CN1670450A - Refrigerating machine - Google Patents
Refrigerating machine Download PDFInfo
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- CN1670450A CN1670450A CNA2005100563939A CN200510056393A CN1670450A CN 1670450 A CN1670450 A CN 1670450A CN A2005100563939 A CNA2005100563939 A CN A2005100563939A CN 200510056393 A CN200510056393 A CN 200510056393A CN 1670450 A CN1670450 A CN 1670450A
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- gas
- heat
- intermediate pressure
- compressor
- liquid separator
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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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
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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
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/04—Preventing the formation of frost or condensate
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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
- 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
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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
- F25B2400/13—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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2511—Evaporator distribution 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
- 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
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
- F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
- F25D17/042—Air treating means within refrigerated spaces
- F25D17/045—Air flow control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
- F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
- F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
- F25D17/065—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators with compartments at different 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
- F25D2317/0682—Two or more fans
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
- F25D2400/04—Refrigerators with a horizontal mullion
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Compressor (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
A refrigerating machine is equipped with a compressor 1, a radiator 2, a pressure-reducing device 3, a gas-liquid separator 4, a unit for introducing the gas refrigerant separated in gas-liquid separator 4 into an intermediate pressure portion of the compressor, and a low pressure side circuit 9 in which liquid refrigerant separated in the gas-liquid separator is circulated. The low pressure side circuit 9 is provided with a heat absorbing unit 10 which selectively functions in different temperature zones. When the heat absorbing unit 10 is made to function in a high temperature zone, the gas refrigerant separated in the gas-liquid separator is inhibited from being introduced into the intermediate pressure portion of the compressor 1 is inhibited, or allowed to be introduced into another intermediate pressure portion which is lower in pressure than the intermediate pressure portion.
Description
Technical field
The present invention relates to comprise the refrigerating plant of the mechanism of the intermediate pressure department that the cold-producing medium of separating in the gas-liquid separator can be incorporated into compressor.
Background technology
Usually, known a kind of refrigerating plant, wherein possess compressor, radiator, decompressor, gas-liquid separator, it possesses, and this gas-liquid can be divided isolated gas refrigerant in the device be incorporated into mechanism's (opening the 2003-106693 communique with reference to the spy) of the intermediate pressure department of above-mentioned compressor.In this refrigerating plant, because isolated gas refrigerant in the above-mentioned gas-liquid separator is incorporated into the intermediate pressure department of above-mentioned compressor with the original state of gas, so can obtain to improve the effect of the efficient of this compressor.
But, in this existing refrigerating plant, the heat-absorbing body be included in the freeze cycle optionally at the heat dump of different temperatures zone performance function is set sometimes.
For example, it is applied in possesses refrigerating chamber, under the situation of the freezer of refrigerating chamber, disposed the heat dump that in freeze cycle, plays refrigeration or refrigeration, utilize the function of one of them heat dump, can refrigerate or freezing running.But in this case, no matter be in which kind of when running, do not reduce its efficient and the high efficiency running is important.
Summary of the invention
Therefore, the objective of the invention is to, provide a kind of and in freeze cycle, be provided with optionally under the situation of the heat-absorbing body of different temperatures zone performance function, no matter be in which temperature province, can not reduce its efficient and the refrigerating plant that can high efficiency turns round.
In order to achieve the above object, the present invention is a kind of refrigerating plant, comprising compressor, radiator, decompressor, gas-liquid separator, it possess can will isolated gas refrigerant be introduced the intermediate pressure department of described compressor in this gas-liquid separator mechanism; And possesses the low-pressure side loop that makes isolated liquid refrigerant circulation in the described gas-liquid separator; In this low-pressure side loop, possesses optionally heat-absorbing body in different temperatures zone performance function; And possess and make this heat-absorbing body under the situation of high-temperature area performance function, the isolated gas refrigerant of blocking gas-liquid separator institute to the introducing of described compressor intermediate pressure department or gas refrigerant is incorporated into the also low low-pressure side of the described compressor intermediate pressure department of pressure ratio other intermediate pressure departments, blocking introducing switching mechanism.
The part that switching mechanism is introduced in described gas refrigerant blocking can be made of switch valve.In addition, the other part of described gas refrigerant blocking introducing switching mechanism also can and divide bronchus constitute by triple valve.
Described heat-absorbing body possesses a plurality of heat dumps in different temperatures zone performance function; Each heat dump is optionally brought into play function, and possesses and will also can through the cold wind of this heat dump to being controlled as the mechanism that introduce the chamber in corresponding temperature zone separately.Described heat dump can be arranged on and be controlled as the indoor of corresponding temperature province separately.Described heat-absorbing body also can possess one optionally at the heat dump of different temperatures zone performance function, and possess cold wind through this heat dump, by switching damper, introduce being controlled as the mechanism of a plurality of chambers in different temperatures zone separately selectively.Described heat dump also can be arranged on and be controlled as the indoor of low temperature zone.In all cases, can be enclosed in the cold-producing medium that running mesohigh side becomes supercritical pressure.
In addition, constitute gas refrigerant by described triple valve and branch bronchus and introduce mechanism, thereby isolated gas refrigerant can be incorporated into first intermediate pressure department of described compressor in the gas-liquid separator, or than second intermediate pressure department of the more close low pressure of this first intermediate pressure department suction side.Under the situation that heat-absorbing body is worked in the low temperature zone, isolated gas refrigerant in the described gas-liquid separator is incorporated into first intermediate pressure department of described compressor; Under the situation about working in the high-temperature zone, this gas refrigerant is incorporated into second intermediate pressure department of described compressor.
