CN102753915B - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
CN102753915B
CN102753915B CN201080063497.1A CN201080063497A CN102753915B CN 102753915 B CN102753915 B CN 102753915B CN 201080063497 A CN201080063497 A CN 201080063497A CN 102753915 B CN102753915 B CN 102753915B
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CN
China
Prior art keywords
heat exchanger
mentioned
utilize
side heat
cold
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Expired - Fee Related
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CN201080063497.1A
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Chinese (zh)
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CN102753915A (en
Inventor
小松智弘
小谷正直
内田麻理
高藤亮一
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Hitachi Ltd
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Hitachi Ltd
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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
    • F24F5/0003—Exclusively-fluid systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

In order to exert cooling and heating abilities using a natural circulation cycle heat exchanger as the heat exchanger of a pressure cycle, the disclosed air conditioner has a configuration that can form at least three refrigeration cycles: a natural circulation cycle (TS1) formed in a loop by sequentially connecting with pipework a first heat-source-side heat exchanger (4), a first expansion valve (5), and a first use-side heat exchanger (6); a first pressure cycle (PC1) formed in a loop by sequentially connecting with pipework the discharge port (1b) of a compressor (1), a duct switching valve (2), a second heat-source-side heat exchanger (7), a second expansion valve (9), a second use-side heat exchanger (8), and the intake port (1a) of the compressor; and a second pressure cycle (PC2) formed in a loop by sequentially connecting with pipework the discharge port (1b) of the compressor, the duct switching valve (2), the second heat-source-side heat exchanger (7), the first heat-source-side heat exchanger (4), the first expansion valve (5), the first use-side heat exchanger (6), the second use-side heat exchanger (8), and the intake port (1a) of the compressor.

Description

Aircondition
Technical field
The present invention relates to be arranged on the aircondition such as on house or office building etc., relate in particular to and cold-producing medium is set in the lump utilizes density contrast to carry out the natural recirculating type circulation of Natural Circulation and utilize compressor to make forcibly the compression circulation of refrigerant circulation, and can use respectively the aircondition of these two freeze cycle.
Background technology
As the prior art of using respectively two freeze cycle of natural recirculating type circulation and compression circulation, for example in patent documentation 1, disclose following technology: for the air in cooling box, arrange in the lump and utilize refrigerant piping to connect successively compressor, heat forms with condenser and cooler again freeze cycle (compression circulation) and the utilization pipe arrangement that freezes to be connected the natural circulation cooling device (natural recirculating type circulation) that natural circulation cooling forms with cooler with condenser and natural circulation cooling.If utilize this patent documentation 1, can utilize the air in natural circulation cooling device (natural recirculating type circulation) cooling box, therefore can reduce the cooling burden of utilizing freeze cycle (compression circulation).Thus, the technology of recording according to patent documentation 1, can reduce power consumption, can the operating cost of cooling system integral body be suppressed lowlyer.
In addition, in patent documentation 2, disclose and possess indoor heat converter, outdoor heat converter, refrigerant piping, expansion valve, be equivalent to the cold-producing medium natural circulation cooling dehydrating unit of refrigerant compression forced circulation device of the compression refrigerator of other devices.This cold-producing medium natural circulation cooling dehydrating unit has and utilizes refrigerant piping that outdoor heat converter, the indoor heat converter, the expansion valve that are positioned at the position lower than this outdoor heat converter are connected into ring-type and the natural recirculating type circulation forming and the compression circulation that utilizes refrigerant compression forced circulation device, the closely sealed structure of outdoor heat converter circulating for evaporation heat-exchanger and the natural recirculating type of compression circulation.According to this structure, because evaporation heat-exchanger can absorb heat effectively from outdoor heat converter, the occasion that cooling and dehumidifying ability is declined even therefore there is no the air Temperature Difference of indoor and outdoors, by refrigerant compression forced circulation device is worked, can make up the decline of the cooling and dehumidifying ability of cold-producing medium natural circulation cooling dehydrating unit.
In addition, patent documentation 2 discloses on the refrigerant compression forced circulation air-conditioning dual-purpose apparatus (compression circulation) that uses refrigerant compression forced circulation system the aircondition of the cold-producing medium natural circulation cooling dehydrating unit of setup and use cold-producing medium Natural Circulation (natural recirculating type circulation) in the lump.According to this aircondition, can under the state that utilizes cold-producing medium natural circulation cooling dehydrating unit to dehumidify, utilize refrigerant compression forced circulation air-conditioning dual-purpose apparatus to carry out the dry operating pattern that the such quality of heating installation is high, can improve adaptability.
Prior art document
Patent documentation
Patent documentation 1: TOHKEMY 2003-121072 communique
Patent documentation 2: Japanese kokai publication hei 10-300128 communique
Summary of the invention
Invent problem to be solved
But, in above-mentioned existing technology, owing to all forming natural recirculating type circulation and the compression independently freeze cycle that circulates, therefore cannot be using the heat exchanger of natural recirculating type circulation when the peak value of air-conditioning etc. as the heat exchanger utilization of compression circulation.Therefore, existence cannot be used the problem of hot-swap feature and so on of the heat exchanger of natural recirculating type circulation effectively.
In addition, natural recirculating type circulation is, between two heat exchangers, drop is set, the circulation that cold-producing medium utilizes density contrast naturally to circulate, therefore in ambient temperature, be the occasion below indoor temperature, difference hour in ambient temperature and indoor temperature, even if utilize the cold air operation of natural recirculating type circulation, also there is the problem that cannot obtain dehumidifying effect and so on.
The present invention completes in view of above-mentioned actual conditions, its object is, in the aircondition of compression circulation and natural recirculating type circulation is set in the lump, using the heat exchanger of natural recirculating type circulation as the heat exchanger utilization of compression circulation, bring into play air-conditioning ability.In addition, the object of the present invention is to provide aircondition, is the occasion below indoor temperature in ambient temperature, by utilizing in the lump natural recirculating type circulation and compression to circulate, even if the difference hour of ambient temperature and indoor temperature also can improve dehumidifying effect.
For solving the method for problem
To achieve these goals, aircondition of the present invention possesses compressor, first and second heat source side heat exchanger that the heat transmission medium of heat source side and cold-producing medium are carried out to heat exchange, to utilizing the heat transmission medium of side and cold-producing medium carries out heat exchange that first and second utilizes side heat exchanger, switch the flow channel switching valve of the runner direction of cold-producing medium, and first and second expansion valve, can at least form following three freeze cycle: utilize refrigerant piping to connect successively above-mentioned the first heat source side heat exchanger, above-mentioned the first expansion valve and be arranged on above-mentioned first of the position lower than above-mentioned the first heat source side heat exchanger and utilize side heat exchanger and form ring-type, cold-producing medium utilizes density contrast to carry out the natural recirculating type circulation of Natural Circulation, utilize refrigerant piping to connect successively the outlet of above-mentioned compressor, above-mentioned flow channel switching valve, above-mentioned Secondary Heat Source side heat exchanger, above-mentioned the second expansion valve, above-mentioned second and utilize the suction inlet of side heat exchanger and above-mentioned compressor and form ring-type, cold-producing medium utilizes the first compression circulation of above-mentioned compressor forced circulation, and utilize refrigerant piping to connect successively the outlet of above-mentioned compressor, above-mentioned flow channel switching valve, above-mentioned Secondary Heat Source side heat exchanger, above-mentioned the first heat source side heat exchanger, above-mentioned the first expansion valve, above-mentioned first utilizes side heat exchanger, above-mentioned second utilizes side heat exchanger, and the suction inlet of above-mentioned compressor form ring-type, cold-producing medium utilizes the second compression circulation of above-mentioned compressor forced circulation, possesses the cyclic switching mechanism of between the second state that the first state of forming independently in the circulation of above-mentioned natural recirculating type and above-mentioned the first compression circulation and above-mentioned the second compression of formation circulate, freeze cycle being switched.
According to the present invention, if operation cycle switching mechanism also switches to the second compression circulation, the heat exchanger utilization that heat exchanger of natural recirculating type circulation can be circulated as the second compression, therefore can improve air-conditioning ability, especially can when air-conditioning peak value, bring into play larger effect.
In addition, the present invention is in said structure, it is characterized in that, with utilize side heat transmission medium with pipe arrangement connect successively above-mentioned first utilize side heat exchanger, above-mentioned second to utilize side heat exchanger and be arranged on the indoor heat converter being cooled in space and form ring-type utilize side heat transmission medium closed circuit, make forcibly to circulate in utilizing side heat transmission medium closed circuit above-mentioned as the above-mentioned water that utilizes side heat transmission medium or salt solution.
According to the present invention, owing to being configured to arrange, utilize side heat transmission medium closed circuit, by being arranged on the indoor heat converter in the space that is cooled, the air in the space that is cooled is carried out to changes in temperature adjusting etc., therefore, do not need to connect the refrigerant piping of indoor set and off-premises station as existing, and refrigerant amount is few.In addition, utilizing refrigerant piping to connect in the structure of existing indoor set and off-premises station, the occasion forming natural recirculating type circulation, need to be arranged on off-premises station the position higher than indoor set, has the restriction of layout.But, according to the present invention, be that the structure of utilizing side heat transmission medium closed circuit is set, therefore have advantages of that the free degree of layout increases.
In addition, the present invention is in said structure, it is characterized in that, utilize side heat exchanger to be divided into two to be first to cut apart heat exchanger and second and cut apart heat exchanger by above-mentioned second, cut apart link that heat exchanger and above-mentioned second cuts apart heat exchanger with the 3rd expansion valve is set on refrigerant piping connecting above-mentioned first.
