CN201935476U - Heat recovery type air-cooled heat pump unit - Google Patents

Heat recovery type air-cooled heat pump unit Download PDF

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Publication number
CN201935476U
CN201935476U CN2010206340593U CN201020634059U CN201935476U CN 201935476 U CN201935476 U CN 201935476U CN 2010206340593 U CN2010206340593 U CN 2010206340593U CN 201020634059 U CN201020634059 U CN 201020634059U CN 201935476 U CN201935476 U CN 201935476U
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China
Prior art keywords
valve
air
heat exchanger
port
compressor
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CN2010206340593U
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Chinese (zh)
Inventor
黄作忠
陈胜辉
王双
李鹏
罗晓燕
梁其锦
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广东欧科空调制冷有限公司
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Priority to CN2010206340593U priority Critical patent/CN201935476U/en
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    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02BCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02BCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Abstract

A heat recovery type air-cooled heat pump unit comprises first and second refrigerant circulatory systems, wherein the first refrigerant circulatory system comprises a first compressor, a first four-way valve, a second four-way valve, a first air side fin-type heat exchanger, an air conditioner side heat exchanger, a first gas-liquid separator, a full heat recovery exchanger, a hot water circulating water pump, a heat preservation water tank and valves; and the second refrigerant circulatory system comprises a second compressor, a third four-way valve, a fourth four-way valve, a second air side fin-type heat exchanger, the air conditioner side heat exchanger, a third liquid receiver, a second gas-liquid separator, a part heat recovery exchanger, the heat preservation water tank and valves. The heat recovery type air-cooled heat pump unit not only guarantees that the heat quantity is effectively recovered and reused, but also protects the environment from heat pollution, is environment-friendly and energy-saving, and effectively solves the defects that the air conditioner heating and domestic hot water generation can not be conducted at the same time, and the traditional full heat recovery air-conditioning system only having a single heat recovery system can not be used for generating higher-temperature domestic hot water when the environmental temperature is lower in winter.

Description

A kind of recovery type heat Air-Cooled Heat Pump Unit

Technical field

The utility model relates to air-conditioning technical field, particularly relates to a kind of recovery type heat Air-Cooled Heat Pump Unit.

Background technology

Heat pump all has bigger advantage as the alternative means that solves the heat supply problem from technology and economic angle.Heat pump techniques is a kind of low-grade heat that utilizes, and for example: heats such as air, water (comprising: surface water, underground water etc.), solar energy, soil, used heat are converted to high-grade heat, for example: the heat of heating.Its operation principle is: when operation of heat pump, by evaporimeter from thermal source draw heat (adopting heat), and to providing heat with heat target.

At present, along with The development in society and economy, increasing wind-cooling type heat pump unit is adopted by people.In summer, this wind-cooling type heat pump unit can give out a large amount of condensation heat by air side fins formula heat exchanger in environment in operation, and the discharging of condensation heat not only makes the temperature in city constantly raise, and can form " heat island " effect in the down town.If can the energy of this part be reclaimed and be used, not only can energy savings, reduce CO2 emission, and can protect environment.

For addressing the above problem, Granted publication number is: the Chinese utility model patent of CN 2548058Y disclosed a kind of " air-conditioning recuperation of heat unit " on April 30th, 2003, its technical scheme is: " be connected with heat recovering heat exchanger on the pipeline between compressor and the four-way change-over valve; and the delivery port of heat recovering heat exchanger is connected with a boiler, and the water inlet of heat recovering heat exchanger is connected with water inlet pipe." by heat recovering heat exchanger with the cooling of the superheated steam of high temperature, high pressure, be condensed into the liquid of high temperature, high pressure, simultaneously exhaust sensible heat and partial condensation latent heat are heated cold water, the hot water that heat is kept in the boiler, can provide lives uses hot water.

