Fig. 5 is the heating running in the aircondition.
The pressure of the freeze cycle when Fig. 6 is the heating running-enthalpy line chart.
The temperature of the freeze cycle when Fig. 7 is the heating running-entropy line chart.
Fig. 8 is the flow chart that refrigeration begins to control.
Fig. 9 is the schematic diagram of the expression refrigeration mobility status of the cold-producing medium in the aircondition when beginning to control.
Figure 10 is the structure sketch plan of the aircondition in the variation 1.
Figure 11 is the outward appearance oblique view (when pulling down fan guard) of heat source unit.
Figure 12 is the side view of the heat source unit when pulling down the right panel of heat source unit.
Figure 13 represent than critical pressure low in the middle of the characteristic of pyroconductivity when pressing carbon dioxide to flow through in the heat transfer stream and the high-pressure carbon dioxide that the surpasses critical pressure pyroconductivity when flowing through in the heat transfer stream.
Figure 14 is the structure sketch plan of the aircondition in the variation 3.
The pressure of the freeze cycle when Figure 15 is aircondition cooling operation in the variation 3-enthalpy line chart.
The temperature of the freeze cycle when Figure 16 is aircondition cooling operation in the variation 3-entropy line chart.
Figure 17 is the pressure-enthalpy line chart of the freeze cycle in aircondition heating when running in the variation 3.
Figure 18 is the temperature-entropy line chart of the freeze cycle in aircondition heating when running in the variation 3.
Figure 19 is the structure sketch plan of the aircondition in the variation 4.
Figure 20 is the pressure-enthalpy line chart of the freeze cycle in aircondition heating when running in the variation 4.
Figure 21 is the temperature-entropy line chart of the freeze cycle in aircondition heating when running in the variation 4.
Figure 22 is the structure sketch plan of the aircondition in the variation 5.
The pressure of the freeze cycle when Figure 23 is aircondition cooling operation in the variation 5-enthalpy line chart.
The temperature of the freeze cycle when Figure 24 is aircondition cooling operation in the variation 5-entropy line chart.
Figure 25 is the structure sketch plan of the aircondition in the variation 6.
Figure 26 is the structure sketch plan of the aircondition in the variation 7.
Figure 27 is the structure sketch plan of the aircondition in the variation 8.
Figure 28 is the structure sketch plan of the aircondition in the variation 9.
Figure 29 is the structure sketch plan of the aircondition in the variation 10.
Figure 30 is the structure sketch plan of the aircondition in the variation 11.
Figure 31 is the structure sketch plan of the aircondition in the variation 11.
Figure 32 is the structure sketch plan of the aircondition in the variation 12.
Figure 33 is the structure sketch plan of the aircondition in the variation 13.
Symbol description
1: aircondition (refrigerating plant)
2,102,202,302: compressing mechanism
3: switching mechanism
4: the heat source side heat exchanger
6: utilize the side heat exchanger
7,307: intermediate heat exchanger
8,308: the intermediate refrigerant pipe
9,309: the intermediate heat exchanger bypass pipe
92, sucked recurrent canal in 392: the 2
94,394: the intermediate heat exchanger recurrent canal
94b, 394b: intermediate heat exchanger returns valve (flow control valve)
97: expansion gear
17: commutating circuit (bridge circuit)
18: reservoir (memory) (gas-liquid separator)
18c: the 2nd rear-stage side playpipe
The specific embodiment
Below, with reference to the accompanying drawings, the embodiment of the refrigerating plant that the present invention relates to is described.
(1) structure of aircondition
Fig. 1 is the structure sketch plan as the aircondition 1 of an embodiment of refrigerating plant of the present invention.Aircondition 1 has the refrigerant line 10 that can switch cooling operation and heating running, and it uses at the cold-producing medium of supercritical region work (being carbon dioxide herein) and carries out two-stage compression formula freeze cycle.
The refrigerant line 10 of aircondition 1 mainly comprises: compressing mechanism 2; Switching mechanism 3; Heat source side heat exchanger 4; Bridge circuit 17; Reservoir 18; The 1st expansion mechanism 5a; The 2nd expansion mechanism 5b; Utilize side heat exchanger 6; And intermediate heat exchanger 7.
In the present embodiment, compressing mechanism 2 is by using two compression member that the compressor 21 that cold-producing medium carries out two-stage compression is consisted of.Compressor 21 adopts a kind of closed structure of taking in drive motor for compressor 21b, driving shaft 21c and compression member 2c, 2d in casing 21a.Drive motor for compressor 21b and driving shaft 21c link.This driving shaft 21c and two compression member 2c, 2d link.That is, compressor 21 adopts a kind of so-called axle two-stage compression structure: two compression member 2c, 2d and a driving shaft 21c link, and two compression member 2c, 2d are all by compressor drive motors 21b rotary actuation.In the present embodiment, compression member 2c, 2d are rotary or vortex isometric(al) formula compression member.Compressor 21 sucks cold-producing medium from suction line 2a, utilize compression member 2c to compress the cold-producing medium that this is inhaled into, then discharge to intermediate refrigerant pipe 8, the cold-producing medium that is discharged to intermediate refrigerant pipe 8 is sucked among the compression member 2d continue compressed refrigerant, then discharge to discharge pipe 2b.Herein, intermediate refrigerant pipe 8 be will be connected from the prime with compression member 2b the compression member 2c freeze cycle of discharging middle compression refrigerant suction and compression member 2d that the rear class of compression member 2c is connected in refrigerant pipe.In addition, discharge pipe 2b will be sent to from the cold-producing medium of compressing mechanism 2 discharges the refrigerant pipe of switching mechanism 3, and oily separating mechanism 41 and one-way mechanism 42 are set in discharge pipe 2b.Oil separating mechanism 41 is used for the refrigerator oil of discharging from compressing mechanism 2 with cold-producing medium separated from cold-producing medium and then makes its suction of returning compressing mechanism 2 one side, and it mainly comprises: the oil eliminator 41a that will separate from cold-producing medium with the refrigerator oil that cold-producing medium is discharged from compressing mechanism 2; Be connected with oil eliminator 41a and make refrigerator oil separated from cold-producing medium return the oily recurrent canal 41b of the suction line 2a of compressing mechanism 2.The mechanism of decompressor 41c that refrigerator oil to the oily recurrent canal 41b that flows through reduces pressure is set in oily recurrent canal 41b.In the present embodiment, mechanism of decompressor 41c uses capillary.One-way mechanism 42 is used for allowing that cold-producing medium is from discharge one effluent of compressing mechanism 2 to the heat source side heat exchanger 4 as radiator, and being used for block refrigerant flows to discharge one side of compressing mechanism 2 from the heat source side heat exchanger 4 as radiator, use in the present embodiment check valve.
In the present embodiment, compressing mechanism 2 has two compression member 2c, 2d, compresses successively the cold-producing medium that the preceding-stage side compression member from these compression member 2c, 2d is discharged with the rear-stage side compression member.
Switching mechanism 3 is used for switching the refrigerant flow direction in the refrigerant line 10, in order to make the radiator of the cold-producing medium that heat source side heat exchanger 4 can compress as compressed mechanism 2 when the cooling operation, and make the evaporimeter that utilizes side heat exchanger 6 can be used as the cold-producing medium that in heat source side heat exchanger 4, is cooled, can connect discharge one side of compressing mechanism 2 and an end of heat source side heat exchanger 4, suction one side that connects simultaneously compressor 21 with utilize side heat exchanger 6 (with reference to the solid line of the switching mechanism 3 of Fig. 1, below, the state of this switching mechanism 3 is " cooling operation state "), in order when heating turns round, to make the radiator that utilizes the cold-producing medium that side heat exchanger 6 can compress as compressed mechanism 2, and make heat source side heat exchanger 4 can be used as the evaporimeter of the cold-producing medium that in utilizing side heat exchanger 6, is cooled, can connect discharge one side of compressing mechanism 2 and utilize side heat exchanger 6, connect simultaneously suction one side of compressing mechanism 2 and an end of heat source side heat exchanger 4 (with reference to the dotted line of the switching mechanism 3 of Fig. 1, below, the state of this switching mechanism 3 is " heating operating condition ").In the present embodiment, switching mechanism 3 is and suction one side of compressing mechanism 2, discharge one side, the heat source side heat exchanger 4 of compressing mechanism 2 and the four phase transfer valves that utilize side heat exchanger 6 to be connected.In addition, switching mechanism 3 is not limited to four phase transfer valves, for example also can be by a plurality of magnetic valves of combination, and make it have function with above-mentioned same switching refrigerant flow direction.
So, if only be conceived to consist of compressing mechanism 2, the heat source side heat exchanger 4 of refrigerant line 10 and utilize side heat exchanger 6, so, switching mechanism 3 can switch following two states: make cold-producing medium successively at compressing mechanism 2, have heat source side heat exchanger 4 as the radiator function of cold-producing medium, have the cooling operation state that utilizes circulation in the side heat exchanger 6 as the evaporator function of cold-producing medium; And make cold-producing medium successively compressing mechanism 2, have as the radiator function of cold-producing medium utilize side heat exchanger 6, have as the evaporator function heat source side heat exchanger 4 of cold-producing medium in the heating operating condition of circulation.
Heat source side heat exchanger 4 is to have as the radiator of cold-producing medium or the heat exchanger of evaporator function.One end of heat source side heat exchanger 4 is connected with switching mechanism 3, and the other end is connected with the 1st expansion mechanism 5a by bridge circuit 17.In addition, expression among the figure herein, still, thermotropism source heat exchanger 4 is supplied with as carrying out the water and air of the cooling source of heat exchange with the cold-producing medium of the heat source side heat exchanger 4 of flowing through.
Bridge circuit 17 is arranged on heat source side heat exchanger 4 and utilizes between the side heat exchanger 6, and the reservoir inlet tube 18a that is connected with entrance with reservoir 18 and the reservoir outlet 18b that is connected with the outlet of reservoir 18 connect.In the present embodiment, bridge circuit 17 has 4 check valve 17a, 17b, 17c and 17d.Inlet one-way valve 17a only allows that cold-producing medium is from the flow through check valve of reservoir inlet tube 18a of heat source side heat exchanger 4.Inlet one-way valve 17b only allows that cold-producing medium is from utilizing the flow through check valve of reservoir inlet tube 18a of side heat exchanger 6.That is, inlet one-way valve 17a, 17b have and make cold-producing medium from heat source side heat exchanger 4 and utilize the function of the reservoir inlet tube 18a that flows through the side heat exchanger 6.Outlet check valve 17c only allows that cold-producing medium is flowed through from reservoir outlet 18b to utilize the check valve of side heat exchanger 6.Outlet check valve 17d only allows that cold-producing medium is from the flow through check valve of heat source side heat exchanger 4 of reservoir outlet 18b.That is, outlet check valve 17c, 17d have and make cold-producing medium from flow through heat source side heat exchanger 4 and utilize another function the side heat exchanger 6 of reservoir outlet 18b.
The 1st expansion mechanism 5a is provided in a side of the mechanism that being used among the reservoir inlet tube 18a reduced pressure to cold-producing medium, has used in the present embodiment electric expansion valve.In addition, in the present embodiment, when cooling operation, the high-pressure refrigerant that will be cooled in heat source side heat exchanger 4 is sent to by reservoir 18 and utilizes before the side heat exchanger 6, the 1st expansion mechanism 5a is decompressed near the saturation pressure of cold-producing medium to it, when heating turned round, the high-pressure refrigerant that will be cooled in utilizing side heat exchanger 6 was sent to by reservoir 18 before the heat source side heat exchanger 4, and the 1st expansion mechanism 5a is decompressed near the saturation pressure of cold-producing medium it.
The 2nd expansion mechanism 5b is provided in a side of the mechanism that being used among the reservoir outlet 18b reduced pressure to cold-producing medium, has used in the present embodiment electric expansion valve.In addition, in the present embodiment, when cooling operation, will be sent to by reservoir 18 by the post-decompression cold-producing medium of the 1st expansion mechanism 5a utilize side heat exchanger 6 before, the 2nd expansion mechanism 5b continues it is reduced pressure, until become the low pressure in the freeze cycle, when heating turns round, before will being sent to heat source side heat exchanger 4 by reservoir 18 by the post-decompression cold-producing medium of the 1st expansion mechanism 5a, the 2nd expansion mechanism 5b continues it is reduced pressure, until become the low pressure in the freeze cycle.
Utilizing side heat exchanger 6 is to have as the evaporimeter of cold-producing medium or the heat exchanger of radiator function.Utilize an end of side heat exchanger 6 to be connected with the 1st expansion mechanism 5a by bridge circuit, the other end is connected with switching mechanism 3.In addition, expression among the figure herein is to utilizing side heat exchanger 6 to supply with as carrying out the water and air of the heating source of heat exchange with the cold-producing medium that utilizes side heat exchanger 6 of flowing through.
So, in the present embodiment, utilize bridge circuit 17, reservoir 18, reservoir inlet tube 18a and reservoir outlet 18b, when switching mechanism 3 becomes cooling during operating condition, the 2nd expansion mechanism 5b of the 1st expansion mechanism 5a of the high-pressure refrigerant that just can will be cooled in heat source side heat exchanger 4 by inlet one-way valve 17a, the reservoir inlet tube 18a of bridge circuit 17, reservoir 18, reservoir outlet 18b and the outlet check valve 17c of bridge circuit 17 are sent to and utilize side heat exchanger 6.In addition, when switching mechanism 3 became the heating operating condition, the high-pressure refrigerant that just can will be cooled in utilizing side heat exchanger 6 was sent to heat source side heat exchanger 4 by the 1st expansion mechanism 5a, reservoir 18, the 2nd expansion mechanism 5b of reservoir outlet 18b and the outlet check valve 17d of bridge circuit 17 of inlet one-way valve 17b, the reservoir inlet tube 18a of bridge circuit 17.
In addition, intermediate refrigerant pipe 8 is connected with intermediate heat exchanger bypass pipe 9, thus bypass intermediate heat exchanger 7.This intermediate heat exchanger bypass pipe 9 is flow through refrigerant pipes of flow of cold-producing medium of intermediate heat exchanger 7 of restriction.In intermediate heat exchanger bypass pipe 9, be provided with intermediate heat exchanger bypass shut off valve 11.In the present embodiment, intermediate heat exchanger bypass cock valve 11 is magnetic valves.In the present embodiment, begin to control so temporary transient running except carrying out refrigeration described later, this intermediate heat exchanger bypass cock valve 11 is cut out by control when switching mechanism 3 switches to the cooling operating condition basically, is opened by control when switching mechanism 3 switches to the heating operating condition.That is, intermediate heat exchanger bypass cock valve 11 is cut out by control when carrying out cooling operation, is opened by control when carrying out the heating running.
In addition, in intermediate refrigerant pipe 8, from the connecting portion of the preceding-stage side compression member 2c side of intermediate heat exchanger bypass pipe 9 to the part of the preceding-stage side compression member 2c side of intermediate heat exchanger 7 intermediate heat exchanger switch valve 12 being set.This intermediate heat exchanger switch valve 12 is used for limiting the flow of cold-producing medium of intermediate heat exchanger 7 of flowing through.In the present embodiment, intermediate heat exchanger switch valve 12 is magnetic valves.In the present embodiment, begin to control so temporary transient running except carrying out refrigeration described later, this intermediate heat exchanger switch valve 12 is opened by control when switching mechanism 3 switches to the cooling operating condition basically, is closed by control when switching mechanism 3 switches to the heating operating condition.That is, intermediate heat exchanger switch valve 12 is opened by control when carrying out cooling operation, is closed by control when carrying out the heating running.
In addition, in intermediate refrigerant pipe 8, be provided with one-way mechanism 15, be used for allowing suction one side of cold-producing medium from discharge one effluent of prime side pressure contracting parts 2c to rear class side pressure contracting parts 2d, and be used for discharge one side of block refrigerant from suction one effluent of rear-stage side compression member 2d to prime side pressure contracting parts 2c.In the present embodiment, one-way mechanism 15 is check valves.In addition, in the present embodiment, one-way mechanism 15 be arranged on from the rear-stage side compression member 2d side of the intermediate heat exchanger 7 of middle refrigerant pipe 8 to the part of the connecting portion of the rear-stage side compression member 2d side of intermediate heat exchanger bypass pipe 9.
One end of intermediate heat exchanger 7 (herein being preceding-stage side compression member 2c side) and the 2nd sucks recurrent canal 92 and is connected, and the other end of intermediate heat exchanger 7 (herein being rear-stage side compression member 2d side) is connected with intermediate heat exchanger recurrent canal 94.The 2nd when to suck recurrent canal 92 are states make the cold-producing medium suction rear-stage side compression member 2d that discharges from prime side pressure contracting parts 2c by intermediate heat exchanger bypass pipe 9, are used for connecting the refrigerant pipe of suction one side (being suction line 2a) of an end and the compressing mechanism 2 of intermediate heat exchanger 7 herein.In addition, this intermediate heat exchanger recurrent canal 94 is when the state that makes by intermediate heat exchanger bypass pipe 9 from the cold-producing medium suction rear-stage side compression member 2d of prime side pressure contracting parts 2c discharge, and switch to heating during operating condition at switching mechanism 3, be used for connecting the refrigerant pipe that utilizes the other end of (being that the cold-producing medium decompression is become between the 2nd expansion mechanism 5b and the heat source side heat exchanger 4 as evaporimeter of the low pressure in the freeze cycle) and intermediate heat exchanger 7 between side heat exchanger 6 and the heat source side heat exchanger 4 herein.In the present embodiment, the 2nd end that sucks recurrent canal 92 is connected with part from the connecting portion of the preceding-stage side compression member 2c side of the intermediate heat exchanger bypass pipe 9 of middle refrigerant pipe 8 to the preceding-stage side compression member 2c side of intermediate heat exchanger 7, and the other end is connected with suction one side (being suction line 2a) of compressing mechanism 2 herein.In addition, an end of intermediate heat exchanger recurrent canal 94 is connected to the part of heat source side heat exchanger 4 with the 2nd expansion mechanism 5b, and the other end is connected with part from the preceding-stage side compression member 2c side of the intermediate heat exchanger 7 of middle refrigerant pipe 8 to one-way mechanism 15.In the 2nd suction recurrent canal 92, be provided with the 2nd and suck Returning switch valve 92a, in intermediate heat exchanger recurrent canal 94, be provided with intermediate heat exchanger Returning switch valve 94a.In the present embodiment, the 2nd suction Returning switch valve 92a and intermediate heat exchanger Returning switch valve 94a are magnetic valves.In the present embodiment, begin to control so temporary transient running except carrying out refrigeration described later, the 2nd sucks Returning switch valve 92a is closed by control when switching mechanism 3 switches to the cooling operating condition basically, is opened by control when switching mechanism 3 switches to the heating operating condition.In addition, comprise the situation that refrigeration described later begins to control so temporary transient running of carrying out, intermediate heat exchanger Returning switch valve 94a is closed by control when switching mechanism 3 switches to the cooling operating condition, is opened by control when switching mechanism 3 switches to the heating operating condition.
So, in the present embodiment, mainly utilize intermediate heat exchanger bypass pipe 9, the 2nd sucks recurrent canal 92 and intermediate heat exchanger recurrent canal 94, when cooling operation, utilize intermediate heat exchanger 7 with regard to the middle compression refrigerant of energy cool stream through intermediate refrigerant pipe 8, when heating turns round, utilize intermediate heat exchanger bypass pipe 9 to make intermediate heat exchanger 7 bypass, can bypass flow through the middle compression refrigerant of intermediate refrigerant pipe 8, and, utilize the 2nd to suck recurrent canal 92 and intermediate heat exchanger recurrent canal 94, the part of the cold-producing medium that will be cooled in utilizing side heat exchanger 6 imports and then makes its evaporation in the intermediate heat exchanger 7, and returns suction one side of compressing mechanism 2.