According to the present invention, utilize first to cut apart heat exchanger, second and cut apart heat exchanger and the 3rd expansion valve, while the warm dehumidifying of heat again dehumidifying of air in the space of can carrying out making being cooled is turned round.And, owing to can using in the lump natural recirculating type circulation and the circulation of the first compression, in ambient temperature, be therefore the occasion below indoor temperature, even if the difference hour of ambient temperature and indoor temperature also can improve dehumidifying effect.And, also have advantages of that the control range of temperature, humidity broadens and so on.
In addition, the present invention is in said structure, it is characterized in that, utilize heat source side heat transmission medium to connect above-mentioned Secondary Heat Source side heat exchanger and heat storage container with pipe arrangement and form the heat source side heat transmission medium closed circuit of ring-type, making forcibly to circulate in above-mentioned heat source side heat transmission medium closed circuit as the water of the heat transmission medium of above-mentioned heat source side.
According to the present invention, owing to can utilizing the heat extraction of heat source side heat exchanger to make middle warm water, therefore, by this centre warm water is used for to supplying hot water etc., raise the efficiency.Therefore in addition, in the present invention, owing to can utilizing heat storage container to carry out accumulation of heat to the heat extraction of heat source side heat exchanger, can eliminate different that for example air conditioner load and the time of supplying hot water load are with.
In addition, according to the present invention, in said structure, it is characterized in that, utilize supplying hot water to connect successively compressor for supplying hot water, supplying hot water with utilizing side heat exchanger, supplying hot water to form the supplying hot water circulation of ring-type with expansion valve and above-mentioned Secondary Heat Source side heat exchanger with refrigerant piping, utilize above-mentioned supplying hot water to make forcibly in above-mentioned supplying hot water circulation, to circulate with cold-producing medium as the supplying hot water of above-mentioned heat source side heat transmission medium with compressor.
According to the present invention, can produce the warm water that temperature is higher than middle warm water.
In addition, the present invention is in said structure, it is characterized in that, be provided with and make the suction inlet of above-mentioned compressor and the bypass pipe arrangement of outlet bypass and the runner of cold-producing medium is switched to the bypass switching mechanism with any runner of runner via above-mentioned bypass pipe arrangement via the runner of above-mentioned compressor.
According to the present invention, owing to forming, use two heat source side heat exchangers and two natural recirculating type circulations that utilize side heat exchanger, therefore can utilize the running of the natural recirculating type circulation that the efficiency of heat exchange is high, can realize saving cost.
Invention effect
According to the present invention, due to the heat exchanger utilization that the heat exchanger of natural recirculating type circulation can be circulated as compression, therefore to compare with only utilizing the heat exchanger of compression circulation, it is large that the heat-conducting area of heat exchanger becomes, improve heat exchanger effectiveness, can realize saving energy.In addition, owing to can using in the lump natural recirculating type circulation and compression circulation, in ambient temperature, be therefore the occasion below indoor temperature, even if the temperature difference hour of outdoor temperature and indoor temperature also can improve dehumidifying effect.
Accompanying drawing explanation
Fig. 1 means each structural element of aircondition and the basic block diagram of their annexation that forms the first embodiment example of the present invention.
Fig. 2 means the cold-producing medium of operation mode No.1 and the mobile action diagram of heat transmission medium of the aircondition of the first embodiment example of the present invention.
Fig. 3 means the cold-producing medium of operation mode No.2 and the mobile action diagram of heat transmission medium of the aircondition of the first embodiment example of the present invention.
Fig. 4 means the cold-producing medium of operation mode No.3 and the mobile action diagram of heat transmission medium of the aircondition of the first embodiment example of the present invention.
Fig. 5 means the cold-producing medium of operation mode No.4 and the mobile action diagram of heat transmission medium of the aircondition of the first embodiment example of the present invention.
Fig. 6 means each structural element of the aircondition that forms the second embodiment example of the present invention and the basic block diagram of their annexation.
Fig. 7 means the cold-producing medium of operation mode No.5 and the mobile action diagram of heat transmission medium of the aircondition of the second embodiment example of the present invention.
Fig. 8 means each structural element of the aircondition that forms the 3rd embodiment example of the present invention and the basic block diagram of their annexation.
Fig. 9 means the cold-producing medium of operation mode No.6 and the mobile action diagram of heat transmission medium of the aircondition of the 3rd embodiment example of the present invention.
Figure 10 means the cold-producing medium of operation mode No.7 and the mobile action diagram of heat transmission medium of the aircondition of the 3rd embodiment example of the present invention.
Figure 11 means the cold-producing medium of operation mode No.8 and the mobile action diagram of heat transmission medium of the aircondition of the 3rd embodiment example of the present invention.
Figure 12 means the cold-producing medium of operation mode No.9 and the mobile action diagram of heat transmission medium of the aircondition of the 3rd embodiment example of the present invention.
Figure 13 means the cold-producing medium of operation mode No.10 and the mobile action diagram of heat transmission medium of the aircondition of the 3rd embodiment example of the present invention.
Figure 14 means the cold-producing medium of operation mode No.11 and the mobile action diagram of heat transmission medium of the aircondition of the 3rd embodiment example of the present invention.
Figure 15 means each structural element of the aircondition that forms the 4th embodiment example of the present invention and the basic block diagram of their annexation.
The specific embodiment
(the first embodiment of the present invention)
Use Fig. 1～Fig. 5 to describe the structure of the aircondition of the first embodiment of the present invention, function and action.In addition, the arrow that the heat exchanger in Fig. 2～Fig. 5 marks represents flowing of heat.In Fig. 1, 1 represents the volume-variable formula compressor that cold-producing medium is used, 2 expression compressions are cubic valve (transfer valve flows) for circulation, 3 represent cubic valve (cyclic switching mechanism) for cyclic switching, 4 represent the first heat source side heat exchanger that atmosphere (heat transmission medium of heat source side) and cold-producing medium are carried out to heat exchange, 5 represent the first expansion valve, 6 represent that water (utilizing the heat transmission medium of side) and cold-producing medium are carried out to first of heat exchange utilizes side heat exchanger, 7 represent the Secondary Heat Source side heat exchanger that atmosphere (heat transmission medium of heat source side) and cold-producing medium are carried out to heat exchange, 8 represent water (utilizing the heat transmission medium of side) and the cold-producing medium to exchange second utilize side heat exchanger, 9 represent the second expansion valve.In addition, first utilize side heat exchanger 6 to be arranged on than the first low position of heat source side heat exchanger 4.That is, first utilize side heat exchanger 6 and the first heat source side heat exchanger 4 to be provided with drop.In addition, in the present embodiment, as cold-producing medium, use R410A.
Natural recirculating type circulation TS1 utilizes refrigerant piping 14 to connect the first heat source side heat exchanger 4 and the first expansion valve 5, utilize refrigerant piping 15 to connect the first expansion valve 5 and first and utilize side heat exchanger 6, utilize refrigerant piping 16 to connect first and utilize side heat exchanger 6 and cubic valve 3 cyclic switching for, utilize refrigerant piping 13 connection cyclic switchings with cubic valve 3 and the first heat source side heat exchanger 4, to form the freeze cycle of ring-type.And cold-producing medium utilizes density contrast to carry out Natural Circulation in this natural recirculating type circulation.
The first compression cycle P C1 is cubic valve 2 for the outlet 1b that utilizes refrigerant piping 10 to connect compressors 1 circulates with compression, utilize refrigerant piping 11 to connect cubic valve 2 and Secondary Heat Source side heat exchanger 7 for compression circulation, utilize refrigerant piping 12 to connect Secondary Heat Source side heat exchanger 7 and cubic valve 3 for cyclic switching, utilize refrigerant piping 17 to connect cubic valve 3 and the second expansion valve 9 for cyclic switching, utilize refrigerant piping 18 to connect the second expansion valve 9 and second and utilize side heat exchanger 8, utilize refrigerant piping 19 to connect second and utilize side heat exchanger 8 and compression cubic valve 2 for circulation, utilize refrigerant piping 20 to connect compression circulation and form the freeze cycle of ring-type with the suction inlet 1a of compressor 1 with cubic valve 2.And, utilize compressor 1 to make forcibly cold-producing medium circulate in the first compression cycle P C1.
The second compression cycle P C2 is cubic valve 2 for the outlet 1b that utilizes refrigerant piping 10 to connect compressors 1 circulates with compression, utilize refrigerant piping 11 to connect cubic valve 2 and Secondary Heat Source side heat exchanger 7 for compression circulation, utilize refrigerant piping 12 to connect Secondary Heat Source side heat exchanger 7 and cubic valve 3 for cyclic switching, utilize refrigerant piping 13 to connect cubic valve 3 and the first heat source side heat exchanger 4 for cyclic switching, utilize refrigerant piping 14 to connect the first heat source side heat exchanger 4 and the first expansion valve 5, utilize refrigerant piping 15 to connect the first expansion valve 5 and first and utilize side heat exchanger 6, utilize refrigerant piping 16 to connect first and utilize side heat exchanger 6 and cubic valve 3 for cyclic switching, utilize refrigerant piping 17 to connect cubic valve 3 and the second expansion valve 9 for cyclic switching, utilize refrigerant piping 18 to connect the second expansion valve 9 and second and utilize side heat exchanger 8, utilize refrigerant piping 19 to connect second and utilize side heat exchanger 8 and compression cubic valve 2 for circulation, utilize refrigerant piping 20 to connect compression circulation and form the freeze cycle of ring-type with the suction inlet 1a of compressor 1 with cubic valve 2.And, utilize compressor 1 to make forcibly cold-producing medium circulate in the second compression cycle P C2.
