CN101932891B - Refrigeration device - Google Patents
Refrigeration device Download PDFInfo
- Publication number
- CN101932891B CN101932891B CN2009801035683A CN200980103568A CN101932891B CN 101932891 B CN101932891 B CN 101932891B CN 2009801035683 A CN2009801035683 A CN 2009801035683A CN 200980103568 A CN200980103568 A CN 200980103568A CN 101932891 B CN101932891 B CN 101932891B
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- Prior art keywords
- compression member
- cold
- producing medium
- intercooler
- stage side
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- 238000005057 refrigeration Methods 0.000 title abstract description 38
- 230000007246 mechanism Effects 0.000 claims abstract description 358
- 230000006835 compression Effects 0.000 claims abstract description 297
- 238000007906 compression Methods 0.000 claims abstract description 297
- 239000003507 refrigerant Substances 0.000 claims abstract description 136
- 238000007599 discharging Methods 0.000 claims description 30
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 26
- 239000008400 supply water Substances 0.000 claims description 10
- 230000002265 prevention Effects 0.000 abstract 1
- 238000009736 wetting Methods 0.000 abstract 1
- 238000001816 cooling Methods 0.000 description 64
- 239000007788 liquid Substances 0.000 description 44
- 239000003921 oil Substances 0.000 description 39
- 238000002347 injection Methods 0.000 description 28
- 239000007924 injection Substances 0.000 description 28
- 239000010721 machine oil Substances 0.000 description 27
- 238000010438 heat treatment Methods 0.000 description 17
- 239000007921 spray Substances 0.000 description 16
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 8
- 238000003825 pressing Methods 0.000 description 8
- 239000000498 cooling water Substances 0.000 description 7
- 230000001143 conditioned effect Effects 0.000 description 6
- 230000006837 decompression Effects 0.000 description 6
- 230000005855 radiation Effects 0.000 description 6
- 238000000926 separation method Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 230000000306 recurrent effect Effects 0.000 description 5
- 229910002092 carbon dioxide Inorganic materials 0.000 description 4
- 239000001569 carbon dioxide Substances 0.000 description 4
- 239000013256 coordination polymer Substances 0.000 description 4
- MWUXSHHQAYIFBG-UHFFFAOYSA-N Nitric oxide Chemical compound O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- 230000005144 thermotropism Effects 0.000 description 3
- 230000001052 transient effect Effects 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 239000012266 salt solution Substances 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- TVEXGJYMHHTVKP-UHFFFAOYSA-N 6-oxabicyclo[3.2.1]oct-3-en-7-one Chemical compound C1C2C(=O)OC1C=CC2 TVEXGJYMHHTVKP-UHFFFAOYSA-N 0.000 description 1
- 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
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 235000019628 coolness Nutrition 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 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
- 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
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
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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
- 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
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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
- 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
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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
- 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
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
-
- 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
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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
- 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
- F25B2400/23—Separators
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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
- F25B2500/00—Problems to be solved
- F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
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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
- 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
Abstract
A refrigeration device for performing a multi-stage compression refrigeration cycle, in which, even if the refrigeration device becomes under operating conditions in which the temperature of a heat source for an intermediate cooler is low, a refrigerant sucked into a rear stage-side compression element does not become wet. An air conditioner (1) has a two-stage compression type compression mechanism (2), a heat source-side heat exchanger (4), a utilization-side heat exchanger (6), an intermediate cooler (7) provided in an intermediate refrigerant pipe (8) for causing a rear stage-side compression element (2d) to suck the refrigerant discharged from a front stage-side compression element (2c), and an intermediate cooler bypassing pipe (9) connected to the intermediate refrigerant pipe (8) so as to bypass the intermediate cooler (7). When the temperature of the heat source for the intermediate cooler (7) or the temperature of the refrigerant at the exit of the intermediate cooler (7) is lower than or equal to the saturation temperature of the refrigerant sent from the front stage-side compression element (2c) to the rear stage-side compression element (2d), the air conditioner (1) uses the intermediate cooler bypassing pipe (9) to perform wetting prevention control for preventing the refrigerant from flowing to the intermediate cooler (7).
Description
Technical field
The present invention relates to a kind of refrigerating plant, particularly carry out the refrigerating plant of multi-stage compression formula kind of refrigeration cycle.
Background technology
In the past,, the aircondition that carries out the circulation of secondary compression-type refrigeration shown in the patent documentation 1 is arranged as a routine refrigerating plant that carries out multi-stage compression formula kind of refrigeration cycle.This aircondition mainly comprises: compressor, outdoor heat converter, expansion valve and indoor heat converter with two compression member that are connected in series.
Patent documentation 1: TOHKEMY 2007-232263 communique
Summary of the invention
The refrigerating plant of the 1st invention comprises: the heat source side heat exchanger, utilize side heat exchanger, intercooler and intercooler bypass pipe.Compressing mechanism has a plurality of compression member, and uses back level compression member to compress the cold-producing medium that the preceding-stage side compression member from a plurality of compression member is discharged successively.Said here " compressing mechanism " comprises through connecting the compressing mechanism that multiple compressors forms, and compressor comprises the assembled all-in-one-piece compressor of a plurality of compression member and assembling single compressed parts and the compressor that constitutes and/or assemble a plurality of compression member and the compressor that constitutes.In addition; " compressing the cold-producing medium that the preceding-stage side compression member from a plurality of compression member is discharged successively with the rear-stage side compression member " is not two compression member that only refer to that " preceding-stage side compression member " and " rear-stage side compression member " is connected in series; And be meant that a plurality of compression member are connected in series, and the relation between each compression member is meant to have above-mentioned " the preceding-stage side compression member " and the relation of " rear-stage side compression member ".Intercooler is set to be used for making from contract cold-producing medium that parts discharge of prime side pressure and sucks in the intermediate refrigerant pipe the rear-stage side compression member and can discharge the cooler that be inhaled into the cold-producing medium the rear-stage side compression member then as the parts that contract from the prime side pressure.The intercooler bypass pipe is connected with the intermediate refrigerant pipe, with the bypass intercooler.For this refrigerating plant; When becoming from the prime side pressure parts that contract, the outlet refrigerant temperature of the heat source temperature of middle cooler or intercooler is sent to the saturation temperature of cold-producing medium of rear-stage side compression member when following; Utilize the intercooler bypass pipe, do not make the flow through damp proof control of intercooler of cold-producing medium.
In traditional aircondition; The cold-producing medium of discharging from the rudimentary compression member of compressor is inhaled into the rear-stage side compression member of compressor then by further compression, therefore, and the increase in temperature of the cold-producing medium of discharging from the rear-stage side compression member of compressor; For example; In the outdoor heat converter that has as the cooler function of cold-producing medium, will increase as the empty G&W of thermal source and the temperature difference between the cold-producing medium, the 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; This method below the employing: can be arranged on as the intercooler that the parts that contract from the prime side pressure are discharged the cooler be inhaled into the cold-producing medium the rear-stage side compression member then and be used for the refrigeration that the parts that contract from the prime side pressure are discharged is sucked the intermediate refrigerant pipe of rear-stage side compression member; Reduce the temperature of the cold-producing medium that is inhaled into the rear-stage side compression member like this; Thereby reduce from the temperature of the cold-producing medium of rear-stage side compression member discharge, reduce the radiation loss in the outdoor heat converter.
But; In this structure, if become the low operating condition of temperature, so as the empty G&W of intercooler thermal source; From parts are contracted in the prime side pressure, discharging the cold-producing medium that is inhaled into then in the rear-stage side compression member just might be by sub-cooled; Like this, the cold-producing medium that is inhaled in the rear-stage side compression member will become moisture state, and the reliability of compressor might be damaged.
Therefore; In this refrigerating plant; When becoming from the prime side pressure parts that contract, the outlet refrigerant temperature of the heat source temperature of middle cooler or intercooler is sent to the saturation temperature of cold-producing medium of rear-stage side compression member when following; Use the intercooler bypass pipe, make the do not flow through damp proof control of intercooler of cold-producing medium.
Like this, in this refrigerating plant, under the low operating condition of the heat source temperature of intercooler, can prevent that also the cold-producing medium that is inhaled in the rear-stage side compression member from becoming moisture state.
The refrigerating plant of the 2nd invention, in the refrigerating plant of the 1st invention, intercooler is with the heat exchanger of air as thermal source.
In this refrigerating plant, under the operating condition low, can prevent that also the cold-producing medium that is inhaled in the rear-stage side compression member from becoming moisture state as the air themperature of intercooler thermal source.
The refrigerating plant of the 3rd invention, in the refrigerating plant of the 1st invention, intercooler is with the heat exchanger of water as thermal source, in damp proof control, also is used for stopping to supply water to intercooler.
In this refrigerating plant,, can prevent that also the cold-producing medium that is inhaled into the rear-stage side compression member from becoming moisture state even become the low operating condition of temperature as the water of the thermal source of intercooler.And, in this refrigerating plant, in damp proof control, stop to supply water to intercooler, therefore, can prevent that cold-producing medium in the intercooler from becoming liquid condition and accumulate in wherein.
The refrigerating plant of the 4th invention comprises: compressing mechanism, heat source side heat exchanger, utilize side heat exchanger and intercooler.Compressing mechanism has a plurality of compression member, and uses the rear-stage side compression member to compress the cold-producing medium that the preceding-stage side compression member from a plurality of compression member is discharged successively.Said here " compressing mechanism " is meant and comprises through connecting the compressing mechanism that multiple compressors forms, and compressor comprises the assembled all-in-one-piece compressor of a plurality of compression member and assembling single compressed parts and the compressor that constitutes and/or assemble a plurality of compression member and the compressor that constitutes.In addition; " compressing the cold-producing medium that the preceding-stage side compression member from a plurality of compression member is discharged successively with the rear-stage side compression member " is not only to refer to that " preceding-stage side compression member " reaches two compression member that " rear-stage side compression member " is connected in series; And be meant that a plurality of compression member are connected in series, and the relation between each compression member is meant to have above-mentioned " the preceding-stage side compression member " and the relation of " rear-stage side compression member ".Intercooler is set to be used for making from the prime side pressure and contracts that cold-producing medium that parts discharge sucks in the intermediate refrigerant pipe the rear-stage side compression member and can discharge and will be inhaled into the cooler of the cold-producing medium the rear-stage side compression member from the prime side pressure parts that contract as cooling.For this refrigerating plant; When becoming from the prime side pressure parts that contract, the outlet refrigerant temperature of the heat source temperature of middle cooler or intercooler is sent to the saturation temperature of cold-producing medium of rear-stage side compression member when following, the damp proof control that the flow of the water of the intercooler of flowing through is reduced.Said here " flow of the water of the intercooler of flowing through is reduced " also comprises " stopping to supply water to intercooler ".
In traditional aircondition; Because the cold-producing medium of discharging from the rudimentary compression member of compressor is inhaled into the rear-stage side compression member of compressor then by further compression, therefore, the increase in temperature of the cold-producing medium of discharging from the rear-stage side compression member of compressor; For example; In the outdoor heat converter of the cooler that can be used as cold-producing medium, will increase as the empty G&W of thermal source and the temperature difference between the cold-producing medium, the radiation loss in the outdoor heat converter increases; Therefore, the such problem of high running efficiency will appear being difficult to obtain.
In order to address this problem; This method below the employing: can be arranged on as the intercooler that the parts that contract from the prime side pressure are discharged the cooler be inhaled into the cold-producing medium the rear-stage side compression member then and be used for the refrigeration that the parts that contract from the prime side pressure are discharged is sucked the intermediate refrigerant pipe of rear-stage side compression member; Reduce the temperature that is inhaled into the cold-producing medium in the rear-stage side compression member like this; Thereby reduce from the temperature of the cold-producing medium of rear-stage side compression member discharge, reduce the radiation loss in the outdoor heat converter.
But; In this structure, if become the low operating condition of temperature, so as the empty G&W of intercooler thermal source; From parts are contracted in the prime side pressure, discharging the cold-producing medium that is inhaled into then in the rear-stage side compression member just might be by sub-cooled; Like this, the cold-producing medium that is inhaled in the rear-stage side compression member just might become moisture state, and the reliability of compressor is damaged.
Therefore; In this refrigerating plant; When becoming from the prime side pressure parts that contract, the outlet refrigerant temperature of the heat source temperature of middle cooler or intercooler is sent to the saturation temperature of cold-producing medium of rear-stage side compression member when following, the damp proof control that the flow of the water of the intercooler of flowing through is reduced.
Like this, in this refrigerating plant, under the operating condition low, can prevent that also the cold-producing medium that is inhaled in the rear-stage side compression member from becoming moisture state as the temperature of the water of intercooler thermal source.