In addition, not expression among the figure herein, aircondition 1 have to control the compressing mechanism 2, switching mechanism 3, expansion mechanism 5a, 5b, intermediate heat exchanger bypass cock valve 11, the intermediate heat exchanger switch valve 12, the 1st that consist of aircondition 1 and suck the control part that Returning switch valve 18g, the 2nd sucks the operation of the various pieces such as Returning switch valve 92a and intermediate heat exchanger Returning switch valve 94a.
(2) operation of aircondition
Below, use Fig. 1～Fig. 9, the operation of the aircondition 1 of present embodiment is described.Herein, the schematic diagram of the mobility status of the cold-producing medium when Fig. 2 is cooling operation in the aircondition 1, the pressure of the freeze cycle when Fig. 3 is cooling operation-enthalpy line chart, the temperature of the freeze cycle when Fig. 4 is cooling operation-entropy line chart, the schematic diagram of the mobility status of the cold-producing medium when Fig. 5 is the heating running in the aircondition 1, the pressure of the freeze cycle when Fig. 6 is the heating running-enthalpy line chart, the temperature of the freeze cycle when Fig. 7 is the heating running-entropy line chart, Fig. 8 is the refrigeration flow chart that begins to control, and Fig. 9 is the schematic diagram of refrigeration mobility status of the cold-producing medium in the aircondition 1 when beginning to control.In addition, the running in the running of following cooling operation and heating is controlled and is freezed to begin to control by above-mentioned control part (not shown) and undertaken.In addition, in the following description, high pressure in " high pressure " expression freeze cycle (namely, some D among Fig. 3,4, the pressure of D ', E and the some D among Fig. 6,7, the pressure of D ', F), low pressure in " low pressure " expression freeze cycle (namely, the pressure of some A, F among Fig. 3,4 and the some A among Fig. 6,7, the pressure of E, V), press (that is, the pressure of some B1, the C1 among Fig. 3,4 and the some B1 among Fig. 6,7, the pressure of C1, C1 ') in the middle of in " intermediate pressure " expression freeze cycle.
(cooling operation)
When cooling operation, switching mechanism 3 is switched to the cooling operating condition shown in the solid line of Fig. 1 and Fig. 2.The aperture of the 1st expansion mechanism 5a and the 2nd expansion mechanism 5b is conditioned.Because switching mechanism 3 becomes the cooling operating condition, therefore, the intermediate heat exchanger switch valve 12 of intermediate refrigerant pipe 8 is opened, the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9 is closed, so, intermediate heat exchanger 7 just becomes can be as the state of cooler, and, the 2nd the 2nd suction Returning switch valve 92a that sucks recurrent canal 92 is closed, so, suction one side of intermediate heat exchanger 7 and compressing mechanism 2 is in the state that is not connected (still, except when refrigeration described later begins to control), perhaps, the intermediate heat exchanger Returning switch valve 94a of intermediate heat exchanger recurrent canal 94 is closed, so, utilize between side heat exchanger 6 and the heat source side heat exchanger 4 to be in the state that is not connected with intermediate heat exchanger 7.
Under the state of this refrigerant line 10, the cold-producing medium of low pressure (with reference to the some A among Fig. 1～Fig. 4) is inhaled into the compressing mechanism 2 from suction line 2a, at first, after compressed parts 2c is compressed to intermediate pressure, discharge (with reference to the some B among Fig. 1～Fig. 4) to intermediate refrigerant pipe 8.The middle compression refrigerant of discharging from this preceding-stage side compression member 2c carries out heat exchange be cooled thereby (with reference to the some C1 among Fig. 1～Fig. 4) with water and air as cooling source in intermediate heat exchanger 7.Then, the cold-producing medium that is cooled in this intermediate heat exchanger 7 is inhaled among the compression member 2d that is connected with the rear class of compression member 2c and is further compressed, and discharges from compressing mechanism 2 to discharge pipe 2b (with reference to the some D Fig. 1～Fig. 4).The high-pressure refrigerant of herein, discharging from compressing mechanism 2 is compressed into pressure above critical pressure (that is, the critical pressure Pcp among the critical point CP shown in Figure 3) according to the two-stage compression operation of compression member 2c, 2d.The high-pressure refrigerant of discharging from this compressing mechanism 2 flows into the oil eliminator 41a that consists of oily separating mechanism 41, and refrigerator oil wherein is separated.In addition, the refrigerator oil that is separated from high-pressure refrigerant in oil eliminator 41a flows into the oily recurrent canal 41b that consists of oily separating mechanism 41, be arranged on the suction line 2a that returns compressing mechanism 2 after the mechanism of decompressor 41c decompression among the oily recurrent canal 41b, again be inhaled in the compressing mechanism 2.Then, in oily separating mechanism 41, the high-pressure refrigerant after refrigerator oil wherein is separated is sent to the heat source side heat exchanger 4 that can be used as the radiator of cold-producing medium by one-way mechanism 42 and switching mechanism 3.The high-pressure refrigerant that is sent to heat source side heat exchanger 4 carries out heat exchange be cooled thereby (with reference to the some E among Fig. 2～Fig. 4) with water and air as cooling source in heat source side heat exchanger 4.The high-pressure refrigerant that is cooled in heat source side heat exchanger 4 flows into reservoir inlet tube 18a by the inlet one-way valve 17a of bridge circuit 17, be decompressed near the saturation pressure by the 1st expansion mechanism 5a, then be temporarily stored in reservoir 18 (with reference to the some I among Fig. 1 and Fig. 2).Then, the cold-producing medium that is stored in the reservoir 18 is sent to reservoir outlet 18b, become the cold-producing medium of the gas-liquid two-phase state of low pressure after the 2nd expansion mechanism 5b decompression, by the outlet check valve 17c of bridge circuit 17, be sent to can be as the evaporimeter of cold-producing medium utilize side heat exchanger 6 (with reference to the some F among Fig. 1～Fig. 4).Thereby be sent to the low pressure of utilizing side heat exchanger 6 the gas-liquid two-phase state cold-producing medium with carry out heat exchange as the water and air of heating source and be heated then evaporation (with reference to the some A among Fig. 1～Fig. 4).Utilize at this that heated low pressure refrigerant is inhaled in the compressing mechanism 2 again via switching mechanism 3 in side heat exchanger 6.Adopt above-mentioned this mode to carry out cooling operation.
So, in the aircondition 1 of present embodiment, in the intermediate refrigerant pipe 8 among the cold-producing medium suction compression member 2d that is used for to discharge from compression member 2c intermediate heat exchanger 7 is set, and in cooling operation, open intermediate heat exchanger switch valve 12, perhaps close the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9, like this.Intermediate heat exchanger 7 just becomes the state that has as the cooler function, therefore, with the situation that intermediate heat exchanger 7 is not set (in the case, in Fig. 3, Fig. 4, carry out freeze cycle according to the order of an an an an A → B1 → D ' → E → F) compare, be inhaled into the drop in temperature (with reference to some B1, the C1 among Fig. 4) of the cold-producing medium among the rear-stage side compression member 2d of compression member 2c, the temperature of the cold-producing medium of discharging from compression member 2d also can descend (with reference to some D, the D ' Fig. 4).Therefore, in this aircondition 1, in the heat source side heat exchanger 4 that has as the radiator function of high-pressure refrigerant, compare with the situation that intermediate heat exchanger 7 is not set, not only can dwindle the temperature difference as water and air and the cold-producing medium of cooling source, and can reduce the radiation loss of the size that the some B1, D ', D, the C1 that are equivalent to link among Fig. 4 consist of, therefore can improve running efficiency.
(heating running)
When heating running, switching mechanism 3 becomes the heating operating condition shown in the dotted line of Fig. 1 and Fig. 5.The aperture of the 1st expansion mechanism 5a and the 2nd expansion mechanism 5b is conditioned.Because switching mechanism 3 becomes the heating operating condition, therefore, the intermediate heat exchanger switch valve 12 of intermediate refrigerant pipe 8 is closed, and the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9 is opened, so intermediate heat exchanger 7 just becomes can not be as the state of cooler.And, because switching mechanism 3 becomes the heating operating condition, therefore, the 2nd the 2nd suction Returning switch valve 92a that sucks recurrent canal 92 is opened, so suction one side of intermediate heat exchanger 7 and compressing mechanism 2 becomes the state that is connected, perhaps the intermediate heat exchanger Returning switch valve 94a of intermediate heat exchanger recurrent canal 94 is opened, so, utilize between side heat exchanger 6 and the heat source side heat exchanger 4 to become the state that is connected with intermediate heat exchanger 7.
Under the state of this refrigerant line 10, low pressure refrigerant (with reference to the some A among Fig. 1, Fig. 5～Fig. 7) is inhaled into the compressing mechanism 2 from suction line 2a, at first, after compressed parts 2c is compressed to intermediate pressure, be discharged to intermediate refrigerant pipe 8 (with reference to the some B1 among Fig. 1, Fig. 5～Fig. 7).Different during from cooling operation, the middle compression refrigerant of discharging from this preceding-stage side compression member 2c is not by intermediate heat exchanger 7 (namely, be not cooled), but by intermediate heat exchanger bypass pipe 9 (with reference to the some C1 among Fig. 1, Fig. 5～Fig. 7), be inhaled among the compression member 2d that is connected with the rear class of compression member 2c and then continued compression, discharge from compressing mechanism 2 to discharge pipe 2b (with reference to the some D Fig. 1, Fig. 5～Fig. 7).Herein, same during with cooling operation, the high-pressure refrigerant of discharging from compressing mechanism 2 is compressed into pressure above critical pressure (that is, the critical pressure Pcp among the critical point CP shown in Figure 6) according to the two-stage compression operation of compression member 2c, 2d.The high-pressure refrigerant of discharging from this compressing mechanism 2 flows into the oil eliminator 41a that consists of oily separating mechanism 41, and refrigerator oil wherein is separated.In addition, the refrigerator oil that is separated from high-pressure refrigerant in oil eliminator 41a flows into the oily recurrent canal 41b that consists of oily separating mechanism 41, be arranged on the suction line 2a that returns compressing mechanism 2 after the mechanism of decompressor 41c decompression among the oily recurrent canal 41b, again be inhaled in the compressing mechanism 2.Then, in oily separating mechanism 41, high-pressure refrigerant after being mixed in wherein refrigerator oil and being separated is by one-way mechanism 42 and switching mechanism 3, be sent to have as the radiator function of cold-producing medium utilize side heat exchanger 6, thereby carry out heat exchange be cooled (with reference to the some F among Fig. 1, Fig. 5～Fig. 7) with water and air as cooling source.The inlet one-way valve 17b of the high-pressure refrigerant that is cooled in utilizing side heat exchanger 6 by bridge circuit 17 flows into reservoir inlet tube 18a, is temporarily stored in reservoir 18 (with reference to the some I among Fig. 1 and Fig. 5) after being decompressed near the saturation pressure by the 1st expansion mechanism 5a.The cold-producing medium that is stored in the reservoir 18 is sent to reservoir outlet 18b, become the cold-producing medium of the gas-liquid two-phase state of low pressure after the 2nd expansion mechanism 5b decompression, outlet check valve 17d by bridge circuit 17 is sent to the heat source side heat exchanger 4 that has as the evaporator function of cold-producing medium, and by intermediate heat exchanger recurrent canal 94, also be sent to the intermediate heat exchanger 7 (with reference to the some E among Fig. 1, Fig. 5～Fig. 7) that has as the evaporator function of cold-producing medium.Thereby be sent to heat source side heat exchanger 4 low pressure the gas-liquid two-phase state cold-producing medium with carry out heat exchange as the water and air of heating source and be heated then evaporation (with reference to the some A among Fig. 1, Fig. 5～Fig. 7).Thereby the cold-producing medium of gas-liquid two-phase state that is sent to the low pressure of intermediate heat exchanger 7 also carries out heat exchange with water and air as heating source and is heated then evaporation (with reference to the some V among Fig. 1, Fig. 5～Fig. 7).The cold-producing medium of the low pressure that is heated in this heat source side heat exchanger 4 and evaporates is inhaled in the compressing mechanism 2 again via switching mechanism 3.In addition, in this intermediate heat exchanger 7, be heated and the cold-producing medium of the low pressure of evaporating sucks recurrent canal 92 by the 2nd, again be inhaled in the compressing mechanism 2.Adopt above-mentioned this mode to carry out the heating running.
So, in the aircondition 1 of present embodiment, become in the heating running of heating operating condition at switching mechanism 3, close intermediate heat exchanger switch valve 12, perhaps open intermediate heat exchanger bypass cock valve 11, like this, intermediate heat exchanger 7 just becomes the state that does not have as the cooler function, therefore, with the situation that only is provided with intermediate heat exchanger 7, and make equally the intermediate heat exchanger 7 can be as the situation of cooler (in these cases with above-mentioned cooling operation, at Fig. 6, carry out freeze cycle according to the order of an an an an an an A → B1 → C1 ' → D ' → F → E among Fig. 7) to compare, the drop in temperature of the cold-producing medium that is discharged from from compressing mechanism 2 is controlled (with reference to the some D among Fig. 7, D ').Therefore, in this aircondition 1, with the situation that only is provided with intermediate heat exchanger 7 and with above-mentioned cooling operation intermediate heat exchanger 7 can be compared as the situation of cooler, not only can suppress the heat radiation to the outside, suppress to be supplied to the drop in temperature that has as the cold-producing medium that utilizes side heat exchanger 6 of the radiator function of cold-producing medium, and can suppress to be equivalent to the decline of the enthalpy difference of some D and some F among Fig. 7 and some D ' and the heating efficiency of the difference of the enthalpy difference of some F, thereby can prevent the decline of running efficiency.
And, in the aircondition 1 of present embodiment, become in the heating running of heating operating condition at switching mechanism 3, be not use intermediate heat exchanger 7 to make it become the state that can not be used as cooler, but with heat source side heat exchanger 4 together, make intermediate heat exchanger 7 have the function that is used as the evaporimeter of the cold-producing medium after the heat radiation in utilizing side heat exchanger 7, and when turning round, heating also uses, by suppressing the heat radiation from middle heat exchanger 7 to the outside, the evaporability of cold-producing medium when improving simultaneously the heating running, be increased in the flow etc. of the cold-producing medium of refrigerant line 10 interior circulations, thereby suppress to utilize the heating efficiency in the side heat exchanger 4 to descend.Like this, in the aircondition 1 of present embodiment, when cooling operation, have as the radiation loss in the heat source side heat exchanger 4 of the radiator function of cold-producing medium and reduce, running efficiency in the time of can improving the heating running when heating turns round, can effectively utilize intermediate heat exchanger 7, and can suppress to utilize the heating efficiency in the side heat exchanger 4 to descend, the running efficiency when making the heating running can not reduce.
(refrigeration begins control)
In above-mentioned intermediate heat exchanger 7, when aircondition 1 stops etc. in the situation, liquid refrigerant might accumulate, if accumulate in the above-mentioned cooling operation of beginning under the state in the intermediate heat exchanger 7 at liquid refrigerant, so, the liquid refrigerant that accumulates in the intermediate heat exchanger 7 will be inhaled among the rear-stage side compression member 2d, therefore, in rear-stage side compression member 2d liquid compression occurs, the reliability of compressing mechanism 2 will be damaged.
Therefore, in the present embodiment, when beginning above-mentioned cooling operation, freeze and begin control, it is become by intermediate heat exchanger bypass pipe 9 state from the cold-producing medium suction rear-stage side compression member 2d that prime side pressure contracting parts 2c discharges, and, suck suction one side that recurrent canal 92 connects intermediate heat exchanger 7 and compressing mechanism 2 by the 2nd.
Below, use Fig. 8 and Fig. 9, the refrigeration of present embodiment is begun control describe.
At first, in step S1, if send the instruction that cooling operation begins, then enter the processing of the various valves of operation of step S2.
Secondly, in step S2, the on off state of switch valve 11,12,92a is switched to the cold-producing medium return state: will suck from the cold-producing medium that prime side pressure contracting parts 2c discharges the rear-stage side compression member 2d by intermediate heat exchanger bypass pipe 9, and suck the suction one side connection that recurrent canal 92 makes intermediate heat exchanger 7 be connected with compressing mechanism by the 2nd.Specifically, open intermediate heat exchanger bypass cock valve 11, close intermediate heat exchanger switch valve 12.So, by intermediate heat exchanger bypass pipe 9, will produce the cold-producing medium of discharging from prime side pressure contracting parts 2c not by intermediate heat exchanger 7 but be inhaled into cold-producing medium stream the rear-stage side compression member 2d.That is, intermediate heat exchanger 7 becomes can not be as the state of cooler, and becomes by intermediate heat exchanger bypass pipe 9 and be inhaled into state (with reference to Fig. 9) the rear-stage side compression member 2d from the cold-producing medium of prime side pressure contracting parts 2c discharge.In this state, open the 2nd and suck Returning switch valve 92a.So, suction one side that intermediate heat exchanger 7 is connected with compressing mechanism is sucked recurrent canal 92 by the 2nd and connects, intermediate heat exchanger 7 (more specifically, to comprise the intermediate heat exchanger switch valve 12 of intermediate heat exchanger 7 and the part between the one-way mechanism 15) in the low pressure of pressure drop to the freeze cycle of cold-producing medium near, become the state (with reference to Fig. 9) that the cold-producing mediums in the intermediate heat exchanger 7 can be expelled to suction one side of compressing mechanism 2.
Then, in step S3, with on off state (that is, cold-producing medium return state) the maintenance stipulated time of the switch valve 11,12 among the step S2,92a.Like this, even when aircondition 1 stops etc. in the situation, liquid refrigerant accumulates in the intermediate heat exchanger 7, the liquid refrigerant that accumulates in the intermediate heat exchanger 7 also can reduction vaporization, can not be inhaled among the rear-stage side compression member 2d, but be discharged to intermediate heat exchanger 7 outer (more specifically, being suction one side of compressing mechanism 2), be inhaled in the compressing mechanism 2 (herein being preceding-stage side compression member 2c).Herein, the stipulated time is configured to and the liquid refrigerants that accumulate in the intermediate heat exchanger 7 can be expelled to intermediate heat exchanger 7 time outward.
Below, in step S4, the on off state of switch valve 11,12,92a is switched to the cold-producing medium non-return state: will suck from the cold-producing medium that prime side pressure contracting parts 2c discharges the rear-stage side compression member 2d by intermediate heat exchanger 7, and not suck the suction one side connection that recurrent canal 92 makes intermediate heat exchanger 7 be connected with compressing mechanism by the 2nd.That is, the valve 11,12 when switching to above-mentioned cooling operation, the on off state of 92a finish refrigeration and begin control.Specifically, close the 2nd and suck Returning switch valve 92a.So just become the state that intermediate heat exchanger 7 interior cold-producing mediums can not flow out suction one side of compressing mechanism 2.In this state, open intermediate heat exchanger switch valve 12, close intermediate heat exchanger bypass cock valve 11.So just becoming intermediate heat exchanger 7 can be as the state of cooler.
Like this, in this aircondition 1, when cooling operation begins, can not occur that liquid refrigerant accumulates in the intermediate heat exchanger 7 and the liquid compression among the rear-stage side compression member 2d that causes, can improve the reliability of compressing mechanism 2.