Though above-mentioned CN 2548058Y utility model patent technology is by setting up heat recovering heat exchanger, a large amount of condensation heat can be reclaimed, avoided the thermal pollution of air-conditioning system effectively to surrounding environment, but, this air-conditioning recuperation of heat unit only just can obtain the domestic hot-water under the operation of air conditioner situation, air-conditioning does not just have domestic hot-water's supply under the operation conditions, can't satisfy the demand of people to real-time domestic hot-water.Moreover this air-conditioning recuperation of heat unit can only be converted into the condensation heat of part hot water and realize that portion of hot reclaims, and heat recovery efficiency is low, is difficult to guarantee the normal domestic consumption of user, thereby makes that the use of air-conditioning recuperation of heat unit is limited.

Thereupon, people for the heat recovery system that solves air-conditioning system under the situation that air-conditioning does not move, do not have the problem of hot water supply, a kind of recovery type heat air-cooled type air conditioning system has entirely been proposed.

For example: Granted publication number is: the Chinese utility model patent of CN 200965375Y disclosed a kind of " recuperation of heat air-conditioning unit " on October 24th, 2007, its technical scheme is: " it comprises the compressor (1) that connects into the closed-loop path; first cross valve (3); heat recovering heat exchanger (14); outdoor heat exchanger (4); fluid reservoir (9); device for drying and filtering (10), indoor heat exchanger (15), vapour liquid separator (16) and a plurality of magnetic valve, check valve and expansion valve, wherein, between compressor (1) and above-mentioned first cross valve (3), establish second cross valve (2) in addition, an outlet of second cross valve (2) of close compressor connects above-mentioned heat recovering heat exchanger (14), another outlet connects the inlet of first cross valve (3), junction chamber external heat exchanger (4) in turn between two outlets of first cross valve (3), fluid reservoir (9), device for drying and filtering (10), indoor heat exchanger (15); Vapour liquid separator (16) is positioned between first cross valve (3) outlet and compressor (1) inlet; Second cross valve (2), heat recovering heat exchanger (14), fluid reservoir (9), device for drying and filtering (10), indoor heat exchanger (15) and first cross valve (3) are linked to be the closed-loop path, heat recovering heat exchanger (14) one ends are divided into two-way, one the tunnel is connected in fluid reservoir (9), it has magnetic valve (6) between the two, another road is connected outdoor heat exchanger (4) near first cross valve (3) one ends, magnetic valve (7) is arranged between the two, between indoor heat exchanger (15) and fluid reservoir (9), be provided with the check valve (8) in parallel with device for drying and filtering (10); Establish a pipeline in addition between outdoor heat exchanger (4) and indoor heat exchanger (15), this pipeline is provided with an expansion valve (13)." this recuperation of heat air-conditioning unit not only can provide Waste Heat Recovery when operation of air conditioner, and heat the air-conditioning unit of water when can realize not using air-conditioning separately.

Although the heat recovery system that above-mentioned recuperation of heat air-conditioning unit has solved air-conditioning system of the prior art does not have the problem of hot water supply under the situation that air-conditioning does not move.But,, from air, draw thermal source, so single recuperation of heat unit is to carry out air-conditioning heating mode and domestic hot-water's pattern simultaneously because heating with two kinds of mode of operations of domestic hot-water of this recuperation of heat air-conditioning system is to use same heat-exchange system; And owing to only adopt single recuperation of heat unit, the temperature that makes unit produce the domestic hot-water is subjected to the restriction of the performance of air-conditioning system own, domestic hot-water's (for example: 〉=65 ℃) of higher temperature can not be produced, the domestic hot-water's of higher temperature defective can not be produced when existing winter than low ambient temperature; Simultaneously, owing to adopt a plurality of magnetic valves in the air-conditioning system, make that the cost of air-conditioning system is higher.To sum up, above-mentioned reason all makes the use of air-conditioning system be restricted.

Therefore; for fear of deficiency of the prior art; needing badly provides a kind of effective recycling that had both guaranteed heat; protect environment to avoid thermal pollution, environmental protection and energy saving again; and effectively solving air-conditioning heats with the domestic hot-water and produces and can not carry out simultaneously; and can not produce the domestic hot-water's of higher temperature defective during in the winter time than low ambient temperature, simple in structure, lower-cost recovery type heat Air-Cooled Heat Pump Unit simultaneously.