In this case, above-mentioned heat-absorbing body also can possess a plurality of heat dumps in different mutually temperature province performance functions; Each heat dump is optionally brought into play function, and possesses to be incorporated into through the cold wind of this heat dump and be controlled as the indoor mechanism in corresponding temperature zone separately.In addition, also can be arranged on above-mentioned heat dump and be controlled as the indoor of corresponding temperature zone separately.
Moreover above-mentioned heat-absorbing body also can possess optionally a heat dump in different temperatures zone performance function; And possess the cold wind through this heat dump, optionally be incorporated into a plurality of indoor mechanism that is controlled as the different temperatures zone by switching damper.In this case, also can be arranged on heat dump and be controlled as the indoor of low temperature zone.For above-mentioned all situations, also can be enclosed in the cold-producing mediums such as carbon dioxide that running mesohigh side becomes supercritical pressure.
In the present invention, because in making the low-pressure side loop of liquid refrigerant circulation, possess optionally heat-absorbing body in different temperatures zone performance function, and possess at this heat-absorbing body under the situation of high-temperature zone performance function, the gas refrigerant that the gas refrigerant that blocking is gone out by gas-liquid separator separates is introduced to the intermediate pressure department of compressor interdicts mechanism, so in each temperature province, can both the high efficiency running.
In the present invention, owing in making the low-pressure side loop of liquid refrigerant circulation, possess optionally heat-absorbing body in different temperatures zone performance function, and possess: under the situation of low temperature zone performance function, the gas refrigerant that is come out by gas-liquid separator separates is incorporated into first intermediate pressure department of compressor at this heat-absorbing body; Under the situation of high-temperature zone performance function, this gas refrigerant be incorporated into compressor second intermediate pressure department, gas refrigeration introduce mechanism, so, can both high efficiency turn round in each temperature province.
Description of drawings
Fig. 1 is the refrigerant loop figure of first embodiment of the refrigerating plant that the present invention relates to of expression.
Fig. 2 is the enthalpy pressure line chart of freeze cycle.
Fig. 3 is the figure of suitable example of the freezer of expression first embodiment.
Fig. 4 is the figure of expression to the suitable example of freezer.
Fig. 5 is the refrigerant loop figure of the variation of expression first embodiment.
Fig. 6 is the figure of expression to the suitable example of freezer.
Fig. 7 is the figure of expression to the suitable example of freezer.
Fig. 8 is the refrigerant loop figure of second embodiment of the refrigerating plant that the present invention relates to of expression.
Fig. 9 is the enthalpy pressure line chart of freezing running.
Figure 10 is the figure to the suitable example of freezer of expression second embodiment, and is corresponding with Fig. 3.
Figure 11 is the figure of expression to the suitable example of freezer, and is corresponding with Fig. 4.
Figure 12 is the refrigerant loop figure of the variation of expression second embodiment, and is corresponding with Fig. 5.
Figure 13 is the figure of expression to the suitable example of freezer, and is corresponding with Fig. 6.
Figure 14 is the figure of expression to the suitable example of freezer, and is corresponding with Fig. 7.
The specific embodiment
Below, embodiments of the present invention are described with reference to the accompanying drawings.
Fig. 1 is the refrigerant loop figure of expression first embodiment of the present invention.This refrigerating plant 30 is to possess compressor 1, radiator 2, first expansion valve (decompressor) 3, gas-liquid separator 4 in order and constitute.Constitute the loop, high-pressure side from this compressor 1 through the refrigerant loop of radiator 2 till the porch of first expansion valve 3.Above-mentioned compressor 1 is a split-compressor, comprises one-level compression unit 1A and secondary compression unit 1B, also possesses intercooler 1C between one-level compression unit 1A and secondary compression unit 1B.The 8th, check-valves.In addition, this refrigerating plant 30 also comprises: the mechanism 5 that the gas refrigerant of separating in the gas-liquid separator 4 can be incorporated into the intermediate pressure department of compressor 1.In this formation, intermediate pressure department is meant between intercooler 1C and the secondary compression unit 1B.Compressor 1 herein is not limited to split-compressor.For example, if its stage compressor is then introduced mechanism 5 so long as can to get back to the parts of intermediate pressure department of a stage compressor just passable.This introducing mechanism 5 is made of tracheae 6 and the switch valve 91 that is arranged in this tracheae 6.Thus, according to the switching of switch valve 91, gas refrigerant begins or stops to the introducing of intermediate pressure department.
In addition, this refrigerating plant 30 is provided with the low-pressure side loop 9 that makes the liquid refrigerant circulation usefulness that gas-liquid separator 4 separates, and in this low-pressure side loop 9, is provided with optionally the heat-absorbing body 10 in different temperatures zone performance function.This heat-absorbing body 10 constitutes and comprises second expansion valve 11 and a heat dump 14.By controlling the valve opening of this second expansion valve 11, thereby can control an evaporating pressure in the heat dump 14.If evaporating pressure herein raises, then the evaporating temperature in the heat dump 14 raises, and becomes the refrigeration running.In addition, if evaporating pressure herein descends, then evaporating temperature reduces, and becomes freezing running.Through the cold-producing medium of this heat dump 14, turn back to the suction portion of compressor 1 through check-valves 8.
In the present embodiment, constitute and comprise: will optionally be incorporated into through the cold wind of heat dump 14 and be controlled as the mechanism 23 of a plurality of chambers in different temperatures zone (refrigerating chamber 21, refrigerating chamber 22) separately.This mechanism 23 comprises air-supply passage 24 and switches damper 25, be connected with the controller 26 that switches refrigeration, freezing running on this switching damper 25.