The refrigerating plant of the 5th invention; In the refrigerating plant of the 4th invention; The control flow of water of intercooler of flowing through also in said damp proof control, thus it is high to make the outlet refrigerant temperature of intercooler be sent to the saturation temperature of cold-producing medium of rear-stage side compression member than the parts that contract from the prime side pressure.
In this refrigerating plant; In damp proof control, the saturation temperature of cold-producing medium that is sent to the rear-stage side compression member for the outlet refrigerant temperature that makes intercooler than the parts that contract from the prime side pressure is high, also the control flow of water of intercooler of flowing through; Therefore; Not only can prevent that the cold-producing medium that is inhaled in the rear-stage side compression member from becoming moisture state, and, the temperature that is inhaled into the cold-producing medium in the rear-stage side compression member can greatly be reduced; So just the temperature of the cold-producing medium of from the rear-stage side compression member, discharging can be reduced, and the consumption of power of compressing mechanism can be reduced.
Refrigerating plant in the 6th invention; In any one refrigerating plant (1) of the 1st～the 5th invention; It also comprises: to after being compressed mechanism compression, flowing through heat source side heat exchanger and utilize the cold-producing medium between the side heat exchanger to shunt, make it return the rear-stage side playpipe of rear-stage side compression member then.
In this refrigerating plant; Except using intercooler to being inhaled into cold-producing medium in the rear-stage side compression member cools off; Also, so just can further reduce the temperature that is inhaled into the cold-producing medium in the rear-stage side compression member, therefore through having used the intermediate injection of rear-stage side playpipe; Can further reduce from the temperature of the cold-producing medium of compressing mechanism discharge, and can reduce the consumption of power of compressing mechanism.
Description of drawings
Fig. 1 is the structure sketch plan as the aircondition of an embodiment of refrigerating plant of the present invention.
Pressure-enthalpy the line chart of the kind of refrigeration cycle when Fig. 2 is the expression cooling operation.
Temperature-entropy the line chart of the kind of refrigeration cycle when Fig. 3 is the expression cooling operation.
Fig. 4 is the structure sketch plan of the aircondition in the variation 1.
Fig. 5 is the structure sketch plan of the aircondition in the variation 1.
Fig. 6 is the structure sketch plan of the aircondition in the variation 2.
Fig. 7 is the structure sketch plan of the aircondition in the variation 4.
Pressure-enthalpy the line chart of kind of refrigeration cycle when Fig. 8 is the cooling operation of the aircondition of expression in the variation 4.
Temperature-entropy the line chart of kind of refrigeration cycle when Fig. 9 is the cooling operation of the aircondition of expression in the variation 4.
Figure 10 is pressure-enthalpy line chart that the system of the aircondition in the expression variation 4 warms up kind of refrigeration cycle when turning round.
Figure 11 is temperature-entropy line chart that the system of the aircondition in the expression variation 4 warms up kind of refrigeration cycle when turning round.
Figure 12 is the structure sketch plan of the aircondition in the variation 4.
Figure 13 is the structure sketch plan of the aircondition in the variation 5.
Figure 14 is the structure sketch plan of the aircondition in the variation 5.
Symbol description
1, aircondition (refrigerating plant)
2,102, compressing mechanism
4, the heat source side heat exchanger
6, utilize the side heat exchanger
7, intercooler
8, the intermediate refrigerant pipe
9, the intercooler bypass pipe
18c, the 1st rear-stage side playpipe
19, the 2 rear-stage side playpipes
The specific embodiment
Below, according to accompanying drawing, 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 carry out cooling operation, and it uses at the cold-producing medium of supercritical region work (being carbon dioxide here) and carries out the circulation of secondary compression-type refrigeration.
The refrigerant line 10 of aircondition 1 mainly comprises: compressing mechanism 2, heat source side heat exchanger 4, expansion mechanism 5, utilize side heat exchanger 6 and intercooler 7.
In this embodiment, compressing mechanism 2 constitutes by using two compression member that cold-producing medium is carried out secondary compressor for compressing 21.Compressor 21 adopts a kind of closed structure that in casing 21a, holds drive motor for compressor 21b, driving shaft 21c and compression member 2c, 2d.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 an a kind of so-called secondary compressed configuration: two compression member 2c, 2d and driving shaft 21c link, and two compression member 2c, 2d all are compressed machine drive motors 21b rotation and drive.In this embodiment, compression member 2c, 2d are rotary or the positive displacement compression member of vortex etc.Compressor 21 sucks cold-producing medium from suction line 2a; Utilize this cold-producing medium that is inhaled into of compression member 2c compression; Discharge to intermediate refrigerant pipe 8 then, the cold-producing medium that is discharged to intermediate refrigerant pipe 8 is sucked among the compression member 2d continue compressed refrigerant, discharge to discharge pipe 2b then.Here, intermediate refrigerant pipe 8 is the refrigerant pipes the compression member 2d that cold-producing medium sucks with the rear-stage side of compression member 2c is connected that is used for the compression member 2c that is connected from the preceding-stage side with compression member 2d is discharged.In addition, discharge pipe 2b is used for the cold-producing medium of discharging from compressing mechanism 2 is sent to the refrigerant pipe of heat source side heat exchanger 4, and oil content disembark structure 41 and unidirectional mechanism 42 are set in discharge pipe 2b.The oil content structure 41 of disembarking is used for the refrigerating machine oil of from compressing mechanism 2, discharging with cold-producing medium separated from cold-producing medium and makes its suction of returning compressing mechanism 2 one side then, and it mainly comprises: the oil eliminator 41a that will from cold-producing medium, separate with the refrigerating machine oil that cold-producing medium is discharged from compressing mechanism 2, be connected with oil eliminator 41a and make refrigerating machine oil separated from cold-producing medium return the oil return pipe 41b of the suction line 2a of compressing mechanism 2.The mechanism of decompressor 41c that refrigerating machine oil to the oil return pipe 41b that flows through reduces pressure is set in oil return pipe 41b.In this embodiment, mechanism of decompressor 41c uses capillary.Unidirectional mechanism 42 is used for allowing the discharge one effluent thermotropism source heat exchanger 4 of cold-producing medium from compressing mechanism 2, and is used for block refrigerant and flows to discharge one side of compressing mechanism 2 from heat source side heat exchanger 4, in this embodiment, uses check valve.
In this embodiment, compressing mechanism 2 has two compression member 2c, 2d, in the rear-stage side compression member, compresses the cold-producing medium that the preceding-stage side compression member from these compression member 2c, 2d is discharged successively.
Heat source side heat exchanger 4 is the heat exchangers that can be used as the cooler of cold-producing medium.One end of heat source side heat exchanger 4 is connected with compressing mechanism 2, and the other end is connected with expansion mechanism 5.Heat source side heat exchanger 4 is with the heat exchanger of air as thermal source (that is cooling source).Air as thermal source is supplied to heat source side heat exchanger 4 through heat source side fan not shown in the figures.
Utilizing side heat exchanger 6 is the heat exchangers that can be used as the heater of cold-producing medium.Utilize an end of side heat exchanger 6 to be connected with expansion mechanism 5, the other end is connected with compressing mechanism 2.Utilizing side heat exchanger 6 is with the heat exchanger of empty G&W as thermal source (that is heating source).
Intercooler 7 is set in the intermediate refrigerant pipe 8, and it is the heat exchanger that can discharge the cooler that is inhaled into the cold-producing medium the compression member 2d then as the parts 2c that contracts from the prime side pressure.Intercooler 7 is with the heat exchanger of air as thermal source (that is cooling source).Air as thermal source is supplied to intercooler 7 through heat source side fan not shown in the figures.In addition, intercooler 7 is integrally formed with heat source side heat exchanger 4 sometimes, in the case, also supplies with the air as thermal source through heat source side fan shared in heat source side heat exchanger 4 and middle cooling tube 7 sometimes.So intercooler 7 is not the cold-producing medium that use circulates in refrigerant line 10, in this, it is the cooler that can use external heat source.
In addition, intermediate refrigerant pipe 8 is connected with intercooler bypass pipe 9, thus bypass intercooler 7.This intercooler bypass pipe 9 is flow through refrigerant pipes of flow of cold-producing medium of intercooler 7 of restriction.In intercooler bypass pipe 9, be provided with intercooler bypass shut off valve 11.In this embodiment, intercooler bypass cock valve 11 is magnetic valves.In this embodiment, the such temporary transient running of the damp proof control of after carrying out, stating, this intercooler bypass cock valve 11 is closed basically.
In addition; In intermediate refrigerant pipe 8; From position (that is the part of the connecting portion of outlet one side of connecting portion to the intercooler 7 of the inlet side of intercooler 7 and intercooler bypass pipe 9) cooler switch valve 12 is being set with connecting portion to intercooler 7 one sides of intercooler bypass pipe 9.This cooler switch valve 12 is used for limiting the flow of cold-producing medium of intercooler 7 of flowing through.In this embodiment, cooler switch valve 12 is magnetic valves.In this embodiment, the such temporary transient running of the damp proof control of after carrying out, stating, this cooler switch valve 12 is opened basically.In addition, in this embodiment, cooler switch valve 12 is set at the position of the inlet side of intercooler 7.
In addition; In intermediate refrigerant pipe 8, be provided with unidirectional mechanism 15; Be used for allowing cold-producing medium from prime side pressure discharge one effluent level side pressure suction one side of parts 2d that contracts backward of parts 2c that contracts, and be used for block refrigerant from discharge one effluent of rear-stage side compression member 2d to the prime side pressure parts 2c that contracts.In this embodiment, unidirectional mechanism 15 is check valves.In addition, in this embodiment, unidirectional mechanism 15 is set at from the part of the connecting portion of outlet one side of the intercooler 7 of middle refrigerant pipe 8 to it and intercooler bypass pipe 9.
And, in aircondition 1, be provided with various sensors.Specifically, be provided with the intercooler outlet temperature sensor 52 of the refrigerant temperature in the outlet that detects intercooler 7 in the outlet of intercooler 7.In aircondition 1, be provided with the air temperature sensor 53 that detects as the temperature of the air of the thermal source of intercooler 7.In intermediate refrigerant pipe 8, be provided with the intermediate pressure sensor 54 of intermediate pressure that detects as the compressing mechanism of the pressure of the cold-producing medium of the intermediate refrigerant pipe 8 of flowing through.In addition, expression among the figure here, aircondition 1 has the control part of the operation of various pieces such as being used for controlling the compressing mechanism 2 that constitutes aircondition 1, expansion mechanism 5, intercooler bypass cock valve 11, cooler switch valve 12.
(2) operation of aircondition
Below, use Fig. 1～Fig. 3, the operation of the aircondition 1 of this embodiment is described.Here, the temperature-entropy line chart of the kind of refrigeration cycle the when pressure-enthalpy line chart of the kind of refrigeration cycle when Fig. 2 is the expression cooling operation, Fig. 3 are the expression cooling operation.In addition, the control of the running in the following cooling operation and prevent to be inhaled into the control that cold-producing medium in the rear-stage side compression member becomes moisture state according to the cooling of intercooler 7 and carry out through above-mentioned control part (not shown).In addition; In following explanation, the high pressure (that is the pressure of the some D among Fig. 2,3, D ', E) in " high pressure " expression kind of refrigeration cycle; Low pressure in " low pressure " expression kind of refrigeration cycle (promptly; Some A among Fig. 2,3, the pressure of F), the intermediate pressure (that is, the some B1 among Fig. 2,3, the pressure of C1) in " intermediate pressure " expression kind of refrigeration cycle.
When cooling operation, the aperture of expansion mechanism 5 is conditioned.Cooler switch valve 12 is opened, and perhaps the intercooler bypass cock valve 11 of intercooler bypass pipe 9 is closed, so intercooler 7 just becomes can be as the state of cooler.
