CN1294672A - Refrigerator - Google Patents
Refrigerator Download PDFInfo
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- CN1294672A CN1294672A CN99804304A CN99804304A CN1294672A CN 1294672 A CN1294672 A CN 1294672A CN 99804304 A CN99804304 A CN 99804304A CN 99804304 A CN99804304 A CN 99804304A CN 1294672 A CN1294672 A CN 1294672A
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- heat exchanger
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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
- F25B13/00—Compression machines, plants or systems, with 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
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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
- 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
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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
- F25B2400/24—Storage receiver heat
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/14—Thermal energy storage
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
A refrigerator, comprising a refrigeration circuit in which a first refrigerant path having a first compressor and an outdoor heat exchanger, a second refrigerant path having a second compressor and a heat exchanger for heat accumulation, and a third refrigerant path having indoor expansion valves and indoor heat exchangers are connected to each other, the refrigerant discharged from the first and second compressors has been condensed in the heat exchanger, it is pressure-reduced in the indoor expansion valves, evaporated in the indoor heat exchangers, and returned to the first and second compressors. The refrigerator can improve the refrigeration capability.
Description
The present invention relates to refrigerating plant, relate in particular to the refrigerating plant that carries out condensation with two kinds of different temperatures.
In the past,, disclosed 1991 No. 28672 communique as Japanese patent of invention and disclosed, the aircondition of heat accumulating type was arranged as refrigerating plant.This aircondition has the main channel that is connected successively by compressor, outdoor heat converter, wealthy, the indoor expansion valve of outdoor expansion and indoor heat converter, and has the accumulation of heat heat exchanger that carries out heat exchange between the accumulation of heat medium that are contained in the heat storage tank and the cold-producing medium.And described aircondition is divided into common cooling operation that can not utilize accumulation of heat and the structures such as accumulation of heat cooling operation of utilizing accumulation of heat.
In this common cooling operation, after the outdoor heat converter condensation,, return compressor in the indoor heat converter evaporation and circulate in indoor expansion valve decompression from the cold-producing medium of compressor.
And, in a kind of form of accumulation of heat cooling operation, cold-producing medium from compressor be emitted in accumulation of heat with condensation the heat exchanger after, in indoor expansion valve, reduce pressure, evaporation returns compressor and circulates in indoor heat converter.
In addition, in another form of accumulation of heat cooling operation, cold-producing medium after the condensation, is used in the heat exchanger by supercooling in accumulation of heat outdoor heat converter from compressor, in indoor expansion valve, reduce pressure then, in indoor heat-exchanging chamber, return compressor after the evaporation and circulate.
So, in described aircondition, utilize accumulation of heat can obtain the reduction and the overcooled increase of cold-producing medium of condensation temperature, and can obtain the raising of refrigerating capacity.
In described aircondition, exist accumulation of heat with may not effectively utilizing cold and hot problem in the heat exchanger.Therefore, a kind of scheme of carrying out the aircondition of two kinds of temperature condensations has been proposed.
In this aircondition, 2 compressors are being set.And the 1st compressor is connected with outdoor heat converter, and the 2nd compressor is connected with heat exchanger with accumulation of heat.The system cooling agent of discharging from above-mentioned the 1st compressor condensation and become liquid refrigerant outdoor heat converter, in addition, the cold-producing medium of discharging from the 2nd compressor becomes liquid refrigerant after the condensation in accumulation of heat with heat exchanger.Then, behind the two liquid refrigerants interflow, in indoor expansion valve, reduce pressure, in indoor heat converter, evaporate, return compressor.
Yet in above-mentioned aircondition, because cold-producing medium is collaborated after the condensation in heat exchanger in outdoor heat converter and accumulation of heat, the supercooling degree that opposes cold-producing medium diminishes.That is to say that because the refrigerant temperature height of the outlet of above-mentioned outdoor heat converter, accumulation of heat is low with the refrigerant temperature of the outlet of heat exchanger, so when two cold-producing mediums mixed, the supercooling degree diminished, existence can not fully improve the problem of refrigerating capacity.
The present invention in view of the above problems, its purpose is, effectively utilizes 2 different heat exchangers of condensation temperature, with the reduction of the supercooling degree that suppresses cold-producing medium and try to achieve the raising of ability.
The present invention makes respectively from the liquid refrigerant of the 1st heat exchanger 23 and the structure of collaborating after shunting and supplying with to the 2nd heat exchanger 32 from the gaseous refrigerant of the 2nd compressor 31.
Specifically, as shown in Figure 1, the 1st technical scheme be have the 1st coolant channel 20 that constitutes by the 1st compressor 21 and the 1st heat exchanger 23, by the 2nd compressor to the 2nd coolant channel 30 that constitutes with the 2nd heat exchanger 32 and the refrigerating circuit 1R that is connected with the 3rd coolant channel 40 that the 3rd heat exchanger 42 constitutes by expansion mechanism E4.And, with the refrigerating plant that carries out the circulation of following cold-producing medium at least as object, promptly the cold-producing medium of discharging from above-mentioned the 1st compressor 21 is the 1st heat exchanger 23 after the condensation, with the cold-producing medium interflow of discharging from the 2nd compressor 31, cold-producing medium in the 2nd heat exchanger 32 behind the interflow is with than after the lower temperature condensation of above-mentioned the 1st heat exchanger 23, in expansion mechanism E4, reduce pressure, in the 3rd heat exchanger 42, get back to the 1st compressor 21 and the 2nd compressor centering after the evaporation.In addition, above-mentioned the 2nd heat exchanger 32 has many passages.Also have, above-mentioned refrigerating circuit 1R is at above-mentioned cold-producing medium circulation time, chilled cold-producing medium collaborates it respectively with after many shuntings of cold-producing medium difference of the 2nd compressor 31 discharges in the 1st heat exchanger 23, and the cold-producing medium behind the interflow flows in each passage of above-mentioned the 2nd heat exchanger 32.