This controller 26 also connects expansion valve 3,11 and switch valve 91.For example, under the situation that the load of refrigerating chamber 22 increases, make and switch damper 25 and swing to shown position, cold wind is introduced refrigerating chamber 22 (freezing running).When this freezing running, open switch valve 91, shown in dotted arrow, 4 isolated gas refrigerants of gas-liquid separator are incorporated into the intermediate pressure department of compressor 1.In addition, under the situation that the load of refrigerating chamber 21 increases, make and switch damper 25 and swing to the position opposite, cold wind is incorporated into refrigerating chamber 21 (refrigeration running) with shown position.When this refrigeration running, close switch valve 91, the blocking gas refrigerant is to the introducing of the intermediate pressure department of compressor 1.Switch valve 91 constitutes gas refrigerant blocking mechanism.
In summer, the situation or the load that reach more than 30 ℃ according to outside air temperature become big conditions such as situation, are enclosed in the cold-producing medium that running mesohigh side becomes supercritical pressure in above-mentioned refrigerant loop, such as carbon dioxide coolant.Can be in the loop, high-pressure side with the cold-producing medium of supercritical pressure running, other also have for example ethene, diborane, ethane, nitrogen oxide etc.
In the above-described configuration, in low-pressure side loop 9, circulate, can not be applied to cooling even make by gas-liquid separator 4 isolated gas refrigerants; Cold-producing medium is turned back to the suction of one-level compression unit 1A, can reduce the efficient of freeze cycle.
Therefore, though gas refrigerant is introduced the intermediate pressure department of compressor 1, but in the present embodiment, control according to above-mentioned controller 26, when the low freezing running of temperature province, this gas refrigerant is incorporated into the intermediate pressure department of compressor 1, and when the high refrigeration of temperature province is turned round, interdicts the introducing of gas refrigerant to this intermediate pressure department.
Fig. 2 is that expression and refrigeration, freezing running have nothing to do, ph line chart under the situation of the first intermediate pressure department X that gas refrigerant is introduced in compressor 1, secondary compression compound expansion circulation.
In Fig. 2, when carrying out freezing running (freezing about-26 ℃), form the running of representing with solid line.(1) is the suction casing of one-level compression unit 1A; (2) be the discharge section of one-level compression unit 1A; (3) suction casing of secondary compression unit 1B; (4) be the discharge section of secondary compression unit 1A.Cold-producing medium from compressor 1 is discharged circulates and is cooled by radiator 2.(5) be the inlet of first expansion valve 3, (6) are the outlets of first expansion valve 3.In this state, become the biphasic mixture of gas/liquid.
The gas here and the ratio of liquid are equivalent to the ratio of the length along path of the length along path of L1 (gas) and L2 (liquid).This cold-producing medium enters gas-liquid separator 4 with the state of two-phase mixture.Then, at this gas refrigerant of separating, with regard to the intermediate pressure department that is introduced in compressor 1 be intercooler 1C and secondary compression unit 1B between.(21) be the outlet of gas-liquid separator 4, arrive the suction casing of the secondary compression unit 1B of (3), in secondary compression unit 1B, be compressed through the cold-producing medium here.On the other hand, the liquid refrigerant of separating in gas-liquid separator 4 is circulation in low-pressure side loop 9.(7) being the outlet of gas-liquid separator 4, is the inlet of second expansion valve 11; (8) be the outlet of second expansion valve 11; (22) be the outlet of heat dump 14.Enter the liquid refrigerant of this heat dump 14, evaporation also absorbs heat.(1) is the suction casing of one-level compression unit 1A.
In contrast, when refrigerating running (refrigerating about-5 ℃), form the circulation that is represented by dotted lines.Promptly, according to (9) is that suction casing, (10) of one-level compression unit 1A are that the discharge section (11) of one-level compression unit 1A is that suction casing, (12) of secondary compression unit 1B are that the discharge section of secondary compression unit 1B, the inlet that (5) are first expansion valve 3, the outlet that (13) are first expansion valve 3, the outlet that (14) are gas-liquid separator 4, the inlet of second expansion valve 11, outlet, (9) that (15) are second expansion valve 11 are the orders of the suction casing of one-level compression unit 1A, and state changes.
But if with reference to Fig. 2, outlet pressure (6) in the circulation (during freezing running) of outlet pressure (13) in the then circulation of dotted line when running (refrigeration), first expansion valve 3 and solid line, first expansion valve 3 is compared, and is quite high.If the outlet pressure of first expansion valve 3 uprises, the gas flow that then enters in the cold-producing medium before the gas-liquid separator 4 tails off.As mentioned above, this is because the ratio of the porch gas of gas-liquid separator 4 and liquid is equivalent to the cause of the ratio of the ratio of L1 (gas) and L2 (liquid) or L3 (gas) and L4 (liquid).Corresponding therewith, when the circulation that is in solid line (during freezing running), a large amount of gas refrigerants is introduced in the intermediate pressure department of compressor 1; But when being in the circulation (during the refrigeration running) of dotted line, the amount of the gas refrigerant of introducing just becomes seldom.