The switching of the circulation between natural recirculating type circulation TS1, the first compression cycle P C1 and the second compression cycle P C2 is carried out with the operation of cubic valve 3 by cyclic switching.If illustrate in greater detail, operation cycle is switched with cubic valve 3, if refrigerant piping 13 is communicated with refrigerant piping 16, and the first state that refrigerant piping 12 is communicated with refrigerant piping 17, forms independently freeze cycle of these two of natural recirculating type circulation TS1 and the first compression cycle P C1.That is, form natural recirculating type circulation TS1 and these two freeze cycle of the first compression cycle P C1 simultaneously.With respect to this, operation cycle is switched with cubic valve 3, if refrigerant piping 12 is communicated with refrigerant piping 13, and the second state of being communicated with refrigerant piping 17 of refrigerant piping 16, only form the second compression cycle P C2.Like this, the aircondition of the first embodiment example switches with cubic valve 4 by operation cycle, can make the state that can simultaneously utilize natural recirculating type circulation TS1 and the first compression cycle P C1 and these two states of state that can only utilize the second compression cycle P C2.
In addition, 30 represent house, and 31 expressions are arranged on the indoor heat converter of indoor (space is cooled) of house, and 32 represent circulating pumps, and 33 represent the cubic valves in cold warm water loop.Cold Warm water circulation loop (utilizing side heat transmission medium closed circuit) CW utilizes cold warm water pipe arrangement (utilizing side heat transmission medium pipe arrangement) 35 to connect indoor heat converter 31 and circulating pump 32, utilize cold warm water pipe arrangement 36 to connect circulating pump 32 and cubic valve 33 for cold warm water loop, utilize cold warm water pipe arrangement 37 to connect cold warm water loop and utilize side heat exchanger 8 with cubic valve 33 and second, utilizing cold warm water pipe arrangement 38 to connect second utilizes side heat exchanger 8 and first to utilize side heat exchanger 6, utilize cold warm water pipe arrangement 39 to connect first and utilize side heat exchanger 6 and cubic valve 33 for cold warm water loop, utilize cold warm water pipe arrangement 40 to connect cold warm water loop and form the loop of ring-type with indoor heat converter 31 with cubic valve 33.And, utilize the circulating pump Final 32 system water circulated in cold Warm water circulation loop CW.
Then, the operation mode that utilizes the aircondition of the first embodiment example to carry out is described.In the aircondition of the first embodiment example, as shown below, can carry out tetra-operation modes of operation mode No.1～No.4.In addition, in the following description, hs is the abbreviation of heat source, and app is the abbreviation of application, and H is the abbreviation of Humidity.
(operation mode No.1(Fig. 2))
Operation mode No.1 is the pattern of utilizing separately the cold air operation of the second compression cycle P C2, is the high and cold air of outside air temperatures such as daytime in the summer operation mode that large occasion used of loading.This operation mode No.1 is at " outdoor temperature Ths-design temperature Tuser >=0 " and " indoor temperature Tapp-design temperature Tuser >=0 ", for example outdoor temperature Ths=35 ℃, design temperature Tuser=23 ℃, the pattern that the occasion of indoor temperature Tapp=27 ℃ is used.In addition, in this operation mode No.1, the circulating path of cold-producing medium is the direction of arrow of Fig. 2.
In this operation mode, first, utilize cubic valve 2 for compression circulation, refrigerant piping 10 is communicated with refrigerant piping 11, and refrigerant piping 19 is communicated with refrigerant piping 20.In addition, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 13, and refrigerant piping 16 is communicated with refrigerant piping 17.Like this, by switching cubic valve 2 and cubic valve 3 for cyclic switching for compression circulation, form the second compression cycle P C2.At this, in operation mode No.1, the first expansion valve 5 is adjusted into the aperture of regulation, and the second expansion valve 9 is for all opening.
The gas refrigerant of the HTHP of discharging from the outlet 1b of compressor circulate with cubic valve 2 inflow Secondary Heat Source side heat exchangers 7 by compression, in this Secondary Heat Source side heat exchanger 7, between flow periods, to atmosphere, dispels the heat and condenses.In addition, the cold-producing medium flowing out at Secondary Heat Source side heat exchanger 7 uses cubic valve 3 to flow into the first heat source side heat exchanger 4 by cyclic switching, dispels the heat and condenses, finally liquefaction in this first heat source side heat exchanger 4 between flow periods to atmosphere.The cold-producing medium utilization of having liquefied be adjusted to the aperture of regulation the first expansion valve 5 decompressions, expand, under the state of the gas-liquid two-phase of low-temp low-pressure, flow into first and utilize side heat exchanger 6.
The cold-producing medium of this gas-liquid two-phase state absorbs heat and evaporates between flow periods in first utilizes side heat exchanger 6 from the water circulating in cold Warm water circulation loop CW, in addition, by the cubic valve 3 of cyclic switching, the second expansion valve 9, flow into second and utilize side heat exchanger 8 successively.And, flow into the second cold-producing medium that utilizes side heat exchanger 8 this second utilize side heat exchanger 8 in heat absorption and evaporate finally gasification from the water circulating in cold Warm water circulation loop CW between flow periods.The cold-producing medium having gasified is circulated and with cubic valve 2, is flowed into the suction inlet 1a of compressors 1 by compression, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
In this operation mode No.1, owing to utilizing first to utilize side heat exchanger 6 and second to utilize the water in the cooling cold Warm water circulation loop CW of side heat exchanger 8, so the air in house 30 is cooling by indoor heat converter 31.That is, operation mode No.1 is cold air operation pattern.Therefore in this operation mode No.1, cold-producing medium utilizes two heat source side heat exchangers 4,7 to dispel the heat in atmosphere, utilizes two to utilize side heat exchanger 6,8 from water, to absorb heat, can effectively use heat exchanger and improves cold air ability.
(operation mode No.2(Fig. 3))
Operation mode No.2 is the pattern of utilizing separately the heating installation running of the second compression cycle P C2, is the operation mode of loading large occasion, for example using at the night in winter at indoor heating installation.This operation mode No.2 is at " outdoor temperature Ths-design temperature Tuser≤0 " and " indoor temperature Tapp-design temperature Tuser≤0 " occasion, for example outdoor temperature Ths=7 ℃, design temperature Tuser=23 ℃, the pattern that the occasion of indoor temperature Tapp=18 ℃ is used.In addition, the circulating path of the cold-producing medium of this operation mode No.2 is the direction of arrow of Fig. 3, if comparison diagram 2 can find out with Fig. 3, the circulating path of the cold-producing medium of operation mode No.2 is contrary with the circulating path of the cold-producing medium of operation mode No.1.
In this operation mode, first, utilize cubic valve 2 for compression circulation, refrigerant piping 10 is communicated with refrigerant piping 19, and refrigerant piping 11 is communicated with refrigerant piping 20.In addition, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 13, and refrigerant piping 16 is communicated with refrigerant piping 17.Like this, by switching cubic valve 2 and cubic valve 3 for cyclic switching for compression circulation, form the second compression cycle P C2.At this, in operation mode No.2, the first expansion valve 5 is adjusted into the aperture of regulation, and the second expansion valve 9 is for all opening.
The gas refrigerant of the HTHP of discharging from the outlet 1b of compressor circulate and is utilized side heat exchanger 8 with cubic valve 2 inflows second by compression, this second utilize side heat exchanger 8 between flow periods to the water-cooled circulating in cold Warm water circulation loop CW and condense.In addition, second, utilize the cold-producing medium that side heat exchanger 8 flows out by the second expansion valve 9, cyclic switching, with cubic valve 3 inflows first, to utilize side heat exchanger 6 successively, at this, first utilize between 6 flow periods of side heat exchanger to the water-cooled circulating in cold Warm water circulation loop CW and condense, finally liquefaction.The cold-producing medium utilization of having liquefied be adjusted to the aperture of regulation the first expansion valve 5 decompressions, expand, under the state of the gas-liquid two-phase of low-temp low-pressure, flow into the first heat source side heat exchanger 4.
The cold-producing medium of this gas-liquid two-phase state absorbs heat and evaporates from atmosphere between flow periods in the first heat source side heat exchanger 4, in addition, by cyclic switching, uses cubic valve 3 between flow periods, from atmosphere, absorb heat and evaporate in Secondary Heat Source side heat exchanger 7, finally gasification.The cold-producing medium having gasified is circulated and with cubic valve 2, is flowed into the suction inlet 1a of compressors 1 by compression, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
In this operation mode No.2, owing to utilizing first to utilize side heat exchanger 6 and second to utilize the water in the cold Warm water circulation of side heat exchanger 8 heating loop CW, so the air in house 30 is heated by indoor heat converter 31.That is, operation mode No.2 is heating installation operation mode.Therefore in this operation mode No.2, cold-producing medium utilizes two heat source side heat exchangers 4,7 to absorb heat from atmosphere, utilizes two to utilize side heat exchanger 6,8 to dispel the heat in water, can effectively use heat exchanger and improves heating installation ability.