In addition, the 2nd technical scheme is in above-mentioned the 1st technical scheme, and the 1st refrigerant passage 20 of refrigerating circuit 1R has expansion mechanism E9, so that chilled cold-producing medium is shunted after decompression in the 1st heat exchanger 23.
The 3rd technical scheme adopts following structure, that is, in above-mentioned the 1st technical scheme, the 1st heat exchanger 23 is air heat exchangers, and the 2nd heat exchanger 32 is water heat exchangers.
The device of the 4th technical scheme is in above-mentioned the 1st technical scheme, and the 2nd heat exchanger 32 is placed in the heat storage tank 11, with the cold and hot condensation of refrigerant of this heat storage tank 11.
According to above-mentioned specific item, in the 1st technical scheme, at first, when driving the 1st compressor 21 and the 2nd compression power traction, the high-pressure gaseous refrigerant of discharging from the 1st compressor 21 flows into the 1st heat exchanger 23.In the 1st heat exchanger 23, liquefy cold-producing medium after the gaseous refrigerant condensation.Especially, in the 3rd technical scheme, because the 1st heat exchanger 23 is air heat exchangers, gaseous refrigerant and air carry out heat exchange and condensation.Then, above-mentioned liquid refrigerant is split into many, but reduces pressure with the expansion mechanism E9 in the 2nd technical scheme before by shunting.
Then, liquid refrigerant after the above-mentioned shunting, because the high-pressure gaseous refrigerant of discharging from the 2nd compressor 31 also is split into many, so above-mentioned liquid refrigerant and gaseous refrigerant collaborate respectively and become the two-phase system cryogen, this two-phase system cryogen flows into each passage of the 2nd heat exchanger 32.Because the 2nd heat exchanger 32 is accommodated in the heat storage tank 11 in single technical scheme,, flow in the 3rd coolant channel 40 behind the liquefy cold-producing medium so the accumulation of heat medium of above-mentioned two-phase system cryogen and heat storage tank 11 carry out heat exchange and condensation.
After this, after above-mentioned liquid refrigerant reduces pressure in expansion mechanism E4, evaporation in the 3rd heat exchanger 42 and become gaseous refrigerant.Then, this gaseous refrigerant is got back in the 1st compression power traction and the 2nd compressor 31.Carry out this cold-producing medium circulation repeatedly.
Therefore, adopt the present invention, since in the 1st heat exchanger 23 chilled liquid refrigerant with from the 2nd compressor the gaseous refrigerant of discharging is collaborated after shunting respectively and flows into the 2nd heat exchanger 32, therefore can fully guarantee the supercooling degree of cold-producing medium, so can improve ability such as refrigeration reliably.
Especially, because above-mentioned liquid refrigerant and gaseous refrigerant are collaborated after shunting, so this liquid refrigerant and gaseous refrigerant are distributed and in the ratio of approximate equality to each passage supply of the 2nd heat exchanger 32.
That is to say, if when above-mentioned liquid refrigerant and gaseous refrigerant are shunted behind the interflow, the cold-producing medium after each shunting, the ratio of its liquid and gas has very big-difference, for example, can produce the passage that has only the mobile passage of liquid refrigerant or have only gaseous refrigerant to flow.Its result for example, can not make the ice integral body in the heat storage tank 11 melt equably.
Yet, in the present invention, because the ratio that can make liquid refrigerant and gaseous refrigerant in each passage of the 2nd heat exchanger 32 is about equally, so can melt ice equably, make the efficient raising of accumulation of heat utilization.Simultaneously and since can make in each passage of above-mentioned the 2nd heat exchanger 32 cold-producing medium supercooling degree about equally, so can make cold-producing medium integral body the increase of supercooling degree, can further try to achieve the raising of ability.
And, when liquid refrigerant is reduced pressure before shunting, comparing with situation about after shunting, reducing pressure, available 1 expansion mechanism E9 reduces pressure, and its result can prevent that the number of components from increasing.
In addition, above-mentioned the 2nd heat exchanger 32 is accommodated in the heat storage tank 11, during condensation of refrigerant after making the interflow with the 2nd heat exchanger 32, owing to can more effectively utilize the cold and hot of heat storage tank 11, can change the peak value of consumption electric power reliably.
The simple declaration of accompanying drawing
Fig. 1 is the refrigerant loop figure of expression the invention process form.
Fig. 2 is the matched tube structure figure of the interflow portion of expression liquid refrigerant and gaseous refrigerant.
Fig. 3 is the refrigerant loop figure of the cold-producing medium loop direction during the accumulation of heat when being illustrated in refrigeration is turned round.
Fig. 4 is the refrigerant loop figure of the cold-producing medium loop direction in the high loaded process that is illustrated in when freezing.
Fig. 5 is the Mollier calculation of thermodynamics figure of the refrigerant property of expression high loaded process.
Fig. 6 is the Mollier calculation of thermodynamics figure of comparative example of the refrigerant property of expression high loaded process.