That is, when carrying out freezing running, the gas refrigeration dosage that is incorporated into the intermediate pressure department of compressor 1 increases, and to cooling off the part amount that inoperative gas flow does not circulate in low-pressure side loop 9, just can play the effect of the efficient that improves freezing running.Particularly, in this formation, because of in refrigerant loop, enclosing carbon dioxide coolant, so in the ratio of gas that gas-liquid separator 4 is separated and liquid, compare with fluon class cold-producing medium, gas flow increases, and is incorporated into the intermediate pressure department of compressor 1 by the gas flow that these are had more, thereby can seek to obtain higher efficient.In contrast to this, when the high refrigeration of temperature province is turned round, because of the generation (L3) of the gas refrigerant of the intermediate pressure department of introducing compressor 1 itself less, even there is the formation of introducing gas refrigerant the there, for example, compare with the complexity of pipe arrangement formation etc., can not improve how much freeze cycle efficient.
In the present embodiment, only when freezing running more efficiently, gas refrigerant is incorporated into the intermediate pressure department of compressor 1, when carrying out the high refrigeration of temperature province running, because of being arranged, blocking introduces the formation of gas refrigerant to intermediate pressure department, can constitute and simple control with simple pipe arrangement, realize variable circulation, can seek the raising of freeze cycle efficient.
In addition, in the present embodiment, the whole of heat-absorbing body 10 in different temperatures zone performance function are second expansion valve 11 and heat dumps 14 selectively, because of being arranged in the low-pressure side loop 9, even so for example refrigerate when turning round or under the situation of freezing running, its efficient can not descend yet, and can turn round very efficiently.
Fig. 3 is the suitable example of expression to freezer.
This freezer 40 constitutes at epimere to be possessed refrigerating chamber 41, possesses refrigerating chamber 42 at hypomere.Be provided with spaced walls 43 in the storehouse in the inside of this refrigerating chamber 42.Be provided with above-mentioned heat dump 14 in the air channel 44 by 43 intervals of spaced walls in this storehouse.Switch damper 45 in the inlet A in above-mentioned air channel 44 configuration first, this first switches damper 45 and switches between the position of the inlet A that closes air channel 44 (dotted line position) and the position (solid line position) of opening.In addition, form rear side air channels 46 at the rear wall 47 of freezer 40, switch damper 45 and switch under the situation of dotted line position when first, by this rear side air channel 46, the inlet A in air channel 44 is communicated with refrigerating chamber 41.In addition, the outlet B in above-mentioned air channel 44 disposes fan 48 and second and switches damper 49, and this second switching damper 49 switches between the position of the outlet B that cuts out air channel 44 (dotted line position) and open position (solid line position).On this solid line position, second switches the opening 51 that damper 49 stops up middle ware next door 50.
In the above-described configuration, compressor 1 is connected in freezing running, and fan 48 is connected, and switch valve 91 is opened, and each damper 45,49 switches to solid line position.Thus, the air in the refrigerating chamber 42 circulates in heat dump 14, and supplies with to refrigerating chamber 42.In the refrigeration running, switch valve 91 cuts out, each damper 45,49 switches to dotted line position.Thus, the air in the refrigerating chamber 41 enters air channel 44 by rear side air channel 46, circulation 4 in heat dump 1, and to refrigerating chamber 41 supplies.
Fig. 4 represents other formations.Under situation about comparing with Fig. 3, the damper at place, the gateway in air channel 44 constitutes different.The damper of inlet A is made of two damper 145A, 145B; The damper of outlet B is made of two damper 149A, 149B.Even such formation also can obtain essentially identical action effect.
Fig. 5 represents the formation of the refrigerant loop of first embodiment.
In this formation, under situation about comparing with Fig. 1, the formation of heat-absorbing body 10 is different.This heat-absorbing body 10 constitutes and comprises: connect with heat dump 57, with these second capillaries 13 that are arranged in parallel, with the second capillary 13 freezing usefulness heat dump 58 of setting of triple valve 11, first capillary 12, the refrigeration that is provided with of connecting with first capillary 12.The 59th, check-valves.By the conversion of triple valve 11, if cold-producing medium flows into first capillary 12, the flow that then flows into a heat dump 14 increases, and will refrigerate running.In addition, if cold-producing medium flows into second capillary 13, the flow that then flows into a heat dump 14 reduces, and will carry out freezing running.
Fig. 6 represents the suitable example to freezer.
This freezer 40 constitutes at epimere to be possessed refrigerating chamber 41, possesses refrigerating chamber 42 at hypomere.And, be respectively equipped with spaced walls 61,62 in the storehouse in the inside of each chamber 41,42, in by this storehouse, dispose above-mentioned heat dump 57,58 and fan 63,64 in spaced walls 61,62 air channel 44 at interval.In this formation, along with thermal starting, the heat of refrigeration running and freezing running are closed, crossover tee valve 11 makes cold-producing medium flow into one of them heat dump 57,58, drives corresponding fan 62,63.
Fig. 7 represents other formations.Under situation about comparing with Fig. 6, the formation of heat-absorbing body 10 is different.This heat-absorbing body 10 has omitted triple valve, and motor-driven valve 65,66 is connected in series with each capillary 12,13 respectively.In this formation, along with thermal starting, the heat of refrigeration running and freezing running are closed, said electric valve 65,66 is opened or closed, cold-producing medium is flowed in any one heat dump in the heat dump 57,58, to drive corresponding fan 62,63 selectively.Even in such embodiment, also can obtain essentially identical action effect.