(3) variation 1
In the above-described embodiment, by changing the on off state of switch valve 11,12,92a, begin to switch between the control at cooling operation and refrigeration, that is, switch cold-producing medium non-return state and cold-producing medium return state, still, as shown in figure 10, also can replace switch valve 11,12,92a, setting can be switched the intermediate heat exchanger transfer valve 93 of cold-producing medium non-return state and cold-producing medium return state, forms refrigerant line 110.
Herein, intermediate heat exchanger transfer valve 93 is the valves that can switch cold-producing medium non-return state and cold-producing medium return state, in this variation, it is and the inlet side of the intermediate heat exchanger 7 of discharge one side of the preceding-stage side compression member 2c of intermediate refrigerant pipe 8, intermediate refrigerant pipe 8, the preceding-stage side compression member 2c side of intermediate heat exchanger bypass pipe 9, the four phase transfer valves that the 2nd intermediate heat exchanger 7 sides that suck recurrent canal 92 are connected.In addition, in intermediate heat exchanger bypass pipe 9, be provided with one-way mechanism 9a, be used for allowing suction one side of cold-producing medium from discharge one effluent of prime side pressure contracting parts 2c to rear class side pressure contracting parts 2d, and allow that cold-producing medium is from suction one effluent of rear-stage side compression member 2d to discharge one side of prime side pressure contracting parts 2c and suction one side of compressing mechanism 2.In this variation, one-way mechanism 9a is check valve.
In this variation, detailed explanation will be omitted, but, intermediate heat exchanger transfer valve 93 is switched to will be from the cold-producing medium suction rear-stage side compression member 2d that prime side pressure contracting parts 2c discharges by intermediate heat exchanger 7, and do not suck the cold-producing medium non-return state that suction one side that recurrent canal 92 makes intermediate heat exchanger 7 be connected with compressing mechanism connects (with reference to the solid line of the intermediate heat exchanger transfer valve 93 of Figure 10) by the 2nd, thereby can carry out the cooling operation same with above-mentioned embodiment, intermediate heat exchanger transfer valve 93 is switched to will be from the cold-producing medium suction rear-stage side compression member 2d that prime side pressure contracting parts 2c discharges by intermediate heat exchanger bypass pipe 9, and suck the cold-producing medium return state that suction one side that recurrent canal 92 makes intermediate heat exchanger 7 be connected with compressing mechanism connects (with reference to the dotted line of the intermediate heat exchanger transfer valve 93 of Figure 10) by the 2nd, thereby can carry out beginning control with same heating running and the refrigeration of above-mentioned embodiment.
In the structure of this variation, also can obtain the action effect same with above-mentioned embodiment.And, in this variation, by intermediate heat exchanger transfer valve 93, can switch cold-producing medium non-return state and cold-producing medium return state, therefore, switch the cold-producing medium non-return state and compare with the mode of the structure of cold-producing medium return state by the described a plurality of valves 11 of above-mentioned embodiment, 12,92a with employing, can reduce the quantity of valve.In addition, compare with the mode of using magnetic valve, compression losses also reduces, and therefore, the decline of pressing in the middle of in can the freezing-inhibiting circulation also can suppress the decline of running efficiency.
(variation 2)
In above-mentioned embodiment and variation thereof, adopt a kind of with intermediate heat exchanger 7 and heat source side heat exchanger 4 as with the heat exchanger of air as thermal source (being cooling source or heating source), then by the heat source side fan 40 (aftermentioned) that shares to two heat exchangers 4,7 structures of supplying with as the air of thermal source.
For example, adopt a kind of heat source unit 1a that mainly is provided with heat source side fan 40, heat source side heat exchanger 4 and intermediate heat exchanger 7 at aircondition 1; And mainly be provided with in the situation of the structure that the range site (not shown) that utilizes side heat exchanger 6 is connected, adopt Figure 11 and heat source unit 1a shown in Figure 12.Herein, Figure 11 is the outward appearance oblique view (pulling down the state of fan guard) of heat source unit 1a, and Figure 12 is the side view of heat source unit 1a when pulling down the right panel of heat source unit 1a.In addition, " left side " in the following description and " right side " take from front panel 24 unilateral observation heat source unit 1a the time as benchmark.
The heat source unit 1a that consists of the aircondition 1 of this variation is that it mainly comprises from the side air amount so-called upward type of blow out air upward then: casing 71, at parts such as the refrigerant line members such as the heat source side heat exchanger 4 of the internal configurations of casing 71 and intermediate heat exchanger 7 and heat source side fans 40.
In this variation, casing 71 is the casings that slightly are cuboid, and it mainly is made of the top board 72 that consists of casing 71, left panel 73, right panel 74, front panel 75, rear board 76 and the base plate 77 of outer peripheral face that consist of casing 71.Top board 72 mainly is the parts that consist of the end face of casing 71, and in this variation, it is to form in the substantial middle position to blow out the plate-shaped member that looking squarely of opening 71a slightly is rectangle.Top board 72 be provided with from above cover the fan guard 78 blow out opening 71a.Left panel 73 mainly is the parts that consist of the left side of casing 71, in this variation, and the plate-shaped member that the side-looking of extending downwards from the left hand edge of top board 72 slightly is rectangle.On left panel 73, form suction opening 73a in the roughly whole part except top.Right panel 74 mainly is the parts that consist of the right side of casing 71, in this variation, and the plate-shaped member that the side-looking of extending downwards from the right hand edge of top board 72 slightly is rectangle.On right panel 74, form suction opening 74a in the roughly whole part except top.Front panel 75 mainly is the parts that consist of the front of casing 71, and in this variation, it is made of the plate-shaped member that slightly is rectangle of seeing from the front that the leading edge from top board 72 configures downwards successively.Rear board 76 mainly is the parts that consist of the back of casing 71, and in this variation, it is made of the plate-shaped member that slightly is rectangle of seeing from the front that the back edge from top board 72 configures downwards successively.On the plate 76, form suction opening 76a in the roughly whole part except top in the back.Base plate 77 mainly is the parts that consist of the bottom surface of casing 71, and in this variation, it is to look squarely the plate-shaped member that slightly is rectangle.
In this variation, intermediate heat exchanger 7 be configured in heat source side heat exchanger 4 above state under form one with heat source side heat exchanger 4, and be configured on the base plate 77.More specifically, intermediate heat exchanger 7 is by sharing heat transfer fan and heat source side heat exchanger 4 formation one.In addition, heat source side heat exchanger 4 and intermediate heat exchanger 7 shape all-in-one-piece parts are looked squarely the heat-exchanger panels that slightly is the U word shape according to formation in this variation, with suction opening 73a, 74a, 76a in opposite directions mode and establish.In addition, heat source side fan 40 blows out opening 71a in opposite directions with top board 72, and is configured in the upside of heat source side heat exchanger 4 and intermediate heat exchanger 7 shape all-in-one-pieces parts (that is, heat-exchanger panels).In this variation, heat source side fan 40 is aerofoil fans, it passes through fan driving motor 40a and rotary actuation, so just can from suction opening 73a, 74a, 76a will the air intake casing 71 as thermal source in, after making it pass through heat source side heat exchanger 4 and intermediate heat exchanger 7, blow out (with reference to the arrow of expression air flow Figure 12) towards the top from blowing out opening 71a.That is, heat source side fan 40 thermotropism source heat exchangers 4 and intermediate heat exchanger 7 both supplies are as the air of thermal source.In addition, the shape of the face shaping of heat source unit 1a and heat source side heat exchanger 4 and intermediate heat exchanger 7 shape all-in-one-pieces parts (that is, heat-exchanger panels) is not limited to above-mentioned.Like this, intermediate heat exchanger 7 consists of and heat source side heat exchanger 4 shape all-in-one-piece heat-exchanger panels, and is configured in the top of this heat-exchanger panels.
Herein, intermediate heat exchanger 7 and heat source side heat exchanger 4 are formed one, reason at the top of both shape all-in-one-piece heat-exchanger panels configuration intermediate heat exchanger 7 is, be that the aircondition 1 of having considered this variation uses cold-producing medium (the being carbon dioxide) this point in supercritical region work herein, and heat source unit 1a adopt from the side air amount then towards the type this point of top blow out air.If explain this point, so, as follows.When cooling operation, sometimes carry out the freeze cycle of cooling operation etc.: than critical pressure Pcp (in carbon dioxide, being approximately 7.3MPa) low middle compression refrigerant flows through in the intermediate heat exchanger 7 as cooler, the high-pressure refrigerant that surpasses critical pressure Pcp is flowed through can be as in the heat source side heat exchanger 4 of the radiator of cold-producing medium (with reference to Fig. 3), in the case, as shown in figure 13, because of than the physical property of the cold-producing medium in the low pressure of critical pressure Pcp with surpass the difference of the physical property (particularly pyroconductivity and specific heat at constant pressure) of the cold-producing medium in the pressure of critical pressure Pcp, compare with the pyroconductivity of heat source side heat exchanger 4 in cold-producing medium as the radiator of cold-producing medium, be downward trend as the pyroconductivity of intermediate heat exchanger 7 in cold-producing medium of cooler.The numerical value (corresponding with the pyroconductivity of intermediate heat exchanger 7 in cold-producing medium as cooler) of the pyroconductivity in the time of herein, in the heat transfer stream of Figure 13 stream basal area of representing to make the carbon dioxide mass velocity according to the rules of 6.5MPa to flow through to have regulation; And the numerical value (corresponding with the pyroconductivity of heat source side heat exchanger 4 in cold-producing medium as radiator) of the pyroconductivity of the carbon dioxide of 10MPa under the condition of the heat transfer stream identical with the carbon dioxide of 6.5MPa and mass velocity, by this numerical value as can be known, have as the heat source side heat exchanger 4 of the radiator function of cold-producing medium and have temperature range (about 35～70 ℃) as the cold-producing medium in the intermediate heat exchanger 7 of the cooler function of cold-producing medium flowing through, the numerical value of the pyroconductivity of the carbon dioxide of the numeric ratio 10MPa of the pyroconductivity of the carbon dioxide of 6.5MPa is low.Therefore, at the heat source unit 1a of the aircondition 1 of this variation (namely, from the side air amount then towards the heat source unit of top blow out air), if under the state that is configured in below the heat source side heat exchanger 4, make intermediate heat exchanger 7 and heat source side heat exchanger 4 form one, so, just in bottom configuration and heat source side heat exchanger 4 shape all-in-one-piece intermediate heat exchangers 7 as the little heat source unit 1a of the flow velocity of the air of thermal source, be subject to causing because of the bottom that intermediate heat exchanger 7 is configured in heat source unit 1a the impact of intermediate heat exchanger 7 aerial pyroconductivities declines, and the pyroconductivity of intermediate heat exchanger 7 in cold-producing medium compared the double influence of the impact of step-down, the heat-conductive characteristic decline of intermediate heat exchanger 7 with the pyroconductivity of heat source side heat exchanger 4 in cold-producing medium.
In this heat source unit 1a, when heating turns round, use intermediate heat exchanger bypass pipe 9 to carry out bypass, in intermediate heat exchanger 7, be not cooled so that discharge the cold-producing medium that then is inhaled into the rear-stage side compression member 2d from prime side pressure contracting parts 2c, make it become the state that does not use intermediate heat exchanger 7, so, pyroconductivity when considering cooling operation, be configured in intermediate heat exchanger 7 as the position of the flow velocity maximum of the air of thermal source when heating turns round just without any renting, its maximum shortcoming can not effectively utilize intermediate heat exchanger 72 exactly.
But, in this variation, same with above-mentioned embodiment and variation thereof, when heating turns round, use intermediate heat exchanger bypass pipe 9 to carry out bypass, in intermediate heat exchanger 7, be not cooled so that discharge the cold-producing medium then be inhaled into the rear-stage side compression member 2d from prime side pressure contracting parts 2c, and make the intermediate heat exchanger 7 can be as the evaporimeter of cold-producing medium, the evaporability when so just helping to improve heating and turning round.
(5) variation 3
In above-mentioned embodiment and variation thereof, in the aircondition 1 that carries out two-stage compression formula freeze cycle that can consist of by switching mechanism 3 switching cooling operations and heating running, setting has as the intermediate heat exchanger 7 of discharging the cooler function that then is inhaled into the cold-producing medium the rear-stage side compression member 2d from prime side pressure contracting parts 2c, the intermediate heat exchanger bypass pipe 9 that is connected with intermediate refrigerant pipe 8 in the mode of bypass intermediate heat exchanger 7, be used for connecting an end of intermediate heat exchanger 7 and compressing mechanism 2 suction one side the 2nd suck recurrent canal 92, and be used for connecting the intermediate heat exchanger recurrent canal 94 that utilizes between side heat exchanger 6 and the heat source side heat exchanger 4 with the other end of intermediate heat exchanger 7, except this structure, also can carry out middle pressure of the 1st rear-stage side playpipe 19 and economizer heat exchanger 20 and spray.
For example, as shown in figure 14, in the refrigerant line 10 (with reference to Fig. 1) of the above-mentioned embodiment of the compressing mechanism 2 that adopts the two-stage compression formula, the 1st rear-stage side playpipe 19 and economizer heat exchanger 20 are set, thereby can form refrigerant line 210.
The 1st rear-stage side playpipe 19 has and will flow through heat source side heat exchanger 4 and utilize cold-producing medium shunting between the side heat exchanger 6 then to return the function of the rear-stage side compression member 2d of compressing mechanism 2.In this variation, then the 1st rear-stage side playpipe 19 makes its mode of returning suction one side of rear-stage side compression member 2d arrange according to the cold-producing medium shunting of the reservoir inlet tube 18a that will flow through.More specifically, the 1st rear-stage side playpipe 19 is according to from the position of upper reaches one side of the 1st expansion mechanism 5a of reservoir inlet tube 18a (namely, when switching mechanism 3 becomes the cooling operating condition, between heat source side heat exchanger 4 and the 1st expansion mechanism 5a) cold-producing medium is shunted, the mode of position of a dirty side of its intermediate heat exchanger that returns intermediate refrigerant pipe 87 is arranged.In addition, in the 1st rear-stage side playpipe 19, be provided with the 1st rear class injection valve 19a that can control its aperture.In this variation, the 1st rear class injection valve 19a is electric expansion valve.
Economizer heat exchanger 20 be flow through heat source side heat exchanger 4 and utilize cold-producing medium and the 1st rear-stage side playpipe 19 of flowing through between the side heat exchanger 6 cold-producing medium (more specifically, press in the middle of in the 1st rear class injection valve 19a, being depressurized near after cold-producing medium) the heat exchanger of heat exchange.In this variation, economizer heat exchanger 20 is according to the position of upper reaches one side of the 1st expansion mechanism 5a of the reservoir inlet tube 18a that flows through (namely, when switching mechanism 3 becomes the cooling operating condition, between heat source side heat exchanger 4 and the 1st expansion mechanism 5a) cold-producing medium carry out the mode of heat exchange with the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through and establish, and, have the stream that two cold-producing mediums flow in opposite directions.In this variation, economizer heat exchanger 20 is arranged on the 1st rear-stage side playpipe 19 from a dirty side of the position of reservoir inlet tube 18a branch.Therefore, the heat source side of flowing through heat exchanger 4 and utilize cold-producing medium between the side heat exchanger 6 in reservoir inlet tube 18a, in economizer heat exchanger 20 by heat exchange before by the 1st rear-stage side playpipe 19 branches, then in economizer heat exchanger 20, carry out heat exchange with the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through.
So, when switching mechanism 3 becomes the cooling operating condition, the 1st expansion mechanism 5a, reservoir 18, the 2nd expansion mechanism 5b of reservoir outlet 18b and the outlet check valve 17c of bridge circuit 17 of inlet one-way valve 17a by bridge circuit 17, economizer heat exchanger 20, reservoir inlet tube 18a, the high-pressure refrigerant that just can will be cooled in heat source side heat exchanger 4 is sent to and utilizes side heat exchanger 6.In addition, when switching mechanism 3 becomes the heating operating condition, the 1st expansion mechanism 5a, reservoir 18, the 2nd expansion mechanism 5b of reservoir outlet 18b and the outlet check valve 17d of bridge circuit 17 of inlet one-way valve 17b by bridge circuit 17, economizer heat exchanger 20, reservoir inlet tube 18a, the high-pressure refrigerant that just can will be cooled in utilizing side heat exchanger 6 is sent to heat source side heat exchanger 4.
In this variation, in intermediate refrigerant pipe 8 or compressing mechanism 2, be provided with the intermediate pressure sensor 54 of the refrigerant pressure that detects the intermediate refrigerant pipe 8 of flowing through.Detect the energy-saving appliance outlet temperature sensor 55 of the refrigerant temperature in the outlet of the 1st rear-stage side playpipe 19 sides of economizer heat exchanger 20 in the outlet setting of the 1st rear-stage side playpipe 19 sides of economizer heat exchanger 20.
Below, use Figure 14～Figure 18, the operation of the aircondition 1 of this variation is described.Herein, the pressure of the freeze cycle when Figure 15 is cooling operation-enthalpy line chart, the temperature of the freeze cycle when Figure 16 is cooling operation-entropy line chart, the temperature of the freeze cycle the when pressure of the freeze cycle when Figure 17 is the heating running-enthalpy line chart, Figure 18 are the heating running-entropy line chart.Herein, it is identical with above-mentioned embodiment that refrigeration begins control, and therefore, the description thereof will be omitted herein.In addition, the running control in following cooling operation and the heating running (comprising that also unaccounted refrigeration begins control herein) is what to be undertaken by the control part (not shown) in the above-mentioned embodiment.In the following description, " high pressure " refer in the freeze cycle high pressure (namely, the pressure of the pressure of some D among Figure 15,16, D ', E, H and the some D among Figure 17,18, D ', F, H), " low pressure " refer in the freeze cycle low pressure (namely, the pressure of some A, F among Figure 15,16 and the some A among Figure 17,18, the pressure of E, V), " the middle pressure " refers to middle press (that is, the pressure of the some B1 in Figure 15～18, C1, G, J, K) in the freeze cycle.
(cooling operation)
When cooling operation, switching mechanism 3 becomes the cooling operating condition shown in the solid line of Figure 14.The aperture of the 1st expansion mechanism 5a and the 2nd expansion mechanism 5b is conditioned.In addition, the aperture of the 1st rear class injection valve 19a also is conditioned.More specifically, the 1st rear class injection valve 19a is implemented the so-called degree of superheat control of regulation, thereby makes the degree of superheat of the cold-producing medium in the outlet of the 1st rear-stage side playpipe 19 1 sides of economizer heat exchanger 20 become desired value.In this variation, the degree of superheat of the cold-producing medium in the outlet of the 1st rear-stage side playpipe 19 1 sides of economizer heat exchanger 20 is converted into saturation temperature by pressing in the middle of intermediate pressure sensor 54 is detected, and deducts the saturation temperature value of this cold-producing medium and obtain from the refrigerant temperature that energy-saving appliance outlet temperature sensor 55 detects.In addition, in this variation, do not adopt, but, also can be at the entrance set temperature sensor of the 1st rear-stage side playpipe 19 1 sides of economizer heat exchanger 20, from the refrigerant temperature that energy-saving appliance outlet temperature sensor 55 detects, deduct the refrigerant temperature that is detected by this temperature sensor, thereby obtain the degree of superheat of the cold-producing medium in the outlet of the 1st rear-stage side playpipe 19 1 sides of economizer heat exchanger 20.In addition, the regulation of the 1st rear class injection valve 19a is not limited to degree of superheat control, for example, also can make it open the regulation aperture according to the circulating mass of refrigerant in the refrigerant line 10 etc.Because switching mechanism 3 becomes the cooling operating condition, therefore, the intermediate heat exchanger switch valve 12 of intermediate refrigerant pipe 8 is opened, the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9 is closed, like this, intermediate heat exchanger 7 just becomes can be as the state of cooler, and, the 2nd the 2nd suction Returning switch valve 92a that sucks recurrent canal 92 is closed, suction one side of intermediate heat exchanger 7 and compressing mechanism 2 just becomes the state (except when still, refrigeration begins to control) that is not connected like this.In addition, the intermediate heat exchanger Returning switch valve 94a of intermediate heat exchanger recurrent canal 94 is closed, and like this, utilizes between side heat exchanger 6 and the heat source side heat exchanger 4 just to become the state that is not connected with intermediate heat exchanger 7.