If drive compression mechanism 2 under the state of this refrigerant line 10; So; Low pressure refrigerant (with reference to the some A among Fig. 1～Fig. 3) is inhaled into the compressing mechanism 2 from suction line 2a; At first, be compressed after parts 2c is compressed to intermediate pressure, discharge (with reference to the some B1 among Fig. 1～Fig. 3) to intermediate refrigerant pipe 8.The compacting cryogen carries out heat exchange be cooled thereby (with reference to the some C1 among Fig. 1～Fig. 3) with air as thermal source in the middle of from this preceding-stage side compression member 2c, being discharged from intercooler 7.Then, the cold-producing medium that in this intercooler 7, is cooled is inhaled into back quilt continuation compression among the compression member 2d that is connected with the rear-stage side of compression member 2c, discharges (with reference to the some D Fig. 1～Fig. 3) from compressing mechanism 2 to discharge pipe 2b.Here, the high-pressure refrigerant that is discharged from from compressing mechanism 2 is compressed into the pressure above critical pressure (that is the critical pressure Pcp among the critical point CP shown in Figure 2) according to the secondary squeeze operation of compression member 2c, 2d.The high-pressure refrigerant that is discharged from from this compressing mechanism 2 flows into and constitutes the disembark oil eliminator 41a of structure 41 of oil content, and the refrigerating machine oil that is mixed in wherein is separated.In addition; The refrigerating machine oil that in oil eliminator 41a, from high-pressure refrigerant, is separated flows into and constitutes the disembark oil return pipe 41b of structure 41 of oil content; Return the suction line 2a of compressing mechanism 2 after being arranged on the mechanism of decompressor 41c decompression among the oil return pipe 41b, and sucked once more in the compressing mechanism 2.Then, in oil content was disembarked structure 41, being mixed in that high-pressure refrigerant after separated the going out of refrigerating machine oil wherein is sent to through unidirectional mechanism 42 can be as the heat source side heat exchanger 4 of the cooler of cold-producing medium.The high-pressure refrigerant that is sent to heat source side heat exchanger 4 in heat source side heat exchanger 4 with carry out heat exchange be cooled thereby (with reference to the some E among Fig. 1～Fig. 3) as the water of cooling source or air.The high-pressure refrigerant that in heat source side heat exchanger 4, is cooled becomes the cold-producing medium of the gas-liquid two-phase state of low pressure after being inflated mechanism 5 decompression, and be sent to can be as the heater of cold-producing medium utilize side heat exchanger 6 (with reference to the some F among Fig. 1～Fig. 3).Thereby the cold-producing medium that is sent to the low-pressure gas-liquid two phase states that utilize side heat exchanger 6 in utilizing side heat exchanger 6 with carry out heat exchange as the water of heating source or air and be heated evaporation (with reference to the some A among Fig. 1～Fig. 3) then.Utilize at this that heated low pressure refrigerant is sucked in the compressing mechanism 2 once more in side heat exchanger 6.Adopt above-mentioned this mode to carry out cooling operation.
In aircondition 1; In being used for, intercooler 7 is set, and in cooling operation, opens cooler switch valve 12 the intermediate refrigerant pipe 8 among the cold-producing medium suction compression member 2d that from compression member 2c, discharges; Perhaps close the intercooler bypass cock valve 11 of intercooler bypass pipe 9; So intercooler 7 becomes can be as the state of cooler, therefore; With the situation that intercooler 7 is not set (in the case; In Fig. 2, Fig. 3, carry out kind of refrigeration cycle according to the order of an an an an A → B1 → D ' → E → F) to compare, the temperature that is inhaled into the cold-producing medium among the rear-stage side compression member 2d of compression member 2c descends (with reference to some B1, the C1 among Fig. 3), the temperature of the cold-producing medium that is discharged from from compression member 2d also can descend (with reference to some D, the D ' Fig. 3).Therefore; In this aircondition 1; In the heat source side heat exchanger 4 of the cooler that can be used as high-pressure refrigerant, compare with the situation that intercooler 7 is not set, not only can dwindle the temperature difference as water or the air and the cold-producing medium of cooling source; And can reduce the radiation loss of the area size that the some B1, D ', D, the C1 that are equivalent to link among Fig. 3 constituted, therefore can improve running efficiency.
(damp proof control)
In the cooling operation that the compacting cryogen carries out simultaneously in the middle of cooling off with above-mentioned intercooler 7; If become the low operating condition of air as the thermal source of intercooler 7; So, from the prime side pressure contract parts 2c discharge the cold-producing medium be inhaled into then the rear-stage side compression member 2d just might be by sub-cooled, like this; The cold-producing medium that is inhaled among the rear-stage side compression member 2d becomes moisture state, and the reliability of compressing mechanism 2 might be damaged.
Therefore; In this embodiment; Be sent to the saturation temperature of cold-producing medium of rear-stage side compression member 2d when following when the heat source temperature of middle cooler 7 becomes from the prime side pressure parts 2c that contracts, use intercooler bypass pipe 9 to make the do not flow through damp proof control of intercooler 7 of cold-producing medium.Specifically; In this embodiment; If become through below the saturation temperature that obtains behind the compressing mechanism intermediate pressure that is detected by intermediate pressure sensor 54 that converts as the air themperature of the thermal source of the intercooler that is detected by air temperature sensor 53 7; So, open the intercooler bypass cock valve 11 of intercooler bypass pipe 9 and close cooler switch valve 12 simultaneously, like this; Flow into suction one side of rear-stage side compression member 2d from contract cold-producing medium that parts 2c discharges of prime side pressure through intercooler bypass pipe 9, the compacting cryogen intercooler 7 of not flowing through in the middle of so just making.In addition, if use the described cold-producing medium of this embodiment, so in supercritical region work; Increase from the contract pressure of the cold-producing medium that parts 2c discharges of prime side pressure, also surpass the operating condition of critical pressure (that is the critical pressure Pcp among the critical point CP shown in Figure 2) sometimes by the intermediate pressure that possibly become compressing mechanism; But; Under this operating condition, not only in high-pressure refrigerant, in centre compacting cryogen, there is not the such notion of saturation state yet; Therefore, needn't carry out above-mentioned damp proof control.Therefore, in this damp proof control, before judging whether temperature as the air of thermal source becomes below the saturation temperature of cold-producing medium that the parts 2c that contracts from the prime side pressure is sent to rear-stage side compression member 2d; Judge whether the compressing mechanism intermediate pressure is lower than critical pressure, if the compressing mechanism intermediate pressure is more than critical pressure, so; Make the cold-producing medium intercooler 7 of flowing through; Reduce the temperature that is inhaled into the cold-producing medium among the rear-stage side compression member 2d, if the compressing mechanism intermediate pressure is lower than critical pressure, so as far as possible; As stated; Whether judgement becomes below the saturation temperature that the compressing mechanism intermediate pressure that detected by intermediate pressure sensor 54 through converting obtains as the air themperature of the thermal source of the intercooler that is detected by air temperature sensor 53 7, if become through below the saturation temperature that obtains behind the conversion compressing mechanism intermediate pressure, so as the air themperature of the thermal source of intercooler 7; The compacting cryogen intercooler 7 of not flowing through in the middle of making; If than high, so, make the cold-producing medium intercooler 7 of flowing through through the saturation temperature that obtains behind the conversion compressing mechanism intermediate pressure as the air themperature of the thermal source of intercooler 7.
So; In the aircondition 1 of this embodiment; When the air themperature as the thermal source of intercooler 7 become the parts 2c that contracts from the prime side pressure be sent to rear-stage side compression member 2d in the middle of the saturation temperature of compacting cryogen when following; Use intercooler bypass pipe 9 to make the cold-producing medium intercooler 7 damp proof controls of not flowing through; Therefore, even become the low operating condition of air themperature, can prevent that also the cold-producing medium that is inhaled among the rear-stage side compression member 2d from becoming moisture state as the thermal source of intercooler 7.
In addition; In this aircondition 1; When becoming from the prime side pressure parts 2c that contracts, the air themperature as the thermal source of intercooler 7 is sent to the saturation temperature of cold-producing medium of rear-stage side compression member 2d when following; Be closed in the cooler switch valve 12 that the entrance side of intercooler 7 is provided with, therefore, can make from the prime side pressure cold-producing medium that parts 2c discharges that contracts all to flow into the intercooler bypass pipe 9; And the compacting cryogen flows into the intercooler 7 and accumulates in the intercooler 7 from the entrance side of middle cooler 7 in the middle of can prevent to flow through intermediate refrigerant pipe 8 and the intercooler bypass pipe 9.And; In this embodiment; Outlet side at intercooler 7 is provided with unidirectional mechanism 15; Therefore, can prevent to flow through intermediate refrigerant pipe 8 and intercooler bypass pipe 9 in the middle of the compacting cryogen flow into the intercooler 7 and accumulate in the intercooler 7 from the outlet side of middle cooler 7.Particularly intercooler 7 is integrally formed with heat source side heat exchanger 4, and, through general heat source side fan (not shown) in heat source side heat exchanger 4 and intercooler 7; Thermotropism source heat exchanger 4 and the air of intercooler 7 supplies as thermal source are in this structure, as long as the air that thermotropism source heat exchanger 4 is supplied with as thermal source; So; Also continue to supply with the air as thermal source to intercooler 7, like this, middle compacting cryogen just might flow in the intercooler 7 and accumulate in the intercooler 7; Therefore, it is very effective with unidirectional mechanism 15 cooler switch valve 12 to be set.
In addition; Replacement according to the air themperature as the thermal source of intercooler 7 whether become from the prime side pressure contract parts 2c be sent to rear-stage side compression member 2d in the middle of the saturation temperature of compacting cryogen judge whether the mode of the damp proof control of needs to get off, also can according to the refrigerant temperature of the outlet of intercooler 7 (temperature of the cold-producing medium that is here detected by intercooler outlet temperature sensor 52) whether become from the prime side pressure contract parts 2c be sent to rear-stage side compression member 2d in the middle of the saturation temperature of compacting cryogen need to judge whether damp proof control to get off.
(3) variation 1
In the above-described embodiment,, used, but, also can use with the heat exchanger of water as thermal source as intercooler 7 with the heat exchanger of air as thermal source as intercooler 7.
For example; As shown in Figure 4; Supply water to intercooler 7 through middle cooling water pipe arrangement 14; Judgement as the temperature of the water of the thermal source of intercooler 7 (here being the temperature of the water that is supplied to intercooler 7 that detects by cooling-water temperature sensor 58) in the water inlet side setting of intercooler 7 whether be contract from the prime side pressure parts 2c be sent to rear-stage side compression member 2d in the middle of below the saturation temperature of compacting cryogen; Perhaps; The temperature of the cold-producing medium of intercooler 7 outlet (here being the temperature of the cold-producing medium that detects by intercooler outlet temperature sensor 52) whether be from the prime side pressure contract parts 2c be sent to rear-stage side compression member 2d in the middle of below the saturation temperature of compacting cryogen, be sent to below the saturation temperature of cold-producing medium of rear-stage side compression member 2d, so if judge that temperature as the cold-producing medium of the temperature of the water of the thermal source of intercooler 7 or intercooler 7 outlets becomes from the prime side pressure parts 2c that contracts; Same with above-mentioned embodiment; Open the intercooler bypass cock valve 11 of intercooler bypass pipe 9, close cooler switch valve 12 simultaneously, like this; Flow into suction one side of rear-stage side compression member 2d from contract cold-producing medium that parts 2c discharges of prime side pressure through intercooler bypass pipe 9, suppress the do not flow through damp proof control of intercooler 7 of cryogen in the middle of so also can making.
In the structure of this variation, the thermal source of intercooler 7 is not an air but the water this point is different, still, can obtain the action effect same with above-mentioned embodiment yet.
As shown in Figure 5; Also taps valve 14a can be set in middle cooling water pipe arrangement 14; Thereby the compacting cryogen intercooler 7 of not flowing through in the middle of using above-mentioned intercooler bypass pipe 9 to control to make, and also control and stop to supply water to intercooler 7 through closing taps valve 14a.Here, taps valve 14a be can gauge tap magnetic valve.
In the case, thus the cold-producing medium liquefy states in the intercooler 7 that can also prevent accumulate.
(variation 2)
In above-mentioned variation 1; Supply water to intercooler 7 through middle cooling water pipe arrangement 14; And taps valve 14a is set in middle cooling water pipe arrangement 14; If judge temperature as the cold-producing medium of the temperature of the water of the thermal source of intercooler 7 or intercooler 7 outlets become from the prime side pressure contract parts 2c be sent to rear-stage side compression member 2d in the middle of below the saturation temperature of compacting cryogen, so, adopt damp proof control (with reference to Fig. 5); Thereby use intercooler bypass pipe 9 to implement control and make the cold-producing medium intercooler 7 of not flowing through; And through closing taps valve 14a, control stops to supply water to intercooler 7, and it is such with cooler switch valve 12 also can to omit the intercooler bypass pipe 9 that comprises intercooler bypass cock valve 11; The compacting cryogen structure of control of intercooler 7 of not flowing through in the middle of being used for making adopts the damp proof control of the control that only stops to supply water to intercooler 7.
In the structure of this variation, different with the foregoing description 1, although become often the flow through state of intercooler 7 of cold-producing medium; But; Stop to supply water to intercooler 7, in fact, the cold-producing medium of the intercooler 7 of flowing through is not by water-cooled but; Therefore, can obtain the action effect same with above-mentioned variation 1.
(5) variation 3
In the structure (with reference to Fig. 6) of above-mentioned variation 2; The valve that employing can be regulated aperture constitutes taps valve 14a; If judge the temperature of the cold-producing medium of intercooler 7 outlets become from the prime side pressure contract parts 2c be sent to rear-stage side compression member 2d in the middle of below the saturation temperature of compacting cryogen; So; Reduce the flow of the water of supplying with intercooler 7 through the aperture that reduces taps valve 14a, thereby prevent that the cold-producing medium that is inhaled among the rear-stage side compression member 2d from becoming moisture state, and; Also can adopt the control damp proof control of flow of water of intercooler 7 of flowing through, thus make intercooler 7 outlets cold-producing medium temperature than the parts 2c that contracts from the prime side pressure be sent to rear-stage side compression member 2d in the middle of the saturation temperature of compacting cryogen high.