Though according to above-mentioned embodiment the present invention has been described, the present invention is not limited to these, also can implement various changes.In the above-described embodiment, constitute gas refrigerant blocking mechanism by switch valve 91, but be not limited to this, such as, if when freezing running, can introduce gas flow the intermediate pressure department of compressor 1, and when the refrigeration running, can interdict its introducing, then also can be that loop that form constitutes by assembling check-valves etc. is back.In addition, in the above-described embodiment, enclosed carbon dioxide coolant at refrigerant loop, but be not limited to this, also be applicable to inclosure fluon family cold-producing medium in addition, this is certain.In addition, above-mentioned introducing mechanism 5 is so long as just passable the intermediate pressure department that gas flow is incorporated into compressor 1 according to its operating condition, and its concrete formation with and to introduce the position can be arbitrarily.
In the above-described embodiment, when refrigeration when running of carrying out the high-temperature region, be prerequisite less with the gas refrigerant generation (L3) of the intermediate pressure department of introducing compressor 1 itself, it is characterized in that interdicting gas refrigerant to intermediate pressure department.Yet, under the generation (L3) of gas refrigerant and many situation, make cooling off inoperative gas refrigerant by formation, thereby can seek the further raising of freezing efficiency not in the formation of low tension loop side circulation.
The following describes:, by gas refrigerant is introduced compressor 1, and can realize the embodiment of the efficient activity of freezing running in when running refrigeration.
Fig. 8 is the refrigerant loop figure of expression second embodiment of the present invention.This refrigerating plant 130 has the formation identical with the refrigerant loop of first embodiment except the formation of a part.Below, describe with the different centers of constituting, attached to identical or corresponding inscape with identical symbol, and omit its detailed explanation.
This refrigerating plant 130 replaces the switch valve 91 as gas refrigerant blocking mechanism that is possessed in first embodiment, but possesses the first intermediate pressure department X that isolated gas refrigerant in the gas-liquid separator 4 can be incorporated into compressor 1 or than the mechanism 105 in any one of the second intermediate pressure department Y of the more close low pressure of this first intermediate pressure department X suction side.In this formation, the first intermediate pressure department X is the centre of intercooler 1C and secondary compression unit 1B, and the second intermediate pressure department Y is in the way of one-level compression unit 1A.The compressor 1 here is not limited to split-compressor.
This introducing mechanism 105 by tracheae 6, be located at the triple valve 81 in this tracheae 6 and constitute from two branch bronchuses 82,83 of these triple valve 81 branches, wherein a side branch bronchus 82 is connected with the first intermediate pressure department X, another minute bronchus 83 be connected with the second intermediate pressure department Y.And, constitute gas refrigerant at this by triple valve 81 and branch bronchus 83 and introduce mechanism.Therefore, by the switching of triple valve 81, if tracheae 6 and branch bronchus 82 communicate, then shown in dotted arrow, gas refrigerant is introduced into the first intermediate pressure department X; If tracheae 6 and branch bronchus 83 communicate, then gas refrigerant is introduced into the second intermediate pressure department Y.The triple valve 81 here is not limited to electromagnetic type, also can consider differential pressure drive-type etc.
This controller 26 is connected on compressor 1 and expansion valve 3,11 and the triple valve 81, for example under the situation that the load of refrigerating chamber 22 increases, enlarge the valve opening of second expansion valve 11, strengthen the flow that flows into a heat dump 14, allow switching damper 25 swing to illustrated position, cold wind is introduced refrigerating chamber 22 (freezing running).When this freezing running, according to the switching of triple valve 81, make tracheae 6 and divide bronchus 82 to be communicated with, shown in dotted arrow, gas-liquid separator 4 isolated gas refrigerants are introduced the first intermediate pressure department X.In addition, under the situation that the load of refrigerating chamber 21 increases, swing to the position opposite, cold wind is introduced refrigerating chamber 21 (refrigeration running) with shown position with switching damper 25.When this freezing running, by the switching of triple valve 81, make tracheae 6 and divide bronchus 83 to communicate, gas refrigerant is introduced the second intermediate pressure department Y.
Same with first embodiment, in above-mentioned refrigerant loop, in summer, the situation or the load that reach more than 30 ℃ according to outside air temperature become big conditions such as situation, and the high-pressure side became the cold-producing medium of supercritical pressure when inclosure had running, as carbon dioxide coolant.In the cold-producing medium with supercritical pressure running in the loop, high-pressure side, can also enumerate as ethene, diborane (diborane), ethane, nitrogen oxide etc.
In the above-described configuration, make gas-liquid separator 4 isolated gas refrigerants,, it is turned back to the suction inlet of one-level compression unit 1A, then can reduce the efficient of freezing running even circulation in low-pressure side loop 9 can not be applied to cooling.Therefore, gas refrigerant is introduced the intermediate pressure department of compressor 1.Yet, as described in first embodiment,,, the efficient of freezing running is not had much influences yet even allow it in low-pressure side loop 9, circulate if the generation of gas refrigerant (L3) is few.In other words, if a spot of like this gas refrigerant is only introduced the pars intermedia of compressor, then can not improve the efficient of freezing running.Therefore, in the present embodiment, by control according to above-mentioned controller 26, when carrying out the low freezing running of temperature province, this gas refrigerant is only introduced the first intermediate pressure department X of compressor 1, and when the high refrigeration of temperature province is turned round, introduce the second intermediate pressure department Y, thereby seek further to raise the efficiency than the low pressure suction side of the more close compressor 1 of this first intermediate pressure department X.