Under the state of this refrigerant line 210, the cold-producing medium of low pressure (with reference to the some A among Figure 14～Figure 16) is inhaled into the compressing mechanism 2 from suction line 2a, at first, after compressed parts 2c is compressed to intermediate pressure, discharge (with reference to the some B1 among Figure 14～Figure 16) to intermediate refrigerant pipe 8.The middle compression refrigerant that is discharged from from this preceding-stage side compression member 2c carries out heat exchange be cooled thereby (with reference to the some C1 among Figure 14～Figure 16) with water and air as cooling source intermediate heat exchanger 7.The cold-producing medium that is cooled in this intermediate heat exchanger 7 and cold-producing medium (with reference to the some K Figure 14～Figure 16) interflow of returning rear class compressing mechanism 2d from the 1st rear-stage side playpipe 19 are further cooled (with reference to the some G among Figure 14～Figure 16).Then, rear (namely with the cold-producing medium interflow of returning from the 1st rear-stage side playpipe 19, carry out economizer heat exchanger 20 in the middle of press to spray) middle compression refrigerant be inhaled among the compression member 2d that is connected with the rear class of compression member 2c and be further compressed, be expelled to discharge pipe 2b (with reference to the some D Figure 14～Figure 16) from compressing mechanism 2.The high-pressure refrigerant of herein, discharging from compressing mechanism 2 is compressed into pressure above critical pressure (that is, the critical pressure Pcp among the critical point CP shown in Figure 15) according to the two-stage compression operation of compression member 2c, 2d.The high-pressure refrigerant of discharging from this compressing mechanism 2 flows into the oil eliminator 41a that consists of oily separating mechanism 41, and refrigerator oil wherein is separated.In addition, the refrigerator oil that is separated from high-pressure refrigerant in oil eliminator 41a flows into the oily recurrent canal 41b that consists of oily separating mechanism 41, be arranged on the suction line 2a that returns compressing mechanism 2 after the mechanism of decompressor 41c decompression among the oily recurrent canal 41b, again be inhaled into compressing mechanism 2.Then, the high-pressure refrigerant after refrigerator oil is separated in oily separating mechanism 41 is sent to the heat source side heat exchanger 4 that has as the radiator function of cold-producing medium by one-way mechanism 42 and switching mechanism 3.Be sent to the high-pressure refrigerant of heat source side heat exchanger 4 in heat source side heat exchanger 4, thereby carry out heat exchange be cooled (with reference to the some E among Figure 14～Figure 16) with water and air as cooling source.The high-pressure refrigerant that is cooled in heat source side heat exchanger 4 is by flowing into reservoir inlet tube 18a behind the inlet one-way valve 17a of bridge circuit 17, its part is by 19 shuntings of the 1st rear-stage side playpipe.After near pressing in the middle of the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through is depressurized to, be sent to economizer heat exchanger 20 (with reference to the some J among Figure 14～Figure 16) in the 1st rear class injection valve 19a.In addition, flowed into economizer heat exchanger 20 by the cold-producing medium after the shunting of the 1st rear-stage side playpipe 19, with the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through carry out being cooled after the heat exchange (with reference to the some H among Figure 14～Figure 16).The cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through carries out being heated after the heat exchange (with reference to the some K among Figure 14～Figure 16) with the high-pressure refrigerant that is cooled in the heat source side heat exchanger 4 that has as the radiator function, then as mentioned above, with the middle compression refrigerant interflow of discharging from prime side pressure contracting parts 2c.The high-pressure refrigerant that is cooled in economizer heat exchanger 20 is decompressed near the saturation pressure by the 1st expansion mechanism 5a, then is temporarily stored in reservoir 18 (with reference to the some I among Figure 14).The cold-producing medium that is stored in the reservoir 18 is sent to reservoir outlet 18b, become the cold-producing medium of the gas-liquid two-phase state of low pressure after the 2nd expansion mechanism 5b decompression, the outlet check valve 17c by bridge circuit 17 is sent to have and utilizes side heat exchanger 6 (with reference to the some F among Figure 14～Figure 16) as the evaporator function of cold-producing medium.Thereby be sent to the low pressure of utilizing side heat exchanger 6 the gas-liquid two-phase state cold-producing medium with carry out heat exchange as the water and air of heating source and be heated then evaporation (with reference to the some A among Figure 14～Figure 16).Utilize at this that heated low pressure refrigerant is inhaled into compressing mechanism 2 again via switching mechanism 3 in side heat exchanger 6.Adopt above-mentioned this mode to carry out cooling operation.
In the structure of this variation, same with above-mentioned variation 2, because in the cooling operation when switching mechanism 3 switches to the cooling operating condition, intermediate heat exchanger 7 is become can be as the state of cooler, therefore, compare with the mode that intermediate heat exchanger 7 is not set, can reduce the radiation loss in the heat source side heat exchanger 4.
And, in the structure of this variation, the 1st rear-stage side playpipe 19 and economizer heat exchanger 20 are set, the cold-producing medium that is sent to expansion mechanism 5a, 5b from heat source side heat exchanger 4 shunted then make it return rear-stage side compression member 2d, therefore, can to the such external cooling of intermediate heat exchanger 7, can further not reduce the temperature (with reference to some C1, the G among Figure 16) that is inhaled into the cold-producing medium among the rear-stage side compression member 2d.Like this, the temperature of the cold-producing medium of discharging from compressing mechanism 2 is further reduced (with reference to some D, the D ' Figure 16), compare with the mode that the 1st rear-stage side playpipe 19 is not set, the radiation loss of the size that the some C1, D ', D, the G that are equivalent to link among Figure 16 consist of can be further reduced, therefore running efficiency can be further improved.
In addition, in this variation 2, same with above-mentioned variation, switch to the cooling operation of cooling operating condition when beginning at switching mechanism 3, because by intermediate heat exchanger bypass pipe 9, to suck from the cold-producing medium that prime side pressure contracting parts 2c discharges the rear-stage side compression member 2d, and, suck suction one side that recurrent canal 92 connects intermediate heat exchanger 7 and compressing mechanism 2 by the 2nd, therefore, switching mechanism 2 switch to the cooling operating condition running begin before, even liquid refrigerant accumulates in the intermediate heat exchanger 7, also this liquid refrigerant can be expelled to outside the intermediate heat exchanger 7, like this, the running that switches to the cooling operating condition at switching mechanism 3 is when beginning, and just can avoid occuring liquid refrigerant and accumulate in the interior state of intermediate heat exchanger 7, can not occur to improve the reliability of compressing mechanism 2 because liquid refrigerant accumulates in liquid compression among the rear-stage side compression member 2d that produce in the intermediate heat exchanger 7.
(heating control)
When heating turned round, switching mechanism 3 became the heating operating condition shown in the dotted line of Figure 14.In addition, the aperture of the 1st expansion mechanism 5a and the 2nd expansion mechanism 5b is conditioned.In addition, the 1st rear class injection valve 19a is implemented the regulation same with above-mentioned cooling operation.Because switching mechanism 3 becomes the heating operating condition, therefore, the intermediate heat exchanger switch valve 12 of intermediate refrigerant pipe 8 is closed, and the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9 is opened, and intermediate heat exchanger 7 just becomes the state that can not be used as cooler like this.And, because switching mechanism 3 becomes the heating operating condition, therefore, the 2nd the 2nd suction Returning switch valve 92a that sucks recurrent canal 92 is opened, so just become the state that suction one side that intermediate heat exchanger 7 is connected with compressing mechanism is connected, perhaps, the intermediate heat exchanger Returning switch valve 94a of intermediate heat exchanger recurrent canal 94 is opened, and so just becomes the state that is connected with intermediate heat exchanger 7 between side heat exchanger 6 and the heat source side heat exchanger 4 that utilizes.
Under the state of this refrigerant line 210, low pressure refrigerant (with reference to the some A among Figure 14, Figure 17, Figure 18) is inhaled into the compressing mechanism 2 from suction line 2a, at first, after compressed parts 2c is compressed to intermediate pressure, discharged (with reference to the some B1 among Figure 14, Figure 17, Figure 18) to intermediate refrigerant pipe 8.Different during from cooling operation, the middle compression refrigerant of discharging from this preceding-stage side compression member 2c does not pass through intermediate heat exchanger 7 (not namely, be not cooled), but by intermediate heat exchanger bypass pipe 9 (with reference to the some C1 among Figure 14, Figure 17, Figure 18), then with the cold-producing medium that returns rear class compressing mechanism 2d from the 1st rear-stage side playpipe 19 (with reference to the some K Figure 14, Figure 17, Figure 18) thereby the interflow is cooled (with reference to the some G among Figure 14, Figure 17, Figure 18).Then, be inhaled into the compression member 2d that is connected with the rear class of compression member 2c with the middle compression refrigerant behind the cold-producing medium interflow of returning from the 1st rear-stage side playpipe 19, and be further compressed, then discharge from compressing mechanism 2 to discharge pipe 2b (with reference to the some D Figure 14, Figure 17, Figure 18).Herein, same during with cooling operation, the high-pressure refrigerant of discharging from compressing mechanism 2 is according to the two-stage compression operation of compression member 2c, 2d, the compressed pressure that becomes above critical pressure (that is, the critical pressure Pcp among the critical point CP shown in Figure 17).Then, the high-pressure refrigerant of discharging from this compressing mechanism 2 flows into the oil eliminator 41a that consists of oily separating mechanism 41, and refrigerator oil wherein is separated.In addition, the refrigerator oil that is separated from high-pressure refrigerant in oil eliminator 41a flows into the oily recurrent canal 41b that consists of oily separating mechanism 41, be arranged on the suction line 2a that returns compressing mechanism 2 after the mechanism of decompressor 41c decompression among the oily recurrent canal 41b, again be inhaled into compressing mechanism 2.Then, high-pressure refrigerant after refrigerator oil is separated in oily separating mechanism 41 is by one-way mechanism 42 and switching mechanism 3, be sent to have as the radiator function of cold-producing medium utilize side heat exchanger 6, thereby carry out heat exchange be cooled (with reference to the some F among Figure 14, Figure 17, Figure 18) with water and air as cooling source.The high-pressure refrigerant that is cooled in utilizing side heat exchanger 6 is by flowing into reservoir inlet tube 18a behind the inlet one-way valve 17b of bridge circuit 17, its part is by 19 shuntings of the 1st rear-stage side playpipe.After near pressing in the middle of the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through is depressurized to, be sent to economizer heat exchanger 20 (with reference to the some J among Figure 14, Figure 17, Figure 18) in the 1st rear class injection valve 19a.In addition, flowed into economizer heat exchanger 20 by the cold-producing medium after the shunting of the 1st rear-stage side playpipe 19, with the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through carry out being cooled after the heat exchange (with reference to the some H among Figure 14, Figure 17, Figure 18).The cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through carries out being heated after the heat exchange (with reference to the some K among Figure 14, Figure 17, Figure 18) with the high-pressure refrigerant that is cooled in the heat source side heat exchanger 4 that has as the radiator function, then as mentioned above, with the middle compression refrigerant interflow of discharging from prime side pressure contracting parts 2c.The high-pressure refrigerant that is cooled in economizer heat exchanger 20 is decompressed near the saturation pressure by the 1st expansion mechanism 5a, then is temporarily stored in reservoir 18 (with reference to the some I among Figure 14).The cold-producing medium that is stored in the reservoir 18 is sent to reservoir outlet 18b, become the cold-producing medium of the gas-liquid two-phase state of low pressure after the 2nd expansion mechanism 5b decompression, outlet check valve 17d by bridge circuit 17 is sent to the heat source side heat exchanger 4 that has as the evaporator function of cold-producing medium, and by intermediate heat exchanger recurrent canal 94, be sent to the intermediate heat exchanger 7 (with reference to the some E among Figure 14, Figure 17, Figure 18) that has as the evaporator function of cold-producing medium.Thereby be sent to heat source side heat exchanger 4 low pressure the gas-liquid two-phase state cold-producing medium with carry out heat exchange as the water and air of heating source and be heated then evaporation (with reference to the some A among Figure 14, Figure 17, Figure 18).In addition, thus be sent to intermediate heat exchanger 7 low pressure the gas-liquid two-phase state cold-producing medium with carry out heat exchange as the water and air of heating source and be heated then evaporation (with reference to the some V among Figure 14, Figure 17, Figure 18).The low pressure refrigerant of evaporation is inhaled into compressing mechanism 2 again via switching mechanism 3 after being heated in this heat source side heat exchanger 4.In addition, the low pressure refrigerant of evaporation sucks recurrent canal 92 by the 2nd after being heated in this intermediate heat exchanger 7, again is inhaled into compressing mechanism 2.Adopt above-mentioned this mode to carry out the heating running.
In the structure of this variation, same with above-mentioned variation 2, in the heating running when switching mechanism 3 switches to the heating operating condition, with the mode that intermediate heat exchanger 7 only is set and with above-mentioned cooling operation intermediate heat exchanger 7 is had as the mode of cooler function to compare, can suppress the heat radiation to the outside, suppress the decline of heating efficiency, thereby prevent that running efficiency from reducing.
And, in the structure of this variation, same during with cooling operation, the 1st rear-stage side playpipe 19 and economizer heat exchanger 20 are set, the cold-producing medium that is sent to expansion mechanism 5a, 5b from heat source side heat exchanger 4 shunted then make it return rear-stage side compression member 2d, therefore, can not carry out further to reduce the temperature (with reference to some B1, the G among Figure 18) that is inhaled into the cold-producing medium among the rear-stage side compression member 2d to the such external cooling of intermediate heat exchanger 7.Like this, the temperature of the cold-producing medium of discharging from compressing mechanism 2 is further reduced (with reference to some D, the D ' Figure 18), compare with the mode that the 1st rear-stage side playpipe 19 is not set, the radiation loss of the size that the some B1, D ', D, the G that are equivalent to link among Figure 18 consist of can be further reduced, therefore running efficiency can be further improved.
In addition, in the structure of this variation, same with above-mentioned embodiment, during cooling operation, have as the radiation loss in the heat source side heat exchanger 4 of the radiator function of cold-producing medium and reduce the running efficiency in the time of to improve cooling operation, when heating turns round, intermediate heat exchanger 7 is effectively utilized, and can prevent from utilizing the heating efficiency in the side heat exchanger 4 to descend, and the running efficiency when making the heating running can not descend.
In addition, the common advantage of cooling operation and heating running is, in the structure of this variation, as economizer heat exchanger 20, adopted and had from heat source side heat exchanger 4 or utilize side heat exchanger 6 to be sent to expansion mechanism 5a, the heat exchanger of the stream that the cold-producing medium of the cold-producing medium of 5b and the rear-stage side playpipe 19 of flowing through flows in opposite directions, therefore, can dwindle the heat source side heat exchanger 4 from economizer heat exchanger 20 or utilize side heat exchanger 6 to be sent to expansion mechanism 5a, the temperature difference of the cold-producing medium of the cold-producing medium of 5b and the rear-stage side playpipe 19 of flowing through, and can obtain high heat exchanger effectiveness.
In addition, in this variation, on off state according to switch valve 11,12,92a, begin to switch between the control at cooling operation and refrigeration, that is, switch cold-producing medium non-return state and cold-producing medium return state, but, shown in above-mentioned variation 1, also can replace switch valve 11,12,92a, setting can be switched the intermediate heat exchanger transfer valve 93 of cold-producing medium non-return state and cold-producing medium return state.
And, in the situation of the structure of the heat source unit 1a that adopts variation 2, can obtain especially favourable effect.
(6) variation 4
In the refrigerant line 210 (with reference to Figure 14) in above-mentioned variation 3, as mentioned above, switching mechanism 3 switch to cooling during operating condition cooling operation and during a running in the heating running of switching mechanism 3 when switching to the heating operating condition, also carrying out middle pressure of economizer heat exchanger 20 sprays, like this, make from the temperature reduction of the cold-producing medium of rear-stage side compression member 2d discharge, and reduce the power consumption of compressing mechanism 2, improve running efficiency.Since centre in freeze cycle press also can use under near the condition that rises to the critical pressure economizer heat exchanger 20 in the middle of press and spray, therefore, shown in the refrigerant line 10,110,210 in above-mentioned embodiment and the variation thereof (with reference to Fig. 1,10,14), in having a structure that utilizes side heat exchanger 6, advantageous particularly in situation about using at the cold-producing medium of supercritical region work.
But, in order to carry out the refrigeration corresponding with the air conditioner load of a plurality of conditioned spaces and heating etc., employing has a plurality of structures that utilize side heat exchanger 6 of connection parallel with one another, and, each utilizes the flow of the cold-producing medium of side heat exchanger 6 in order to flow through by control, thereby can obtain to utilize freezing load required in the side heat exchanger 6 at each, sometimes adopt a kind of as the reservoir 18 of gas-liquid separator with utilize between the side heat exchanger 6 and utilize side heat exchanger 6 that the structure of the side of utilization expansion mechanism 5c is set accordingly with each.
For example, do not represent its details among the figure, it is in the refrigerant line with bridge circuit 17 210 (with reference to Figure 14) in above-mentioned variation 3 that a kind of method is arranged, some (being two) that connection parallel with one another is set utilize side heat exchanger 6 herein, and, as the reservoir 18 (more specifically being bridge circuit 17) of gas-liquid separator with utilize between the side heat exchanger 6, utilize side heat exchanger 6 that the side of utilization expansion mechanism 5c (with reference to Figure 19) is set accordingly with each, deletion set the 2nd expansion mechanism 5b in reservoir outlet 18b, the outlet check valve 17d that perhaps replaces bridge circuit 17 is arranged on the 3rd expansion mechanism that heating when running is decompressed to cold-producing medium the low pressure in the freeze cycle.
In this structure, also as switching mechanism 3 becomes the cooling operation that cools off under the operating condition, after in the heat source side heat exchanger 4 as radiator, being cooled, beyond the 1st expansion mechanism 5a as the heat source side expansion mechanism, do not carry out large-scale decompression operation, can utilize high pressure to the centre in the freeze cycle in the freeze cycle to press near pressure differential, under this condition, same with above-mentioned variation 3, press in the middle of the economizer heat exchanger 20 spray useful.