Fig. 7 is the refrigerant loop figure of the cold-producing medium loop direction in the low load operation that is illustrated in when freezing.
The refrigerant loop figure of the cold-producing medium loop direction in the common running when Fig. 8 is the expression heating.
The refrigerant loop figure of the cold-producing medium loop direction in the accumulation of heat running when Fig. 9 is the expression heating.
The refrigerant loop figure of the cold-producing medium loop direction in the utilization running when Figure 10 is the expression heating.
Below, be described with reference to the accompanying drawings example of the present invention.
As shown in Figure 1, the aircondition 10 of this example is the refrigerating plant with heat storage tank 11, adopts to have many indoor sets 12,12 ... the multi-model structure.
Above-mentioned aircondition 10 has the refrigerating circuit 1R that is made of the 1st coolant channel the 20, the 2nd coolant channel 30 and the 3rd coolant channel 40.And this refrigerating circuit 1R has the major loop 1M that is made of the 1st coolant channel 20 and the 2nd coolant channel 40.
Above-mentioned the 1st coolant channel 20 is from the discharge side of the 1st compressor 21, and being connected in series by refrigerant piping 24 by three-way change-over valve 22, outdoor heat converter 23, outdoor expansion valve W2 and the 1st open and close valve constitutes.And above-mentioned outdoor heat converter 23 is the 1st heat exchangers, constitutes with air heat exchanger.
In above-mentioned the 3rd coolant channel 40, many indoor sets 12,12 ... connect in parallel mutually.And in the 3rd coolant channel 40, three-way change-over valve 41 is many indoor sets 12,12 relatively ... be connected in series.This indoor set 12 forms by being connected in series as the indoor expansion valve E4 of expansion mechanism with as the indoor heat converter 42 of the 3rd heat exchanger.Above-mentioned indoor expansion valve E4, indoor heat converter 42 and three-way change-over valve 41 usefulness refrigerant pipings 43 are connected.
One end of the 1st open and close valve S2 side in one end of the indoor expansion valve E4 side in above-mentioned the 3rd coolant channel 40 and the 1st coolant channel 20 is connected, and an end of three-way change-over valve 41 sides in the 3rd coolant channel 40 is connected with the suction side of the 1st compressor 21.And, constitute the living loop 1M of closed-loop path by above-mentioned the 1st coolant channel 20 and the 3rd coolant channel 40.
Above-mentioned the 2nd coolant channel 30 is from the discharge side of the 2nd compressor 31, and being connected in series by refrigerant piping 33 with expansion valve E3 with heat exchanger 32 and accumulation of heat by the 2nd open and close valve S3, accumulation of heat forms.And the suction side of above-mentioned the 2nd compression power traction is connected with the 3rd coolant channel 40, and the accumulation of heat in the 2nd coolant channel 30 is connected with the tie point X of the 1st coolant channel 20 with the 3rd coolant channel 40 with an end of expansion valve E3 side.
Above-mentioned accumulation of heat is that the 2nd heat exchanger is accommodated in and stores in the heat storage tank 11 that accumulation of heat medium such as water are arranged with heat exchanger 32, is made of than outdoor heat converter 23 low water heat exchangers condensation temperature.The accumulation of heat medium of water or salt solution etc. are stored in this heat storage tank 11.In addition, the passage (not shown) that above-mentioned accumulation of heat has many flow of refrigerant with heat exchanger 32, it is cold and hot to generate ice back savings in heat storage tank 11 at heat-exchanger surface, and after generating warm water with warm savings in heat storage tank 11.
Between the discharge side of the right discharge side of the 1st compressor of above-mentioned the 1st coolant channel 20 and the 2nd compressor 31 of the 2nd coolant channel 30, be connected connecting pipings 50, in this connecting pipings 50, be provided with the 3rd open and close valve S5.
An end that sucks pipe arrangement 60 is connected with the three-way change-over valve 22 of above-mentioned the 1st coolant channel 20, and the suction of two compressors 21,31 in the other end of this suction pipe arrangement 60 and the 3rd coolant channel 40 is connected.And above-mentioned three-way change-over valve 22 can make the discharge side of outdoor heat converter 23 and two compressors 21,31 and suck either party that fall and be communicated with.
One end of high press fit pipe 70 is connected with the three-way change-over valve 41 of above-mentioned the 3rd coolant channel 40, and the other end of this high press fit pipe 70 is connected between the 2nd compressor 31 and the 2nd open and close valve S3 of above-mentioned the 2nd coolant channel 30.
One end Y of low-pressure fitting pipe 80 is connected the 2nd open and close valve S3 and the accumulation of heat of above-mentioned the 2nd coolant channel 30 and uses between the heat exchanger 32, this low-pressure fitting pipe 80 has the 4th open and close valve S8, between the suction that its other end is connected the three-way change-over valve 41 of the 3rd coolant channel 40 and two compressors 21,31 is fallen.
Between the outdoor expansion valve EZ and the 1st open and close valve S2 of branch's pipe arrangement 90 branches in above-mentioned the 1st coolant channel 20.This branch's pipe arrangement 90 is provided with the expansion valve E9 of branch as expansion mechanism, and with above-mentioned the 2nd coolant channel 30 in the tie point Y of accumulation of heat with heat exchanger 32 and low-pressure fitting pipe 80 between be connected.
In branch's pipe arrangement 90 of above-mentioned the 1st coolant channel 20 with the 2nd coolant channel 30 be connected end (the L part of Fig. 1), as shown in Figure 2, be provided with isocon 9a.This isocon 9a is connecting many refrigerant pipe 9b, 9b ..., and make many shuntings of cold-producing medium from outdoor heat converter 23.