Fig. 9 is expression: when the low freezing running of temperature province, the first intermediate pressure department X of gas refrigerant introducing compressor 1; When the high refrigeration of temperature province running, be incorporated under the situation than the second intermediate pressure department Y of the more close low pressure of this first intermediate pressure department X suction side the ph line chart of secondary compression compound expansion circulation.At this, irrelevant with refrigeration, freezing running, Fig. 2 and Fig. 9 of its gas refrigerant of expression being introduced the ph line chart under the situation of the first intermediate pressure department X of compressor 1 compare.
In Fig. 2 and Fig. 9, when freezing running (freezing about-26 ℃), form the circulation of representing with solid line respectively.(1) is the suction casing of one-level compression unit 1A; (2) be the discharge section of one-level compression unit 1A; (3) be the suction casing of secondary compression unit 1B; (4) be the discharge section of secondary compression unit 1B.Cold-producing medium from compressor 1 is discharged circulates and is cooled by radiator 2.(5) be the inlet of first expansion valve 3; (6) be the outlet of first expansion valve 3, under this state, become the two-phase mixture of gas/liquid.
The gas here and the ratio of liquid are equivalent to the ratio of the length along path of the length along path of L1 (gas) and L2 (liquid).This cold-producing medium enters gas-liquid separator 4 with the state of two-phase mixture.Then, the gas refrigerant of here separating, the intermediate pressure department that is introduced in compressor 1 be intercooler 1C and secondary compression unit 1B between.(21) be the outlet of gas-liquid separator 4, arrive the i.e. suction casing of the secondary compression unit 1B of (3) of the first intermediate pressure department X, in secondary compression unit 1B, be compressed through the cold-producing medium here.On the other hand, isolated liquid refrigerant circulates in low-pressure side loop 9 in the gas-liquid separator 4.(7) be that the outlet of gas-liquid separator 4 is again that the inlet of second expansion valve 11, outlet, (22) that (8) are second expansion valve 11 are the outlets of heat dump 14.Enter the liquid refrigerant evaporates of this heat dump 14 and absorb heat.(1) is the suction casing of one-level compression unit 1A.
In contrast, when the refrigeration running (refrigerating about-5 ℃), form the circulation that is represented by dotted lines.Promptly, in Fig. 9, according to (9) is the suction casing of one-level compression unit 1A, (11) be that the second intermediate pressure department Y is the pars intermedia of one-level compression unit 1A, (12) be the discharge section of one-level compression unit 1A, it is again the inlet of intercooler 1C, (13) be the outlet of intercooler 1C, it is again the suction casing of secondary compression unit 1B, (14) be the discharge section of secondary compression unit 1B, (5) be the inlet of first expansion valve 3, (15) be the outlet of first expansion valve 3, (16) be the outlet of gas-liquid separator 4, it is again the inlet of second expansion valve 11, (17) be the outlet of second expansion valve 11, (9) be the order of the suction casing of one-level compression unit 1A, state changes.
In Fig. 2, the first intermediate pressure department X because of gas refrigerant introducing compressor 1 becomes as described below.Promptly, according to (9) be suction casing, (10) of one-level compression unit 1A be discharge section, (11) of one-level compression unit 1A be the first intermediate pressure department X be the outlet of intercooler 1C, not only be suction casing, (12) of secondary compression unit 1B are the discharge section of secondary compression unit 1B, inlet that (5) are first expansion valve 3, (13) are first expansion valve 3 outlets, outlet that (14) are gas-liquid separator 4, but also be that the inlet of second expansion valve 11, outlet, (9) that (15) are second expansion valve 11 are the orders of the suction casing of one-level compression unit 1A, state changes.
Under the situation of comparison diagram 2 and Fig. 9, as mentioned above, when the freezing running in low temperature zone, gas refrigerant is all introduced the first intermediate pressure department X of compressor 1.Therefore, when this freezing running, in figure separately, form the circulation of essentially identical solid line.
On the other hand, when the high refrigeration of temperature province is turned round, the situation of the first intermediate pressure department X that is introduced into compressor 1 with gas refrigerant among Fig. 2 is relative, in Fig. 9, is introduced in the second intermediate pressure department Y than the more close low pressure of first intermediate pressure department suction side.The pressure of this second intermediate pressure department Y becomes also lower than the pressure of the first intermediate pressure department X, therefore, introduce at gas refrigerant under the situation of the second low intermediate pressure department Y of this pressure, introduce the situation of the first intermediate pressure department X with gas refrigerant and compare, can reduce the pressure of the outlet of first expansion valve 3.
That is, when the refrigeration running, in the circulation that dots, the pressure of the line segment of L5, L6 (Fig. 9) is lower than the pressure of the line segment (Fig. 2) of L3, L4.If the pressure of the outlet of first expansion valve 3 descends, the gas quantitative change that then enters in the cold-producing medium before the gas-liquid separator 4 is many.This also can be from line segment L5 than knowing the also long situation of line segment L3.As mentioned above, this be because the ratio of the gas of the porch of gas-liquid separator 4 and liquid be equivalent to L5 (gas) and L6 (liquid) among Fig. 9 ratio, be equivalent to the cause of the ratio of L3 (gas) among Fig. 2 and L4 (liquid).Therefore, in Fig. 9, compare with Fig. 2, the gas refrigerant quantitative change of intermediate pressure department of introducing compressor 1 is many and can not ignore, and has only cooling off the not part of circulation in low tension loop 9 of inoperative gas flow, could improve the efficient of freezing running.Particularly, in this formation, because of in refrigerant loop, enclosing carbon dioxide coolant, so the gas of in gas-liquid separator 4, separating and the ratio of liquid, compare with fluon family cold-producing medium, it is many that gas flow can become, and by the many gas flows of this change are partly introduced the intermediate pressure department of compressor 1, improves thereby can seek higher efficient.