But, as switching mechanism 3 becomes the heating running of heating under the operating condition, in order to obtain to utilize freezing load required in the side heat exchanger 6 as each of radiator, each side of utilization expansion mechanism 5c control is flowed through and is utilized the flow of the cold-producing medium of side heat exchanger 6 as each of radiator, flow through and utilize the flow of the cold-producing medium of side heat exchanger 6 as each of radiator, probably by by being determined at the aperture control of the set utilization side expansion mechanism 5c of upper reaches one side of a dirty side of utilizing side heat exchanger 6 as each of radiator and economizer heat exchanger 20 decompression operation to cold-producing medium, under this condition, the control of the aperture of each side of utilization expansion mechanism 5c not only utilizes the flow of the cold-producing medium of side heat exchanger 6 because flowing through as each of radiator to the decompression degree of cold-producing medium, and change because of a plurality of states that utilize the assignment of traffic between the side heat exchanger 6 as radiator, the very large state of decompression degree difference appears between a plurality of utilization side expansion mechanism 5c sometimes, and the more situation of decompression among the side of the utilization expansion mechanism 5c, therefore, the pressure of the cold-producing medium in the entrance of economizer heat exchanger 20 might descend, in this case, heat-shift in the economizer heat exchanger 20 (namely, the flow through flow of cold-producing medium of the 1st rear-stage side playpipe 19) might reduce, cause being difficult to using.Particularly connect the heat source unit that mainly comprises compressing mechanism 2, heat source side heat exchanger 4 and reservoir 18 by connecting pipings at this aircondition 1; Thereby and mainly comprise in the situation of range site formation as Split for conditioner of utilizing side heat exchanger 6, configuration according to range site and heat source unit, this contact pipe arrangement might become very long, therefore, except the impact that is subject to its pressure loss generation, the pressure of the cold-producing medium in the entrance of economizer heat exchanger 20 further descends.In the situation that the pressure of the cold-producing medium in the entrance of economizer heat exchanger 20 might descend, so long as the pressure of the gas and liquid separator pressure lower than critical pressure, so, in pressure of the gas and liquid separator and freeze cycle in the middle of press the gas-liquid separator that also can use under the little condition of the pressure differential of the pressure of cold-producing medium of intermediate refrigerant pipe 8 (herein be flow through) in the middle of press spray just useful.
Therefore, in this variation, as shown in figure 19, press injection for reservoir 18 being carried out the centre as gas-liquid separator, in reservoir 18, connect the 2nd rear-stage side playpipe 18c, thereby form refrigerant line 310, when cooling operation, carry out middle pressure of economizer heat exchanger 20 and spray, when heating turns round, carry out the middle pressure injection as the reservoir 18 of gas-liquid separator.
In addition, the 2nd rear-stage side playpipe 18c can carry out taking out the middle refrigerant pipe that sprays of pressing that then cold-producing medium sends it back to the rear-stage side compression member 2d of compressing mechanism 2 from reservoir 18, in this variation, arrange according to the top that connects reservoir 18 and the mode of intermediate refrigerant pipe 8 (that is, suction one side of the rear-stage side compression member 2d of compressing mechanism 2).In the 2nd rear-stage side playpipe 18c, be provided with the 2nd rear class injection cock valve 18d and the 2nd rear class and spray one-way mechanism 18e.The 2nd rear class injection cock valve 18d is the valve that can carry out switching manipulation, is magnetic valve in this variation.The 2nd rear class is sprayed one-way mechanism 18e and is used for allowing that cold-producing medium flows to rear-stage side compression member 2d from reservoir 18, and block refrigerant flows to reservoir 18 from rear-stage side compression member 2d, uses check valve in this variation.In addition, the 2nd rear-stage side playpipe 18c and the 1st sucks recurrent canal 18f and forms one in the part of reservoir 18 1 sides.In addition, the 2nd rear-stage side playpipe 18c and the 1st rear-stage side playpipe 19 form one in the part of intermediate refrigerant pipe 8 one sides.In addition, in this variation, the side of utilization expansion mechanism 5c is electric expansion valve.In this variation, as mentioned above, when cooling operation, use the 1st rear-stage side playpipe 19 and economizer heat exchanger 20, no matter use the 2nd rear-stage side playpipe 18c when heating turns round, therefore, be when cooling operation or heating running, cold-producing medium is fixed towards the flow direction of economizer heat exchanger 20, therefore, omit bridge circuit 17, thereby simplify the structure of refrigerant line 310.
Below, use Figure 19, Figure 15, Figure 16, Figure 20, Figure 21, the operation of the aircondition 1 of this variation is described.Herein, the temperature of the freeze cycle the when pressure of the freeze cycle when Figure 20 is the heating running-enthalpy line chart, Figure 21 are the heating running-entropy line chart.Herein, it is identical with above-mentioned embodiment that refrigeration begins control, and therefore, the description thereof will be omitted herein.Freeze cycle during for the cooling operation in this variation uses Figure 15, Figure 16 to describe.In addition, the running control in the running of following cooling operation and heating (comprising that also unaccounted refrigeration begins control herein) is to be undertaken by the control part (not shown) in the above-mentioned embodiment.In the following description, " high pressure " refer in the freeze cycle high pressure (namely, the pressure of some D among Figure 15, Figure 16, D ', E, H and the some D among Figure 20, Figure 21, the pressure of D ', F), " low pressure " refer in the freeze cycle low pressure (namely, the pressure of some A, F among Figure 15, Figure 16 and the some A among Figure 20, Figure 21, the pressure of E, V), " the middle pressure " refers to middle press (that is, the pressure of the pressure of the some B1 among Figure 15, Figure 16, C1, G, J, K and the some B1 among Figure 20, Figure 21, C1, G, I, L, M) in the freeze cycle.
(cooling operation)
When cooling operation, switching mechanism 3 is switched to the cooling operating condition shown in the solid line of Figure 19.Be conditioned as the 1st expansion mechanism 5a of heat source side expansion mechanism and the aperture of the side of utilization expansion mechanism 5c.Because switching mechanism 3 becomes the cooling operating condition, therefore, the intermediate heat exchanger switch valve 12 of intermediate refrigerant pipe 8 is opened, the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9 is closed, so, intermediate heat exchanger 7 just becomes can be as the state of cooler, and, the 2nd the 2nd suction Returning switch valve 92a that sucks recurrent canal 92 is closed, so, suction one side of intermediate heat exchanger 7 and compressing mechanism 2 is in the state that is not connected (still, except when refrigeration described later begins to control), perhaps, the intermediate heat exchanger Returning switch valve 94a of intermediate heat exchanger recurrent canal 94 is closed, so, utilize between side heat exchanger 6 and the heat source side heat exchanger 4 to be in the state that is not connected with intermediate heat exchanger 7.In addition, when switching mechanism 3 switches to the cooling operating condition, do not carry out spraying as pressing in the middle of the reservoir 18 of gas-liquid separator, but carry out by the 1st rear-stage side playpipe 19 make in economizer heat exchanger 20 heated cold-producing medium return rear-stage side compression member 2d economizer heat exchanger 20 in the middle of press and spray.More specifically, the 2nd rear class injection cock valve 18d is in closed condition, and the 1st rear class injection valve 19a is implemented the regulation same with above-mentioned variation 3.
Under the state of this refrigerant line 310, the cold-producing medium of low pressure (with reference to the some A among Figure 19, Figure 15, Figure 16) is inhaled into the compressing mechanism 2 from suction line 2a, at first, after compressed parts 2c is compressed to intermediate pressure, discharge (with reference to the some B1 among Figure 19, Figure 15, Figure 16) to intermediate refrigerant pipe 8.The middle compression refrigerant of discharging from this preceding-stage side compression member 2c carries out heat exchange be cooled thereby (with reference to Figure 19, Figure 15, Figure 16 mid point C1) with water and air as cooling source intermediate heat exchanger 7.The cold-producing medium that in this intermediate heat exchanger 7, is cooled with the cold-producing medium (with reference to the some K Figure 19, Figure 15, Figure 16) that returns rear class compressing mechanism 2d from the 1st rear-stage side playpipe 19 thus the interflow is further cooled (with reference to Figure 19, Figure 15, Figure 16 mid point G).Then, rear (namely with the cold-producing medium interflow of returning from the 1st rear-stage side playpipe 19, carry out economizer heat exchanger 20 in the middle of press to spray) middle compression refrigerant be inhaled among the compression member 2d that is connected with the rear class of compression member 2c, and be further compressed, be expelled to discharge pipe 2b (with reference to the some D of Figure 19, Figure 15, Figure 16) from compressing mechanism 2.The high-pressure refrigerant of herein, discharging from compressing mechanism 2 operates the pressure that is compressed into above critical pressure (that is, the critical pressure Pcp among the critical point CP shown in Figure 15) according to the two-stage compression of compression member 2c, 2d.The high-pressure refrigerant of discharging from this compressing mechanism 2 is via switching mechanism 3, be sent to the heat source side heat exchanger 4 that has as the radiator function of cold-producing medium, with water and air as cooling source carry out being cooled after the heat exchange (with reference to the some E among Figure 19, Figure 15, Figure 16).The part of the high-pressure refrigerant that is cooled in the heat source side heat exchanger 4 as radiator is by 19 shuntings of the 1st rear-stage side playpipe.After near pressing in the middle of the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through is depressurized to, be sent to economizer heat exchanger 20 (with reference to the some J among Figure 19, Figure 15, Figure 16) in the 1st rear class injection valve 19a.In addition, flowed into economizer heat exchanger 20 by the cold-producing medium after the shunting of the 1st rear-stage side playpipe 19, with the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through carry out being cooled after the heat exchange (with reference to the some H among Figure 19, Figure 15, Figure 16).The cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through carries out being heated after the heat exchange (with reference to Figure 19, Figure 15, Figure 16 mid point K) with the high-pressure refrigerant that is cooled in the heat source side heat exchanger 4 that has as the radiator function, then as mentioned above, with the middle compression refrigerant interflow of discharging from prime side pressure contracting parts 2c.The high-pressure refrigerant that is cooled in economizer heat exchanger 20 is decompressed near the saturation pressure by the 1st expansion mechanism 5a, then is temporarily stored in reservoir 18 (with reference to the some I among Figure 19, Figure 15, Figure 16).The cold-producing medium that is stored in the reservoir 18 is sent to the side of utilization expansion mechanism 5c, become the cold-producing medium of the gas-liquid two-phase state of low pressure after the side of the being utilized expansion mechanism 5c decompression, be sent to have and utilize side heat exchanger 6 (with reference to the some F among Figure 19, Figure 15, Figure 16) as the evaporator function of cold-producing medium.Be sent to as the cold-producing medium of the gas-liquid two-phase state of the low pressure of utilizing side heat exchanger 6 of evaporimeter and water and air as heating source and carry out being heated after the heat exchange then evaporation (with reference to the some A among Figure 19, Figure 15, Figure 16).Utilize as evaporimeter that heated low pressure refrigerant is inhaled into compressing mechanism 2 again via switching mechanism 3 in the side heat exchanger 6 at this.Adopt above-mentioned this mode to carry out cooling operation.
(heating running)
When heating turned round, switching mechanism 3 became the heating operating condition shown in the dotted line of Figure 19.Be conditioned as the 1st expansion mechanism 5a of heat source side expansion mechanism and the aperture of the side of utilization expansion mechanism 5c.Because switching mechanism 3 becomes the heating operating condition, therefore, the intermediate heat exchanger switch valve 12 of intermediate refrigerant pipe 8 is closed, and the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9 is opened, so intermediate heat exchanger 7 just becomes can not be as the state of cooler.And, because switching mechanism 3 becomes the heating operating condition, therefore, the 2nd the 2nd suction Returning switch valve 92a that sucks recurrent canal 92 is opened, so, become the state that suction one side that intermediate heat exchanger 7 is connected with compressing mechanism is connected, perhaps the intermediate heat exchanger Returning switch valve 94a of intermediate heat exchanger recurrent canal 94 is opened, so, utilize between side heat exchanger 6 and the heat source side heat exchanger 4 to become the state that is connected with intermediate heat exchanger 7.In addition, when switching mechanism 3 switches to the heating operating condition, do not carry out middle pressure of economizer heat exchanger 20 and spray, but carry out making cold-producing medium return the middle pressure injection of the reservoir 18 of rear-stage side compression member 2d from the reservoir 18 as gas-liquid separator by the 2nd rear-stage side playpipe 18c.More specifically, the 2nd rear class injection cock valve 18d is in open mode, and the 1st rear class injection valve 19a is in buttoned-up status.
Under the state of this refrigerant line 310, low pressure refrigerant (with reference to the some A among Figure 19～Figure 21) is inhaled into the compressing mechanism 2 from suction line 2a, at first, after compressed parts 2c is compressed to intermediate pressure, be discharged to intermediate refrigerant pipe 8 (with reference to the some B1 among Figure 19～Figure 21).Different during from cooling operation, the middle compression refrigerant of discharging from this preceding-stage side compression member 2c does not pass through intermediate heat exchanger 7 (not namely, be not cooled), but by intermediate heat exchanger bypass pipe 9 (with reference to the some C1 among Figure 19～Figure 21), and return the cold-producing medium (with reference to the some M Figure 19～Figure 21) of rear class compressing mechanism 2d thereby the interflow is cooled (with reference to the some G among Figure 19～Figure 21) from reservoir 18 by the 2nd rear-stage side playpipe 18c.Then, rear (namely with the cold-producing medium interflow of returning from the 2nd rear-stage side playpipe 18c, carry out spraying as pressing in the middle of the reservoir 18 of gas-liquid separator) middle compression refrigerant be inhaled into the compression member 2d that is connected with the rear class of compression member 2c, be further compressed, then discharge from compressing mechanism 2 to discharge pipe 2b (with reference to the some D Figure 19～Figure 21).Herein, same during with cooling operation, the high-pressure refrigerant of discharging from compressing mechanism 2 is compressed into pressure above critical pressure (that is, the critical pressure Pcp among the critical point CP shown in Figure 20) according to the two-stage compression operation of compression member 2c, 2d.The high-pressure refrigerant of discharging from this compressing mechanism 2 is via switching mechanism 3, be sent to have as the radiator function of cold-producing medium utilize side heat exchanger 6, with water and air as cooling source carry out being cooled after the heat exchange (with reference to the some F among Figure 19～Figure 21).After in the middle of the high-pressure refrigerant side of the being utilized expansion mechanism 5c that is cooled in the side heat exchanger 6 as utilizing of radiator is decompressed to, pressing, be stored in the reservoir 18 and carry out gas-liquid separation (with reference to some I, L, the M among Figure 19～Figure 21).In reservoir 18, discharged from the top of reservoir 18 by the 2nd rear-stage side playpipe 18c by the gas refrigerant after the gas-liquid separation, as mentioned above, with the middle compression refrigerant interflow of discharging from prime side pressure contracting parts 2c.Be stored in the cold-producing medium that becomes the gas-liquid two-phase state of low pressure after reservoir 18 interior liquid refrigerants are reduced pressure by the 1st expansion mechanism 5a, be sent to the heat source side heat exchanger 4 that has as the evaporator function of cold-producing medium, and, by intermediate heat exchanger recurrent canal 94, also be sent to the intermediate heat exchanger 7 (with reference to the some E among Figure 19～Figure 21) that has as the evaporator function of cold-producing medium.Thereby be sent to heat source side heat exchanger 4 low pressure the gas-liquid two-phase state cold-producing medium with carry out heat exchange as the water and air of heating source and be heated then evaporation (with reference to the some A among Figure 19～Figure 21).Thereby the cold-producing medium of gas-liquid two-phase state that is sent to the low pressure of intermediate heat exchanger 7 also carries out heat exchange with water and air as heating source and is heated then evaporation (with reference to the some V among Figure 19～Figure 21).The cold-producing medium of the low pressure that is heated in this heat source side heat exchanger 4 and evaporates is inhaled in the compressing mechanism 2 again via switching mechanism 3.In addition, in this intermediate heat exchanger 7, be heated and the cold-producing medium of the low pressure of evaporating sucks recurrent canal 92 by the 2nd, again be inhaled in the compressing mechanism 2.Adopt above-mentioned this mode to carry out the heating running.
In the structure of this variation, when heating turns round, replace economizer heat exchanger 20 in the middle of press and spray and carry out spraying as pressing in the middle of the reservoir 18 of gas-liquid separator, this point is different from variation 3, for other aspect, can obtain the action effect same with variation 3.
In addition, in this variation, on off state according to switch valve 11,12,92a, begin to switch between the control at cooling operation and refrigeration, that is, switch cold-producing medium non-return state and cold-producing medium return state, but, shown in above-mentioned variation 1, also can replace switch valve 11,12,92a, setting can be switched the intermediate heat exchanger transfer valve 93 of cold-producing medium non-return state and cold-producing medium return state.
And, in the situation of the structure of the heat source unit 1a that adopts variation 2, can obtain especially favourable effect.
(7) variation 5
In the refrigerant line 310 (with reference to Figure 19) in above-mentioned variation 4, in order to carry out the refrigeration corresponding with the air conditioner load of a plurality of conditioned spaces and heating etc., employing has a plurality of structures that utilize side heat exchanger 6 of connection parallel with one another, and, each utilizes the flow of the cold-producing medium of side heat exchanger 6 in order to flow through by control, thereby can obtain to utilize freezing load required in the side heat exchanger 6 at each, adopt a kind of at reservoir 18 with utilize between the side heat exchanger 6 with each and utilize side heat exchanger 6 corresponding and the structure of the side of utilization expansion mechanism 5c is set.In this structure, when cooling operation, be decompressed near the cold-producing medium (with reference to the some I among Figure 19) that then is temporarily stored in reservoir 18 saturation pressure by the 1st expansion mechanism 5a and be assigned to each side of utilization expansion mechanism 5c, but, if being sent to the cold-producing medium of each side of utilization expansion mechanism 5c from reservoir 18 is the gas-liquid two-phase state, so, dividing timing just might produce bias current to each side of utilization expansion mechanism 5c, therefore, preferably make as much as possible the cold-producing medium that is sent to each side of utilization expansion mechanism 5c from reservoir 18 be in the supercooling state.
Therefore, in this variation, as shown in figure 22, in the refrigerant line 310 in above-mentioned variation 4, supercooling heat exchanger 96 and the 3rd is set between reservoir 18 and the side of utilization expansion mechanism 5c sucks recurrent canal 95, form refrigerant line 410.
Supercooling heat exchanger 96 is heat exchangers that the cold-producing medium that is sent to the side of utilization expansion mechanism 5c from reservoir 18 is cooled off.More specifically, supercooling heat exchanger 96 is when cooling operation, carry out then making its suction of returning compressing mechanism 2 one side (namely with a part that is sent to the cold-producing medium of the side of utilization expansion mechanism 5c from reservoir 18 is shunted, the suction line 2a between side heat exchanger 6 and the compressing mechanism 2 of utilizing as evaporimeter) the 3rd heat exchanger of heat exchange that sucks the cold-producing medium of recurrent canal 95 of flowing through, it has the stream that two cold-producing mediums flow in opposite directions.Herein, the 3rd suction recurrent canal 95 is that the cold-producing medium that is sent to expansion mechanism 5c from the heat source side heat exchanger 4 as radiator is shunted the refrigerant pipe that then makes its suction of returning compressing mechanism 2 one side (being suction line 2a).In the 3rd suction recurrent canal 95, be provided with the 3rd suction that to control its aperture and return valve 95a, in supercooling heat exchanger 96, carry out being sent to the cold-producing medium of the side of utilization expansion mechanism 5c and sucking near the 3rd heat exchange that sucks the cold-producing medium of recurrent canal 95 of flowing through return after being depressurized to the low pressure the valve 95a the 3rd from reservoir 18.In this variation, it is electric expansion valve that valve 95a is returned in the 3rd suction.In addition, in suction line 2a or compressing mechanism 2, be provided with the suction pressure sensor 60 of the refrigerant pressure of suction one side that detects the compressing mechanism 2 of flowing through.Be provided with the supercooling heat exchange outlet temperature sensor 59 that detects the refrigerant temperature in the outlet that the 3rd of supercooling heat exchanger 96 sucks recurrent canal 95 1 sides in the outlet that the 3rd of supercooling heat exchanger 96 sucks recurrent canal 95 1 sides.