The utility model content

The purpose of this utility model is to avoid weak point of the prior art and a kind of effective recycling that had both guaranteed heat is provided; protect environment to avoid thermal pollution, environmental protection and energy saving again; and effectively solving air-conditioning heats with the domestic hot-water and produces and can not carry out simultaneously; and can not produce the domestic hot-water's of higher temperature defective during in the winter time than low ambient temperature, simple in structure, lower-cost recovery type heat Air-Cooled Heat Pump Unit simultaneously.

The purpose of this utility model is achieved through the following technical solutions:

On the one hand, the utility model provides a kind of recovery type heat Air-Cooled Heat Pump Unit, includes first refrigerant-cycle systems and second refrigerant-cycle systems;

Described first refrigerant-cycle systems includes first compressor, first cross valve, second cross valve, the first air side fins formula heat exchanger, first electric expansion valve, second electric expansion valve, first check valve, second check valve, the 3rd check valve, the 4th check valve, the 5th check valve, air-conditioning side heat exchanger, first reservoir, second reservoir, first gas-liquid separator, full heat recovering heat exchanger, hot-water circulating pump and attemperater; The water inlet of described full heat recovering heat exchanger is connected with the delivery port of described attemperater by described hot-water circulating pump, and the delivery port of described full heat recovering heat exchanger is connected with the water inlet of described attemperater;

When described second cross valve and described first cross valve all during no power, the suction side of the E2 of the D2 of the D1 of the outlet side of described first compressor and described first cross valve, C1 port, described second cross valve, C2 port, the described first air side fins formula heat exchanger, described first check valve, described second electric expansion valve, described second check valve, described air-conditioning side heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor joins successively; When the energising of described second cross valve and during the described first cross valve no power, the suction side of the C2 of the D2 of the D1 of the outlet side of described first compressor and described first cross valve, C1 port, described second cross valve, E2 port, described air-conditioning side heat exchanger, described first reservoir, described the 3rd check valve, described the 4th check valve, described first electric expansion valve, the described first air side fins formula heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor is connected successively; When the energising of described first cross valve and during the described second cross valve no power, the suction side of the E2 of the D1 of the outlet side of described first compressor and described first cross valve, e1 port, described full heat recovering heat exchanger, described second reservoir, described the 5th check valve, described second electric expansion valve, described second check valve, described air-conditioning side heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor is connected successively; When described second cross valve and described first cross valve were all switched on, the suction side of the C2 of the D1 of the outlet side of described first compressor and described first cross valve, e1 port, described full heat recovering heat exchanger, described second reservoir, described the 5th check valve, described first electric expansion valve, the described first air side fins formula heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor was connected successively;

Described second refrigerant-cycle systems includes second compressor, the 3rd cross valve, the 4th cross valve, the second air side fins formula heat exchanger, second throttling arrangement, the 6th check valve, the 7th check valve, the 8th check valve, the 9th check valve, air-conditioning side heat exchanger, the 3rd reservoir, second gas-liquid separator, part heat recovering heat exchanger and attemperater; Described part heat recovering heat exchanger is arranged in the described attemperater;

When described the 3rd cross valve and described the 4th cross valve all during no power, the suction side of the E4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, C3 port, described the 6th check valve, described the 4th cross valve, C4 port, the described second air side fins formula heat exchanger, described second throttling arrangement, described the 7th check valve, described air-conditioning side heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor joins successively; When the energising of described the 4th cross valve and during described the 3rd cross valve no power, the suction side of the C4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, C3 port, described the 6th check valve, described the 4th cross valve, E4 port, described air-conditioning side heat exchanger, described the 3rd reservoir, described the 8th check valve, described second throttling arrangement, the described second air side fins formula heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor is connected successively; When the energising of described the 3rd cross valve and during described the 4th cross valve no power, the suction side of the E4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, E3 port, described part heat recovering heat exchanger, described the 9th check valve, described the 4th cross valve, C4 port, the described second air side fins formula heat exchanger, described second throttling arrangement, described the 7th check valve, described air-conditioning side heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor joins successively; When described the 3rd cross valve and described the 4th cross valve were all switched on, the suction side of the C4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, E3 port, described part heat recovering heat exchanger, described the 9th check valve, described the 4th cross valve, E4 port, described air-conditioning side heat exchanger, described the 3rd reservoir, described the 8th check valve, described second throttling arrangement, the described second air side fins formula heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor was connected successively.