In addition, in the present embodiment, with whole at the heat-absorbing body 10 of different temperatures zone performance function optionally, promptly second expansion valve 11 and heat dump 14 are located in the low-pressure side loop 9, therefore, no matter be to refrigerate under the situation of running for example, still carry out under the situation of freezing running, do not reduce its efficient, just can carry out extremely high efficiency running.
In addition, by the gas refrigerant of the gas refrigerant of first embodiment blocking mechanism 105 and second embodiment is introduced mechanism 105, for example install in the mode that is connected in series, thereby the decrease in efficiency of the freezing running that causes according to the gas refrigerant generation by when running refrigeration can make two mechanism's change actions.Be specially, discharge side at the gas refrigerant of gas-liquid separator 4 gas refrigerant blocking mechanism 5 is installed, introduce mechanism 105 at the outlet side installation gas refrigerant of this gas refrigerant blocking mechanism 5 and just can.
And, gas refrigerant is introduced mechanism 105 according to its operational situation, be incorporated into first intermediate pressure department of compressor 1 or than second intermediate pressure department of the more close compressor of this first intermediate pressure department 1 suction side, the formation that it is concrete and to introduce the position be arbitrarily.
Figure 10 to Figure 14 is expression, and present embodiment is applied to the example of freezer, be with gas refrigerant interdict mechanism 5 replace with gas refrigerant introduce under the situation of mechanism 105, with the corresponding figure of Fig. 3 to Fig. 7.Because each action in the freezer is identical with the action that describes with reference to Fig. 3 to Fig. 7, so following omission explanation.
As mentioned above, constitute owing to the present invention: when carrying out freezing more efficiently running, gas refrigerant is incorporated into the intermediate pressure department of compressor 1; And when the high refrigeration of temperature province is turned round, pars intermedia than the lower side of pressure of described intermediate pressure department is introduced or be incorporated into to blocking to the gas refrigerant of intermediate pressure department, so constitute with simple pipe arrangement, and according to simple control, just can realize variable circulation, the efficient of seeking freezing running improves.
Above-mentioned first embodiment disclosed gas refrigerant blocking mechanism and the disclosed gas refrigerant of second embodiment are introduced mechanism, can use separately separately, but for example also can be used as the gas refrigerant switching mechanism that possesses two functions, be configured in the tracheae 6 between gas-liquid separator 4 and the compressor 1.In this case, in gas-liquid separator 4 sides gas refrigerant blocking mechanism is set, the configuration gas refrigerant is introduced mechanism between this gas refrigerant blocking mechanism and compressor 1.And, make gas refrigerant blocking mechanism and gas refrigerant introduce mechanism action,, interdict mechanism by gas refrigerant from the gas refrigerant of gas-liquid separator 4 so that when freezing running, further interdict mechanism, and be introduced into the first intermediate pressure department X of compressor by gas refrigerant.In addition, also can constitute: when refrigerating running, for example, situation according to the gas refrigeration dosage in the exit of first expansion valve 3 etc., carry out change action respectively, so that interdicted mechanism's blocking or make it interdict mechanism by gas refrigerant by cryogen from the gas refrigerant of gas-liquid separator 4, introduce mechanism and be introduced into gas refrigerant, further introduce the second intermediate pressure department Y of compressor.
More than, according to embodiment the present invention has been described, but the present invention is not limited to these, also can carry out various enforcement changes.For example, in the above-described configuration, enclosed carbon dioxide coolant, but be not limited to this, also be applicable to inclosure fluon family cold-producing medium in addition etc. certainly at refrigerant loop.
Claims (13)
1, a kind of refrigerating plant is characterized in that,
Comprise: compressor, radiator, decompressor, gas-liquid separator,
Possess can will isolated gas refrigerant be introduced the intermediate pressure department of described compressor in this gas-liquid separator mechanism;
And possesses the low-pressure side loop that makes isolated liquid refrigerant circulation in the described gas-liquid separator;
In this low-pressure side loop, possesses optionally heat-absorbing body in different temperatures zone performance function;
And possess and make this heat-absorbing body under the situation of high-temperature area performance function, the isolated gas refrigerant of blocking gas-liquid separator institute interdicts mechanism to the gas refrigerant of the introducing of described compressor intermediate pressure department.
2, refrigerating plant according to claim 1 is characterized in that, described gas refrigerant interdicts mechanism and is made of switch valve.
3, refrigerating plant according to claim 1 is characterized in that, described heat-absorbing body possesses a plurality of heat dumps in different temperatures zone performance function; Each heat dump works selectively, and possesses and will pass through the cold wind of this heat dump to being controlled as the mechanism of chamber, corresponding temperature zone introducing separately.
4, refrigerating plant according to claim 3 is characterized in that, described heat dump is arranged on and is controlled as the indoor of corresponding temperature province separately.
5, refrigerating plant according to claim 1 is characterized in that,
Comprise that described heat-absorbing body possesses one optionally at the heat dump of different temperatures zone performance function; And possess the cold wind through this heat dump, by switching damper, optionally be incorporated into and be controlled as the mechanism of a plurality of chambers in different temperatures zone separately.
6, refrigerating plant according to claim 5 is characterized in that, described heat dump is located at and is controlled as the indoor of low temperature zone.
7, refrigerating plant according to claim 1 is characterized in that, has enclosed the cold-producing medium that on-stream high-pressure side becomes supercritical pressure.