In addition, in above-mentioned the 2nd coolant channel 30,, as shown in Figure 2, be provided with collector item lid 3a with the connecting portion (the L part of Fig. 1) of branch's pipe arrangement 90 of the 1st coolant channel 20, this collector top cover 3a is connecting many refrigerant pipe 3b, 3b ..., will be from many shuntings of cold-producing medium of the 2nd compressor 31.Refrigerant pipe 9b, the 9b of above-mentioned isocon 3a ... refrigerant pipe 3b, 3b with collector top cover 3a ... connect refrigerant pipe 3b, the 3b of this collector top cover 3a ... be connected with accumulation of heat each passage with heat exchanger 32.That is to say above-mentioned each refrigerant pipe 9b, 3b ... make from the liquid refrigerant of outdoor heat converter 23 and gaseous refrigerant and after shunting, collaborate from the 2nd compressor 31.
And, above-mentioned refrigerating circuit 1R is except utilizing the high loaded process of accumulation of heat when the cooling operation, at least also can when cooling operation, utilize the low load operation and the cold and hot accumulation of heat running of savings of accumulation of heat, when warming operation, do not utilize the common running of accumulation of heat and utilize the utilization running of accumulation of heat and put aside warm accumulation of heat and turn round.
Below, with regard to each operating condition of running action specification of above-mentioned aircondition 10.
Accumulation of heat running during refrigeration:
During the accumulation of heat running, as shown in Figure 3, at first with the solid lateral conversion of 2 three-way change-over valves 22,41 to Fig. 3, make the 1st open and close valve S2 in opened condition, the 2nd open and close valve S3 be closed condition, the 3rd open and close valve S5 in opened condition, the 4th open and close valve S5 in opened condition, make outdoor expansion valve E4 be full-gear, the expansion valve E9 of branch and indoor expansion valve E4 again and be full-shut position, accumulation of heat are adjusted to regulation with expansion valve E3 aperture.
In this state, drive the 1st compressor 21 and the 2nd compressor 31.From the 1st compressor 21 and the 2nd compressor to the high-pressure gaseous refrigerant interflow of discharging and by flowing to outdoor heat converter 23 behind the three-way change-over valve 22.In this outdoor heat converter 23, gaseous refrigerant and outdoor air carry out condensation after the heat exchange and the liquefy cold-producing medium.This liquid refrigerant passes through not flow in branch's pipe arrangement 90 behind the outdoor expansion valve E2, but flows to the 2nd refrigerating channel 30 by the 1st open and close valve S2 and tie point X.
After this, above-mentioned liquid refrigerant with evaporation in the heat exchanger 32 and cooling accumulation of heat medium, becomes gaseous refrigerant in accumulation of heat after accumulation of heat is with decompression among the expansion valve E3.Then, this gaseous refrigerant low-pressure fitting pipe 80 of flowing through is got back to the 1st compressor 21 and the 2nd compressor 31.This cold-producing medium circulation repeatedly generates ice at heat-exchanger surface, with cold and hot savings in heat storage tank 11.
High loaded process during refrigeration:
This high loaded process is exactly the cooling operation that utilizes above-mentioned accumulation of heat, as shown in Figure 4, also is the running form that has characteristics most of the present patent application.In this high loaded process, 2 three-way change-over valves 22,41 are changed to the solid lateral of Fig. 4, make the 1st open and close valve S2 be closed condition, the 2nd open and close valve S3 in opened condition, the 3rd open and close valve S5 is that closed condition, the 4th open and close valve S8 are closed condition, makes outdoor expansion valve E2 and accumulation of heat be the aperture that full-gear, the indoor expansion valve E4 of the expansion valve E9 of branch are adjusted to regulation with expansion valve E3 again.
At first, drive the 1st compressor 21 and the 2nd compressor 31.The high-pressure gaseous refrigerant of discharging from the 1st compressor 21 flows to outdoor heat converter 23 by three-way change-over valve 22.In this outdoor heat converter 23, gaseous refrigerant and outdoor air carry out condensation liquefy cold-producing medium after the heat exchange.Liquid refrigerant in the 1st coolant channel 20 flows into branch's pipe arrangement 90 by outdoor expansion valve E2, flows into isocon 9a be decompressed to authorized pressure in the expansion valve E9 of branch after.
In addition, the high-pressure gaseous refrigerant of discharging from above-mentioned the 2nd compressor 31 flows to collector top cover 3a by the 2nd open and close valve S3.
The liquid refrigerant of above-mentioned the 1st coolant channel 20 in isocon 9a to each refrigerant pipe 9b, 9b ... shunting.And the gaseous refrigerant of the 2nd coolant channel 30 covers among the 3a to each refrigerant pipe 3b, 3b at the collector item ... shunting.Then, above-mentioned liquid refrigerant and gaseous refrigerant are at each bar refrigerant pipe 9b, 3b ... in interflow and become the two-phase system cryogen, and in accumulation of heat with flowing in each passage of heat exchanger 32.Above-mentioned two-phase system cryogen is condensation liquefy cold-producing medium after accumulation of heat is carried out heat exchange with the accumulation of heat medium in heat exchanger 32, flows into the 3rd coolant channel 40 by accumulation of heat after with expansion valve E3 again.