Preferably, described first refrigerant-cycle systems is provided with magnetic valve and first throttle device, and described magnetic valve and described first throttle device are connected in series and are connected in parallel with described the 5th check valve.

Preferably, described first throttle device is capillary, heating power expansion valve or electric expansion valve.

Preferably, described second throttling arrangement is capillary, heating power expansion valve or electric expansion valve.

Preferably, a side of the described first air side fins formula heat exchanger is provided with first blower fan, and a side of the described second air side fins formula heat exchanger is provided with second blower fan.

On the other hand, the utility model also provides a kind of recovery type heat Air-Cooled Heat Pump Unit, includes first refrigerant-cycle systems and second refrigerant-cycle systems;

Described first refrigerant-cycle systems includes first compressor, first cross valve, second cross valve, the first air side fins formula heat exchanger, first electric expansion valve, second electric expansion valve, first check valve, second check valve, the 3rd check valve, the 4th check valve, the 5th check valve, air-conditioning side heat exchanger, first reservoir, second reservoir, first gas-liquid separator, full heat recovering heat exchanger, hot-water circulating pump and attemperater; The water inlet of described full heat recovering heat exchanger is connected with the delivery port of described attemperater by described hot-water circulating pump, and the delivery port of described full heat recovering heat exchanger is connected with the water inlet of described attemperater;

When described second cross valve and described first cross valve all during no power, the suction side of the E2 of the D2 of the D1 of the outlet side of described first compressor and described first cross valve, C1 port, described second cross valve, C2 port, the described first air side fins formula heat exchanger, described first check valve, described second electric expansion valve, described second check valve, described air-conditioning side heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor joins successively; When the energising of described second cross valve and during the described first cross valve no power, the suction side of the C2 of the D2 of the D1 of the outlet side of described first compressor and described first cross valve, C1 port, described second cross valve, E2 port, described air-conditioning side heat exchanger, described first reservoir, described the 3rd check valve, described the 4th check valve, described first electric expansion valve, the described first air side fins formula heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor is connected successively; When the energising of described first cross valve and during the described second cross valve no power, the suction side of the E2 of the D1 of the outlet side of described first compressor and described first cross valve, e1 port, described full heat recovering heat exchanger, described second reservoir, described the 5th check valve, described second electric expansion valve, described second check valve, described air-conditioning side heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor is connected successively; When described second cross valve and described first cross valve were all switched on, the suction side of the C2 of the D1 of the outlet side of described first compressor and described first cross valve, e1 port, described full heat recovering heat exchanger, described second reservoir, described the 5th check valve, described first electric expansion valve, the described first air side fins formula heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor was connected successively;

Described second refrigerant-cycle systems includes second compressor, the 3rd cross valve, the 4th cross valve, the second air side fins formula heat exchanger, second throttling arrangement, the 6th check valve, the 7th check valve, the 8th check valve, the 9th check valve, air-conditioning side heat exchanger, the 3rd reservoir, second gas-liquid separator, part heat recovering heat exchanger and attemperater; The delivery port of described part heat recovering heat exchanger is connected with the water inlet of described attemperater, and the water inlet of described part heat recovering heat exchanger is connected with the delivery port of described full heat recovering heat exchanger;