(operation mode No.3(Fig. 4))
Operation mode No.3 is the pattern of utilizing in the lump the cold air operation of natural recirculating type circulation TS1 and the first compression cycle P C1, it is pattern lower than indoor temperature in ambient temperature and that have the occasion of cold air load, especially need the occasion (for example, night during plum rains etc.) of dehumidifying to use.This operation mode No.3 is at " outdoor temperature Ths-design temperature Tuser≤-5 " and " indoor temperature Tapp-design temperature Tuser >=0 ", for example outdoor temperature Ths=16 ℃, design temperature Tuser=23 ℃, the pattern that the occasion of indoor temperature Tapp=25 ℃ is used.In addition, in this operation mode No.3, the circulating path of cold-producing medium is the direction of arrow of Fig. 4.
In this operation mode, first, utilize cubic valve 2 for compression circulation, refrigerant piping 10 is communicated with refrigerant piping 11, and refrigerant piping 19 is communicated with refrigerant piping 20.In addition, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 17, and refrigerant piping 13 is communicated with refrigerant piping 16.Like this, by switching cubic valve 2 and cubic valve 3 for cyclic switching for compression circulation, independently form respectively natural recirculating type circulation TS 1 and the first compression cycle P C1.At this, in operation mode No.3, the first expansion valve 5 with want to utilize first to utilize heat-shift that side heat exchanger 6 obtains to be correspondingly adjusted into the aperture of regulation, the second expansion valve 9 is also adjusted into the aperture of regulation.
In the first compression cycle P C1 side, the gas refrigerant of the HTHP of discharging from the outlet 1b of compressor 1 circulate with cubic valve 2 inflow Secondary Heat Source side heat exchangers 7 by compression, gas refrigerant dispels the heat and condenses to atmosphere between flow periods in Secondary Heat Source side heat exchanger 7, and liquefaction.The cold-producing medium utilization of having liquefied be adjusted to the aperture of regulation the second expansion valve 9 decompressions, expand, under the state of the gas-liquid two-phase of low-temp low-pressure, flow into second and utilize side heat exchanger 8.The cold-producing medium of this gas-liquid two-phase state absorbs heat and evaporates between flow periods in second utilizes side heat exchanger 8 from the water circulating in cold Warm water circulation loop CW, and gasification.The cold-producing medium having liquefied is circulated and with cubic valve 2, is flowed into the suction inlet 1a of compressors 1 by compression, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
On the other hand, in natural recirculating type circulation TS1 side, the cold-producing medium being trapped in the first heat source side heat exchanger 4 dispels the heat and condenses to atmosphere, and liquefaction.The liquid refrigerant that density is large is subject to the impact of gravity and declines, and by the first expansion valve 5, in first utilizes side heat exchanger 6, between flow periods, from the water circulating in cold Warm water circulation loop CW, absorb heat and evaporate, and gasification.Now, the barometric gradient causing due to the density contrast that can form by cold-producing medium, therefore vaporized refrigerant flow direction the first heat source side heat exchanger 4.
In this operation mode No.3, owing to utilizing first to utilize side heat exchanger 6 and second to utilize the water in the cooling cold Warm water circulation loop CW of side heat exchanger 8, so the air in house 30 is cooling by indoor heat converter 31.That is, operation mode No.3 is cold air operation pattern.If utilize this operation mode No.3, owing to using in the lump natural recirculating type circulation TS1 and the first compression cycle P C1, therefore compare with utilizing the operation mode 1 of the second compression cycle P C2, can suppress power consumption.
In addition, in ambient temperature, be the occasion below the indoor temperature of house 30, and the little occasion of the difference of ambient temperature and indoor temperature, be difficult to become the Natural Circulation of the cold-producing medium that utilizes natural recirculating type circulation TS1, be difficult to guarantee cooling capacity.In addition, in ambient temperature, be the occasion more than dew-point temperature of room air, only utilize natural recirculating type running to be difficult to dehumidify.But, according to operation mode No.3, owing to utilizing the first compression cycle P C1 to carry out forcibly cold air operation, therefore utilize the water that circulates in cold Warm water circulation loop CW and in second utilizes side heat exchanger 8 mobile cold-producing medium carry out heat exchange, can make the cold warm water of supplying with to indoor heat converter 31 is the temperature of expectation, can carry out the cooling of room air and dehumidifying.Now, the water of cold Warm water circulation loop CW carries out heat exchange by indoor heat converter 31 and the room air of house 30, become the water of lower than indoor temperature and higher than ambient temperature temperature, return to first and utilize side heat exchanger 6, by cold-producing medium, evaporated and absorbed heat, water temperature drops near ambient temperature.Near the water that temperature drops to ambient temperature is sent to the second temperature of utilizing side heat exchanger 2 and being cooled to expect.That is, the cooling capacity of the circulating circulation TS1 of running assisting natural of the first compression cycle P C is in shortage.Like this, operation mode No.3, especially in the little occasion of the difference of ambient temperature and indoor temperature, can utilize natural recirculating type circulation TS1 and the first compression cycle P C1 in the lump, carries out effective cold air operation.
(operation mode No.4(Fig. 5))
Operation mode No.4 is the pattern of only utilizing the cold air operation of natural recirculating type circulation TS1, is pattern more much lower than indoor temperature in ambient temperature and that use except the little occasion of humidity load (such as the occasion that daytime in winter etc. makes indoor temperature increase due to sunshine or internal load).This operation mode No.4 is at " outdoor temperature Ths-design temperature Tuser≤-10 " and " indoor temperature Tapp-design temperature Tuser >=0 ", for example outdoor temperature Ths=10 ℃, design temperature Tuser=23 ℃, the pattern that the occasion of indoor temperature Tapp=25 ℃ is used.This operation mode No.4 is identical with operation mode No.3 with on first this aspect of compression cycle P C1 at formation natural recirculating type circulation TS1, but it is different from operation mode No.3 in the running that makes compressor 1, to stop this point.That is, operation mode No.3 is from the different of operation mode No.4 whether compressor 1 turns round.In addition, in this operation mode No.4, the circulating path of cold-producing medium is the direction of arrow of Fig. 5.
In this operation mode No.4, for example, in the indoor temperature occasion higher than ambient temperature, can only utilize the water in the cooling cold Warm water circulation loop CW of above-mentioned natural recirculating type circulation TS1, the room air that utilizes 31 pairs of these chilled water of indoor heat converter and house 30 carries out heat exchange and in cooling chamber.Like this, though due to operation mode No.4 also can cooling chamber under the state that compressor 1 is stopped in, therefore can significantly reduce power consumption.
At this, in above-mentioned embodiment example, as the cold-producing medium in refrigerant piping, use the R410a as freon class cold-producing medium, but also can replace this material, use R134a, HFO1234yf, HFO1234ze, CO2.In addition, in above-mentioned embodiment example, as the heat transmission medium circulating, make water in cold Warm water circulation loop CW, but replace this material, can use the salt solution such as glycol.In addition, in above-mentioned embodiment example, adopted as utilizing side heat transmission medium to make water and being provided with the structure of cold Warm water circulation loop CW, but also can replace this structure, as utilizing side heat transmission medium to use the air in house 30 also direct to utilizing the air in side heat exchanger 6,8 and house 30 to carry out heat exchange.
In addition, in above-mentioned embodiment example, as cyclic switching mechanism, use cubic valve 3 cyclic switching for, but replace this structure, can adopt and combine two tripartite's valves and have with the structure of cubic valve identical function and combine four two side's valves and there is the structure with cubic valve identical function.At this, as cyclic switching mechanism, using the occasion of cubic valve 3 for cyclic switching, can switch freeze cycle only utilizing a circulating switching valve to form independently the first state of natural recirculating type circulation TS1 and the first compression cycle P C1 with cubic valve 3 and form between the second state of the second compression cycle P C2, therefore have advantages of and can reduce parts number of packages.If adopt two tripartite's valves of combination, there is the structure with cubic valve identical function, have for switching the control of the freeze cycle easy advantage that becomes.In addition, if adopt four two side's valves of combination, there is the structure with cubic valve identical function, because two side's valves are cheap, therefore have advantages of and can reduce costs.
(the second embodiment of the present invention)
Then, use Fig. 6 and Fig. 7 to describe the aircondition of the second embodiment example of the present invention, but the identical structure of the aircondition with the first embodiment example is marked to identical symbol, also the description thereof will be omitted.In addition, the arrow that heat exchanger marks in Fig. 7 represents flowing of heat.As shown in Figure 6, the aircondition of the second embodiment example is configured to, by being assembled in, tripartite's valve for the first bypass (bypass switching mechanism) 41 connects on the refrigerant piping 11 of compression circulation with cubic valve 2 and Secondary Heat Source side heat exchanger 7, tripartite's valve for the second bypass (bypass switching mechanism) 42 is assembled in to second to be utilized on side heat exchanger 8 and the refrigerant piping 19 of compression circulation with cubic valve 2, and utilize refrigerant piping for bypass (bypass pipe arrangement) 43 to connect tripartite's valve 41 and the second bypass tripartite's valve 42 for the first bypass, form cold-producing medium roundabout runner in compressor, it is bypass passageways.The structure that bypass passageways is set like this, different from the first embodiment example.
By this difference, in the aircondition of the second embodiment example, can form the natural recirculating type circulation TS2 that uses two 4,7 and two of heat source side heat exchangers to utilize side heat exchanger 6,8, can utilize the running of the operation mode No.5 of following explanation.In addition, in order to form natural recirculating type circulation TS2, the first heat source side heat exchanger 4 and Secondary Heat Source side heat exchanger 7 are arranged on roughly the same height or by first, utilize side heat exchanger 6 to be arranged on than second and utilize the height and position that side heat exchanger is low, first utilizes side heat exchanger 6 and second to utilize side heat exchanger 8 to be arranged on roughly the same height, and the first heat source side heat exchanger 4 is arranged on than first and utilizes side heat exchanger 6 and second to utilize the position that side heat exchanger 8 is high and drop is set with Secondary Heat Source side heat exchanger 7.