In the structure of this variation; Same with above-mentioned variation 2; Not only can prevent that the cold-producing medium that is inhaled among the rear-stage side compression member 2d from becoming moisture state, and, the temperature that is inhaled into the cold-producing medium among the rear-stage side compression member 2d greatly reduced; So just can reduce from the temperature decline of the cold-producing medium of rear-stage side compression member 2d discharge, reduce the consumption of power of compressing mechanism 2.
(6) variation 4
In the refrigerant line 10 in above-mentioned embodiment and variation thereof (with reference to Fig. 1,4,5,6); Have one and utilize side heat exchanger 6; And can carry out cooling operation; For the air conditioner load according to a plurality of conditioned spaces freezes and makes warm etc.; Employing has the structure with lower component: what be used for switching the cooling operation and the switching mechanism 3 of the warm running of system, connection parallel with one another a plurality ofly utilizes side heat exchanger 6, the temporary transient storage to flow through heat source side heat exchanger 4 and utilize the receiver 18 of the cold-producing medium between the side heat exchanger 6, and, thereby each utilizes the flow of the cold-producing medium of side heat exchanger 6 can obtain to utilize cooling load required in the side heat exchanger 6 at each in order to flow through through control; Sometimes as the receiver 18 of gas-liquid separator with utilize between the side heat exchanger 6; With each utilize side heat exchanger 6 be provided with accordingly the side of utilization expansion mechanism 5c (for example, after among Fig. 7,12 of stating, do not have rear-stage side playpipe 18c, 19 and the structure of economizer heat exchanger 20).In this structure; Make cold-producing medium return rear-stage side compression member 2d from receiver 18 as gas-liquid separator; Like this, make itself and from the preceding-stage side compression member 2c of compressing mechanism 2 discharge that the intermediate pressure refrigerant of the compressing mechanism that is inhaled into rear-stage side compression member 2d then converges in the middle of press and spray, the temperature of the cold-producing medium of discharging from rear-stage side compression member 2d is reduced; Reduce the consumption of power of compressing mechanism 2, improve running efficiency.
But; Have a plurality of side heat exchangers 6 that utilize that are connected in parallel; And utilize side heat exchanger 6 corresponding with each, as the receiver 18 of gas-liquid separator with utilize the utilization side expansion mechanism 5c that is provided with between the side heat exchanger 6 as utilizing side expansion valve, expansion mechanism 5c control in these sides of utilization is flowed through, and each utilizes the flow of the cold-producing medium of side heat exchanger 6; Thereby obtain to utilize cooling load required in the side heat exchanger 6 at each; In this structure, when the warm running of system, utilize the flow of the cold-producing medium of side heat exchanger 6 probably to be utilized the aperture of utilization side expansion mechanism 5c of upper reaches one side setting of a dirty side and the receiver 18 of side heat exchanger 6 to determine at each through each; At this moment; Not only each utilizes the flow change of the cold-producing medium of side heat exchanger 6 to the aperture of each side of utilization expansion mechanism 5c because of flowing through, and because of a plurality of assignment of traffic state changes that utilize 6 of side heat exchangers, the situation that aperture differs greatly takes place between a plurality of utilization side expansion mechanism 5c sometimes; And the side of utilization expansion mechanism 5c becomes less aperture; Therefore, because of making the aperture control of the utilization side expansion mechanism 5c in the warm running, might excessive descent as the gas-liquid separator pressure of the pressure of the cold-producing medium in the receiver 18.If this aircondition 1 adopt a kind of mainly comprise the heat source unit of compressing mechanism 2, heat source side heat exchanger 4 and receiver 18, mainly comprise utilize side heat exchanger 6 utilize the structure of unit through the separation air conditioner device getting in touch with pipe arrangement and connect; So; According to the configuration that utilizes unit and heat source unit, this contact pipe arrangement just might be very long, therefore; Except the pressure that causes gas-liquid separator because of its pressure loss descended, gas-liquid separator pressure also can further descend.
Therefore; Spray as pressing in the middle of the receiver 18 of gas-liquid separator; Under the little condition of the pressure differential of gas-liquid separator pressure and compressing mechanism intermediate pressure, also can use; Therefore, as the warm running of the system in this structure, highly beneficial under the situation of excessive descent probably at gas-liquid separator pressure.
But; As cooling operation; In heat source side heat exchanger 4, be cooled the back to flowing into as during the receiver 18 of gas-liquid separator; Except (for example as the 1st expansion mechanism 5a of heat source side expansion mechanism; The Fig. 7 that states after the reference, 12 the 1st expansion mechanism 5a) in addition; Do not carry out significantly decompression operation; Under near the condition of the pressure differential pressing in the middle of in high pressure to the kind of refrigeration cycle that can utilize in the kind of refrigeration cycle; Preferably be provided with the cold-producing medium between heat source side heat exchanger 4 and the 1st expansion mechanism 5a of flowing through shunted and make its 2nd rear-stage side playpipe 19 that returns rear-stage side compression member 2d then and the economizer heat exchanger 20 that the cold-producing medium of the flow through cold-producing medium between heat source side heat exchanger 4 and the 1st expansion mechanism 5a and the 2nd rear-stage side playpipe 19 of flowing through carries out heat exchange, make in this economizer heat exchanger 20 cold-producing medium of the 2nd rear-stage side playpipe 19 of flowing through after being heated through heat exchange return rear-stage side compression member 2d (that is, carry out economizer heat exchanger 20 in the middle of press spray) (for example with reference to after Fig. 7,12 the 2nd rear-stage side playpipe 19 and economizer heat exchanger 20 of stating).Its reason is, sprays for pressing in the middle of the economizer heat exchanger 20, because the flow of cold-producing medium that can return rear-stage side compression member 2d is because of the size change of the heat exchange amount in the economizer heat exchanger 20; Therefore; As make the warm running, under the little situation of the pressure differential of the pressure of the cold-producing medium of the inlet of economizer heat exchanger 20 and compressing mechanism intermediate pressure, the heat exchange amount in the economizer heat exchanger 20 diminishes; The flow that can return the cold-producing medium of rear-stage side compression member 2d reduces; Its application difficult, and under the big situation of the pressure differential of the pressure of the cold-producing medium of the inlet of economizer heat exchanger 20 and compressing mechanism intermediate pressure, the heat exchange amount in the economizer heat exchanger 20 increases; The flow that can return the cold-producing medium of rear-stage side compression member 2d increases, and it is used effectively.Particularly under the situation of using the sort of cold-producing medium in supercritical region work of carbon dioxide; High pressure in the kind of refrigeration cycle becomes the pressure above critical pressure; Therefore; High pressure in the kind of refrigeration cycle further enlarges with middle pressure differential of pressing, and therefore, presses in the middle of the economizer heat exchanger 20 and sprays effectively.And; Under the situation of using the sort of cold-producing medium in supercritical region work of carbon dioxide, gas-liquid separator pressure is increased to the pressure higher than critical pressure, might be difficult to separating into gas refrigerant and liquid refrigerant as the cold-producing mediums in the receiver 18 of gas-liquid separator; Therefore; If also consider this point, so, as cooling operation; Under near the condition of the pressure differential middle pressure that can utilize high pressure to the kind of refrigeration cycle in the kind of refrigeration cycle, preferably use middle pressure of economizer heat exchanger 20 to spray.
Therefore, in this variation, as stated; Adopt a kind of cooling operation that can switch to turn round, and have a plurality of structures that utilize side heat exchanger 6 that are connected in parallel with system is warm, and; Thereby each utilizes the flow of the cold-producing medium of side heat exchanger 6 can obtain to utilize cooling load required in the side heat exchanger 6 at each in order to flow through through control; As the receiver 18 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 is set accordingly with each, and; When the warm running of system; The possible step-down of the pressure of the cold-producing medium of the dirty side of the consideration side of utilization expansion mechanism 5c uses the middle pressure injection as the receiver 18 of gas-liquid separator, when cooling operation; Consider a dirty side of heat source side heat exchanger 4 and keep high pressure as the pressure of the cold-producing medium of upper reaches one side of the 1st expansion mechanism 5a of heat source side expansion mechanism, use economizer heat exchanger 20 in the middle of press and spray.
For example; As shown in Figure 7; In the above-described embodiment have with air as the intercooler 7 of thermal source and with the refrigerant line 10 (with reference to Fig. 1) of intercooler bypass pipe 9 in; Have and be used for switching cooling operation and the switching mechanism 3 of the warm running of system and a plurality of side heat exchangers 6 that utilize that are connected in parallel each other, and, expansion mechanism 5 replaced; The 1st expansion mechanism 5a as the heat source side expansion mechanism, 5d are set and as the utilization side expansion mechanism 5c that utilizes the side heat exchanger; And, bridge circuit 17, receiver the 18, the 1st rear-stage side playpipe 18c, the 2nd rear-stage side playpipe 19, economizer heat exchanger 20 also are set, constitute refrigerant line 610.
Switching mechanism 3 is the mechanisms that are used for switching the flow direction of the cold-producing medium in the refrigerant loop 610; In order to make when the cooling operation heat source side heat exchanger 4 can be as the cooler that is compressed 2 refrigerant compressed of mechanism; And make the heater 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; And suction one side that connects compressor 21 with utilize side heat exchanger 6 (with reference to the solid line of the switching mechanism 3 of Fig. 7, below, the state of this switching mechanism 3 is as " cooling operation state "); Utilize side heat exchanger 6 can be used as the cooler that is compressed 2 refrigerant compressed of mechanism in order when system warms up running, to make; And make the heat source side heat exchanger 4 can be as the heater of the cold-producing medium that in utilizing side heat exchanger 6, is cooled, discharge one side that can connect compressing mechanism 2 with utilize side heat exchanger 6, and connect 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. 7; Below, the state of this switching mechanism 3 is as " heating operating condition ").In this 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-way switching valve that utilizes side heat exchanger 6 to be connected.In addition, switching mechanism 3 is not limited to four-way switching valve, for example also can be through combination a plurality of magnetic valves etc., and make it have the function with the flow direction of above-mentioned same switching cold-producing medium.
So; If only be conceived to constitute compressing mechanism 2, heat source side heat exchanger 4, expansion mechanism 5a, 5b, receiver 18, the side of the utilization expansion mechanism 5c of refrigerant line 610 and utilize side heat exchanger 6; So, switching mechanism 3 can switch make cold-producing medium successively compressing mechanism 2, heat source side heat exchanger 4, as the heat source side expansion mechanism the 1st expansion mechanism 5a, receiver 18, the side of utilization expansion mechanism 5c, utilize the cooling operation state of circulation in the side heat exchanger 6; And make cold-producing medium successively at compressing mechanism 2, utilize side heat exchanger 6, as the utilization side expansion mechanism 5c, receiver 18 that utilize side expansion valve, as the 3rd expansion mechanism 5d of heat source side expansion mechanism, heat source side heat exchanger 4 in the heating operating condition of circulation.
Bridge circuit 17 is set at heat source side heat exchanger 4 and utilizes between the side heat exchanger 6, and the receiver inlet tube 18a that is connected with inlet with receiver 18 and the receiver outlet 18b that is connected with the outlet of receiver 18 connect.In this variation, bridge circuit 17 has 3 check valve 17a, 17b, 17c and as the 3rd expansion mechanism 5d of heat source side expansion mechanism.Inlet one-way valve 17a only allows that cold-producing medium is from the flow through check valve of receiver 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 receiver 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 with utilize the function of the receiver 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 receiver outlet 18b to utilize the check valve of side heat exchanger 6.The 3rd expansion mechanism 5d is the mechanism that cold-producing medium is reduced pressure, and it constitutes the part of bridge circuit 17.That is, outlet check valve 17c and the 3rd expansion mechanism 5d has and makes cold-producing medium from receiver outlet 18b flow through heat source side heat exchanger 4 and another the function of utilizing side heat exchanger 6.Therefore; When switching mechanism 3 is switched to the cooling operation of cooling operation state; The 3rd expansion mechanism 5d is in complete closing state; When switching mechanism 3 being switched to the warm running of system of heating operating condition, it reduces pressure to the cold-producing medium that is sent to heat source side heat exchanger 4 from receiver outlet 18b.In addition, in this variation, the 3rd expansion mechanism 5d is an electric expansion valve.