When described the 3rd cross valve and described the 4th cross valve all during no power, the suction side of the E4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, C3 port, described the 6th check valve, described the 4th cross valve, C4 port, the described second air side fins formula heat exchanger, described second throttling arrangement, described the 7th check valve, described air-conditioning side heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor joins successively; When the energising of described the 4th cross valve and during described the 3rd cross valve no power, the suction side of the C4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, C3 port, described the 6th check valve, described the 4th cross valve, E4 port, described air-conditioning side heat exchanger, described the 3rd reservoir, described the 8th check valve, described second throttling arrangement, the described second air side fins formula heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor is connected successively; When the energising of described the 3rd cross valve and during described the 4th cross valve no power, the suction side of the E4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, E3 port, described part heat recovering heat exchanger, described the 9th check valve, described the 4th cross valve, C4 port, the described second air side fins formula heat exchanger, described second throttling arrangement, described the 7th check valve, described air-conditioning side heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor joins successively; When described the 3rd cross valve and described the 4th cross valve were all switched on, the suction side of the C4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, E3 port, described part heat recovering heat exchanger, described the 9th check valve, described the 4th cross valve, E4 port, described air-conditioning side heat exchanger, described the 3rd reservoir, described the 8th check valve, described second throttling arrangement, the described second air side fins formula heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor was connected successively.

Preferably, described first refrigerant-cycle systems is provided with magnetic valve and first throttle device, and described magnetic valve and described first throttle device are connected in series and are connected in parallel with described the 5th check valve.

Preferably, described first throttle device is capillary, heating power expansion valve or electric expansion valve.

Preferably, described second throttling arrangement is capillary, heating power expansion valve or electric expansion valve.

Preferably, a side of the described first air side fins formula heat exchanger is provided with first blower fan, and a side of the described second air side fins formula heat exchanger is provided with second blower fan.

The beneficial effects of the utility model: this recovery type heat Air-Cooled Heat Pump Unit, include first refrigerant-cycle systems and second refrigerant-cycle systems, wherein, adopt full heat recovering heat exchanger in first refrigerant-cycle systems, adopt the part heat recovering heat exchanger in second refrigerant-cycle systems, this by adopting two refrigerant-cycle systems, four cross valves, the mode of a plurality of electric expansion valves and a plurality of check valves, realized the switching of pipeline in the refrigerant system, and the function of compressor twin-stage adjusting, not only make cold-producing medium have multiple circulation style, and make air-conditioning system under the situation of operation and use hot water, realized the recovery of the whole condensation heat of first refrigerant-cycle systems or the second refrigerant-cycle systems partial condensation heat, guaranteed the recycling of heat, improve the thermal efficiency, also strengthened the hot water deliverability of air-conditioning system simultaneously.Meanwhile, can be implemented in the air source water heater pattern by control to two cross valves in first refrigerant-cycle systems, two electric expansion valves and a plurality of check valves, solve the function that the domestic hot-water is provided under the state that transition season do not use air-conditioning, can guarantee real-time domestic hot-water's supply, solved portion of hot of the prior art and reclaimed air-conditioning system, do not had the problem of domestic hot-water supply at transition season; Can be implemented on the basis of first refrigerant-cycle systems with domestic hot-water's temperature increase by control two cross valves in second refrigerant-cycle systems and two check valves, further with domestic hot-water's temperature increase, make domestic hot-water's temperature to reach 〉=65 ℃, simultaneously the mode of the condensation heat that can heat by shunting solves the full recuperation of heat air-conditioning system that only has single heat recovery system in the prior art, need assisted heating device to promote the defective of domestic hot-water's temperature in the winter time under the low ambient temperature, and the control by computer can realize the function that automatically adjusts under the conditions of demand according to air-conditioning and hot water fully; And the utility model is because the structure that adopts the mode of electric expansion valve, check valve to avoid a plurality of magnetic valves of available technology adopting to control has reduced production cost on the whole.The utility model is by coordinating control to two refrigerant-cycle systems, in the more efficient use condensation heat, make producing of domestic hot-water reach the higher temperature and the temperature of accurate control attemperater, realize the energy recovery is used the purpose of energy savings again; And can realize producing when air-conditioning heats with the domestic hot-water; Further solve the full recuperation of heat air-conditioning system of single heat recovery system of the prior art, can not produce the domestic hot-water's of higher temperature problem during in the winter time than low ambient temperature.In addition, the utility model can have additional magnetic valve and throttling arrangement in first refrigerant-cycle systems, with magnetic valve and throttling arrangement is connected in series and with the mode that the 5th check valve is connected in parallel, can realize that domestic hot-water's pattern Defrost operation pattern of removing air-conditioning heating mode Defrost operation pattern can select for the user.This structure had both guaranteed effective recycling of heat, protected environment to avoid thermal pollution, environmental protection and energy saving again, and have refrigeration, heat, domestic hot-water's Trinity function in real time.