In order to form natural recirculating type circulation TS2, operation cycle is switched with cubic valve 3, connects refrigerant piping 12 and refrigerant piping 13, connects refrigerant piping 16 and refrigerant piping 17.In addition, tripartite's valve 41 and the second bypass tripartite's valve 42 for operation the first bypass, can not flow into compressor 1 and in bypass, by mode mobile in refrigerant piping 43, switch the runner of cold-producing medium with cold-producing medium.Like this, make connect annularly Secondary Heat Source side heat exchanger 7, for cyclic switching cubic valve 3, the first heat source side heat exchanger 4, the first expansion valve 5, first utilize side heat exchanger 6, for cyclic switching cubic valve 3, the second expansion valve 9, second utilize side heat exchanger 8, the natural recirculating type circulation TS2 of tripartite's valve 27 for tripartite's valve 42 for the second bypass, refrigerant piping 43 for bypass, the first bypass.Then, operation mode No.5 is described.
(operation mode No.5(Fig. 7))
Operation mode No.5 is the pattern of only utilizing the cold air operation of natural recirculating type circulation TS2, No.4 is identical with operation mode, is more much lower and use except the little occasion of humidity load (such as the occasion that daytime in winter etc. makes indoor temperature increase due to sunshine or internal load) institute than indoor temperature in ambient temperature.This operation mode No.5 is at " outdoor temperature Ths-design temperature Tuser≤-10 " and " indoor temperature Tapp-design temperature Tuser >=0 ", for example outdoor temperature Ths=10 ℃, design temperature Tuser=23 ℃, the pattern that the occasion of indoor temperature Tapp=25 ℃ is used.In addition, in operation mode No.5, the circulating path of cold-producing medium is the direction of arrow of Fig. 7.
In this operation mode, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 13, and refrigerant piping 16 is communicated with refrigerant piping 17.In addition, utilize tripartite's valve 41 and the second bypass tripartite's valve 42 for the first bypass, cold-producing medium can not flow into compressor 1 and use in refrigerant piping 43 and flow in bypass.In operation mode No.5, the first expansion valve 5 with want to utilize first to utilize heat-shift that side heat exchanger 6 obtains to be correspondingly adjusted into the aperture of regulation, the second expansion valve 9 is for all opening.In addition, in operation mode No.5, compressor 1 stops.
The cold-producing medium being trapped in the first heat source side heat exchanger 4 and Secondary Heat Source side heat exchanger 7 dispels the heat and condenses to atmosphere, and liquefaction.The liquid refrigerant that density is large is subject to the impact of gravity and flows to first utilizing side heat exchanger 6 and second to utilize side heat exchanger 8.Flowing into first utilizes side heat exchanger 6 and second to utilize the cold-producing medium of side heat exchanger 8 to utilize in side heat exchanger 6,8 and from the water circulating in cold Warm water circulation loop CW, absorb heat and evaporate between flow periods at each, the barometric gradient producing by the density contrast by cold-producing medium, rises to Secondary Heat Source side heat exchanger 7.Like this, cold-producing medium utilizes density contrast to carry out Natural Circulation in natural recirculating type circulation TS2.
In this operation mode No.5, owing to utilizing 4,7 and two of two heat source side heat exchangers to utilize side heat exchanger 6,8 to form natural recirculating type circulation TS2, therefore to compare with above-mentioned natural recirculating type circulation TS1, cooling capacity improves.Therefore owing to not needing to utilize the running of compressor 1, on this aspect of power consumption not, saving energy is effective.In addition, owing to utilizing first to utilize side heat exchanger 6 and second to utilize the water in the cooling cold Warm water circulation loop CW of side heat exchanger 8, so the air in house 30 is cooling by indoor heat converter 31.That is, operation mode No.5 is cold air operation pattern.
In addition, in this operation mode No.5, by operation cycle, switch with cubic valve 3, connect refrigerant piping 12 and refrigerant piping 17, connect refrigerant piping 13 and refrigerant piping 16, can form two natural recirculating type circulations of the natural recirculating type circulation of having used natural recirculating type circulation TS1, Secondary Heat Source side heat exchanger 7 and second to utilize side heat exchanger 8.Advantage as this occasion, can enumerate, owing to increasing temperature difference extraneous and water in the first natural recirculating type circulation that utilizes side heat exchanger 6 and the first heat source side heat exchanger 4 to form, therefore compare with systemic circulation mode (using the mode of natural recirculating type circulation TS2), there is the possibility that can guarantee cooling capacity, or correspondingly become easy with the switching of operation mode No.4 with the change of ambient temperature or load.
(the 3rd embodiment of the present invention)
Then, use Fig. 8～Figure 14 to describe the aircondition of the 3rd embodiment example of the present invention, the identical structure of the aircondition with the first embodiment example is marked to identical symbol, and the description thereof will be omitted.In addition, the arrow that heat exchanger marks in Fig. 9～Figure 14 represents flowing of heat.The aircondition of the 3rd embodiment example is configured to, as utilizing the heat transmission medium of side to use the air in house 30, utilize side heat exchanger 58 to be divided into two to be first to cut apart heat exchanger 58a and second and cut apart heat exchanger 58b by second, cut apart link that heat exchanger 58a and second cuts apart heat exchanger 58b and the valve (the 3rd expansion valve) 51 that dehumidifies is set with refrigerant piping 52a and link between with refrigerant piping 52b connecting first.This structure is the difference main with the first embodiment example.According to this structure, the running that operation mode carries out while the heat again that the aircondition of the 3rd embodiment example can utilize the air in the house 30 that warms up to dehumidify dehumidifies.In addition, not shown, but be provided with for the air in house 30 being sent into first, utilize side heat exchanger 1 and second to utilize side heat exchanger 58(first to cut apart heat exchanger 58a and second to cut apart heat exchanger 58b) air blast.
The aircondition of the 3rd embodiment example is identical with the first embodiment example, can utilize cyclic switching with the first state of cubic valve 3 natural recirculating type circulation TS3, first compression cycle P C3 of explanation below using in the lump and can utilize between the second state of the second compression cycle P C4 freeze cycle is switched.
Natural recirculating type circulation TS3 utilizes refrigerant piping 14 to connect the first heat source side heat exchanger 4 and the first expansion valve 5, utilize refrigerant piping 15 to connect the first expansion valve 5 and first and utilize side heat exchanger 6, utilize refrigerant piping 16 to connect first and utilize side heat exchanger 6 and cubic valve 3 cyclic switching for, utilize refrigerant piping 13 connection cyclic switchings with cubic valve 3 and the first heat source side heat exchanger 4, to form the circulation of ring-type.And cold-producing medium utilizes density contrast to carry out Natural Circulation in this natural recirculating type circulation TS3.
The first compression cycle P C3 is cubic valve 2 for the outlet 1b that utilizes refrigerant piping 10 to connect compressors 1 circulates with compression, utilize refrigerant piping 11 to connect cubic valve 2 and Secondary Heat Source side heat exchanger 7 for compression circulation, utilize refrigerant piping 12 to connect Secondary Heat Source side heat exchanger 7 and cubic valve 3 for cyclic switching, utilize refrigerant piping 17 to connect cubic valve 3 and the second expansion valve 9 for cyclic switching, utilize refrigerant piping 18 to connect the second expansion valve 9 and first and cut apart heat exchanger 58a, utilize to link with refrigerant piping 52a connection first and cut apart heat exchanger 58a and dehumidifying valve 51, utilize to link with refrigerant piping 52b connection dehumidifying valve 51 and second and cut apart heat exchanger 58b, utilize refrigerant piping 19 connect second cut apart heat exchanger 58b circulate with compression for cubic valve 2, utilize refrigerant piping 20 to connect compression circulation and form the freeze cycle of ring-type with the suction inlet 1a of compressor 1 with cubic valve 2.And, utilize compressor 1 to make forcibly cold-producing medium circulate in the first compression cycle P C3.
The second compression cycle P C4 is cubic valve 2 for the outlet 1b that utilizes refrigerant piping 10 to connect compressors 1 circulates with compression, utilize refrigerant piping 11 to connect cubic valve 2 and Secondary Heat Source side heat exchanger 7 for compression circulation, utilize refrigerant piping 12 to connect Secondary Heat Source side heat exchanger 7 and cubic valve 3 for cyclic switching, utilize refrigerant piping 13 to connect cubic valve 3 and the first heat source side heat exchanger 4 for cyclic switching, utilize refrigerant piping 14 to connect the first heat source side heat exchanger 4 and the first expansion valve 5, utilize refrigerant piping 15 to connect the first expansion valve 5 and first and utilize side heat exchanger 6, utilize refrigerant piping 16 to connect first and utilize side heat exchanger 6 and cubic valve 3 for cyclic switching, utilize refrigerant piping 17 to connect cubic valve 3 and the second expansion valve 9 for cyclic switching, utilize refrigerant piping 18 to connect the second expansion valve 9 and first and cut apart heat exchanger 58a, utilize to link with refrigerant piping 52a connection first and cut apart heat exchanger 58a and dehumidifying valve 51, utilize to link with refrigerant piping 52b connection dehumidifying valve 51 and second and cut apart heat exchanger 58b, utilize refrigerant piping 19 connect second cut apart heat exchanger 58b circulate with compression for cubic valve 2, utilize refrigerant piping 20 to connect compression circulation and form the freeze cycle of ring-type with the suction inlet 1a of compressor 1 with cubic valve 2.And, utilize compressor 1 to make forcibly cold-producing medium circulate in the second compression cycle P C4.