The 1st expansion mechanism 5a is provided in a side of the mechanism that being used among the receiver inlet tube 18a reduced pressure to cold-producing medium, in this variation, has used electric expansion valve.The end of the 1st expansion mechanism 5a is connected with heat source side heat exchanger 4 through bridge circuit 17, and the other end is connected with receiver 18.In addition; In this variation, when cooling operation, the high-pressure refrigerant that will in heat source side heat exchanger 4, be cooled is sent to and utilizes before the side heat exchanger 6; The 1st expansion mechanism 5a is to reducing pressure to it; When the warm running of system, the high-pressure refrigerant that will in utilizing side heat exchanger 6, be cooled is sent to before the heat source side heat exchanger 4, and the 1st expansion mechanism 5a reduces pressure to it.In receiver inlet tube 18a, be provided with expansion mechanism by-passing valve 5e, the 1st expansion mechanism 5a is carried out bypass.In this variation, this expansion mechanism by-passing valve 5e is a magnetic valve.
The 1st rear-stage side playpipe 18c can select the middle refrigerant pipe that sprays of pressing that cold-producing medium makes its rear-stage side compression member 2d that returns compressing mechanism 2 then from receiver 18; In this variation; It is provided with according to the top that connects receiver 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 1st rear-stage side playpipe 18c, be provided with the 1st rear-stage side injection cock valve 18d and the 1st rear-stage side sprays the unidirectional 18e of mechanism.The 1st rear-stage side injection cock valve 18d is the valve that can carry out switching manipulation, is magnetic valve in this variation.The 1st rear-stage side sprays the unidirectional 18e of mechanism and is used for allowing that cold-producing medium flows to rear-stage side compression member 2d from receiver 18, and block refrigerant flows to receiver 18 from rear-stage side compression member 2d, in this variation, has used check valve.
Sucking recurrent canal 18f can select cold-producing medium from receiver 18 to make it return the refrigerant pipe of the preceding-stage side compression member 2c of compressing mechanism 2 then; In this variation; It is provided with according to top that connects receiver 18 and the mode of suction line 2a (that is suction one side of the preceding-stage side compression member 2c of compressing mechanism 2).In this suction recurrent canal 18f, be provided with and suck Returning switch valve 18g.Sucking Returning switch valve 18g is the valve that can carry out switching manipulation, at this variation Chinese style magnetic valve.
Like this; Use under the situation of the 1st rear-stage side playpipe 18d and suction recurrent canal 18f opening the 1st rear-stage side injection cock valve 18d and suction Returning switch valve 18g; Receiver 18 have can be between expansion mechanism 5a, 5d and utilization side expansion mechanism 5c to flowing through heat source side heat exchanger 4 and utilize cold-producing medium between the side heat exchanger 6 to carry out the function of the gas-liquid separator of gas-liquid separation, it mainly can be with the rear-stage side compression member 2d and the preceding-stage side compression member 2c that in receiver 18, are returned compressing mechanism 2 by the gas refrigerant after the gas-liquid separation from the top of receiver 18.
The side of utilization expansion mechanism 5c is as the receiver 18 (more specifically being bridge circuit 17) of gas-liquid separator with utilize between the side heat exchanger 6 with each and utilize the corresponding and mechanism that cold-producing medium is reduced pressure that establishes of side heat exchanger 6; In this variation, used electric expansion valve.The end of the side of utilization expansion mechanism 5c is connected with receiver 18 by bridge circuit 17, and the other end connects with the corresponding side heat exchanger 6 that utilizes.In addition, in this variation, when cooling operation; Will be sent to by the cold-producing medium of the 1st expansion mechanism 5a decompression utilize side heat exchanger 6 before; The side of utilization expansion mechanism 5c continues it is reduced pressure, until becoming low pressure, when heating running; Before will being sent to receiver 18 through the cold-producing medium that utilizes side heat exchanger 6, it is reduced pressure.
The 2nd rear-stage side playpipe 19 has flowing through heat source side heat exchanger 4 and utilize cold-producing medium between the side heat exchanger 6 to shunt to make it return the function of the rear-stage side compression member 2d of compressing mechanism 2 then.In this variation, the 2nd rear-stage side playpipe 19 makes its mode of returning suction one side of rear-stage side compression member 2d be provided with according to the cold-producing medium of the receiver inlet tube 18a that flows through is shunted then.More specifically; The 2nd rear-stage side playpipe 19 is according to from upper reaches one side position of the 1st expansion mechanism 5a of receiver inlet tube 18a (promptly; When switching mechanism 3 becomes the cooling operation state; Between heat source side heat exchanger 4 and the 1st expansion mechanism 5a) cold-producing medium is shunted, the mode of a dirty side position of its intercooler that returns intermediate refrigerant pipe 87 is provided with.Here, the 1st rear-stage side playpipe 18c and the 2nd rear-stage side playpipe 19 are integrally formed in the part of intermediate refrigerant pipe 8 one sides.In the 2nd rear-stage side playpipe 19, be provided with the 2nd rear-stage side injection valve 19a that can control aperture.In this variation, the 2nd rear-stage side injection valve 19a is an electric expansion valve.
Economizer heat exchanger 20 is to be used for heat exchanger to flowing through heat source side heat exchanger 4 and utilizing the cold-producing medium (near the cold-producing medium after specifically, in the 2nd rear-stage side injection valve 19a, being depressurized to the intermediate pressure) of cold-producing medium and the 2nd rear-stage side playpipe 19 of flowing through between the side heat exchanger 6 to carry out 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 receiver inlet tube 18a that flows through (promptly; 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 establish with the mode of carrying out heat exchange of the cold-producing medium of the 2nd rear-stage side playpipe 19 of flowing through, and, have the stream that two cold-producing mediums flow relatively.In this variation, economizer heat exchanger 20 is set at the dirty side of the 2nd rear-stage side playpipe 19 from the position of receiver inlet tube 18a shunting.Therefore; The heat source side of flowing through heat exchanger 4 and utilize cold-producing medium between the side heat exchanger 6 in receiver inlet tube 18a; In economizer heat exchanger 20 by before the heat exchange by 19 shuntings of the 2nd rear-stage side playpipe, in economizer heat exchanger 20, carry out heat exchange then with the cold-producing medium of the 2nd rear-stage side playpipe 19 of flowing through.
So; Utilize bridge circuit 17, receiver 18, receiver inlet tube 18a and receiver outlet 18b; When switching mechanism 3 becomes cooling during operating condition, the outlet check valve 17c of the inlet one-way valve 17a that the high-pressure refrigerant that in heat source side heat exchanger 4, is cooled just can be through bridge circuit 17, the 1st expansion mechanism 5a of receiver inlet tube 18a, receiver 18, bridge circuit 17 and the side of utilization expansion mechanism 5c are sent to and utilize side heat exchanger 6.In addition; When switching mechanism 3 becomes heating during operating condition, the 3rd expansion mechanism 5d of the inlet one-way valve 17b that the high-pressure refrigerant that in utilizing side heat exchanger 6, is cooled just can be through the side of utilization expansion mechanism 5c, bridge circuit 17, expansion mechanism by-passing valve 5e, receiver 18 and the bridge circuit 17 of receiver inlet tube 18a is sent to heat source side heat exchanger 4.
In this variation, detect the energy-saving appliance outlet temperature sensor 55 of the refrigerant temperature in the outlet of the 2nd rear-stage side playpipe 19 sides of economizer heat exchanger 20 in the outlet setting of the 2nd rear-stage side playpipe 19 sides of economizer heat exchanger 20.In receiver inlet tube 18a, the gas-liquid separator temperature sensor 57 that detects the refrigerant temperature in the receiver 18 is set in the position of comparing with the 1st expansion mechanism 5a near receiver 18 1 sides.In addition, this gas-liquid separator temperature sensor 57 both can be arranged among the receiver outlet 18b, also can be set directly at the bottom of receiver 18, like the bottom of receiver 18.
Like this, in this variation, just can separately use following two kinds of spray regimes: cold-producing medium through the 1st rear-stage side playpipe 18c, is returned middle pressure of the receiver 18 of rear-stage side compression member 2d and sprays from the receiver 18 as gas-liquid separator; Through the 2nd rear-stage side playpipe 19, heated cold-producing medium returns the middle pressure injection of the economizer heat exchanger 20 of rear-stage side compression member 2d in economizer heat exchanger 20.
Below, use Fig. 7～Figure 11, the operation of the aircondition 1 of this variation is described.Here; Pressure-enthalpy the line chart of the kind of refrigeration cycle when Fig. 8 is the cooling operation in this variation of expression; Temperature-entropy the line chart of the kind of refrigeration cycle when Fig. 9 is the cooling operation in this variation of expression; Pressure-enthalpy the line chart of the kind of refrigeration cycle when Figure 10 is warm running of representing in this variation of system, Figure 11 is temperature-entropy line chart that the system in this variation of expression warms up the kind of refrigeration cycle when turning round.In addition, the running control in following cooling operation and the warm running of system and suppress the control that gas-liquid separator pressure descends and carry out through above-mentioned control part (not shown).In following explanation; " high pressure " be meant in the kind of refrigeration cycle high pressure (promptly; The pressure of the pressure of some D among Fig. 8,9, D ', E, H and the some D among Figure 10,11, D ', F, H), " low pressure " is meant the low pressure (that is, the pressure of the some A among Fig. 8,9, F and the some A among Figure 10,11, the pressure of E) in the kind of refrigeration cycle; " intermediate pressure " is meant the intermediate pressure (that is the pressure of the some B1 in Fig. 8～11, C1, G) in the kind of refrigeration cycle.
(cooling operation)
When cooling operation, switching mechanism 3 is in the cooling operation state shown in the solid line of Fig. 7.Be conditioned as the 1st expansion mechanism 5a of heat source side expansion mechanism with as the aperture of the utilization side expansion mechanism 5c that utilizes side expansion valve.The 3rd expansion mechanism 5d and expansion mechanism by-passing valve 5e are in complete closing state.When switching mechanism 3 is become the cooling operation state; Do not carry out middle pressure injection as the receiver 18 of gas-liquid separator; But middle pressure of carrying out economizer heat exchanger 20 sprayed; Through the 2nd rear-stage side playpipe 19, heated cold-producing medium returns rear-stage side compression member 2d in economizer heat exchanger 20.More specifically, the 1st rear-stage side injection cock valve 18d becomes closed condition, and the aperture of the 2nd rear-stage side injection valve 19a is conditioned.Here, the 2nd rear-stage side injection valve 19a implements the so-called degree of superheat control that aperture is conditioned, thereby makes the degree of superheat of the cold-producing medium in the outlet of the 2nd 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 2nd rear-stage side playpipe 19 1 sides of economizer heat exchanger 20 is converted into saturation temperature through pressing in the middle of intermediate pressure sensor 54 is detected, and from the refrigerant temperature that energy-saving appliance outlet temperature sensor 55 detects, deducts the saturation temperature of this cold-producing medium and obtains.In addition; In this variation, do not adopt; But; Also can temperature sensor be set, from the refrigerant temperature that energy-saving appliance outlet temperature sensor 55 detects, deduct the refrigerant temperature that detects by this temperature sensor, thereby obtain the degree of superheat of the cold-producing medium in the outlet of the 2nd rear-stage side playpipe 19 1 sides of economizer heat exchanger 20 at the inlet of the 2nd rear-stage side playpipe 19 1 sides of economizer heat exchanger 20.And cooler switch valve 12 is opened, and the intercooler bypass cock valve 11 of intercooler bypass pipe 9 is closed, and like this, intercooler 7 just becomes can be as the state of cooler.