Below, use Figure 22～Figure 24, Figure 20, Figure 21 that the operation of the aircondition 1 of this variation is described.Herein, the pressure of the freeze cycle when Figure 23 is cooling operation-enthalpy line chart, the temperature of the freeze cycle when Figure 24 is cooling operation-entropy line chart.Herein, it is identical with above-mentioned embodiment that refrigeration begins control, and therefore, the description thereof will be omitted herein.Freeze cycle when turning round for the heating in this variation uses Figure 20, Figure 21 to describe.In addition, the running control in the running of following cooling operation and heating (comprising that also unaccounted refrigeration begins control herein) is to be undertaken by the control part (not shown) in the above-mentioned embodiment.In the following description, " high pressure " refer in the freeze cycle high pressure (namely, Figure 23, some D among Figure 24, E, I, the pressure of R and Figure 20, some D among Figure 21, D ', the pressure of F), " low pressure " refer in the freeze cycle low pressure (namely, Figure 23, some A among Figure 24, F, F, S ', the pressure of U and Figure 20, some A among Figure 21, E, the pressure of V), " the middle pressure " refers to middle (that is, the Figure 23 of pressure in the freeze cycle, some B1 among Figure 24, C1, G, J, the pressure of K and Figure 20, some B1 among Figure 21, C1, G, I, L, the pressure of M).
(cooling operation)
When cooling operation, switching mechanism 3 is switched to the cooling operating condition shown in the solid line of Figure 22.Be conditioned as the 1st expansion mechanism 5a of heat source side expansion mechanism and the aperture of the side of utilization expansion mechanism 5c.Because switching mechanism 3 becomes the cooling operating condition, therefore, the intermediate heat exchanger switch valve 12 of intermediate refrigerant pipe 8 is opened, the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9 is closed, so, intermediate heat exchanger 7 just becomes can be as the state of cooler, and, the 2nd the 2nd suction Returning switch valve 92a that sucks recurrent canal 92 is closed, so, suction one side of intermediate heat exchanger 7 and compressing mechanism 2 becomes the state that is not connected (still, except when refrigeration described later begins to control), perhaps, the intermediate heat exchanger Returning switch valve 94a of intermediate heat exchanger recurrent canal 94 is closed, so, utilize between side heat exchanger 6 and the heat source side heat exchanger 4 to become the state that is not connected with intermediate heat exchanger 7.In addition, when switching mechanism 3 switches to the cooling operating condition, do not carry out spraying as pressing in the middle of the reservoir 18 of gas-liquid separator, but carry out by the 1st rear-stage side playpipe 19 make in economizer heat exchanger 20 heated cold-producing medium return rear-stage side compression member 2d economizer heat exchanger 20 in the middle of press and spray.More specifically, the 2nd rear class injection cock valve 18d is in closed condition, and the 1st rear class injection valve 19a is implemented the regulation same with above-mentioned variation 3.
In addition, when switching mechanism 3 switches to the cooling operating condition, use supercooling heat exchanger 96, therefore, the 3rd sucks the aperture of returning valve 95a also is conditioned.More specifically, in this variation, the 3rd sucks and to return the so-called degree of superheat control that valve 95a is implemented regulation, thereby the degree of superheat that makes the 3rd of supercooling heat exchanger 96 suck the cold-producing medium in the outlet of recurrent canal 95 1 sides becomes desired value.In this variation, the degree of superheat that the 3rd of supercooling heat exchanger 96 sucks the cold-producing medium in the outlet of recurrent canal 95 1 sides is converted into saturation temperature by the low pressure that suction pressure sensor 60 is detected, and deducts the saturation temperature value of this cold-producing medium and obtain from the refrigerant temperature that supercooling heat exchange outlet temperature sensor 59 detects.In addition, in this variation, do not adopt, but, also can suck at the 3rd of supercooling heat exchanger 96 the entrance set temperature sensor of recurrent canal 95 1 sides, from the refrigerant temperature that supercooling heat exchange outlet temperature sensor 59 detects, deduct the refrigerant temperature that is detected by this temperature sensor, thereby obtain the degree of superheat of the cold-producing medium in the outlet that the 3rd of supercooling heat exchanger 96 sucks recurrent canal 95 1 sides.In addition, the 3rd sucks the regulation return valve 95a is not limited to degree of superheat control, for example, also can make it open the regulation aperture according to the circulating mass of refrigerant in the refrigerant line 410 etc.
Under the state of this refrigerant line 410, low pressure refrigerant (with reference to the some A among Figure 22～Figure 24) is inhaled into the compressing mechanism 2 from suction line 2a, at first, after compressed parts 2c is compressed to intermediate pressure, be discharged to intermediate refrigerant pipe 8 (with reference to the some B1 among Figure 22～Figure 24).The middle compression refrigerant of discharging from this preceding-stage side compression member 2c intermediate heat exchanger 7, thereby carry out heat exchange be cooled (with reference to the some C1 among Figure 22～Figure 24) with water and air as cooling source.The cold-producing medium that in this intermediate heat exchanger 7, is cooled with the cold-producing medium (with reference to the some K Figure 22～Figure 24) that returns rear class compressing mechanism 2d from the 1st rear-stage side playpipe 19 thus the interflow is further cooled (with reference to the some G among Figure 22～Figure 24).Then, rear (namely with the cold-producing medium interflow of returning from the 1st rear-stage side playpipe 19, carry out economizer heat exchanger 20 in the middle of press to spray) middle compression refrigerant be inhaled among the compression member 2d that is connected with the rear class of compression member 2c, and be further compressed, be expelled to discharge pipe 2b (with reference to the some D Figure 22～Figure 24) from compressing mechanism 2.The high-pressure refrigerant of herein, discharging from compressing mechanism 2 is compressed into pressure above critical pressure (that is, the critical pressure Pcp among the critical point CP shown in Figure 23) according to the two-stage compression operation of compression member 2c, 2d.The high-pressure refrigerant of discharging from this compressing mechanism 2 is via switching mechanism 3, be sent to the heat source side heat exchanger 4 that has as the radiator function of cold-producing medium, with water and air as cooling source carry out being cooled after the heat exchange (with reference to the some E among Figure 22～Figure 24).The part of the high-pressure refrigerant that is cooled in the heat source side heat exchanger 4 as radiator is by 19 shuntings of the 1st rear-stage side playpipe.After near pressing in the middle of the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through is depressurized to, be sent to economizer heat exchanger 20 (with reference to the some J among Figure 22～Figure 24) in the 1st rear class injection valve 19a.In addition, flowed into economizer heat exchanger 20 by the cold-producing medium after the shunting of the 1st rear-stage side playpipe 19, with the cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through carry out being cooled after the heat exchange (with reference to the some H among Figure 20～Figure 22).The cold-producing medium of the 1st rear-stage side playpipe 19 of flowing through carries out being heated after the heat exchange (with reference to the some K among Figure 22～Figure 24) with the high-pressure refrigerant that is cooled in the heat source side heat exchanger 4 that has as the radiator function, then as mentioned above, with the middle compression refrigerant interflow of discharging from prime side pressure contracting parts 2c.The high-pressure refrigerant that is cooled in economizer heat exchanger 20 is decompressed near the saturation pressure by the 1st expansion mechanism 5a, then is temporarily stored in reservoir 18 (with reference to the some I among Figure 22～Figure 24).A part that is stored in the cold-producing medium in the reservoir 18 is sucked recurrent canal 95 shuntings by the 3rd.Flow through the 3rd cold-producing medium that sucks recurrent canal 95 the 3rd suck return be depressurized near the low pressure among the valve 95a after, be sent to supercooling heat exchanger 96 (with reference to the some S among Figure 20～Figure 22).In addition, flowed into supercooling heat exchanger 96 by the 3rd cold-producing medium that sucks after recurrent canal 95 is shunted, the 3rd cold-producing medium that sucks recurrent canal 95 carries out being further cooled after the heat exchange (with reference to the some R among Figure 22～Figure 24) with flowing through.The 3rd cold-producing medium that sucks recurrent canal 95 of flowing through carries out being heated after the heat exchange (with reference to the some U among Figure 22～Figure 24) with the high-pressure refrigerant that is cooled in economizer heat exchanger 20, then with the cold-producing medium interflow of suction one side (being suction line 2a) of the compressing mechanism 2 of flowing through herein.The cold-producing medium that is cooled in this supercooling heat exchanger 96 is sent to the side of utilization expansion mechanism 5c, become the cold-producing medium of the gas-liquid two-phase state of low pressure after the side of the being utilized expansion mechanism 5c decompression, be sent to have and utilize side heat exchanger 6 (with reference to the some F among Figure 22～Figure 24) as the evaporator function of cold-producing medium.Be sent to as the cold-producing medium of the gas-liquid two-phase state of the low pressure of utilizing side heat exchanger 6 of evaporimeter and water and air as heating source and carry out being heated after the heat exchange, and evaporation (with reference to the some A among Figure 22～Figure 24).This as evaporimeter utilize the low pressure refrigerant that is heated in the side heat exchanger 6 and evaporates via switching mechanism 3, again be inhaled into compressing mechanism 2.Adopt above-mentioned this mode to carry out cooling operation.
(heating running)
When heating turned round, switching mechanism 3 became the heating operating condition shown in the dotted line of Figure 22.Be conditioned as the 1st expansion mechanism 5a of heat source side expansion mechanism and the aperture of the side of utilization expansion mechanism 5c.Because switching mechanism 3 becomes the heating operating condition, therefore, the intermediate heat exchanger switch valve 12 of intermediate refrigerant pipe 8 is closed, and the intermediate heat exchanger bypass cock valve 11 of intermediate heat exchanger bypass pipe 9 is opened, so intermediate heat exchanger 7 just becomes can not be as the state of cooler.And, because switching mechanism 3 becomes the heating operating condition, therefore, the 2nd the 2nd suction Returning switch valve 92a that sucks recurrent canal 92 is opened, so, become the state that suction one side that intermediate heat exchanger 7 is connected with compressing mechanism is connected, perhaps the intermediate heat exchanger Returning switch valve 94a of intermediate heat exchanger recurrent canal 94 is opened, so, utilize between side heat exchanger 6 and the heat source side heat exchanger 4 to become the state that is connected with intermediate heat exchanger 7.In addition, when switching mechanism 3 switches to the heating operating condition, do not carry out middle pressure of economizer heat exchanger 20 and spray, but carry out making cold-producing medium return the middle pressure injection of the reservoir 18 of rear-stage side compression member 2d from the reservoir 18 as gas-liquid separator by the 2nd rear-stage side playpipe 18c.More specifically, the 2nd rear class injection cock valve 18d is in open mode, and the 1st rear class injection valve 19a is in buttoned-up status.When switching mechanism 3 switches to the heating operating condition, do not use supercooling heat exchanger 96, therefore, the 3rd suction is returned valve 95a and also is in buttoned-up status.
Under the state of this refrigerant line 410, low pressure refrigerant (with reference to the some A among Figure 22, Figure 20, Figure 21) is inhaled into the compressing mechanism 2 from suction line 2a, at first, after compressed parts 2c is compressed to intermediate pressure, be discharged to intermediate refrigerant pipe 8 (with reference to the some B1 among Figure 22, Figure 20, Figure 21).Different during from cooling operation, the middle compression refrigerant of discharging from this preceding-stage side compression member 2c does not pass through intermediate heat exchanger 7 (not namely, be not cooled), but by intermediate heat exchanger bypass pipe 9 (with reference to the some C1 among Figure 22, Figure 20, Figure 21), and return the cold-producing medium (with reference to the some M Figure 22, Figure 20, Figure 21) of rear class compressing mechanism 2d thereby the interflow is cooled (with reference to the some G among Figure 22, Figure 20, Figure 21) from reservoir 18 by the 2nd rear-stage side playpipe 18c.Then, rear (namely with the cold-producing medium interflow of returning from the 2nd rear-stage side playpipe 18c, carry out spraying as pressing in the middle of the reservoir 18 of gas-liquid separator) middle compression refrigerant be further compressed the then discharge (with reference to the some D Figure 22, Figure 20, Figure 21) from compressing mechanism 2 to discharge pipe 2b after being inhaled into the compression member 2d that is connected with the rear class of compression member 2c.Herein, same during with cooling operation, the high-pressure refrigerant of discharging from compressing mechanism 2 is compressed into pressure above critical pressure (that is, the critical pressure Pcp among the critical point CP shown in Figure 20) according to the two-stage compression operation of compression member 2c, 2d.The high-pressure refrigerant of discharging from this compressing mechanism 2 is via switching mechanism 3, be sent to have as the radiator function of cold-producing medium utilize side heat exchanger 6, with water and air as cooling source carry out being cooled after the heat exchange (with reference to the some F among Figure 22, Figure 20, Figure 21).After in the middle of the high-pressure refrigerant side of the being utilized expansion mechanism 5c that is cooled in the side heat exchanger 6 as utilizing of radiator is decompressed to, pressing, be stored in the reservoir 18 and carry out gas-liquid separation (with reference to some I, L, the M among Figure 22, Figure 20, Figure 21).In reservoir 18, discharged from the top of reservoir 18 by the 2nd rear-stage side playpipe 18c by the gas refrigerant after the gas-liquid separation, as mentioned above, with the middle compression refrigerant interflow of discharging from prime side pressure contracting parts 2c.Be stored in the cold-producing medium that becomes the gas-liquid two-phase state of low pressure after reservoir 18 interior liquid refrigerants are reduced pressure by the 1st expansion mechanism 5a, be sent to the heat source side heat exchanger 4 that has as the evaporator function of cold-producing medium, and, by intermediate heat exchanger recurrent canal 94, also be sent to the intermediate heat exchanger 7 (with reference to the some E among Figure 22, Figure 20, Figure 21) that has as the evaporator function of cold-producing medium.Thereby be sent to heat source side heat exchanger 4 low pressure the gas-liquid two-phase state cold-producing medium with carry out heat exchange as the water and air of heating source and be heated then evaporation (with reference to the some A among Figure 22, Figure 20, Figure 21).Thereby the cold-producing medium of gas-liquid two-phase state that is sent to the low pressure of intermediate heat exchanger 7 also carries out heat exchange with water and air as heating source and is heated then evaporation (with reference to the some V among Figure 22, Figure 20, Figure 21).The cold-producing medium of the low pressure that is heated in this heat source side heat exchanger 4 and evaporates is inhaled in the compressing mechanism 2 again via switching mechanism 3.In addition, in this intermediate heat exchanger 7, be heated and the cold-producing medium of the low pressure of evaporating sucks recurrent canal 92 by the 2nd, again be inhaled in the compressing mechanism 2.Adopt above-mentioned this mode to carry out the heating running.
In the structure of this variation, can obtain the action effect same with above-mentioned variation 5, and, when cooling operation, utilize supercooling heat exchanger 96 cold-producing medium (with reference to the some I Figure 22～Figure 24) that is sent to the side of utilization expansion mechanism 5c from reservoir 18 can be cooled to the supercooling state (with reference to Figure 23, Figure 24, in some I, R), therefore, can reduce possibility in the bias current that divides timing to produce to each side of utilization expansion mechanism 5c.
In addition, in this variation, on off state according to switch valve 11,12,92a, begin to switch between the control at cooling operation and refrigeration, that is, switch cold-producing medium non-return state and cold-producing medium return state, but, shown in above-mentioned variation 1, also can replace switch valve 11,12,92a, setting can be switched the intermediate heat exchanger transfer valve 93 of cold-producing medium non-return state and cold-producing medium return state.
And, in the situation of the structure of the heat source unit 1a that adopts variation 2, can obtain especially favourable effect.
(8) variation 6
In above-mentioned embodiment and variation thereof, consisted of the compressing mechanism 2 that compresses successively the two-stage compression formula of the cold-producing medium that the preceding-stage side compression member from two compression member 2c, 2d discharges with the rear-stage side compression member by the compressor 21 of axle two-stage compression structure, but, also can adopt the multi-stage compression mechanisms such as three stage compression types of Duoing than the two-stage compression formula, perhaps, thus also can be connected in series and consist of multi-stage compression mechanism with many compressors that consist of by assembling single compressed parts and/or by assembling compressor that a plurality of compression member consist of.In addition, as connect a plurality of the utilization the situations such as side heat exchanger 6, in the situation that must increase the compressing mechanism ability, also can adopt the compressing mechanism of the multi-stage compression shape arranged side by side that the compressing mechanism by two multi-stage compression formulas more than the system of connection arranged side by side consists of.
For example, also can as shown in figure 25, in the refrigerant line 410 (with reference to Figure 22) in above-mentioned variation 5, replace the compressing mechanism 2 of two-stage compression formula, adopt the compressing mechanism 103 that connects side by side the two-stage compression formula, 104 compressing mechanism 102, form refrigerant line 510.