Description of drawings

Utilize accompanying drawing that utility model is described further, but the embodiment in the accompanying drawing does not constitute any restriction of the present utility model, for those of ordinary skill in the art, under the prerequisite of not paying creative work, can also obtain other accompanying drawing according to the following drawings.

Fig. 1 is the structural representation of the embodiment 1 of a kind of recovery type heat Air-Cooled Heat Pump Unit of the present utility model.

Fig. 2 is embodiment 2 structural representations of a kind of recovery type heat Air-Cooled Heat Pump Unit of the present utility model.

Fig. 3 is the structural representation of the embodiment 3 of a kind of recovery type heat Air-Cooled Heat Pump Unit of the present utility model.

Fig. 4 is the structural representation of the embodiment 4 of a kind of recovery type heat Air-Cooled Heat Pump Unit of the present utility model.

At Fig. 1, Fig. 2, comprise among Fig. 3 and Fig. 4: 100---first refrigerant-cycle systems, 200---second refrigerant-cycle systems, 1---first compressor, 2---first cross valve, 3---the first air side fins formula heat exchanger, 4---second cross valve, 5---first electric expansion valve, 6---first check valve, 7---magnetic valve, 8---the 5th check valve, 9---the first throttle device, 10---second electric expansion valve, 11---the 4th check valve, 12---the 3rd check valve, 13---first reservoir, 14---second check valve, 15---air-conditioning side heat exchanger, 16---the 7th check valve, 17---the 8th check valve, 18---the 3rd reservoir, 19---second throttling arrangement, 20---the 4th cross valve, 21---the second air side fins formula heat exchanger, 22---the 6th check valve, 23---the 3rd cross valve, 24---second compressor, 25---second gas-liquid separator, 26---the 9th check valve, 27---the part heat recovering heat exchanger, 28---attemperater, 29---hot-water circulating pump, 30---full heat recovering heat exchanger, 31---second reservoir, 32---first gas-liquid separator.

The specific embodiment

With the following Examples the utility model is further described.

Embodiment 1

One of specific embodiment of a kind of recovery type heat Air-Cooled Heat Pump Unit of the present utility model as shown in Figure 1, includes first refrigerant-cycle systems 100 and second refrigerant-cycle systems 200.First refrigerant-cycle systems 100 and second refrigerant-cycle systems, 200 shared same air-conditioning side heat exchanger 15 and attemperaters 28.Wherein, adopt full heat recovering heat exchanger 30 in first refrigerant-cycle systems 100, adopt part heat recovering heat exchanger 27 in second refrigerant-cycle systems 200, the utility model is by coordinating control to two refrigerant-cycle systems, in the more efficient use condensation heat, make producing of domestic hot-water reach the higher temperature and the temperature of accurate control attemperater 28, realize the energy recovery is used the purpose of energy savings again; And can realize producing when air-conditioning heats with the domestic hot-water; Further solve the full recuperation of heat air-conditioning system of single heat recovery system of the prior art, can not produce the domestic hot-water's of higher temperature problem during in the winter time than low ambient temperature.This structure had both guaranteed effective recycling of heat, protected environment to avoid thermal pollution, environmental protection and energy saving again, and have refrigeration, heat, domestic hot-water's Trinity function in real time.