Then, above-mentioned liquid refrigerant flows to each indoor set 12, decompression back evaporation and become gaseous refrigerant in indoor heat converter 42 in indoor expansion valve E4.Then, this gaseous refrigerant return the 1st compressor 21 by three-way change-over valve 41 and the 2nd compressor right.Carry out this cold-producing medium circulation repeatedly, to indoor cool-air feed.
The refrigerant property of above-mentioned cold-producing medium circulation is described with Mollier calculation of thermodynamics figure shown in Figure 5.
At first, high-pressure gaseous refrigerant was discharged from the 1st compressor 21 at A o'clock, and the condensation in outdoor heat converter 23 of this high-pressure gaseous refrigerant becomes the liquid refrigerant that B is ordered.After reducing pressure, this liquid refrigerant arrives the C point in the expansion valve E9 of branch.
In addition, high-pressure gaseous refrigerant was discharged from the 2nd compressor 31 at D o'clock, liquid refrigerant (C point) interflow in this high-pressure gaseous refrigerant (D point) and above-mentioned the 1st coolant channel 20 and become the two-phase system cryogen that E is ordered.
Then, this two-phase system cryogen accumulation of heat with heat exchanger 32 in condensation and become the liquid refrigerant that F is ordered.This liquid refrigerant back of reducing pressure in indoor expansion valve E4 arrives the G point, evaporation in indoor heat converter 42 and become the gaseous refrigerant that H is ordered, and this gaseous refrigerant returns the 1st compressor 21 and the 2nd compressor 31.
Below, as a comparative example, with the liquid refrigerant of Mollier calculation of thermodynamics figure explanation condensation in outdoor heat converter 23 shown in Figure 6 and the refrigerant property of the cold-producing medium circulation when the liquid refrigerant interflow of condensation in the heat exchanger 32 is used in accumulation of heat.
At this moment, the liquid refrigerant of condensation does not flow into branch's pipe arrangement 90 and flows to tie point X in above-mentioned outdoor heat converter 23, collaborates with chilled liquid refrigerant in the heat exchanger 32 at this tie point X and in accumulation of heat.
At first, the high-pressure gaseous refrigerant in the 1st coolant channel 20 is discharged (A point) from the 1st compressor 21, condensation in outdoor heat converter 23 (B point), decompression (C point) in outdoor expansion valve E2.In addition, the high-pressure gaseous refrigerant in the 2nd coolant channel 30 from the 2nd compressor to discharging (D point), in accumulation of heat with condensation (I point) in the heat exchanger 32.
Then, the interflow of the liquid refrigerant (I point) in the two-phase system cryogen (C point) in above-mentioned the 3rd coolant channel 20 and the 2nd coolant channel 30 and become the liquid refrigerant that F is ordered.Then, this liquid refrigerant reduces pressure in indoor expansion valve E4 (G point), and evaporation returns the 1st compressor 21 and the 2nd compressor 31 (H point) in indoor heat converter 42.
Therefore, in the comparative example of Fig. 6, the cold-producing medium of discharging from the 2nd compressor 31 accumulation of heat with condensation the heat exchanger 32 by supercooling, after this, because with the interflow of chilled cold-producing medium in outdoor heat converter 23, so make the supercooling degree of the cold-producing medium behind the interflow diminish (referring to the F point).In contrast, in this example shown in Figure 5,, the cold-producing medium behind the interflow becomes big because, opposing cold-producing medium supercooling degree (F point) by supercooling.
Low load operation during refrigeration:
This low load operation, as shown in Figure 7,2 three-way change-over valves 22,41 are changed to the solid lateral of Fig. 7, make the 1st open and close valve S2 be that closed condition, the 2nd open and close valve S3 are closed condition, the 3rd open and close valve S5 reaches the 4th open and close valve S8 in opened condition and is closed condition, making outdoor expansion valve E2, the expansion valve E9 of branch and accumulation of heat again is full-gear with expansion valve E3, makes indoor expansion valve E4 be adjusted to the aperture of regulation.In addition, in above-mentioned low load operation, also with the cold and hot savings of accumulation of heat medium in heat storage tank 11.
At first, drive the 1st compressor 21 and the 2nd compression power traction.From the high-pressure gaseous refrigerant interflow that the 1st compressor 21 and the 2nd compressor ejectment go out, by flowing to outdoor heat converter 23 behind the three-way change-over valve 22.In this outdoor heat converter 23, gaseous refrigerant and outdoor air carry out condensation liquefy cold-producing medium after the heat exchange.It is after 90s that this liquid refrigerant flows to branch's pipe arrangement by outdoor expansion valve E2, carries out heat exchange with the accumulation of heat medium in heat exchanger 32 and by supercooling in accumulation of heat.Liquid refrigerant after this supercooling flows into the 3rd coolant channel 40 by accumulation of heat with expansion valve E3.
Then, above-mentioned liquid refrigerant flows to each indoor set 12, in indoor expansion valve E4 after the decompression, and evaporation in indoor heat converter 42 and become gaseous refrigerant.Then, this gaseous refrigerant is got back in the 1st compressor 21 and the 2nd compressor 31 after by three-way change-over valve 41.Carry out this cold-producing medium circulation repeatedly, to indoor cool-air feed.
Common running during heating:
Usually running, as shown in Figure 8, it is that open mode, the 2nd open and close valve S3 are closed condition, the 3rd open and close valve SS reaches the 4th open and close valve SS in opened condition and is closed condition that the solid lateral that 2 three-way change-over valves 22,41 are converted to Fig. 8 makes the 1st open and close valve S2, makes indoor expansion valve E4 be full-gear, the expansion valve E9 of branch and accumulation of heat again and is the aperture that full-shut position, outdoor expansion valve E2 are adjusted to regulation with expansion valve E3.