If drive compression mechanism 2 under the state of this refrigerant line 610; So; The cold-producing medium of low pressure (with reference to the some A among Fig. 7～Fig. 9) is inhaled into the compressing mechanism 2 from suction line 2a; At first, be compressed after parts 2c is compressed to intermediate pressure, discharge (with reference to the some B1 among Fig. 7～Fig. 9) to intermediate refrigerant pipe 8.The compacting cryogen carries out heat exchange be cooled thereby (with reference to the some C1 among Fig. 7～Fig. 9) with empty G&W as thermal source in the middle of from this preceding-stage side compression member 2c, being discharged from intercooler 7.Cold-producing medium that in this intercooler 7, is cooled and cold-producing medium (with reference to the some K Fig. 7～Fig. 9) interflow of returning rear-stage side compressing mechanism 2d from the 2nd rear-stage side playpipe 19 are further cooled (with reference to the some G among Fig. 7～Fig. 9).Then; Collaborate the back (promptly with the cold-producing medium that returns from the 2nd rear-stage side playpipe 19; Pressure injection in the middle of economizer heat exchanger 20 is carried out) the compacting cryogen is inhaled among the compression member 2d that is connected with the rear-stage side of compression member 2c in the middle of; And, be expelled to discharge pipe 2b (with reference to the some D Fig. 7～Fig. 9) from compressing mechanism 2 by further compression.The high-pressure refrigerant of here, from compressing mechanism 2, discharging is compressed into the pressure above critical pressure (that is the critical pressure Pcp among the critical point CP shown in Figure 8) according to the secondary squeeze operation of compression member 2c, 2d.The high-pressure refrigerant of discharging from this compressing mechanism 2 is via switching mechanism 3, and being sent to can be as the heat source side heat exchanger 4 of the cooler of cold-producing medium, carries out heat exchange with empty G&W as cooling source, thereby is cooled (with reference to the some E among Fig. 7～Fig. 9).The high-pressure refrigerant that in heat source side heat exchanger 4, is cooled is through flowing into receiver inlet tube 18a behind the inlet one-way valve 17a of bridge circuit 17, its part is by 19 shuntings of the 2nd rear-stage side playpipe.After near pressing in the middle of the cold-producing medium of the 2nd rear-stage side playpipe 19 of flowing through is depressurized and becomes, be sent to economizer heat exchanger 20 (with reference to the some J among Fig. 7～Fig. 9) in the 2nd rear-stage side injection valve 19a.In addition, flowed into economizer heat exchanger 20, with the cold-producing medium of the 2nd rear-stage side playpipe 19 of flowing through carry out being cooled after the heat exchange (with reference to the some H among Fig. 7～Fig. 9) by the cold-producing medium of the receiver inlet tube 18a that flows through after the shunting of the 2nd rear-stage side playpipe 19.The cold-producing medium of the 2nd rear-stage side playpipe 19 of flowing through carries out being heated after the heat exchange (with reference to the some K among Fig. 7～Fig. 9) with the cold-producing medium of receiver inlet tube 18a of flowing through, then as stated, and with the cold-producing medium interflow that in intercooler 7, is cooled.The high-pressure refrigerant that in economizer heat exchanger 20, is cooled is decompressed to by the 1st expansion mechanism 5a near the saturation pressure, temporarily is stored in then in the receiver 18 (with reference to the some I among Fig. 7～Fig. 9).The cold-producing medium that is stored in the receiver 18 is sent to receiver outlet 18b; Be sent to the side of utilization expansion mechanism 5c behind the outlet check valve 17c through receiver outlet 18b and bridge circuit 17, and become the cold-producing medium (with reference to the some F among Fig. 7～Fig. 9) of the gas-liquid two-phase state of low pressure after the side of the utilization expansion mechanism 5c decompression.Then, be sent to the low pressure of utilizing side heat exchanger 6 the gas-liquid two-phase state cold-producing medium with carry out being heated after the heat exchange evaporation (with reference to the some A among Fig. 7～Fig. 9) then as the empty G&W of heating source.Utilize at this that heated low pressure refrigerant is sucked compressing mechanism 2 once more via switching mechanism 3 in side heat exchanger 6.Adopt aforesaid way to carry out cooling operation.
In the structure of this variation; Except utilizing intercooler 7 coolings to be inhaled into the cold-producing medium among the rear-stage side compression member 2d; Through having used the intermediate injection of economizer heat exchanger 20 and the 2nd rear-stage side playpipe 19, can further reduce the temperature (with reference to some D, the D ' among Fig. 9) that is inhaled into the cold-producing medium among the rear-stage side compression member 2d.So just can reduce the consumption of power of compressing mechanism 2, improve running efficiency.
(the warm running of system)
When cooling operation, switching mechanism 3 is in the warm operating condition of the system shown in the dotted line of Fig. 7.Be conditioned as the 3rd expansion mechanism 5d of heat source side expansion mechanism with as the aperture of the utilization side expansion mechanism 5c that utilizes side expansion valve.Expansion mechanism by-passing valve 5e is in complete closing state, and the 1st expansion mechanism 5a does not reduce pressure.When switching mechanism 3 being become the heating operating condition; Not carrying out middle pressure of economizer heat exchanger 20 sprays; But carry out the middle pressure injection of receiver 18, and make cold-producing medium pass through the 1st rear-stage side playpipe 18c, return rear-stage side compression member 2d from receiver 18 as gas-liquid separator.More specifically, the 1st rear-stage side injection cock valve 18d becomes open mode, and the 2nd rear-stage side injection valve 19a becomes complete closing state.And cooler switch valve 12 is closed, and the intercooler bypass cock valve 11 of intercooler 9 is opened, and like this, intercooler 7 just becomes can not be as the state of cooler.
If drive compression mechanism 2 under the state of this refrigerant line 610; So; Low pressure refrigerant (with reference to the some A among Fig. 7,10,11) is inhaled into the compressing mechanism 2 from suction line 2a; At first, be compressed after parts 2c is compressed to intermediate pressure, discharged (with reference to the some B1 among Fig. 7,10,11) to intermediate refrigerant pipe 8.Different during with cooling operation; The compacting cryogen is not through intercooler 7 (promptly in the middle of from this preceding-stage side compression member 2c, discharging; Be not cooled); But through intercooler bypass pipe 9 (with reference to the some C1 among Fig. 7), then with the cold-producing medium (with reference to the some M Fig. 7,10,11) that returns rear-stage side compressing mechanism 2d through the 1st rear-stage side playpipe 18c from receiver 18 thereby the interflow is cooled (with reference to the some G among Fig. 7,10,11).Then; Collaborate the back (promptly with the cold-producing medium that returns from the 1st rear-stage side playpipe 18c; Press in the middle of carrying out as the receiver 18 of gas-liquid separator and spray) in the middle of the compacting cryogen be inhaled among the compression member 2d that is connected with the rear-stage side of compression member 2c; And, discharge (with reference to the some D Fig. 7,10,11) from compressing mechanism 2 to discharge pipe 2b then by further compression.Here, same during with cooling operation, the high-pressure refrigerant of from compressing mechanism 2, discharging is according to the secondary squeeze operation of compression member 2c, 2d, is compressed the pressure that becomes above critical pressure (that is the critical pressure Pcp among the critical point CP shown in Figure 10).Then; The high-pressure refrigerant of from this compressing mechanism 2, discharging is via switching mechanism 3; Be sent to can as the cooler of cold-producing medium utilize side heat exchanger 6, carry out heat exchange with empty G&W then, thereby be cooled (with reference to the some F among Fig. 7,10,11) as cooling source.The high-pressure refrigerant side of the being utilized expansion mechanism 5c that in utilizing side heat exchanger 6, is cooled is decompressed near the intermediate pressure; Through flowing into receiver inlet tube 18a behind the inlet one-way valve 17b of bridge circuit 17; Through temporarily being stored in the receiver 18 behind the expansion mechanism by-passing valve 5e, carry out gas-liquid separation (with reference to some I, L, the M among Fig. 7,10,11) simultaneously.In receiver 18, sprayed from the top of receiver 18 by the 1st rear-stage side playpipe 18c by the gas refrigerant after the gas-liquid separation, then as stated, with the middle compacting cryogen interflow of from parts 2c is contracted in the prime side pressure, discharging.The liquid refrigerant that is stored in the receiver 18 is sent to bridge circuit 17 through receiver outlet 18b; Become the cold-producing medium of the gas-liquid two-phase state of low pressure after the 3rd expansion mechanism 5d decompression then, and be sent to the heat source side heat exchanger 4 (with reference to the some E among Fig. 7,10,11) that can be used as the heater of cold-producing medium.Then, be sent to heat source side heat exchanger 4 low pressure the gas-liquid two-phase state cold-producing medium with carry out being heated after the heat exchange evaporation (with reference to the some A among Fig. 7,10,11) then as the empty G&W of heating source.Heated low pressure refrigerant is sucked compressing mechanism 2 once more via switching mechanism 3 in this heat source side heat exchanger 4.Adopt aforesaid way to heat running.
In the structure of this variation; According to the intermediate injection of having used receiver 18 and the 1st rear-stage side playpipe 19; So just can reduce the temperature that is inhaled into the cold-producing medium among the rear-stage side compression member 2d; Therefore, can reduce the temperature (with reference to some D, the D ' among Figure 11) of the cold-producing medium of from compressing mechanism 2, discharging.So just can reduce the consumption of power of compressing mechanism 2, improve running efficiency.But; Different during with cooling operation; Can not be at intercooler 7 as under the state of cooler, same with cooling operation, the situation that can be used as cooler with intercooler 7 compared; Suppress the radiation loss of intercooler 7, thereby prevent to utilize the decline of the heating efficiency in the side heat exchanger 6 to the outside.
(being inhaled into the degree of superheat control of the cold-producing medium in the rear-stage side compression member)
In this variation; With as the receiver 18 of gas-liquid separator in the middle of press and spray heating in the running of carrying out simultaneously; Be stored in large quantities as the operating condition in the receiver 18 of gas-liquid separator if become liquid refrigerant for a certain reason, it is difficult that gas-liquid separation becomes, so;, receiver 18 just might sneak into liquid refrigerant through the 1st rear-stage side playpipe 18c from returning the cold-producing medium of rear-stage side compression member 2d; So the middle compacting cryogen that is inhaled among the rear-stage side compression member 2d that presses in the middle of carrying out after spraying will become moisture state, the reliability of compressing mechanism 2 might be damaged.
Therefore, in this variation, control the degree of superheat that is inhaled into the cold-producing medium among the rear-stage side compression member 2d according to the switching manipulation of the 1st rear-stage side injection cock valve 18d.Specifically, in this variation,, carry out the switching manipulation of the 1st rear-stage side injection cock valve 18d in order not make the degree of superheat that is inhaled into the cold-producing medium among the rear-stage side compression member 2d after the middle pressure of carrying out receiver 18 is sprayed littler than setting.Here; The degree of superheat that is inhaled into the cold-producing medium of rear-stage side compression member 2d is converted into saturation temperature through the compressing mechanism intermediate pressure that intermediate pressure sensor 54 is detected, and deducts the saturation temperature of the cold-producing medium corresponding with this pressure mechanism intermediate pressure the temperature of the cold-producing medium that detects from middle temperature sensor 56 and obtains.In addition, for do not make be inhaled among the rear-stage side compression member 2d in the middle of the compacting cryogen become moisture state, the setting of the degree of superheat in this control is configured to the degree of several years～tens for example and waits at least and spend big value than 0.Time t1 that becomes open mode and the time that becomes the time t2 of closed condition recently carry out through changing the 1st rear-stage side injection cock valve 18d in the switching manipulation of the 1st rear-stage side injection cock valve 18d.In this variation, be more than the setting, so if be inhaled into the degree of superheat of the cold-producing medium among the rear-stage side compression member 2d; For middle pressure of carrying out receiver 18 energetically sprayed; The time ratio of time t2 and time t1 is made as 0, thereby the 1st rear-stage side injection cock valve 18d is remained on open mode, if it is littler than setting to be inhaled into the degree of superheat of the cold-producing medium among the rear-stage side compression member 2d; So; In order to reduce the flow that returns the cold-producing medium of rear-stage side compression member 2d from receiver 18, make its direction that becomes the time ratio of increase time t2 and time t1 (that is, prolonging the time that the 1st rear-stage side injection cock valve 18d becomes closed condition).The degree of superheat that is inhaled into the cold-producing medium among the rear-stage side compression member 2d return to setting above after, in order to increase the flow that returns the cold-producing medium of rear-stage side compression member 2d from receiver 18 once more, make it become the direction of the time ratio that reduces time t2 and time t1.
So; In this variation; Because according to the switching manipulation of the 1st rear-stage side injection cock valve 18d, control is contracted from the prime side pressure and is inhaled into the degree of superheat of the cold-producing medium of rear-stage side compression member 2d after parts 2c discharges, therefore; Even be stored in as the operating condition in the receiver 18 of gas-liquid separator becoming a large amount of liquid refrigerants; From receiver 18 returns the cold-producing medium of rear-stage side compression member 2d, sneak under the situation of liquid refrigerant,, can prevent that also the cold-producing medium that is inhaled among the rear-stage side compression member 2d from becoming moisture state through reducing the flow that returns the cold-producing medium of rear-stage side compression member 2d from receiver 18.Like this, in this variation, the reliability of compressing mechanism 2 improves when heating running.
In addition; In this variation; When cooling operation, economizer heat exchanger 20 is carried out the centre and press to be sprayed, and the degree of superheat of returning the cold-producing medium of rear-stage side compression member 2d from the 2nd rear-stage side playpipe 19 is regulated by control through the aperture of the 2nd rear-stage side injection valve 19a and become desired value.Therefore; In this variation; When cooling operation, can prevent to receive because of pressing the influence of spraying the cold-producing medium that returns rear-stage side compression member 2d in the middle of the economizer heat exchanger 20, the cold-producing medium that is inhaled into rear-stage side compression member 2d becomes moisture state; So the reliability of compressing mechanism 2 improves.