In this variation, the 1st compressing mechanism 103 is by consisting of the compressor 29 that cold-producing medium carries out two-stage compression with 2 compression member 103c, 103d, and it is connected with the 1st exhaust outlet 103b that the discharge supervisor 102b that is responsible for the 1st suction manifold 103a of 102a branch from the suction of compressing mechanism 102 and are connected with compressing mechanism converges.In this variation, the 2nd compressing mechanism 104 is by consisting of the compressor 30 that cold-producing medium carries out two-stage compression with 2 compression member 104c, 104d, and it is connected with the 2nd exhaust outlet 104b that the discharge supervisor 102b that is responsible for the 2nd suction manifold 104a of 102a branch from the suction of compressing mechanism 102 and are connected with compressing mechanism converges.In addition, compressor 29,30 structure and the compressor 21 in above-mentioned embodiment and the variation thereof are same, therefore, the symbol of the various piece of expression except compression member 103c, 103d, 104c, 104d are replaced as respectively digital 29 and digital 30, herein, the description thereof will be omitted.Compressor 29 sucks cold-producing medium from the 1st suction manifold 103a, after compressing this cold-producing medium that is inhaled into compression member 103c, discharge to the middle arm 81 of the 1st entrance side that consists of intermediate refrigerant pipe 8, make to the cold-producing medium of middle arm 81 discharges of the 1st entrance side and be responsible among the middle arm 83 rear suction compression member 103d of the 82 and the 1st outlet side by consisting of the middle of intermediate refrigerant pipe 8, then further backward the 1st exhaust outlet 103b of compressed refrigerant discharges.Compressor 30 sucks cold-producing medium from the 1st suction manifold 104a, after compressing this cold-producing medium that is inhaled into compression member 104c, discharge to the middle arm 84 of the 2nd entrance side that consists of intermediate refrigerant pipe 8, make to the cold-producing medium of middle arm 84 discharges of the 2nd entrance side and be responsible among the middle arm 85 rear suction compression member 104d of the 82 and the 2nd outlet side by consisting of the middle of intermediate refrigerant pipe 8, then further backward the 2nd exhaust outlet 104b of compressed refrigerant discharges.In this variation, intermediate refrigerant pipe 8 be with from compression member 103d, the compression member 103c that the prime of 104d connects, the cold-producing medium that 104c discharges sucks and compression member 103c, the compression member 103d that the rear class of 104c connects, refrigerant pipe among the 104d mainly comprises: with arm 81 in the middle of the 1st entrance side that discharge one side of the preceding-stage side compression member 103c of the 1st compressing mechanism 103 is connected, with arm 84 in the middle of the 2nd entrance side that discharge one side of the preceding-stage side compression member 104c of the 2nd compressing mechanism 104 is connected, arm 81 in the middle of two entrance sides, the 84 middle supervisors 82 that converge, be responsible for from the centre 82 branches then with the 1st outlet side that suction one side of the rear-stage side compression member 103d of the 1st compressing mechanism 103 is connected in the middle of arm 83, and be responsible for from the centre 82 branches then with the 2nd outlet side that suction one side of the rear-stage side compression member 104d of the 2nd compressing mechanism 104 is connected in the middle of arm 85.In addition, discharging supervisor 102b is to be sent to from the cold-producing medium of compressing mechanism 102 discharges the refrigerant pipe of switching mechanism 3, with discharge the 1st exhaust outlet 103b that supervisor 102b is connected in be provided with the 1st oily separating mechanism 141 and the 1st one-way mechanism 142, be provided with the 2nd oily separating mechanism 143 and the 2nd one-way mechanism 144 with discharging to be responsible among the 2nd exhaust outlet 104b that 102b is connected.The refrigerator oil that the 1st oily separating mechanism 141 is used for being mingled with from the cold-producing medium that the 1st compressing mechanism 103 is discharged is separated suction one side of then sending compressing mechanism 102 back to from cold-producing medium, mainly comprise: the 1st oil eliminator 141a that the refrigerator oil that will be mingled with from the cold-producing medium that the 1st compressing mechanism 103 is discharged is separated from cold-producing medium, be connected with the 1st oil eliminator 141a and the refrigerator oil that will be separated from cold-producing medium is sent the 1st oily recurrent canal 141b of suction one side of compressing mechanism 102 back to.The refrigerator oil that the 2nd oily separating mechanism 143 is used for being mingled with from the cold-producing medium that the 2nd compressing mechanism 104 is discharged is separated suction one side of then sending compressing mechanism 102 back to from cold-producing medium, mainly comprise: the 2nd oil eliminator 143a that the refrigerator oil that will be mingled with from the cold-producing medium that the 2nd compressing mechanism 104 is discharged is separated from cold-producing medium, be connected with the 2nd oil eliminator 143a and the refrigerator oil that will be separated from cold-producing medium is sent the 2nd oily recurrent canal 143b of suction one side of compressing mechanism 102 back to.In this variation, the 1st oily recurrent canal 141b is connected with the 2nd suction manifold 104a, and the 2nd oily recurrent canal 143c is connected with the 1st suction manifold 103a.Therefore, because of the oil mass of refrigerator oil in being stored in the 1st compressing mechanism 103 and be stored between the oil mass of the refrigerator oil in the 2nd compressing mechanism 104 and deviation occurs, thereby produce deviation between the oil mass of the oil mass that causes the refrigerator oil that from the cold-producing medium that the 1st compressing mechanism 103 is discharged, is mingled with and the refrigerator oil that from the cold-producing medium of the 2nd compressing mechanism 104 discharges, is mingled with, in this case, refrigerator oil also can return compressing mechanism 103 more, few one of the oil mass of refrigerator oil in 104, thus deviation between the oil mass of the oil mass that is stored in the refrigerator oil in the 1st compressing mechanism 103 refrigerator oil interior with being stored in the 2nd compressing mechanism 104 eliminated.In addition, in this variation, the 1st suction manifold 103a according to and the fluidic junction of the 2nd oily recurrent canal 143b to and the part that sucks between the fluidic junction of supervisor 102a consist of towards the mode that is descending grade with the fluidic junction that sucks supervisor 102a, the 2nd suction manifold 104a according to and the fluidic junction of the 1st oily recurrent canal 141b to and the part that sucks between the fluidic junction of supervisor 102a consist of towards the mode that is descending grade with the fluidic junction that sucks supervisor 102a.Therefore, even any one in the compressing mechanism 103,104 is in halted state, the refrigerator oil that returns with suction manifold corresponding to the compressing mechanism that is in halted state from the oily recurrent canal corresponding with the compressing mechanism that is turning round also can return supervisor 102a, the situation that the machine oil of the compressing mechanism that difficult generation is being turned round exhausts of sucking.In oily recurrent canal 141b, 143b, be provided with mechanism of decompressor 141c, 143c that the refrigerator oil to flow through oily recurrent canal 141b, 143b reduces pressure.One-way mechanism 142, the 144th is used for allowing cold-producing medium from compressing mechanism 103,104 discharge one effluent to switching mechanism 3, and block refrigerant flows to the mechanism of compressing mechanism 103,104 discharge one side from switching mechanism 3.
So, in this variation, compressing mechanism 102 consists of with lower member by connecting side by side: the 1st compressing mechanism 103 that has two compression member 103c, 103d and consist of according to the mode of the cold-producing medium that compresses successively the preceding-stage side compression member discharge from these compression member 103c, 103d with the rear-stage side compression member; The 2nd compressing mechanism 104 that has two compression member 104c, 104d and consist of according to the mode of the cold-producing medium that compresses successively the preceding-stage side compression member discharge from these compression member 104c, 104d with the rear-stage side compression member.
In this variation, intermediate heat exchanger 7 be arranged on consist of intermediate refrigerant pipe 8 in the middle of among the supervisor 82, the heat exchanger that the cold-producing medium after its cold-producing medium that to be cold-producing medium that the preceding-stage side compression member 103c from the 1st compressing mechanism 103 is discharged discharge with preceding-stage side compression member 104c from the 2nd compressing mechanism 104 converges cools off.That is, intermediate heat exchanger 7 have can be in 2 compressing mechanisms 103,104 function of general cooler.Therefore, the compressing mechanism 102 of the multi-stage compression formula arranged side by side that consists of with the compressing mechanism 103,104 of multi-stage compression formula by the multisystem that is connected in parallel is compared, and can simplify the circuit structure around the compressing mechanism 102 when intermediate heat exchanger 7 is set.
In addition, in the middle of the 1st entrance side that consists of intermediate refrigerant pipe 8, be provided with one-way mechanism 81a in the arm 81, be used for allowing that cold-producing medium is responsible for 82 1 sides from discharge one effluent of the preceding-stage side compression member 103c of the 1st compressing mechanism 103 to the centre, and block refrigerant is responsible for 82 1 effluents to discharge one side of prime side pressure contracting parts 103c from the centre, in the middle of the 2nd entrance side that consists of intermediate refrigerant pipe 8, be provided with one-way mechanism 84a in the arm 84, be used for allowing that cold-producing medium is responsible for 82 1 sides from discharge one effluent of the preceding-stage side compression member 104c of the 2nd compressing mechanism 103 to the centre, and block refrigerant is responsible for 82 1 effluents to discharge one side of prime side pressure contracting parts 104c from the centre.In this variation, use check valve as one-way mechanism 81a, 84a.Therefore, even compressing mechanism 103, in 104 any one is in halted state, the situation of discharge one side of the preceding-stage side compression member of the compressing mechanism that is in halted state can not occur then to arrive by intermediate refrigerant pipe 8 from the cold-producing medium that the preceding-stage side compression member of the compressing mechanism that turning round is discharged yet, therefore, then the preceding-stage side compression member that the cold-producing medium of discharging from the preceding-stage side compression member of the compressing mechanism that the turning round compressing mechanism by being in halted state can not occur arrives suction one side of compressing mechanism 102, be in the situation that the refrigerator oil of the compressing mechanism of halted state flows out, so, when startup is in the compressing mechanism of halted state, be difficult for occuring the situation of refrigerator oil deficiency.In addition, in the situation of the priority that running is set between the compressing mechanism 103,104 (for example, in with the situation of the 1st compressing mechanism 103 as the compressing mechanism of preferential running), meet the above-mentioned compressing mechanism that is in halted state and only be confined to the 2nd compressing mechanism 104, therefore, in the case, the one-way mechanism 84a corresponding with the 2nd compressing mechanism 104 also can only be set.
In addition, as mentioned above, in with the situation of the 1st compressing mechanism 103 as the compressing mechanism of preferential running, intermediate refrigerant pipe 8 is according at compressing mechanism 103, mode general in 104 arranges, therefore, the cold-producing medium of discharging from the preceding-stage side compression member 103c corresponding with the 1st compressing mechanism 103 that is turning round goes out arm 85 in the middle of the side by the 2nd of intermediate refrigerant pipe 8, arrival is in suction one side of rear-stage side compression member 104d of the 2nd compressing mechanism 104 of halted state, like this, in the rear-stage side compression member 104d of the 2nd compressing mechanism 104 of the cold-producing medium of discharging from the preceding-stage side compression member 103c of the 1st compressing mechanism 103 that turning round by being in halted state, then arrive discharge one side of compressing mechanism 102, the refrigerator oil that causes being in the 2nd compressing mechanism 104 of halted state flows out, when startup was in the 2nd compressing mechanism 104 of halted state, the situation of refrigerator oil deficiency might occur.Therefore, in this variation, in the arm 85 switch valve 85a is set in the middle of the 2nd outlet side, in the situation that the 2nd compressing mechanism 104 is in halted state, utilizes this switch valve 85a to block flowing of the cold-producing medium in the arm 85 in the middle of the 2nd outlet side.Like this, the cold-producing medium of discharging from the preceding-stage side compression member 103c of the 1st compressing mechanism 103 that turning round just can't arrive by arm 85 in the middle of the 2nd outlet side of intermediate refrigerant pipe 8 suction one side of the rear-stage side compression member 104d of the 2nd compressing mechanism 104 that is in halted state, therefore, be difficult for to occur in the rear-stage side compression member 104d of the cold-producing medium of discharging from the preceding-stage side compression member 103c of the 1st compressing mechanism 103 that turning round the 2nd compressing mechanism 104 by being in halted state, then arrive discharge one side of compressing mechanism 102, the refrigerator oil that causes being in the 2nd compressing mechanism 104 of halted state flows out such situation, like this, when being in the 2nd compressing mechanism 104 of halted state, startup also is difficult for occuring the situation of refrigerator oil deficiency.In addition, in variation, 85a has used magnetic valve as switch valve.
In addition, in with the situation of the 1st compressing mechanism 103 as the compressing mechanism of preferential running, after the startup of the 1st compressing mechanism 103, then start the 2nd compressing mechanism 104, but, at this moment, intermediate refrigerant pipe 8 is according at compressing mechanism 103, mode general in 104 arranges, therefore, under the pressure from suction one side of the pressure of discharge one side of the preceding-stage side compression member 103c of the 2nd compressing mechanism 104 and rear-stage side compression member 103d becomes than the high state of the pressure of discharge one side of the pressure of suction one side of preceding-stage side compression member 103c and rear-stage side compression member 103d, start, be difficult to stably start the 2nd compressing mechanism 104.Therefore, in this variation, setting is used for connecting the startup bypass pipe 86 of suction one side of discharge one side of preceding-stage side compression member 104c of the 2nd compressing mechanism 104 and rear-stage side compression member 104d, and in this startup bypass pipe 86, switch valve 86a is set, in the situation that the 2nd compressing mechanism 104 is in halted state, utilize this switch valve 86a blocking-up to start flowing of cold-producing medium in the bypass pipe 86, and, utilize switch valve 85a to block flowing of the cold-producing medium in the arm 85 in the middle of the 2nd outlet side, when starting the 2nd compressing mechanism 104, utilizing switch valve 86a that cold-producing medium is flowed through starts in the bypass pipe 86, thereby the cold-producing medium interflow that the cold-producing medium of discharging from the preceding-stage side compression member 104c of the 2nd compressing mechanism 104 is not discharged with preceding-stage side compression member 104c from the 1st compressing mechanism 103, but by starting bypass pipe 86 it is sucked among the rear-stage side compression member 104d, stable moment of the operating condition of compressing mechanism 102 (for example, the suction pressure of compressing mechanism 102, the moment that discharge pressure and intermediate pressure are stable), utilize switch valve 85a that cold-producing medium is flowed through in the middle of the 2nd outlet side in the arm 85, and, utilize switch valve 86a blocking-up to start flowing of cold-producing medium in the bypass pipe 86, thereby can enter common cooling operation.In addition, in this variation, be connected between suction one side of an end that starts bypass pipe 86 and the rear-stage side compression member 104d of the switch valve 85a of the 2nd outlet side centre arm 85 and the 2nd compressing mechanism 104, be connected between the one-way mechanism 84a of arm 84 in the middle of discharge one side of the other end and the preceding-stage side compression member 104c of the 2nd compressing mechanism 104 and the 2nd entrance side, when starting the 2nd compressing mechanism 104, can make it become the state of the impact that the middle splenium that is not vulnerable to the 1st compressing mechanism 103 divides.In addition, in this variation, 86a has used magnetic valve as switch valve.
In addition, operation during for the cooling operation of the aircondition 1 of this variation and heating running, except the compressing mechanism 102 of establishing because replacing compressing mechanism 2, circuit structure around the compressing mechanism 102 becomes slightly complicated and changes outside this point, all the other are substantially identical with the operation (Figure 22～Figure 24, Figure 20, Figure 21 and relevant record thereof) in the above-mentioned variation 5, therefore, the description thereof will be omitted herein.
In the structure of this variation, also can obtain the action effect identical with above-mentioned variation 5.
In addition, in this variation, on off state according to switch valve 11,12,92a, begin to switch between the control at cooling operation and refrigeration, that is, switch cold-producing medium non-return state and cold-producing medium return state, but, shown in above-mentioned variation 1, also can replace switch valve 11,12,92a, setting can be switched the intermediate heat exchanger transfer valve 93 of cold-producing medium non-return state and cold-producing medium return state.
And, in the situation of the structure of the heat source unit 1a that adopts variation 2, can obtain especially favourable effect.
(9) variation 7
In above-mentioned embodiment and variation thereof, consisted of the compressing mechanism 2 that compresses successively the two-stage compression formula of the cold-producing medium of discharging from prime side pressure contracting parts with the rear-stage side compression member by the compressor 21 of axle two-stage compression structure, the perhaps compressor 29 by two the axle two-stage compression structures that are connected in parallel, 30, thereby consist of the compressing mechanism 102 that compresses successively the two-stage compression formula of the cold-producing medium of discharging from prime side pressure contracting parts with the rear-stage side compression member, but, also can be by being connected in series the compressor 22 of single stage compress structure, 23, thus consist of the compressing mechanism that compresses successively the two-stage compression formula of the cold-producing medium of discharging from prime side pressure contracting parts with the rear-stage side compression member.
For example, as shown in figure 26, in the refrigerant line 110 (with reference to Figure 10) in above-mentioned variation 1, also can replace the compressing mechanism 2 that the compressor 21 by axle two-stage compression structure consists of, the employing compressor 22,23 and the compressing mechanism 202 that consists of of single stage compress structure that is connected in parallel, thus refrigerant line 610 formed.
In this variation, compressing mechanism 202 is by utilizing the compressor 22 that comes compressed refrigerant as the compression member 2c of preceding-stage side compression member; With utilize the compression member 2d as the rear-stage side compression member to come the compressor 22 of compressed refrigerant to consist of.Compressor 22 adopts a kind of closed structure of taking in drive motor for compressor 22b, driving shaft 22c and compression member 2c in casing 22a.Drive motor for compressor 22b and driving shaft 22c link.Compressor 23 adopts a kind of closed structure of taking in drive motor for compressor 23b, driving shaft 23c and compression member 2d in casing 23a.Drive motor for compressor 23b and driving shaft 23c link.In this variation, compression member 2c, 2d are rotary or vortex isometric(al) formula compression member.Compressor 202 sucks cold-producing medium from suction line 2a, utilize the compression member 2c of compressor 22 to compress the cold-producing medium that this is inhaled into, then discharge to intermediate refrigerant pipe 8, the cold-producing medium that is discharged to intermediate refrigerant pipe 8 is sucked among the compression member 2d of compressor 23 and continue compressed refrigerant, then discharge to discharge pipe 2b.
In addition, operation for the cooling operation of the aircondition 1 of this variation and heating running etc., except compressing mechanism 2 is replaced by compressing mechanism 202 this point, all the other are substantially identical with the operation (Figure 10, Fig. 1～Fig. 9 and relevant record thereof) in the above-mentioned variation 1, therefore, the description thereof will be omitted herein.
In the structure of this variation, also can obtain the action effect same with above-mentioned variation 1 grade.
(10) variation 8
In above-mentioned embodiment and variation thereof, in intermediate heat exchanger recurrent canal 94, be provided with the intermediate heat exchanger Returning switch valve 94a that is consisted of by magnetic valve, it is closed by control when switching mechanism 3 switches to the cooling operating condition, it is opened by control when switching mechanism 3 switches to the heating operating condition, but, also can replace this intermediate heat exchanger Returning switch valve 94a, flow control valve is set, the flow of the cold-producing medium of the intermediate heat exchanger 7 of the evaporimeter that can controlling flows through can be used as cold-producing medium when heating turns round.
For example, also can as shown in figure 27, in the refrigerant line 610 (with reference to Figure 26) in above-mentioned variation 7, replace intermediate heat exchanger Returning switch valve 94a, the intermediate heat exchanger that is provided as flow control valve returns valve 94b, thereby forms refrigerant line 710.In this variation, return valve 94b as intermediate heat exchanger and used the electric expansion valve that to regulate aperture.In addition, when intermediate heat exchanger being set returning valve 94b, refrigerant pipe 18h between connection heat source side heat exchanger 4 and bridge circuit 17 (more specifically, the branch location of the intermediate heat exchanger recurrent canal 94 among the refrigerant pipe 18h and the part between the heat source side heat exchanger 4) in be arranged on the 1st set among reservoir inlet tube 18a expansion mechanism 5a, thereby guarantee that intermediate heat exchanger returns the front and back differential pressure of valve 94b, perhaps, be arranged on the 2nd set among reservoir outlet 18b expansion mechanism 5b connecting bridge circuit 17 and utilize among the refrigerant pipe 18i between the side heat exchanger 6, thus make the pressure of the cold-producing medium in the reservoir 18 become in the freeze cycle in the middle of press.
In this variation, when cooling operation, cold-producing medium is by bridge circuit 17, according to the 1st expansion mechanism 5a, reservoir 18, the sequential flow of the 2nd expansion mechanism 5b is through refrigerant line 710, when heating turns round, by bridge circuit 17, according to the 2nd expansion mechanism 5b, reservoir 18, the sequential flow of the 1st expansion mechanism 5a is through refrigerant line 710, this point is different (in variation 7 from above-mentioned variation 7, during a running in the running of cooling operation and heating, cold-producing medium is all according to the 1st expansion mechanism 5a, reservoir, the sequential flow of the 2nd expansion mechanism 5b is through refrigerant line 610), except this point, can obtain the action effect identical with above-mentioned variation 7.And, in the structure of this variation, the intermediate heat exchanger that is provided with in intermediate heat exchanger recurrent canal 94 as flow rate regulating valve returns valve 94b, therefore, not only can prevent when cooling operation that cold-producing medium from flowing into intermediate heat exchanger and returning valve 94, and can when adding heat run, distribute effectively the flow of the cold-producing medium of the flow of cold-producing medium of the heat source side heat exchanger 4 of flowing through and the intermediate heat exchanger 7 of flowing through.
(11) variation 9
In the structure of above-mentioned embodiment and variation thereof, also can and utilize at heat source side heat exchanger 4 to arrange between the side heat exchanger 6 to make flow through heat source side heat exchanger 4 and the expansion gear that utilizes the cold-producing medium constant entropy expansion of side heat exchanger 6.