At first, drive the 1st compressor 21 and the 2nd compressor 31.The high-pressure gaseous refrigerant interflow to discharging from the 1st compressor 21 and the 2nd compressor flows to indoor heat converter 42 from the 2nd coolant channel 30 by high press fit pipe 70 and three-way change-over valve 41.In this indoor heat converter 42, gaseous refrigerant and room air carry out condensation liquefy cold-producing medium after the heat exchange.This liquid refrigerant flows into the 1st coolant channel 20 by indoor expansion valve E4.
Then, above-mentioned liquid refrigerant is by the 1st open and close valve S2, in outdoor expansion valve E2 after the decompression, carries out heat exchange with outdoor air and evaporate in outdoor heat converter 23, becomes gaseous refrigerant.Then, this gaseous refrigerant flows into from three-way change-over valve 22 and sucks pipe arrangement 60, gets back to the 1st compressor 21 and the 2nd compressor 31.Carry out this cold-producing medium circulation repeatedly, to indoor supply heating installation.
Accumulation of heat running during heating:
This accumulation of heat running, as shown in Figure 9,2 three-way change-over valves 22,41 are converted to the solid lateral of Fig. 9, make the 1st open and close valve S2 in opened condition, the 2nd open and close valve S3 in opened condition, the 3rd open and close valve S5 reaches the 4th open and close valve S8 in opened condition and is closed condition, make accumulation of heat be full-gear, the expansion valve E9 of branch and indoor expansion valve E4 again and be the aperture that full-shut position, outdoor expansion valve E2 are adjusted to regulation with expansion valve E3.
Under this state, drive the 1st compressor 21 and the 2nd compressor 31.High-pressure gaseous refrigerant interflow from the 1st compressor 21 and 31 discharges of the 2nd compressor, flow to accumulation of heat heat exchanger 32 by the 2nd coolant channel 30, with in the heat exchanger 32, gaseous refrigerant and accumulation of heat medium carry out heat exchange and condensation, the liquefy cold-producing medium in this accumulation of heat.This liquid refrigerant is by accumulation of heat expansion valve E3, flows to tie point X and flows in the 1st coolant channel 20.
After this, above-mentioned liquid refrigerant is by the 1st open and close valve S2, in outdoor expansion valve E2 after the decompression, carries out heat exchange with outdoor air and evaporate in outdoor heat converter 23, becomes gaseous refrigerant.Then, this gaseous refrigerant sucks pipe arrangement 60 from three-way change-over valve 22 persons who lives in exile, gets back to the 1st compressor to reaching the 2nd compressor 31.Carry out the circulation of this cold-producing medium repeatedly, with the warm savings of warm water etc. in heat storage tank 11.
Utilization running during heating:
This utilization running is the warming operation that utilizes above-mentioned accumulation of heat to carry out, as shown in figure 10,2 three-way change-over valves 22,41 are converted to the solid lateral of Figure 10, make the 1st open and close valve SZ be closed condition, the 2nd open and close valve S3 be closed condition, the 3rd open and close valve S5 in opened condition, the 4th open and close valve S8 in opened condition, make indoor expansion valve E4 be full-gear, the expansion valve E9 of branch and outdoor expansion valve E2 again and be full-shut position, accumulation of heat are adjusted to regulation with expansion valve E3 aperture.
At first, drive the 1st compressor 21 and the 2nd compressor 31.High press fit pipe 70 and three-way change-over valve 41 back inflow indoor heat exchangers 42 are passed through from the 2nd coolant channel 30 in the high-pressure gaseous refrigerant interflow to discharging from the 1st compressor 21 and the 2nd compressor.In this indoor heat converter 42, gaseous refrigerant and room air carry out heat exchange and condensation, the liquefy cold-producing medium.This liquid refrigerant is by flowing into the 2nd coolant channel 30 behind the indoor expansion valve E4.
After this, above-mentioned liquid refrigerant carries out heat exchange with the accumulation of heat medium in heat exchanger 32 and evaporates in accumulation of heat after accumulation of heat is with decompression among the expansion valve E3, becomes gaseous refrigerant.Then, this gaseous refrigerant flows into low-pressure fitting pipe 80, returns the 1st compressor 21 and the 2nd compressor 31.Carry out this cold-producing medium circulation repeatedly, to indoor supply heating installation.
As mentioned above, adopt this example, shunt back interflow and inflow accumulation of heat heat exchanger 32 each bar split channel respectively owing to the liquid refrigerant that makes condensation in the outdoor heat converter 23 and from the gaseous refrigerant that the 2nd compressor 31 is discharged, can fully guarantee the supercooling degree of cold-producing medium, therefore, can improve refrigerating capacity reliably.
Especially, owing to collaborate after making the shunting of above-mentioned liquid refrigerant and gaseous refrigerant, so this liquid refrigerant and gaseous refrigerant can be offered each passage of accumulation of heat usefulness heat exchanger 32 with the pro rate of approximate equality.
That is to say, if shunt after making above-mentioned liquid refrigerant and gaseous refrigerant interflow, then the refrigerant liquid after each shunting and the ratio of gas have very big-difference, for example, can produce the passage that the mobile passage of liquid refrigerant is only arranged or only have gaseous refrigerant to flow.Its result can not be melted the ice integral body of heat storage tank 11 equably.