Then, the operation mode that utilizes the aircondition of the 3rd embodiment example to carry out is described.In the aircondition of the 3rd embodiment example, as shown below, can carry out six operation modes of operation mode No.6～No.11.
(operation mode No.6(Fig. 9))
Operation mode No.6 is the pattern of utilizing separately the dehumidifying of the heat again running of the second compression cycle P C4, is higher than design temperature in indoor temperature, and humidity is slightly high, heating and cooling dehumidify the operation mode that necessary loading condiction is used than setting for indoor humidity.This operation mode No.6 is in the occasion of " indoor temperature Tapp-design temperature Tuser >=0 " and " indoor humidity Happ-sets humidity Huser >=0 " and " outdoor temperature Ths-design temperature Tuser >=0 ", for example sets humidity Huser=50%, the pattern that the occasion of indoor humidity Happ=60% and design temperature Tuser=23 ℃, indoor temperature Tapp=25 ℃, outdoor temperature Ths=27 ℃ is used.In addition, in this operation mode No.6, the circulating path of cold-producing medium is the direction of arrow of Fig. 9.
In this operation mode, first, utilize cubic valve 2 for compression circulation, refrigerant piping 10 is communicated with refrigerant piping 11, and refrigerant piping 19 is communicated with refrigerant piping 20.In addition, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 13, and refrigerant piping 16 is communicated with refrigerant piping 17.Like this, by switching cubic valve 2 and cubic valve 3 for cyclic switching for compression circulation, form the second compression cycle P C4.At this, in operation mode No.6, the first expansion valve 5 and the second expansion valve 9 are for all opening, and dehumidifying valve 51 is adjusted into the aperture of regulation.
The gas refrigerant of the HTHP of discharging from the outlet 1b of compressor Secondary Heat Source side heat exchanger 7, the first heat source side heat exchanger 4 between flow periods the atmosphere to the heat transmission medium as heat source side dispel the heat and condense, under the state of gas-liquid two-phase, flow into first and utilize side heat exchanger 6.The cold-producing medium of this gas-liquid two-phase state in first utilizes side heat exchanger 6 between flow periods by as utilizing the air heat radiation in the house 30 of side heat transmission medium to condense, then, in first cuts apart heat exchanger 58a, between flow periods, same air in house 30 dispels the heat and condenses, and liquefaction.Cold-producing medium utilization dehumidifying valve 51 decompressions of having liquefied, expand, become gas-liquid two-phase state.The cold-producing medium of gas-liquid two-phase state in second cuts apart heat exchanger 52b between flow periods by the air evaporation from house 30, and gasification.The cold-producing medium having gasified flows into the suction inlet 1a of compressor 1, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
In this operation mode No.6, utilize first to utilize side heat exchanger 6 and first to cut apart the air in heat exchanger 52a heating house 30, utilize second to cut apart heat exchanger 52b the air in house 30 is carried out to cooling and dehumidifying.
(operation mode No.7(Figure 10))
Operation mode No.7 is the pattern of utilizing separately the dehumidifying of the heat again running of the second compression cycle P C4, is higher than design temperature in indoor temperature, and humidity is high, heating and cooling dehumidify the operation mode that necessary loading condiction is used than setting for indoor humidity.This operation mode No.7 is in the occasion of " indoor temperature Tapp-design temperature Tuser >=0 " and " indoor humidity Tapp-sets humidity Tuser >=15 " and " outdoor temperature Ths-design temperature Tuser >=0 ", for example sets humidity Huser=50%, the pattern that the occasion of indoor humidity Happ=70% and design temperature Tuser=23 ℃, indoor temperature Tapp=25 ℃, outdoor temperature Ths=27 ℃ is used.
In this operation mode No.7, comparison diagram 9 and Figure 10 can find out, cold-producing medium flows in the circulating path identical with operation mode No.6.But the second expansion valve 9 is different in operation mode No.6 and operation mode No.7 from the open and-shut mode of dehumidifying valve 51, in operation mode No.7, the first expansion valve 5 is for all opening, and the second expansion valve 9 is adjusted into the aperture of regulation, and dehumidifying valve 51 is for all opening.
The gas refrigerant of the HTHP of discharging from the outlet 1b of compressor Secondary Heat Source side heat exchanger 7, the first heat source side heat exchanger 4 between flow periods the atmosphere to the heat transmission medium as heat source side dispel the heat and condense, under the state of gas-liquid two-phase, flow into first and utilize side heat exchanger 6.The cold-producing medium of this gas-liquid two-phase state in first utilizes side heat exchanger 6 between flow periods by as utilizing the air in the house 30 of side heat transmission medium to dispel the heat and condense, and liquefaction.The cold-producing medium having liquefied utilizes the second expansion valve 9 decompressions, expands, and becomes gas-liquid two-phase state.The cold-producing medium of gas-liquid two-phase state is cut apart between heat exchanger 58a flow periods and is absorbed heat and evaporated by the air in house 30 first, then, second, cut apart between heat exchanger 58b flow periods equally by the air heat absorption in house 30 go forward side by side step evaporation gasification.The cold-producing medium having gasified flows into the suction inlet 1a of compressor 1, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
In this operation mode No.7, utilize the first air utilizing in side heat exchanger 6 heating houses 30, utilize first to cut apart heat exchanger 52a and second and cut apart heat exchanger 52b the air in house 30 is carried out to cooling and dehumidifying.
(operation mode No.8(Figure 11))
Operation mode No.8 is the pattern of utilizing separately the dehumidifying of the heat again running of the second compression cycle P C4, is lower than design temperature in indoor temperature, and humidity is high, heating and cooling dehumidify the operation mode that necessary loading condiction is used than setting for indoor humidity.This operation mode No.8 is in the occasion of " indoor temperature Tapp-design temperature Tuser≤0 " and " indoor humidity Happ-set humidity Huser>10 " and " outdoor temperature Ths-design temperature Tuser≤0 ", for example sets humidity Huser=50%, the pattern that the occasion of indoor humidity Happ=70% and design temperature Tuser=23 ℃, indoor temperature Tapp=20 ℃, outdoor temperature Ths=18 ℃ is used.In addition, the circulating path of the cold-producing medium of this operation mode No.8 is the direction of arrow of Figure 11, is the path contrary with operation mode 6.
In this operation mode, first, utilize cubic valve 2 for compression circulation, refrigerant piping 10 is communicated with refrigerant piping 19, and refrigerant piping 11 is communicated with refrigerant piping 20.In addition, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 13, and refrigerant piping 16 is communicated with refrigerant piping 17.At this, in operation mode No.8, the first expansion valve 5 and the second expansion valve 9 are for all opening, and dehumidifying valve 51 is adjusted into the aperture of regulation.
The gas refrigerant of the HTHP of discharging from the outlet 1b of compressor second cuts apart heat exchanger 58b between flow periods to as utilizing the air in the house 30 of heat transmission medium of side dispel the heat and condense, and liquefy.Cold-producing medium utilization dehumidifying valve 51 decompressions of having liquefied, expand, become gas-liquid two-phase state.The cold-producing medium of gas-liquid two-phase state absorbs heat and evaporates from the air in house 30 between flow periods in first cuts apart heat exchanger 58a, then, in first utilizes side heat exchanger 6 between flow periods equally from the step evaporation of going forward side by side of the air heat absorption in house 30.And, first, utilize the cold-producing medium of the gas-liquid two-phase state of side heat exchanger 6 outflows in the first heat source side heat exchanger 4 and Secondary Heat Source side heat exchanger 7, to flow and from the atmosphere of the heat transmission medium as heat source side, absorb heat and evaporate on one side on one side, and gasification.The cold-producing medium having gasified flows into the suction inlet 1a of compressor 1, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
In this operation mode No.8, utilize first to utilize side heat exchanger 6 and first to cut apart the air in heat exchanger 52a cooling and dehumidifying house 30, utilize second to cut apart heat exchanger 52b the air in house 30 is heated.
(operation mode No.9(Figure 12))
Operation mode No.9 is the pattern of utilizing separately the heat dehumidifying running again of the second compression cycle P C4, is lower than design temperature in indoor temperature, the operation mode that humidity is slightly high than setting for indoor humidity, heating and the necessary loading condiction that dehumidifies are a little used.This operation mode No.9 is in the occasion of " indoor temperature Tapp-design temperature Tuser≤0 " and " indoor humidity Happ-sets humidity Huser >=0 " and " outdoor temperature Ths-design temperature Tuser≤0 ", for example sets humidity Huser=50%, the pattern that the occasion of indoor humidity Happ=60% and design temperature Tuser=23 ℃, indoor temperature Tapp=20 ℃, outdoor temperature Ths=18 ℃ is used.In addition, the circulating path of the cold-producing medium of this operation mode No.9 is the direction of arrow of Figure 12, is the path contrary with operation mode No.7.
In this operation mode, first, utilize cubic valve 2 for compression circulation, refrigerant piping 10 is communicated with refrigerant piping 19, and refrigerant piping 11 is communicated with refrigerant piping 20.In addition, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 13, and refrigerant piping 16 is communicated with refrigerant piping 17.At this, in operation mode No.9, the first expansion valve 5 is for all opening, and the second expansion valve 9 is adjusted into the aperture of regulation, and dehumidifying valve 51 is for all opening.