For example, also can as shown in figure 28, in the refrigerant line 710 (with reference to Figure 27) in above-mentioned variation 8, the expansion gear 97 that makes the cold-producing medium constant entropy expansion be set in reservoir inlet tube 18a, thereby form refrigerant line 810.Namely, in this variation, expansion gear 97 is connected by the bridge circuit 17 as rectification circuit, rectification circuit carries out rectification, thereby utilize side heat exchanger 6 and cold-producing medium from utilizing side heat exchanger 6 to flow in any one situation of heat source side heat exchanger 4 at cold-producing medium from heat source side heat exchanger 4 flow directions, cold-producing medium is flowed into from the entrance of expansion gear 97.In this variation, used centrifugal and decompressor positive displacement as expansion gear 97.In addition, in this variation, adopt bridge circuit 17 as rectification circuit, still, be used in combination four phase transfer valves and a plurality of magnetic valve, also can bring into play same function.
In the structure of this variation, also can obtain the action effect same with above-mentioned variation 8 grades.And, in the structure of this variation, when cooling operation, cold-producing medium is by the bridge circuit 17 as rectification circuit, according to the 1st expansion mechanism 5a, expansion gear 97, reservoir 18, the sequential flow of the 2nd expansion mechanism 5b is through refrigerant line 810, when heating turns round, cold-producing medium is by the bridge circuit 17 as rectification circuit, according to the 2nd expansion mechanism 5b, reservoir 18, the sequential flow of the 1st expansion mechanism 5a is through refrigerant line 810, so, during a running in the running of cooling operation and heating, be depressurized in the process of low pressure at the high pressure of cold-producing medium from freeze cycle, the constant entropy of utilizing expansion gear 97 to carry out cold-producing medium reduces pressure (namely, when cooling operation, take Fig. 3 and Fig. 4 as example, point F is on one side to low enthalpy one side and low entropy one side shifting, on one side cold-producing medium is reduced pressure, when heating turns round, take Fig. 6 and Fig. 7 as example, put E on one side to low enthalpy one side and low entropy one side shifting, on one side cold-producing medium is reduced pressure), the coefficient that so just can improve results carries out simultaneously energy and reclaims, therefore, in the time of can further improving cooling operation and the running efficiency in heating when running.In addition, in this variation, also can be when cooling operation, the control of the aperture of the 2nd expansion mechanism 5b of the dirty side by increasing expansion gear 97 and open the 1st and suck the control of returning valve 18g etc., perhaps, when cooling operation, the control of the aperture of the 1st expansion mechanism 5a of the dirty side by increasing expansion gear 97 and open the 1st and suck the control of returning valve 18g etc., increase the decompression amplitude in the expansion gear 97, improve to greatest extent running efficiency.
(12) variation 10
In the structure of above-mentioned variation 9, also can make the reservoir 18 of the exit position that is positioned at expansion gear 97 have function as gas-liquid separator, connect and make the rear-stage side playpipe that in reservoir 18, is returned rear-stage side compression member 2d by the gas refrigerant after the gas-liquid separation, like this, when cooling operation and heating when running, carry out spraying as pressing in the middle of the reservoir 18 of gas-liquid separator.
For example, also can be as shown in figure 29, in the refrigerant line 810 (with reference to Figure 28) in above-mentioned variation 9, in reservoir 18, connect the 2nd rear-stage side playpipe 18c, like this, can carry out pressing injection as the middle of reservoir 18 of gas-liquid separator, thereby form refrigerant line 910.
The 2nd rear-stage side playpipe 18c can carry out the refrigerant pipe that then discharging refrigerant makes the middle pressure of its rear-stage side compression member 2d that returns compressing mechanism 202 spray from reservoir 18, in this variation, arrange according to the top that connects reservoir 18 and the mode of intermediate refrigerant pipe 8 (that is, suction one side of the rear-stage side compression member 2d of compressing mechanism 202).In the 2nd rear-stage side playpipe 18c, be provided with the 2nd rear class injection cock valve 18d and the 2nd rear class and spray one-way mechanism 18e.The 2nd rear class injection cock valve 18d can carry out switching manipulation, and in this variation, it is magnetic valve.The 2nd rear class is sprayed one-way mechanism 18e and is used for allowing that cold-producing medium flows to rear-stage side compression member 2d from reservoir 18, and allows that cold-producing medium flows to reservoir 18 from rear-stage side compression member 2d, in this variation, uses check valve.In addition, the 2nd rear-stage side playpipe 18c and the 1st sucks recurrent canal 18f and forms one in the part of reservoir 18 1 sides.
In the structure of this variation, also can obtain the action effect same with above-mentioned variation 9.And, in the structure of this variation, during a running when the running of cooling operation and heating, make the reservoir 18 that is connected with the outlet of expansion gear 9 have function as gas-liquid separator, make in this reservoir 18 and sprayed (namely by middle pressure that the 2nd rear-stage side playpipe 18c returns rear-stage side compression member 2d by the gas refrigerant after the gas-liquid separation, take Figure 20 and Figure 21 as example, carry out from an I via the stroke of M point of arrival G), so just can reduce the temperature of the middle cold-producing medium of pressing in the freeze cycle that is inhaled into rear-stage side compression member 2d, therefore, can further improve running efficiency.
(13) variation 11
In above-mentioned variation 7～10, in order to carry out the refrigeration corresponding with the air conditioner load of a plurality of conditioned spaces and heating, also can adopt a kind of a plurality of structures that utilize side heat exchanger 6 that are connected in parallel that have.
For example, also can be such as Figure 30 and shown in Figure 31, in above-mentioned variation 9,10 refrigerant line 810,910 (with reference to Figure 28 and Figure 29), have a plurality of (being two) that are connected in parallel herein and utilize side heat exchanger 6, thereby form refrigerant line 1010,1110.Herein, arrange a plurality of when utilizing side heat exchanger 6, each utilizes the flow of the cold-producing medium of side heat exchanger 6 in order to flow through by control, thereby can obtain to utilize freezing load required in the side heat exchanger 6 at each, also can replace the 2nd expansion mechanism 5b, at reservoir 18 with utilize between the side heat exchanger 6, utilize the side heat exchanger 6 corresponding side of the utilization expansion mechanism 5c that arrange with each (that is, the part of being utilized side heat exchanger 6 branches by each in refrigerant pipe 18i).
In the structure of this variation, also can obtain and above-mentioned variation 9, the same action effects such as 10.
(14) variation 12
In above-mentioned variation 7～11, in order to cool off and to make it become the supercooling state being sent to the cold-producing medium that utilizes side heat exchanger 6 and heat source side heat exchanger 4, also subcooler can be set.
For example, also can be shown in figure 32, in the refrigerant line 1010 (with reference to Figure 30) in above-mentioned variation 11, in reservoir outlet 18b, supercooling heat exchanger 96 is set, and via reservoir 18 to (being reservoir 18) between the reservoir outlet 18b the 3rd suction recurrent canal 95 is being set from reservoir inlet tube 18a herein, thereby is forming refrigerant line 1210.
Supercooling heat exchanger 96 is to utilize the cold-producing medium of side heat exchanger 6 to cool off to being sent to each from reservoir 18 via a plurality of (the being two) side of utilization expansion mechanism 5c herein when the cooling operation, and to when heating turns round, returning the heat exchanger that cold-producing medium that valve 94b is sent to heat source side heat exchanger 4 and intermediate heat exchanger 7 cools off from reservoir 18 via the 1st expansion mechanism 5a and intermediate heat exchanger.More specifically, supercooling heat exchanger 96 is the 3rd heat exchangers of heat exchange that suck the cold-producing medium of recurrent canal 95 of flowing through that carry out with suction one side of returning compressing mechanism 2 from reservoir 18 (being suction line 2a).In the 3rd suction recurrent canal 95, be provided with the 3rd suction that to control its aperture and return valve 95a, in supercooling heat exchanger 96, when cooling operation, carry out being sent to the cold-producing medium of the side of utilization expansion mechanism 5c and sucking the 3rd from reservoir 18 returning near flowing through after being depressurized to the low pressure the valve 95a and the 3rd sucking the heat exchange of the cold-producing medium of recurrent canal 95, and carry out from reservoir 18 be sent to cold-producing medium that the 1st expansion mechanism 5a and intermediate heat exchanger return valve 94b with in the 3rd heat exchange that sucks the cold-producing medium that returns near the 3rd suction recurrent canal 95 of flowing through after being depressurized to the low pressure the valve 95a.In this variation, it is electric expansion valve that valve 95a is returned in the 3rd suction.In addition, the 3rd suction recurrent canal 95 and the 1st sucks recurrent canal 18f and forms one in the part of reservoir 18 1 sides.
In the structure of this variation, also can obtain the action effect same with above-mentioned variation 11 grades.And, in the structure of this variation, owing to can be when cooling operation will become the supercooling state from the cold-producing medium that reservoir 18 is sent to each side of utilization expansion mechanism 5c, perhaps when heating turns round will from reservoir 18 be sent to cold-producing medium that the 1st expansion mechanism 5a and intermediate heat exchanger return valve 94b become the supercooling state (, take Figure 23 and Figure 24 as example, carry out from an I to the stroke of putting R), like this, when cooling operation, can reduce to each side of utilization expansion mechanism 5c divides timing issuable bias current, when heating turns round, can reduce and return valve 94b to the 1st expansion mechanism 5a and intermediate heat exchanger and divide timing issuable bias current.
(15) variation 13
In above-mentioned embodiment and variation thereof, adopted the compressing mechanism 2,102,202 of two-stage compression formula, still, also can adopt the multi-stage compression mechanisms such as three stage compression types.
For example, also can be as shown in figure 33, in the refrigerant line 1010 (with reference to Figure 30) in above-mentioned variation 11, the compressing mechanism 22 of employing by being connected in series and consisting of compressing mechanism 202, the compressor 25 that 23 same single stage compress are constructed, 26 and the compressing mechanism 302 of three stage compression types that consist of, in the intermediate refrigerant pipe 8 of the suction side of the outlet side that connects the 1st stage compressor 25 and the 2nd stage compressor 26, arrange with above-mentioned embodiment with and the same intermediate heat exchanger 7 of variation, intermediate heat exchanger bypass pipe 9, the 2nd sucks recurrent canal 92, intermediate heat exchanger transfer valve 93, and intermediate heat exchanger returns valve 94, and, in the intermediate refrigerant pipe 308 of the suction side that connects the 2nd stage compressor 26 and 3rd level compressor 27, arrange and intermediate heat exchanger 7, intermediate heat exchanger bypass pipe 9, the 2nd sucks recurrent canal 92, intermediate heat exchanger transfer valve 93, and intermediate heat exchanger returns the same intermediate heat exchanger 307 of valve 94, intermediate heat exchanger bypass pipe 309, the 2nd sucks recurrent canal 392, intermediate heat exchanger transfer valve 393, and intermediate heat exchanger returns valve 394.
In the structure of this variation, adopted the compressing mechanism 302 of three stage compression types, therefore, when cooling operation, with intermediate heat exchanger transfer valve 93,393 switch to the cold-producing medium non-return state, thereby make intermediate heat exchanger 7,307 have as the middle compression refrigerant in the freeze cycle (from being sent to the cold-producing medium of its rear class side pressure contracting parts 302d after prime side pressure contracting parts 302 are discharged, and from being sent to the cold-producing medium of its rear class side pressure contracting parts 302e after prime side pressure contracting parts 303c discharges) the function of cooler, when heating turns round, with intermediate heat exchanger transfer valve 93,393 switch to the cold-producing medium return state, thereby make intermediate heat exchanger 7,307 have the function as the evaporimeter of the low pressure refrigerant in the freeze cycle (cold-producing medium in utilizing side heat exchanger 6 after the heat radiation), this point is different from above-mentioned variation 11 etc., but, except this point, can obtain the action effect same with above-mentioned variation 11 grades.
(16) other embodiment
Above, with reference to the accompanying drawings, embodiments of the present invention and variation thereof are illustrated, still, concrete structure is not limited to these embodiments and variation thereof, can change in the scope that does not break away from inventive concept.
For example, in above-mentioned embodiment and variation thereof, use as carrying out the heating source of heat exchange or water and the salt solution of cooling source with the cold-producing medium that utilizes side heat exchanger 6 of flowing through, and the secondary heat exchanger that is carried out heat exchange by the water of heat exchange and salt solution and room air in utilizing side heat exchanger 6 is set, and the present invention also can be applicable in the aircondition of this refrigeration-type.
In addition, for the refrigerating plant of other type of above-mentioned box refrigerating air conditioner, as long as use the cold-producing medium in supercritical region work to carry out multi-stage compression formula freeze cycle as cold-producing medium, so, also can use the present invention.
In addition, be not limited to carbon dioxide at the cold-producing medium of supercritical region work, also can use ethene, ethane and nitrogen oxide etc.
Industrial applicibility
Utilize the present invention, having the refrigerant line that can switch the cooling running and add heat run, carry out to obtain high running efficiency in the refrigerating plant of multi-stage compression formula freeze cycle.
Claims (5)
1. a refrigerating plant (1) is characterized in that, comprising:
Compressing mechanism (2,102,202,302), this compressing mechanism (2,102,202,302) has a plurality of compression member, utilizes the rear-stage side compression member in described a plurality of compression member to compress successively the cold-producing medium that the preceding-stage side compression member from described a plurality of compression member is discharged;
As the radiator of cold-producing medium or the heat source side heat exchanger (4) of evaporimeter performance function;
Utilize side heat exchanger (6) as the evaporimeter of cold-producing medium or radiator performance function;
Switching mechanism (3) switches between following two states: according to described compressing mechanism, as the described heat source side heat exchanger of the radiator performance function of cold-producing medium, utilize the order of side heat exchanger to make the cooling operating condition of refrigerant circulation and according to described compressing mechanism, utilize the side heat exchanger, make the heating operating condition of refrigerant circulation as the order of the described heat source side heat exchanger of the evaporimeter performance function of cold-producing medium as the radiator performance function of cold-producing medium described as the evaporimeter performance function of cold-producing medium described; With
Intermediate heat exchanger (7,307), when described switching mechanism is switched to described cooling operating condition, can will be inhaled into as discharging from described preceding-stage side compression member the cooler performance function of the cold-producing medium the described rear-stage side compression member, when described switching mechanism becomes described heating operating condition, can be as in the described evaporimeter performance function of utilizing the cold-producing medium that has carried out heat radiation in the side heat exchanger
Described intermediate heat exchanger (7,307) is arranged on to make the cold-producing medium of discharging from described preceding-stage side compression member to be drawn on the intermediate refrigerant pipe (8,308) the described rear-stage side compression member,
On described intermediate refrigerant pipe, be connected with intermediate heat exchanger bypass pipe (9,309) in the mode of walking around described intermediate heat exchanger,
Described refrigerating plant (1) also comprises: the suction recurrent canal (92,392) that is used for connecting the suction side of an end of described intermediate heat exchanger and described compressing mechanism (2,102,202,302); And be used for connecting and describedly utilize between side heat exchanger (6) and the described heat source side heat exchanger (4) and the intermediate heat exchanger recurrent canal (94,394) of the other end of described intermediate heat exchanger.
2. refrigerating plant as claimed in claim 1 (1) is characterized in that:
When the running that makes described switching mechanism (3) switch to described cooling operating condition begins, make the cold-producing medium of discharging from described preceding-stage side compression member be drawn into described rear-stage side compression member by described intermediate heat exchanger bypass pipe (9,309), and connect the suction side of described intermediate heat exchanger (7,307) and described compressing mechanism (2,102,202,302) by described suction recurrent canal (92,392).
3. such as claim 1 or 2 described refrigerating plants (1), it is characterized in that:
Be provided with flow control valve (94b, 394b) at described intermediate heat exchanger recurrent canal (94,394).
4. such as claim 1 or 2 described refrigerating plants (1), it is characterized in that:
Described heat source side heat exchanger (4) and described the utilization between the side heat exchanger (6), be connected with via commutating circuit (17) and make at described heat source side heat exchanger and the described expansion gear (97) that utilizes between the side heat exchanger cold-producing medium constant entropy expansion of flowing, this commutating circuit (17) is in the situation that cold-producing medium flows to the described side heat exchanger that utilizes from described heat source side heat exchanger, utilize in the situation that the side heat exchanger flows to described heat source side heat exchanger from described with cold-producing medium, all cold-producing medium is carried out rectification so that cold-producing medium flows into from the entrance of described expansion gear.
5. refrigerating plant as claimed in claim 4 (1) is characterized in that:
Be connected with the gas-liquid separator (18) of the gas-liquid separation of carrying out cold-producing medium in the outlet of described expansion gear (97),
Be connected with to make gas refrigerant separated in described gas-liquid separator to turn back to the rear-stage side playpipe (18c) of described rear-stage side compression member at described gas-liquid separator.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
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| JP2008-048904 | 2008-02-29 | ||
| JP2008048904 | 2008-02-29 | ||
| JP2008322497A JP5239824B2 (en) | 2008-02-29 | 2008-12-18 | Refrigeration equipment |
| JP2008-322497 | 2008-12-18 | ||
| PCT/JP2009/053347 WO2009107626A1 (en) | 2008-02-29 | 2009-02-25 | Refrigeration device |
Publications (2)
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| CN101960235A CN101960235A (en) | 2011-01-26 |
| CN101960235B true CN101960235B (en) | 2013-01-02 |
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| CN2009801070403A Active CN101960235B (en) | 2008-02-29 | 2009-02-25 | Refrigeration device |
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| EP (1) | EP2264380B1 (en) |
| JP (1) | JP5239824B2 (en) |
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| CN (1) | CN101960235B (en) |
| AU (1) | AU2009218270B2 (en) |
| WO (1) | WO2009107626A1 (en) |
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| JP5403029B2 (en) * | 2011-10-07 | 2014-01-29 | ダイキン工業株式会社 | Refrigeration equipment |
| JP5403047B2 (en) * | 2011-12-28 | 2014-01-29 | ダイキン工業株式会社 | Refrigeration equipment |
| JP5958022B2 (en) * | 2012-03-30 | 2016-07-27 | ダイキン工業株式会社 | Refrigeration equipment |
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| JP6111655B2 (en) * | 2012-12-26 | 2017-04-12 | ダイキン工業株式会社 | Refrigeration equipment |
| JP2014126284A (en) * | 2012-12-26 | 2014-07-07 | Daikin Ind Ltd | Refrigeration device |
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| JP6334320B2 (en) * | 2014-08-22 | 2018-05-30 | 株式会社Ｎｔｔファシリティーズ | Vapor compression refrigeration cycle |
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| WO2019073517A1 (en) * | 2017-10-10 | 2019-04-18 | 三菱電機株式会社 | Air conditioning device |
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Also Published As
| Publication number | Publication date |
|---|---|
| AU2009218270B2 (en) | 2011-12-22 |
| CN101960235A (en) | 2011-01-26 |
| AU2009218270A1 (en) | 2009-09-03 |
| JP2009229051A (en) | 2009-10-08 |
| KR20100121672A (en) | 2010-11-18 |
| EP2264380A1 (en) | 2010-12-22 |
| US20110005270A1 (en) | 2011-01-13 |
| EP2264380B1 (en) | 2018-04-04 |
| WO2009107626A1 (en) | 2009-09-03 |
| EP2264380A4 (en) | 2015-01-21 |
| JP5239824B2 (en) | 2013-07-17 |
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