Yet, in this example,, make the efficient raising of accumulation of heat utilization so can melt ice equably owing to can make accumulation of heat about equally with the ratio of liquid refrigerant in each passage of heat exchanger 32 and gaseous refrigerant.Simultaneously, owing to can make above-mentioned accumulation of heat about equally,, can try to achieve the further raising of ability so the supercooling degree of cold-producing medium integral body is increased with the cold-producing medium supercooling degree in each passage of heat exchanger 32.
And, because liquid refrigerant is reduced pressure before shunting, comparing with the situation of shunting back decompression, available 1 expansion valve E9 of branch reduces pressure, and its result can prevent that the number of components from increasing.
In addition, during condensation of refrigerant after making the interflow with heat exchanger 32,, can change the peak value of consumption electric power reliably owing to can more effectively utilize the cold and hot of heat storage tank 11 with accumulation of heat.
In above-mentioned example, except cooling operation, also carry out warming operation, yet the present invention also can only carry out cooling operation, in addition, also can only carry out this example in the cold-producing medium circulation of high loaded process in when refrigeration.
And the present invention is not limited to aircondition 10, so long as the rotating device that carries out 2 kinds of temperature condensations of the different what is called of condensation temperature just can, also applicable to the various refrigerating plants of freezer etc.
Therefore, the 1st heat exchanger 23 may not be limited to air heat exchanger, and the 2nd heat exchanger 32 also is not limited to water heat exchanger or accumulation of heat heat exchanger.Also have, the 3rd heat exchanger 42 is not limited to indoor heat converter.
In addition, in this example, the 1st coolant channel 20 is identical with the quantity of the shunting of the 2nd coolant channel 30.That is, the refrigerant pipe 9b of the isocon 9a in the 1st coolant channel 20,9b ... with the refrigerant pipe 3b of collector top cover 3a in the 2nd coolant channel 30,3b ... identical.
Yet, in the present invention, also can make the refrigerant pipe 9b of isocon 9a, 9b ... with the refrigerant pipe 3b of collector top cover 3a, 3b ... different.That is, both can make the refrigerant pipe 9b of isocon 9a, 9b ... than the refrigerant pipe 3b of collector top cover 3a, 3b ... many, also can make the refrigerant pipe 3b of collector top cover 3a, 3b on the contrary ... than the refrigerant pipe 9b of isocon 9a, 9b ... many.In a word, as long as make after liquid refrigerant and some shuntings of gaseous refrigerant some interflow again.
In addition, accumulation of heat is with the port number of heat exchanger 32, both can more than, also can be less than the shunt bar number of cold-producing medium.That is, port number both can more than, also can be less than the refrigerant pipe 3b of collector top cover 3a in this example, 3b ... the bar number.In a word, as long as the cold-producing medium at some interflow is flowed in many passages.
Claims (4)
1. refrigerating plant, the 2nd coolant channel (30) that has the 1st coolant channel (20) that constitutes by the 1st compressor (21) and the 1st heat exchanger (23), constitutes by the 2nd compressor (31) and the 2nd heat exchanger (32) and the refrigerating circuit (1R) that is connected into by the 3rd coolant channel (40) of expansion mechanism (E4) and the 3rd heat exchanger (42) formation, it is characterized in that
It is a kind of refrigerating plant that carries out following cold-producing medium circulation at least, promptly, the cold-producing medium of discharging from described the 1st compressor (21) is the 1st heat exchanger (23) after the condensation, with the cold-producing medium interflow of discharging from the 2nd compressor (31), cold-producing medium behind the interflow in the 2nd heat exchanger (32) with than after the low temperature condensation of described the 1st heat exchanger (23), decompression in expansion mechanism (E4) is got back to the 1st compressor (21) and the 2nd compressor (31) after the evaporation in the 3rd heat exchanger (42)
Described the 2nd heat exchanger (32) has many passages, in addition, described refrigerating circuit (1R) is at described cold-producing medium circulation time, make chilled cold-producing medium in the 1st heat exchanger (23) and the cold-producing medium of discharging respectively after many shuntings from the 2nd compressor (31), interflow is respectively flowed the cold-producing medium behind the interflow in each passage of described the 2nd heat exchanger (32) again.
2. refrigerating plant as claimed in claim 1 is characterized in that, the 1st coolant channel (20) of described refrigerating circuit (1R) has expansion mechanism (E9), so that condensed refrigerant is shunted after decompression in the 1st heat exchanger (23).
3. refrigerating plant as claimed in claim 1 is characterized in that, described the 1st heat exchanger (23) is an air heat exchanger, and described the 2nd heat exchanger (32) is a water heat exchanger.