The gas refrigerant of the HTHP of discharging from the outlet 1b of compressor second cuts apart heat exchanger 58b between flow periods to as utilizing the air in the house 30 of heat transmission medium of side to dispel the heat and condense, then, in first cuts apart heat exchanger 58a, between flow periods, same air in house 30 dispels the heat and condenses, and liquefaction.The cold-producing medium having liquefied utilizes the second expansion valve 9 decompressions, expands, and becomes gas-liquid two-phase state.The cold-producing medium of gas-liquid two-phase state in first utilizes side heat exchanger 6 between flow periods from the step evaporation of going forward side by side of the air heat absorption in house 30.And, first, utilize the cold-producing medium of the gas-liquid two-phase state of side heat exchanger 6 discharges in the first heat source side heat exchanger 4 and Secondary Heat Source side heat exchanger 7, to flow and from the atmosphere of the heat transmission medium as heat source side, absorb heat and evaporate on one side on one side, and gasification.The cold-producing medium having gasified flows into the suction inlet 1a of compressor 1, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
In this operation mode No.9, utilize the first air utilizing in side heat exchanger 6 cooling and dehumidifying houses 30, utilize first to cut apart heat exchanger 58a and second and cut apart heat exchanger 58b the air in house 30 is heated.
(operation mode No.10(Figure 13))
Operation mode No.10 is the pattern of utilizing in the lump the dehumidifying of the heat again running of natural recirculating type circulation TS3 and the first compression cycle P C3, because indoor temperature is slightly higher than design temperature, indoor humidity is higher than setting humidity, therefore being the loading condiction that cooling and dehumidifying is necessary with heating, is the operation mode using in the ambient temperature occasion more much lower than indoor temperature.This operation mode No.10 is in the occasion of " indoor temperature Tapp-design temperature Tuser≤0 " and " indoor humidity Happ-sets humidity Huser >=0 " and " outdoor temperature Ths-design temperature Tuser≤-10 ", for example sets humidity Huser=50%, the pattern that the occasion of indoor humidity Happ=70% and design temperature Tuser=23 ℃, indoor temperature Tapp=25 ℃, outdoor temperature Ths=10 ℃ is used.In addition, in this operation mode No.10, the circulating path of cold-producing medium is the direction of arrow of Figure 13.
In this operation mode, first, utilize cubic valve 2 for compression circulation, refrigerant piping 10 is communicated with refrigerant piping 11, and refrigerant piping 19 is communicated with refrigerant piping 20.In addition, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 17, and refrigerant piping 13 is communicated with refrigerant piping 16.At this, in operation mode No.10, the first expansion valve 5 with want to utilize first to utilize heat-shift that side heat exchanger 6 obtains to be correspondingly adjusted into the aperture of regulation, the second expansion valve 9 is for all opening, the valve 51 that dehumidifies is adjusted into the aperture of regulation.
In the first compression cycle P C3 side, the gas refrigerant of the HTHP of discharging from the outlet 1b of compressor Secondary Heat Source side heat exchanger 7 between flow periods the atmosphere to the heat transmission medium as heat source side dispel the heat and condense, under the state of gas-liquid two-phase, flow into first and cut apart heat exchanger 58a.The cold-producing medium of this gas-liquid two-phase state in first cuts apart heat exchanger 58a between flow periods by as utilizing the air heat radiation in the house 30 of heat transmission medium of side to condense, and liquefaction.Cold-producing medium utilization dehumidifying valve 51 decompressions of having liquefied, expand, and become gas-liquid two-phase state.The cold-producing medium of gas-liquid two-phase state is cut apart between heat exchanger 52b flow periods from the air in house 30 and is absorbed heat and evaporate second, and gasification.The cold-producing medium having gasified flows into the suction inlet 1a of compressor 1, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
On the other hand, in natural recirculating type circulation TS3 side, the cold-producing medium being trapped in the first heat source side heat exchanger 4 dispels the heat and condenses to atmosphere, and liquefaction.The liquid refrigerant that density is large is subject to the impact of gravity and declines, and by the first expansion valve 5, in first utilizes side heat exchanger 6, between flow periods, from the air in house 30, absorbs heat and evaporates.Now, due to the barometric gradient that can form by the density contrast generation of cold-producing medium, therefore vaporized refrigerant flow direction the first heat source side heat exchanger 4.
At this operation mode No.10, utilize the first air utilizing in the cooling house 30 of side heat exchanger 6, utilize first to cut apart heat exchanger 58a and again heat, utilize second to cut apart heat exchanger 58b and carry out cooling and dehumidifying.Thus, in ambient temperature, be the occasion below the indoor temperature of house 30, even the little occasion of the difference of ambient temperature and indoor temperature, by utilizing natural recirculating type circulation TS3 and the first compression cycle P C3, suitable cooling and dehumidifying and heating can be carried out, the humiture of expectation can be accessed.Thus, compare with natural recirculating type circulation, can improve dehumidifying effect.
(operation mode No.11(Figure 14))
Operation mode No.11 is the pattern of utilizing in the lump the dehumidifying of the heat again running of natural recirculating type circulation TS3 and the first compression cycle P C3, because indoor temperature is lower than design temperature, indoor humidity is higher than setting humidity, therefore being the loading condiction that cooling and dehumidifying is necessary with heating, is the operation mode that the ambient temperature occasion more much lower than indoor temperature used.This operation mode No.11 is in the occasion of " indoor temperature Tapp-design temperature Tuser≤0 " and " indoor humidity Happ-design temperature Huser >=0 " and " outdoor temperature Ths-design temperature Tuser≤-10 ", for example sets humidity Huser=50%, the pattern that the occasion of indoor humidity Happ=70% and design temperature Tuser=23 ℃, indoor temperature Tapp=21 ℃, outdoor temperature Ths=10 ℃ is used.In addition, the circulating path of the cold-producing medium in this operation mode No.11 is the direction of arrow of Figure 14, and relatively Figure 13 and Figure 14 can find out, the direction of the circulating path of the cold-producing medium of the first compression cycle P C3 is contrary with operation mode No.10.
In this operation mode, first, utilize cubic valve 2 for compression circulation, refrigerant piping 10 is communicated with refrigerant piping 19, and refrigerant piping 11 is communicated with refrigerant piping 20.In addition, utilize cubic valve 3 for cyclic switching, refrigerant piping 12 is communicated with refrigerant piping 17, and refrigerant piping 13 is communicated with refrigerant piping 16.At this, in operation mode No.11, the first expansion valve 5 with want to utilize first to utilize heat-shift that side heat exchanger 6 obtains to be correspondingly adjusted into the aperture of regulation, the second expansion valve 9 is for all opening, the valve 51 that dehumidifies is adjusted into the aperture of regulation.
In the first compression cycle P C3 side, the gas refrigerant of the HTHP of discharging from the outlet 1b of compressor second cuts apart heat exchanger 58b between flow periods to as utilizing the air in the house 30 of heat transmission medium of side dispel the heat and condense, and liquefy.Cold-producing medium utilization dehumidifying valve 51 decompressions of having liquefied, expand, become the state of gas-liquid two-phase.The cold-producing medium of gas-liquid two-phase state absorbs heat and evaporates from the air in house 30 between flow periods in first cuts apart heat exchanger 58a, and between flow periods, the atmosphere from the heat transmission medium as heat source side absorbs heat and evaporates in Secondary Heat Source side heat exchanger 7, and gasification.The cold-producing medium having gasified flows into the suction inlet 1a of compressor 1, utilizes compressor 1 again compressed and become the gas refrigerant of HTHP.
On the other hand, in natural recirculating type circulation TS3 side, the cold-producing medium being trapped in the first heat source side heat exchanger 4 dispels the heat and condenses to atmosphere, and liquefaction.The liquid refrigerant that density is large is subject to the impact of gravity and declines, and by the first expansion valve 5, in first utilizes side heat exchanger 6, between flow periods, from the air in house 30, absorbs heat and evaporates.Now, due to the barometric gradient that can form by the density contrast generation of cold-producing medium, therefore vaporized refrigerant flow direction the first heat source side heat exchanger 4.
In this operation mode No.11, utilize the first air utilizing in the cooling house 30 of side heat exchanger 6, utilize first to cut apart heat exchanger 58a and carry out cooling and dehumidifying, utilize second to cut apart heat exchanger 58b and again heat.Thus, it in ambient temperature, is the occasion below the indoor temperature of house 30, especially the little occasion of the difference of ambient temperature and indoor temperature, by utilizing in the lump natural recirculating type circulation TS3 and the first compression cycle P C3, suitable cooling and dehumidifying and heating can be carried out, the humiture environment of expectation can be accessed.Thus, compare with natural recirculating type circulation, can improve dehumidifying effect.
In addition, in the aircondition of the 3rd embodiment example, if make compressor 1 stop, can only utilizing the running of natural recirculating type circulation TS3 in operation mode No.10, No.11.
(the 4th embodiment of the present invention)
Then, use Figure 15 to describe the aircondition of the 4th embodiment example of the present invention, but the identical structure of the aircondition with the first embodiment example is marked to identical symbol, and the description thereof will be omitted.The aircondition of the 4th embodiment is characterised in that, be configured to, formation comprises middle Warm water circulation loop (the heat source side heat transmission medium closed circuit) MW of Secondary Heat Source side heat exchanger 7, as the heat transmission medium of heat source side, water is circulated in the MW of this Warm water circulation loop, centre.