8, a kind of refrigerating plant is characterized in that,
Comprise: compressor, radiator, decompressor, gas-liquid separator,
Possess first intermediate pressure department that isolated gas refrigerant in this gas-liquid separator can be incorporated into described compressor or than this first intermediate pressure department more near the mechanism of second intermediate pressure department of low pressure suction side;
And possesses the low-pressure side loop that makes the liquid refrigerant circulation that described gas-liquid separator separates goes out;
In this low-pressure side loop, possesses optionally heat-absorbing body in different temperatures zone performance function;
And possess under the situation that this heat-absorbing body works in the low temperature zone, the gas refrigerant that described gas-liquid separator separates is gone out is incorporated into first intermediate pressure department of described compressor, under the situation about working in the high-temperature region, this gas refrigerant be incorporated into described compressor second intermediate pressure department, gas refrigerant introduce mechanism.
9, refrigerating plant according to claim 8 is characterized in that, described heat-absorbing body possesses a plurality of heat dumps in mutual different temperatures zone performance function; Each heat dump optionally works, and possesses to be incorporated into through the cold wind of this heat dump and be controlled as the indoor mechanism in corresponding temperature zone separately.
10, refrigerating plant according to claim 9 is characterized in that, described heat dump is arranged on and is controlled as the indoor of each self-corresponding temperature province.
11, refrigerating plant according to claim 8 is characterized in that, described heat-absorbing body possesses one optionally at the heat dump of different temperatures zone performance function; And possess the cold wind through this heat dump, be incorporated into selectively by the switching damper and be controlled as a plurality of indoor mechanism in different temperatures zone separately.
12, refrigerating plant according to claim 11 is characterized in that, described heat dump is arranged on and is controlled as the indoor of low temperature zone.
13, refrigerating plant according to claim 8 is characterized in that, has enclosed the cold-producing medium that on-stream high-pressure side becomes supercritical pressure.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
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| JP2004079342 | 2004-03-19 | ||
| JP2004079341 | 2004-03-19 | ||
| JP2004079341A JP2005265316A (en) | 2004-03-19 | 2004-03-19 | Refrigeration device |
| JP2004079342A JP4115414B2 (en) | 2004-03-19 | 2004-03-19 | Refrigeration equipment |
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| Publication Number | Publication Date |
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| CN1670450A true CN1670450A (en) | 2005-09-21 |
| CN100338409C CN100338409C (en) | 2007-09-19 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2005100563939A Expired - Fee Related CN100338409C (en) | 2004-03-19 | 2005-03-18 | Refrigerating machine |
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| Country | Link |
|---|---|
| US (1) | US20050204773A1 (en) |
| EP (1) | EP1577622A3 (en) |
| KR (1) | KR100642709B1 (en) |
| CN (1) | CN100338409C (en) |
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| JP3841039B2 (en) * | 2002-10-25 | 2006-11-01 | 株式会社デンソー | Air conditioner for vehicles |
| JP2005257236A (en) * | 2004-03-15 | 2005-09-22 | Sanyo Electric Co Ltd | Freezing device |
| US6973797B2 (en) * | 2004-05-10 | 2005-12-13 | York International Corporation | Capacity control for economizer refrigeration systems |
-
2005
- 2005-03-08 KR KR1020050018959A patent/KR100642709B1/en not_active IP Right Cessation
- 2005-03-15 EP EP05005611A patent/EP1577622A3/en not_active Withdrawn
- 2005-03-16 US US11/080,422 patent/US20050204773A1/en not_active Abandoned
- 2005-03-18 CN CNB2005100563939A patent/CN100338409C/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101688700B (en) * | 2007-06-29 | 2013-03-27 | 大金工业株式会社 | Freezing device |
| CN103216964A (en) * | 2007-11-13 | 2013-07-24 | 开利公司 | Refrigerating system and method used for refrigerating |
| CN103216964B (en) * | 2007-11-13 | 2016-01-20 | 开利公司 | Refrigeration system and the method for freezing |
| CN101765749A (en) * | 2008-06-03 | 2010-06-30 | 松下电器产业株式会社 | Refrigeration cycle device |
| CN102654324A (en) * | 2012-05-24 | 2012-09-05 | 东华大学 | Twin-stage compression heat pump system with hot gas bypass defrosting device |
| CN109983288A (en) * | 2016-11-21 | 2019-07-05 | Bsh家用电器有限公司 | Refrigerating appliance with the optimal storage cell compartment of air humidity |
| CN109990538A (en) * | 2017-12-13 | 2019-07-09 | Lg电子株式会社 | Refrigerator |
| US10969156B2 (en) | 2017-12-13 | 2021-04-06 | Lg Electronics Inc. | Refrigerator having a switchable chamber |
| CN109990538B (en) * | 2017-12-13 | 2021-06-11 | Lg电子株式会社 | Refrigerator with a door |
| CN108444138A (en) * | 2018-04-17 | 2018-08-24 | 山东美琳达再生能源开发有限公司 | A kind of Two-stage Compression low-temperature air source heat pump unit and method with refrigerating function |
| CN109539629A (en) * | 2018-11-15 | 2019-03-29 | 珠海格力电器股份有限公司 | Heat pump equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| US20050204773A1 (en) | 2005-09-22 |
| EP1577622A3 (en) | 2007-01-31 |
| KR100642709B1 (en) | 2006-11-10 |
| CN100338409C (en) | 2007-09-19 |
| EP1577622A2 (en) | 2005-09-21 |
| KR20060043489A (en) | 2006-05-15 |
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Granted publication date: 20070919 |