And, in this variation, of above-mentioned embodiment; When the temperature as the air of the thermal source of intercooler 7 become the parts 2c that contracts from the prime side pressure be sent to rear-stage side compression member 2d in the middle of the saturation temperature of compacting cryogen when following; Use intercooler bypass pipe 9, make the do not flow through damp proof control of intercooler 7 of cold-producing medium, therefore; Becoming under the operating condition low as the temperature of the air of the thermal source of intercooler 7; Can prevent that also the cold-producing medium that is inhaled among the rear-stage side compression member 2d from becoming moisture state, like this, the reliability of compressing mechanism 2 will improve.
Like this; In this variation, spray according to the cooling down operation and middle pressure of intercooler 7, can prevent to receive the influence of the cold-producing medium that returns rear-stage side compression member 2d; The cold-producing medium that is inhaled into rear-stage side compression member 2d becomes moisture state; So when cooling operation and when heating any running in when running, the reliability of compressing mechanism 2 also can improve.
In above-mentioned refrigerant line 610 (with reference to Fig. 7); The 1st expansion mechanism 5a and receiver 18 be by bridge circuit 17 (comprising the 3rd expansion mechanism 5d), with heat source side heat exchanger 4 with utilize between the side heat exchanger 6 and be connected, still; Shown in figure 12; Also can omit bridge circuit 17, between heat source side heat exchanger 4 and receiver 18, connect the 1st expansion mechanism 5a, when switching mechanism 3 becomes the state of cooling running; The heat source side of flowing through heat exchanger 4 and utilize cold-producing medium between the side heat exchanger 6 flow through successively the 1st expansion mechanism 5a, receiver 18, the side of utilization expansion mechanism 5c; When switching mechanism 3 became the state that adds heat run, the heat source side of flowing through heat exchanger 4 and utilize cold-producing medium between the side heat exchanger 6 flow through the successively side of utilization expansion mechanism 5c, receiver the 18, the 1st expansion mechanism 5a constituted refrigerant line 710 with this.
In this structure; Bridge circuit 17 is omitted this point; And when switching mechanism 3 becomes the heating operating condition; The heat source side of flowing through heat exchanger 4 and utilize cold-producing medium between the side heat exchanger 6 flow through the successively side of utilization expansion mechanism 5c, receiver the 18, the 1st expansion mechanism 5a this point different (therefore, some I among Figure 10,11 and some L transposing), but also can obtain and above-mentioned same action effect.
In above-mentioned refrigerant line 610,710 (with reference to Fig. 7,12), as the structure of intercooler 7 grades, adopted the structure in the above-mentioned embodiment, still not limited thereto, also can adopt the structure of variation 1～3.
(7) variation 5
In above-mentioned embodiment and variation thereof; Compressor 21 by a secondary compressed configuration constitutes the compressing mechanism 2 that compresses two stage compression types of the cold-producing medium of discharging in the preceding-stage side compression member from 2 compression member 2c, 2d with the rear-stage side compression member successively; Also can adopt the many multi-stage compression mechanisms of three stage compression type geometric ratios, two stage compression types; Perhaps, with the compressor of having assembled a compression member and/or assembled a plurality of compression member some compressors be connected in series and constitute multi-stage compression mechanism.In addition, also can be as connecting a plurality of the utilization the situation such as side heat exchanger 6, under the situation of the ability that must increase compressing mechanism, adopt the compressing mechanism of parallelly connected multi-stage compression formula of the compressing mechanism of the above multi-stage compression formula of two systems that is connected in parallel.
Shown in figure 13; In the refrigerant line 610 (with reference to Fig. 7) of the bridge circuit 17 in not having above-mentioned variation 4; The compressing mechanism 2 that also can replace two stage compression types adopts the compressing mechanism 102 of the compressing mechanism 103,104 of two stage compression types that are connected in parallel, and constitutes refrigerant line 810.
In this variation; The 1st compressing mechanism 103 constitutes by using two compression member 103c, 103d that cold-producing medium is carried out secondary compressor for compressing 29, and is connected with being responsible for the 1st suction manifold 103a that 102a tells from the suction of compressing mechanism 102 and being responsible for the 1st exhaust outlet 103b that 102b converges with the discharge of compressing mechanism 102.In this variation; The 2nd compressing mechanism 104 constitutes by using two compression member 104c, 104d that cold-producing medium is carried out secondary compressor for compressing 30, and is connected with being responsible for the 2nd suction manifold 104a that 102a tells from the suction of compressing mechanism 102 and being responsible for the 2nd exhaust outlet 104b that 102b converges with the discharge of compressing mechanism 102.In addition; The structure of compressor 29,30 is identical with compressor 21 in above-mentioned embodiment and the variation thereof, therefore, expression is replaced as numeral 29 and digital 30 respectively except compression member 103c, 103d, 104c, the symbol of various piece 104d; Omit its explanation here.Compressor 29 sucks cold-producing medium from the 1st suction manifold 103a; Behind this cold-producing medium that is inhaled into of compression member 103c compression; Arm 81 is discharged in the middle of the 1st entrance side that constitutes intermediate refrigerant pipe 8; Make behind the middle the person in charge 82 and 1st outlet side middle arm 83 of cold-producing medium that the middle arm 81 of the 1st entrance side is discharged it is sucked among compression member 103d, discharge to the 1st exhaust outlet 103b behind the further then compressed refrigerant through formation intermediate refrigerant pipe 8.Compressor 30 sucks cold-producing medium from the 1st suction manifold 104a; Behind this cold-producing medium that is inhaled into of compression member 104c compression; Arm 84 is discharged in the middle of the 2nd entrance side that constitutes intermediate refrigerant pipe 8; Make behind the middle the person in charge 82 and 2nd outlet side middle arm 85 of cold-producing medium that the middle arm 84 of the 2nd entrance side is discharged it is sucked among compression member 104d, discharge to the 2nd exhaust outlet 104b behind the further then compressed refrigerant through formation intermediate refrigerant pipe 8.In this variation; Intermediate refrigerant pipe 8 is to be used for the cold-producing medium of discharging the compression member 103c that is connected from the preceding-stage side with compression member 103d, 104d, the 104c is sucked the compression member 103d that is connected with the rear-stage side of compression member 103c, 104c, the 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 the 2nd entrance side that discharge one side of the preceding-stage side compression member 104c of the 2nd compressing mechanism 104 is connected in the middle of in the middle of the arm 84, two entrance sides arm 81,84 interflow in the middle of be responsible for 82, be responsible for 82 from the centre and shunt then the middle arm 83 of the 1st outlet side that is connected with suction one side of the rear-stage side compression member 103d of the 1st compressing mechanism 103 and the person in charge 82 shunts then the middle arm 85 of the 2nd outlet side that is connected with suction one side of the rear-stage side compression member 104d of the 2nd compressing mechanism 104 from the centre.In addition; Discharge to be responsible for 102b and to be and be used for the cold-producing medium of discharging from compressing mechanism 102 is sent to the refrigerant pipe of switching mechanism 3; With discharge to be responsible for the 1st exhaust outlet 103b that 102b is connected in be provided with the 1st oil content disembark structure 141 and the 1st unidirectional mechanism 142, with the 2nd exhaust outlet 104b that discharge person in charge 102b is connected in be provided with the 2nd oil content disembark structure 143 and the 2nd unidirectional mechanism 144.The 1st oil content structure 141 of disembarking is used for the refrigerating machine oil of from the 1st compressing mechanism 103, discharging with cold-producing medium is separated suction one side of sending compressing mechanism 102 then back to from cold-producing medium, mainly comprises: the 1st oil eliminator 141a that will from cold-producing medium, separate with the refrigerating machine oil that cold-producing medium is discharged from the 1st compressing mechanism 103, be connected with the 1st oil eliminator 141a and the refrigerating machine oil that will from cold-producing medium, separate is sent the 1st oil return pipe 141b of suction one side of compressing mechanism 102 back to.The 2nd oil content structure 143 of disembarking is used for the refrigerating machine oil of from the 2nd compressing mechanism 104, discharging with cold-producing medium is separated suction one side of sending compressing mechanism 102 then back to from cold-producing medium, mainly comprises: the 2nd oil eliminator 143a that will from cold-producing medium, separate with the refrigerating machine oil that cold-producing medium is discharged from the 2nd compressing mechanism 104, be connected with the 2nd oil eliminator 143a and the refrigerating machine oil that will from cold-producing medium, separate is sent the 2nd oil return pipe 143b of suction one side of compressing mechanism 102 back to.In this variation, the 1st oil return pipe 141b is connected with the 2nd suction manifold 104a, and the 2nd oil return pipe 143c is connected with the 1st suction manifold 103a.Therefore; Even because the oil mass of refrigerating machine oil in being stored in the 1st compressing mechanism 103 and be stored between the oil mass of the refrigerating machine oil in the 2nd compressing mechanism 104 and difference occurs; Thereby cause occurring under the situation of difference between the oil mass of the refrigerating machine oil of the 2nd compressing mechanism 104 discharges from the oil mass of the refrigerator oil amount of the 1st compressing mechanism 103 discharges with cold-producing medium with cold-producing medium; Refrigerating machine oil also can return compressing mechanism 103,104 few one of refrigeration machine amount among both more, and the difference between the oil mass of the refrigerating machine oil that the oil mass that is stored in the refrigerating machine oil in the 1st compressing mechanism 103 is interior with being stored in the 2nd compressing mechanism 104 also is eliminated.In addition; In this variation; The 1st suction manifold 103a according to and the interflow portion of the 2nd oil return pipe 143b to and suck between the interflow portion that is responsible for 102a part towards with suck the mode that the interflow portion that is responsible for 102a becomes descending grade and constitute, the 2nd suction manifold 104a according to and the interflow portion of the 1st oil return pipe 141b to and suck between the interflow portion that is responsible for 102a part towards with suck the mode that the interflow portion that is responsible for 102a becomes descending grade and constitute.Therefore; Even any one in the compressing mechanism 103,104 is in halted state; Return refrigerating machine oil with the corresponding suction manifold of the compressing mechanism that is in halted state from the oil return pipe corresponding with the compressing mechanism that is turning round and will return to suck and be responsible for 102a, the compressing mechanism that is turning round is difficult for the generator oil consumption to the greatest extent.In oil return pipe 141b, 143b, be provided with mechanism of decompressor 141c, 143c that the refrigerating machine oil to flow through oil return pipe 141b, 143b reduces pressure.Unidirectional mechanism 142,144 be used for allowing cold-producing medium from discharge one effluent of compressing mechanism 103,104 to switching mechanism 3, and block refrigerant flows to discharge one side of compressing mechanism 103,104 from switching mechanism 3.
So; In this variation; Compressing mechanism 102 has formed the structure of be connected in parallel compressing mechanism 103 and compressing mechanism 104; The 1st compressing mechanism 103 has 2 compression member 103c, 103d, and compresses the cold-producing medium that the preceding-stage side compression member from these compression member 103c, 103d is discharged successively with the rear-stage side compression member; The 2nd compressing mechanism 104 has 2 compression member 104c, 104d, and compresses the cold-producing medium that the preceding-stage side compression member from these compression member 104c, 104d is discharged successively with the rear-stage side compression member.
In this variation; Intercooler 7 be set at constitute intermediate refrigerant pipe 8 in the middle of be responsible in 82 the heat exchanger that the cold-producing medium behind its cold-producing medium interflow 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 cools off.That is, intercooler 7 can be as general cooler in two compressing mechanisms 103,104.Therefore, when in the compressing mechanism 102 of the parallelly connected multi-stage compression formula of the compressing mechanism 103,104 of the multi-stage compression formula of the multisystem that is connected in parallel, intercooler 7 being set, can simplify the circuit structure around the compressing mechanism 102.
In addition; In the middle of the 1st entrance side that constitutes intermediate refrigerant pipe 8, be provided with the unidirectional 81a of mechanism in the arm 81; It is 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 contract discharge one side of parts 103c of prime side pressure from the centre; In the middle of the 2nd entrance side that constitutes intermediate refrigerant pipe 8, be provided with the unidirectional 84a of mechanism in the arm 84; It is 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 contract discharge one side of parts 104c of prime side pressure from the centre.In this variation, used check valve as the unidirectional 81a of mechanism, 84a.Therefore; Even any one in the compressing mechanism 103,104 is in halted state; Discharge one side of the preceding-stage side compression member of the compressing mechanism that is in halted state can not take place to arrive then through 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; The preceding-stage side compression member of the compressing mechanism of the cold-producing medium that can not take place to discharge from the preceding-stage side compression member of the compressing mechanism that turning round through being in halted state arrives suction one side of compressing mechanism 102 then, and the refrigerating machine oil that causes being in the compressing mechanism of halted state flows out such situation, so; When startup is in the compressing mechanism of halted state, be difficult for taking place the not enough situation of refrigerating machine oil.In addition; If at compressing mechanism 103, be provided with the priority (for example, under the situation of the 1st compressing mechanism 103) of running between 104, so as the compressing mechanism of preferential running; Have only the 2nd compressing mechanism 104 to meet the above-mentioned compressing mechanism that is in halted state; Therefore, in the case, the unidirectional mechanism 84a corresponding with the 2nd compressing mechanism 104 can only be set also.