Middle Warm water circulation loop MW is that in the middle of utilizing, warm water pipe arrangement (heat source side heat transmission medium pipe arrangement) 62,63 connects Secondary Heat Source side heat exchanger 7 with heat storage container 61 and the loop of the ring-type forming.And, utilizing not shown circulating pump, water is forced circulation in middle Warm water circulation loop MW.In addition, in heat storage container 61, be filled with heat-storing material.
In the aircondition of the 4th embodiment example of this formation, for example, if utilize above-mentioned operation mode No.1 and the running of No.3, utilize warm to outside refrigerant release of Secondary Heat Source side heat exchanger 7, in middle Warm water circulation loop MW, mobile water absorbs from Secondary Heat Source side heat exchanger 7 that this is warm.It is warm by heat storage container 61 accumulation of heats that water absorbs, and the water circulating in middle Warm water circulation loop MW is middle warm water.Like this, according to the 4th embodiment example, can effectively utilize the heat extraction of Secondary Heat Source side heat exchanger 7 and warm water in the middle of making.Usually, what with respect to indoor cold air, need by day is many, supplying hot water needs manyly at night, but according to the aircondition of the 4th embodiment example, owing to can utilizing the heat extraction of the Secondary Heat Source side heat exchanger 7 while carrying out cold air operation by day, on heat storage container 61, middle warm water is carried out to accumulation of heat, therefore can utilize the middle warm water of heat storage container 61 to carry out supplying hot water at night, realize effective utilization of energy.In addition, solar heat collection device is connected on heat storage container 61, can utilizes the energy that can regenerate.
In addition, the evaporimeter as hot water supply circulation also can use Secondary Heat Source side heat exchanger 7.Specifically, as shown in figure 15, utilize supplying hot water with refrigerant piping 74a～74d connect successively compressor 71 for supplying hot water, condenser 72 for supplying hot water, expansion valve 73 for supplying hot water, Secondary Heat Source side heat exchanger 7 and form the supplying hot water circulation of ring-type, utilize supplying hot water to connect supplying hot waters with pipe arrangement 76,77 and construct the hot water supply system for supplying hot water with condenser 72 and storage hot water tank 75.In hot water supply system, utilize the supplying hot water of expansion valve 73 decompressions for supplying hot water, dilated gas-liquid two-phase state absorb heat and evaporate from Secondary Heat Source side heat exchanger 7 with cold-producing medium, and gasification.That is,, in hot water supply system, Secondary Heat Source side heat exchanger 7 works as evaporimeter.In addition, in this example, the heat transmission medium that carries out the heat source side of heat exchange with Secondary Heat Source side heat exchanger 7 is supplying hot water cold-producing medium.According to this structure, owing to can, by Secondary Heat Source side heat exchanger 7 for hot water supply system and air-conditioning system both sides, therefore reducing costs.In addition, as supplying hot water cold-producing medium, can use R134a, HFO1234yf, HFO1234ze, CO2 etc.
As mentioned above, the embodiment example according to above-mentioned, because the heat exchanger as compression circulation can utilize the heat exchanger for Natural Circulation, therefore can improve the efficiency of heat exchange.In addition, in above-mentioned embodiment example, owing to can utilizing in the lump natural recirculating type circulation and compression circulation, therefore in the ambient temperature occasion lower than indoor temperature, even if the difference hour of ambient temperature and indoor temperature also can improve dehumidifying effect.In addition, in above-mentioned embodiment example, owing to can, by the heat extraction of heat exchanger for supplying water or the equipment of supplying hot water, therefore effectively utilizing energy.
Symbol description
1-compressor, 1a-suction inlet, 1b-outlet, 2-compression circulates with cubic valve (flow channel switching valve), cubic valve for 3-cyclic switching (cyclic switching mechanism), the 4-the first heat source side heat exchanger, the 5-the first expansion valve, 6-the first utilizes side heat exchanger, 7-Secondary Heat Source side heat exchanger, 8-the second utilizes side heat exchanger, the 9-the second expansion valve, 10～20-refrigerant piping, 30-house (space is cooled), 31-indoor heat converter, 32-circulating pump, the cubic valve in 33-cold warm water loop, 35～40-cold warm water pipe arrangement (utilizing side heat transmission medium pipe arrangement), 41-the first tripartite's valve (bypass switching mechanism) for bypass, 42-the second tripartite's valve (bypass switching mechanism) for bypass, refrigerant piping for 43-bypass (bypass pipe arrangement), 51-dehumidifying valve (the 3rd expansion valve), 52a, 52b-link refrigerant piping, 58a-the first cut apart heat exchanger, 58b-second is cut apart heat exchanger, 61-heat storage container, 62, warm water pipe arrangement (heat source side heat transmission medium pipe arrangement) in the middle of 63-, 71-supplying hot water compressor, 72-supplying hot water condenser, 73-supplying hot water expansion valve, 74a～74d-supplying hot water refrigerant piping, 75-storage hot water tank, 76, 77-supplying hot water pipe arrangement, the circulation of TS1～TS3-natural recirculating type, PC1, the circulation of PC3-the first compression, PC2, the circulation of PC4-the second compression, CW-cold Warm water circulation loop (utilizing side heat transmission medium closed circuit), MW-middle Warm water circulation loop (heat source side heat transmission medium closed circuit).

Claims (6)

1. an aircondition, it possess compressor, to the heat transmission medium of heat source side and cold-producing medium carry out first and second heat source side heat exchanger of heat exchange, to utilizing the heat transmission medium of side and cold-producing medium carries out heat exchange that first and second utilizes side heat exchanger, switches flow channel switching valve and first and second expansion valve of the runner direction of cold-producing medium, this aircondition is characterised in that
Can at least form following three freeze cycle:
Utilize refrigerant piping to connect successively above-mentioned the first heat source side heat exchanger, above-mentioned the first expansion valve and be arranged on above-mentioned first of the position lower than above-mentioned the first heat source side heat exchanger and utilize side heat exchanger and form ring-type, cold-producing medium utilizes density contrast to carry out the natural recirculating type circulation of Natural Circulation;
Utilize refrigerant piping to connect successively the outlet of above-mentioned compressor, above-mentioned flow channel switching valve, above-mentioned Secondary Heat Source side heat exchanger, above-mentioned the second expansion valve, above-mentioned second and utilize the suction inlet of side heat exchanger and above-mentioned compressor and form ring-type, utilize above-mentioned compressor to make forcibly the first compression circulation of refrigerant circulation; And
Utilizing refrigerant piping to connect successively the outlet of above-mentioned compressor, above-mentioned flow channel switching valve, above-mentioned Secondary Heat Source side heat exchanger, above-mentioned the first heat source side heat exchanger, above-mentioned the first expansion valve, above-mentioned first utilizes side heat exchanger, above-mentioned the second expansion valve, above-mentioned second utilize the suction inlet of side heat exchanger and above-mentioned compressor and form ring-type, utilize above-mentioned compressor to make forcibly the second compression circulation of refrigerant circulation
This aircondition possesses the cyclic switching mechanism of between the second state of the first state that above-mentioned natural recirculating type circulates and above-mentioned the first compression circulation forms independently and above-mentioned the second compression circulation of formation, freeze cycle being switched.
2. aircondition according to claim 1, is characterized in that,
With utilize side heat transmission medium with pipe arrangement connect successively above-mentioned first utilize side heat exchanger, above-mentioned second to utilize side heat exchanger and be arranged on the indoor heat converter being cooled in space and form ring-type utilize side heat transmission medium closed circuit,
Make forcibly to circulate in utilizing side heat transmission medium closed circuit above-mentioned as the above-mentioned water that utilizes side heat transmission medium or salt solution.
3. aircondition according to claim 1 and 2, is characterized in that,
Utilize side heat exchanger to be divided into two to be first to cut apart heat exchanger and second and cut apart heat exchanger by above-mentioned second, cut apart link that heat exchanger and above-mentioned second cuts apart heat exchanger with the 3rd expansion valve is set on refrigerant piping connecting above-mentioned first.
4. aircondition according to claim 3, is characterized in that,
Utilize heat source side heat transmission medium to connect above-mentioned Secondary Heat Source side heat exchanger and heat storage container with pipe arrangement and form the heat source side heat transmission medium closed circuit of ring-type,
Make forcibly to circulate in above-mentioned heat source side heat transmission medium closed circuit as the water of the heat transmission medium of above-mentioned heat source side.
5. aircondition according to claim 3, is characterized in that,
Utilize supplying hot water to connect successively compressor for supplying hot water, supplying hot water with utilizing side heat exchanger, supplying hot water to circulate with expansion valve and above-mentioned Secondary Heat Source side heat exchanger the supplying hot water that forms ring-type with refrigerant piping,
Utilize above-mentioned supplying hot water to make forcibly the cold-producing medium circulation in above-mentioned supplying hot water circulation for supplying hot water as the heat transmission medium of above-mentioned heat source side with compressor.
6. aircondition according to claim 5, is characterized in that,
Be provided with and make the suction inlet of above-mentioned compressor and the bypass pipe arrangement of outlet bypass and the runner of cold-producing medium is switched to the bypass switching mechanism with any runner of runner via above-mentioned bypass pipe arrangement via the runner of above-mentioned compressor.
CN201080063497.1A 2010-02-24 2010-02-24 Air conditioner Expired - Fee Related CN102753915B (en)

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CN110425776A (en) * 2019-08-19 2019-11-08 北京丰联奥睿科技有限公司 A kind of V-type vertical tube evaporative cooling tower and its double control air-conditioning system
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