4. refrigerating plant as claimed in claim 1 is characterized in that, described the 2nd heat exchanger (32) is contained in the heat storage tank (11) and with the cold and hot condensation of refrigerant that makes of described heat storage tank (11).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10341903A JP3087745B2 (en) | 1998-12-01 | 1998-12-01 | Refrigeration equipment |
| JP341903/1998 | 1998-12-01 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1294672A true CN1294672A (en) | 2001-05-09 |
| CN1120968C CN1120968C (en) | 2003-09-10 |
Family
ID=18349646
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN99804304A Expired - Fee Related CN1120968C (en) | 1998-12-01 | 1999-11-30 | Refrigerator |
| CN99247971U Expired - Lifetime CN2409462Y (en) | 1998-12-01 | 1999-12-01 | Refrigerating device |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN99247971U Expired - Lifetime CN2409462Y (en) | 1998-12-01 | 1999-12-01 | Refrigerating device |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP3087745B2 (en) |
| KR (1) | KR100381634B1 (en) |
| CN (2) | CN1120968C (en) |
| AU (1) | AU1412300A (en) |
| WO (1) | WO2000033002A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1300526C (en) * | 2005-06-14 | 2007-02-14 | 上海理工大学 | Energy saving and environmental protective in the four seasons cooling and warming air conditioner possessing hot water function |
| CN105299797A (en) * | 2014-07-07 | 2016-02-03 | Lg电子株式会社 | Heat accumulating type air conditioning plant and control method thereof |
| CN107883601A (en) * | 2016-09-30 | 2018-04-06 | 大金工业株式会社 | Air-conditioning system |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20060117775A (en) * | 2005-05-13 | 2006-11-17 | 엘지전자 주식회사 | Air conditioner with cooler and ice-storage, and method of controlling it |
| US9423159B2 (en) * | 2009-12-21 | 2016-08-23 | Trane International Inc. | Bi-directional cascade heat pump system |
| EP2678612B1 (en) * | 2011-02-25 | 2018-01-10 | Carrier Corporation | Air conditioning system with ice storage |
| JP5327308B2 (en) * | 2011-09-30 | 2013-10-30 | ダイキン工業株式会社 | Hot water supply air conditioning system |
| CN103375845B (en) * | 2012-04-28 | 2015-05-20 | 青岛海信日立空调系统有限公司 | Air conditioner circulation system |
| CN103388920B (en) * | 2013-08-15 | 2015-07-15 | 湖北美的电冰箱有限公司 | Refrigerating system and refrigerator provided with same |
| CN104567075B (en) * | 2013-10-28 | 2017-10-03 | 珠海格力电器股份有限公司 | Air conditioner circulating device and control method thereof |
| JP6020549B2 (en) * | 2014-12-26 | 2016-11-02 | ダイキン工業株式会社 | Thermal storage air conditioner |
| CN105571193B (en) * | 2016-02-27 | 2017-12-19 | 李建华 | A kind of heat pump application and energy storing system |
| CN105783332B (en) * | 2016-05-13 | 2019-04-16 | 李建华 | Realize the heat pump system of green state cell |
| TWI658238B (en) * | 2016-08-12 | 2019-05-01 | 國立勤益科技大學 | Split energy storage system and method |
| US20230392829A1 (en) * | 2020-11-05 | 2023-12-07 | Daikin Industries, Ltd. | Refrigerant circuit for a refrigeration apparatus with a thermal storage and method for controlling a refrigerant circuit |
| EP3995761A1 (en) * | 2020-11-05 | 2022-05-11 | Daikin Industries, Ltd. | Refrigerant circuit for a refrigeration apparatus with a thermal storage and method forcontrolling a refrigerant circuit |
| GB2606518B (en) * | 2021-04-30 | 2024-05-01 | Dyson Technology Ltd | A refrigeration system |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2503659B2 (en) * | 1989-06-23 | 1996-06-05 | ダイキン工業株式会社 | Heat storage type air conditioner |
| JP2684814B2 (en) * | 1990-04-11 | 1997-12-03 | ダイキン工業株式会社 | Air conditioner |
| JP3297178B2 (en) * | 1993-02-19 | 2002-07-02 | 東京電力株式会社 | Thermal storage type air conditioner |
| JPH10227497A (en) * | 1996-12-13 | 1998-08-25 | Daikin Ind Ltd | Ice thermal storage apparatus |
-
1998
- 1998-12-01 JP JP10341903A patent/JP3087745B2/en not_active Expired - Fee Related
-
1999
- 1999-11-30 CN CN99804304A patent/CN1120968C/en not_active Expired - Fee Related
- 1999-11-30 AU AU14123/00A patent/AU1412300A/en not_active Abandoned
- 1999-11-30 KR KR10-2001-7000753A patent/KR100381634B1/en not_active IP Right Cessation
- 1999-11-30 WO PCT/JP1999/006666 patent/WO2000033002A1/en active IP Right Grant
- 1999-12-01 CN CN99247971U patent/CN2409462Y/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1300526C (en) * | 2005-06-14 | 2007-02-14 | 上海理工大学 | Energy saving and environmental protective in the four seasons cooling and warming air conditioner possessing hot water function |
| CN105299797A (en) * | 2014-07-07 | 2016-02-03 | Lg电子株式会社 | Heat accumulating type air conditioning plant and control method thereof |
| US9970688B2 (en) | 2014-07-07 | 2018-05-15 | Lg Electronics Inc. | Regenerative air-conditioning apparatus and method of controlling the same |
| CN105299797B (en) * | 2014-07-07 | 2018-05-15 | Lg电子株式会社 | Regenerative type air regulating device and its control method |
| CN107883601A (en) * | 2016-09-30 | 2018-04-06 | 大金工业株式会社 | Air-conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| AU1412300A (en) | 2000-06-19 |
| JP2000171117A (en) | 2000-06-23 |
| CN1120968C (en) | 2003-09-10 |
| JP3087745B2 (en) | 2000-09-11 |
| KR100381634B1 (en) | 2003-04-21 |
| WO2000033002A1 (en) | 2000-06-08 |
| KR20010074725A (en) | 2001-08-09 |
| CN2409462Y (en) | 2000-12-06 |
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