In addition; As stated; Under the situation of the 1st compressing mechanism 103 as the compressing mechanism of preferential running, intermediate refrigerant pipe 8 is according to universal mode setting in compressing mechanism 103,104, therefore; The cold-producing medium of from the preceding-stage side compression member 103c corresponding with the 1st compressing mechanism 103 that is turning round, discharging is through arm 85 in the middle of the 2nd outlet side 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, and in the rear-stage side compression member 104d of the 2nd compressing mechanism 104 of the cold-producing medium of from the preceding-stage side compression member 103c of the 1st compressing mechanism 103 that turning round, discharging through being in halted state; Arrive the side that spues of compressing mechanism 102 then; The refrigerating machine oil that causes being in the 2nd compressing mechanism 104 of halted state flows out, and when startup is in the 2nd compressing mechanism 104 of halted state, the not enough situation of refrigerating machine oil might take place.Therefore, in this variation, in the arm 85 switch valve 85a is set in the middle of the 2nd outlet side, is under the situation of halted state, utilize this switch valve 85a to block flowing of the cold-producing medium in the arm 85 in the middle of the 2nd outlet side at the 2nd compressing mechanism 104.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 not arrive suction one side of the rear-stage side compression member 104d of the 2nd compressing mechanism 104 that is in halted state through arm 85 in the middle of the 2nd outlet side of intermediate refrigerant pipe 8; Therefore; Arrive discharge one side of compressing mechanism 102 in the rear-stage side compression member 104d of the 2nd compressing mechanism 104 of the cold-producing medium that be difficult for to take place to discharge from the preceding-stage side compression member 103c of the 1st compressing mechanism 103 that turning round through being in halted state then; The refrigerating machine oil that causes being in the 2nd compressing mechanism 104 of halted state flows out such situation; Like this,, startup is difficult for taking place the not enough situation of refrigerating machine oil when being in the 2nd compressing mechanism 104 of halted state.In addition, in variation, 85a has used magnetic valve as switch valve.
In addition; Under the situation of the 1st compressing mechanism 103, after the startup of the 1st compressing mechanism 103, then start the 2nd compressing mechanism 104 as the compressing mechanism of preferential running; But; At this moment, intermediate refrigerant pipe 8 is according to universal mode setting in compressing mechanism 103,104, therefore; The high state of pressure that becomes than discharge one side of the pressure of suction one side of preceding-stage side compression member 103c and rear-stage side compression member 103d from the pressure of 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 starts down, is difficult to stably start the 2nd compressing mechanism 104.Therefore, in this variation, the startup bypass pipe 86 of suction one side of discharge one side and the rear-stage side compression member 104d of the preceding-stage side compression member 104c be used for connecting the 2nd compressing mechanism 104 is set; In this startup bypass pipe 86, switch valve 86a is set; Be under the situation of halted state at the 2nd compressing mechanism 104, 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, utilize switch valve 86a that cold-producing medium is flowed through and start in the bypass pipe 86, so; 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 it is sucked among the rear-stage side compression member 104d, in the stable moment of the operating condition of compressing mechanism 102 (for example, the stable moment of the suction pressure of compressing mechanism 102, discharge pressure and intermediate pressure) through starting bypass pipe 86; 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 make it can get into 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 unidirectional 84a of mechanism 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 influence of the middle splenium branch that is not vulnerable to the 1st compressing mechanism 103.In addition, in this variation, 86a has used magnetic valve as switch valve.
In addition; For the cooling operation of the aircondition 1 of this variation, heat the operation of running and damp proof control etc.; The compressing mechanism of establishing except utilize replacing compressing mechanism 2 102, the loop configuration around the compressing mechanism 102 become slightly complicated and outside the change carried out, and the operation (Fig. 7～Figure 12 and relevant record the thereof) in basic and above-mentioned embodiment and the variation thereof is identical; Therefore, omit its explanation here.
In the structure of this variation, also can obtain and above-mentioned embodiment and the identical action effect of variation thereof.
Shown in figure 14; In the refrigerant line 710 (with reference to Figure 12) of the bridge circuit 17 in not having above-mentioned variation 4; The compressing mechanism 2 that also can replace two stage compression types adopts the compressing mechanism 102 of the compressing mechanism 103,104 of two stage compression types that are connected in parallel, and forms refrigerant line 910.
In this structure; Owing to omitted bridge circuit 17; Therefore, when switching mechanism 3 becomes heating during operating condition, the heat source side of flowing through heat exchanger 4 and utilize cold-producing medium between the side heat exchanger 6 flow through the successively side of utilization expansion mechanism 5c, receiver the 18, the 1st expansion mechanism 5a; This point is different with refrigerant line 810 (with reference to Figure 13), but also can obtain and above-mentioned same action effect.
(8) other embodiment
More than, according to accompanying drawing embodiment of the present invention and variation thereof are illustrated, still, concrete structure is not limited to these embodiments and variation thereof, in the scope that does not break away from inventive concept, can change.
For example; In above-mentioned embodiment and variation thereof; Use the cold-producing medium of conduct and the side's of the utilization interchanger 6 of flowing through to carry out the heating source of heat exchange or the water and the salt solution of cooling source; And be provided with and be used for making in utilizing side heat exchanger 6 secondary heat exchanger that is carried out heat exchange by the water of heat exchange and salt solution and room air, also can in the aircondition of this so-called cooling-water machine formula, use the present invention.
In addition, even the refrigerating plant of other type of the aircondition of above-mentioned cooling-water machine formula as long as use the cold-producing medium of in supercritical region, working to carry out multi-stage compression formula kind of refrigeration cycle then as cold-producing medium, so, also can be used the present invention.
In addition, be not to be defined in carbon dioxide as the cold-producing medium of in supercritical region, working, also can use ethene, ethane and nitrogen oxide etc.
Industrial applicibility
Utilize the present invention, in the refrigerating plant that carries out multi-stage compression formula kind of refrigeration cycle,, can prevent that also the cold-producing medium that is inhaled in the rear-stage side compression member from becoming moisture state even under the low operating condition of the heat source temperature of intercooler.
Claims (6)
1. a refrigerating plant (1), it comprises:
Compressing mechanism (2,102), this compressing mechanism (2,102) has a plurality of compression member, utilizes the rear-stage side compression member in said a plurality of compression member to compress the cold-producing medium that the preceding-stage side compression member from said a plurality of compression member is discharged successively;
Heat source side heat exchanger (4);
Utilize side heat exchanger (6);
Intercooler (7); This intercooler (7) is set at the cold-producing medium that is used for discharging from said preceding-stage side compression member and is drawn into the intermediate refrigerant pipe (8) of said rear-stage side compression member, is inhaled into the cooler of the cold-producing medium the said rear-stage side compression member as discharging from said preceding-stage side compression member; With
According to the intercooler bypass pipe (9) that the mode of walking around said intercooler is connected with said intermediate refrigerant pipe, this refrigerating plant (1) is characterised in that:
Be sent to the saturation temperature of cold-producing medium of said rear-stage side compression member when following when the outlet refrigerant temperature of the heat source temperature of said intercooler or said intercooler becomes from said preceding-stage side compression member, utilize said intercooler bypass pipe to make the do not flow through damp proof control of said intercooler of cold-producing medium.
2. refrigerating plant as claimed in claim 1 (1) is characterized in that:
Said intercooler (7) is with the heat exchanger of air as thermal source.
3. refrigerating plant as claimed in claim 1 (1) is characterized in that:
Said intercooler (7) is with the heat exchanger of water as thermal source,
In said damp proof control, also stop to supply water to said intercooler.
4. a refrigerating plant (1) is characterized in that, comprising:
Compressing mechanism (2,102), this compressing mechanism (2,102) has a plurality of compression member, utilizes the rear-stage side compression member in said a plurality of compression member to compress the cold-producing medium that the preceding-stage side compression member from said a plurality of compression member is discharged successively;
Heat source side heat exchanger (4);
Utilize side heat exchanger (6); With
Intercooler (7); This intercooler (7) is with the heat exchanger of water as thermal source; It is set at the cold-producing medium that is used for discharging from said preceding-stage side compression member and is drawn in the intermediate refrigerant pipe (8) the said rear-stage side compression member; And can will be inhaled into the cooler of the cold-producing medium the said rear-stage side compression member as discharging from said preceding-stage side compression member
Be sent to the saturation temperature of cold-producing medium of said rear-stage side compression member when following when the outlet refrigerant temperature of the heat source temperature of said intercooler or said intercooler becomes from said preceding-stage side compression member, reduce the damp proof control of flow of the water of the said intercooler of flowing through.
5. refrigerating plant as claimed in claim 4 (1) is characterized in that:
In said damp proof control, also control the flow of the water of the said intercooler of flowing through, so that the outlet refrigerant temperature of said intercooler (7) is higher than the saturation temperature of the cold-producing medium that is sent to said rear-stage side compression member from said preceding-stage side compression member.
6. like each described refrigerating plant (1) in the claim 1～5, it is characterized in that, also comprise:
Rear-stage side playpipe (18c, 19), this rear-stage side playpipe (18c, 19) makes it return said rear-stage side compression member to flowing through said heat source side heat exchanger (4) and saidly utilize the cold-producing medium between the side heat exchanger (6) to shunt.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008019764A JP5141269B2 (en) | 2008-01-30 | 2008-01-30 | Refrigeration equipment |
| JP2008-019764 | 2008-07-31 | ||
| PCT/JP2009/051235 WO2009096372A1 (en) | 2008-01-30 | 2009-01-27 | Refrigeration device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101932891A CN101932891A (en) | 2010-12-29 |
| CN101932891B true CN101932891B (en) | 2012-09-26 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2009801035683A Active CN101932891B (en) | 2008-01-30 | 2009-01-27 | Refrigeration device |
Country Status (8)
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| US (1) | US20110005269A1 (en) |
| EP (1) | EP2251622B1 (en) |
| JP (1) | JP5141269B2 (en) |
| KR (1) | KR101157802B1 (en) |
| CN (1) | CN101932891B (en) |
| AU (1) | AU2009210093B2 (en) |
| ES (1) | ES2685433T3 (en) |
| WO (1) | WO2009096372A1 (en) |
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| EP2737264B1 (en) | 2011-07-26 | 2020-07-22 | Carrier Corporation | Startup logic for refrigeration system |
| EP2551401A1 (en) * | 2011-07-28 | 2013-01-30 | Electrolux Home Products Corporation N.V. | A heat pump system for a laundry dryer |
| EP2551402A1 (en) * | 2011-07-28 | 2013-01-30 | Electrolux Home Products Corporation N.V. | A heat pump system for a laundry dryer |
| JP5403029B2 (en) * | 2011-10-07 | 2014-01-29 | ダイキン工業株式会社 | Refrigeration equipment |
| JP5288020B1 (en) * | 2012-03-30 | 2013-09-11 | ダイキン工業株式会社 | Refrigeration equipment |
| US20160015818A1 (en) * | 2014-07-18 | 2016-01-21 | Medipath, Inc. | Compositions and methods for physiological delivery using cannabidiol |
| SG11202012506VA (en) | 2018-11-12 | 2021-05-28 | Carrier Corp | Compact heat exchanger assembly for a refrigeration system |
| CN111256388B (en) * | 2018-11-30 | 2021-10-19 | 广东美芝精密制造有限公司 | Refrigeration system |
| EP3980699A1 (en) | 2019-06-06 | 2022-04-13 | Carrier Corporation | Refrigerant vapor compression system |
| JP7356049B2 (en) * | 2019-09-30 | 2023-10-04 | ダイキン工業株式会社 | air conditioner |
| JP7343765B2 (en) * | 2019-09-30 | 2023-09-13 | ダイキン工業株式会社 | air conditioner |
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Also Published As
| Publication number | Publication date |
|---|---|
| KR101157802B1 (en) | 2012-06-22 |
| WO2009096372A1 (en) | 2009-08-06 |
| AU2009210093A1 (en) | 2009-08-06 |
| EP2251622A4 (en) | 2017-03-29 |
| US20110005269A1 (en) | 2011-01-13 |
| EP2251622B1 (en) | 2018-08-01 |
| KR20100113574A (en) | 2010-10-21 |
| JP5141269B2 (en) | 2013-02-13 |
| ES2685433T3 (en) | 2018-10-09 |
| EP2251622A1 (en) | 2010-11-17 |
| JP2009180428A (en) | 2009-08-13 |
| AU2009210093B2 (en) | 2011-09-15 |
| CN101932891A (en) | 2010-12-29 |
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