Concrete, first refrigerant-cycle systems 100 includes first compressor 1, first cross valve 2, second cross valve 4, the first air side fins formula heat exchanger 3, first electric expansion valve 5, second electric expansion valve 10, first check valve 6, second check valve 14, the 3rd check valve 12, the 4th check valve 11, the 5th check valve 8, air-conditioning side heat exchanger 15, first reservoir 13, second reservoir 31, first gas-liquid separator 32, full heat recovering heat exchanger 30, hot-water circulating pump 29 and attemperater 28; The water inlet of full heat recovering heat exchanger 30 is connected by the delivery port of hot-water circulating pump 29 with attemperater 28, and the delivery port of full heat recovering heat exchanger 30 is connected with the water inlet of attemperater 28.

When second cross valve 4 and first cross valve 2 all during no power, the suction side of the E2 of the D2 of the D1 of the outlet side of first compressor 1 and first cross valve 2, C1 port, second cross valve 4, C2 port, the first air side fins formula heat exchanger 3, first check valve 6, second electric expansion valve 10, second check valve 14, air-conditioning side heat exchanger 15, second cross valve 4, S2 port, first gas-liquid separator 32, first compressor 1 joins successively.

When the energising of second cross valve 4 and during first cross valve, 2 no powers, the suction side of the C2 of the D2 of the D1 of the outlet side of first compressor 1 and first cross valve 2, C1 port, second cross valve 4, E2 port, air-conditioning side heat exchanger 15, first reservoir 13, the 3rd check valve 12, the 4th check valve 11, first electric expansion valve 5, the first air side fins formula heat exchanger 3, second cross valve 4, S2 port, first gas-liquid separator 32, first compressor 1 is connected successively.

When the energising of first cross valve 2 and during second cross valve, 4 no powers, the D1 of the outlet side of first compressor 1 and first cross valve 2, e1 port, E2, S2 port, first gas-liquid separator 32, the suction side of first compressor 1 of heat recovering heat exchanger 30, second reservoir 31, the 5th check valve 8, second electric expansion valve 10, second check valve 14, air-conditioning side heat exchanger 15, second cross valve 4 are connected successively entirely.

When second cross valve 4 and first cross valve 2 were all switched on, the suction side of the C2 of the D1 of the outlet side of first compressor 1 and first cross valve 2, e1 port, full heat recovering heat exchanger 30, second reservoir 31, the 5th check valve 8, first electric expansion valve 5, the first air side fins formula heat exchanger 3, second cross valve 4, S2 port, first gas-liquid separator 32, first compressor 1 was connected successively.

Concrete, second refrigerant-cycle systems 200 includes second compressor 24, the 3rd cross valve 23, the 4th cross valve 20, the second air side fins formula heat exchanger 21, second throttling arrangement 19, the 6th check valve 22, the 7th check valve 16, the 8th check valve 17, the 9th check valve 26, air-conditioning side heat exchanger 15, the 3rd reservoir 18, second gas-liquid separator 25, part heat recovering heat exchanger 27 and attemperater 28; Part heat recovering heat exchanger 27 is arranged in the attemperater 28.

When the 3rd cross valve 23 and the 4th cross valve 20 all during no power, the suction side of the E4 of the D4 of the D3 of the outlet side of second compressor 24 and the 3rd cross valve 23, C3 port, the 6th check valve 22, the 4th cross valve 20, C4 port, the second air side fins formula heat exchanger 21, second throttling arrangement 19, the 7th check valve 16, air-conditioning side heat exchanger 15, the 4th cross valve 20, S4 port, second gas-liquid separator 25, second compressor 24 joins successively.

When the energising of the 4th cross valve 20 and during the 3rd cross valve 23 no powers, the suction side of the C4 of the D4 of the D3 of the outlet side of second compressor 24 and the 3rd cross valve 23, C3 port, the 6th check valve 22, the 4th cross valve 20, E4 port, air-conditioning side heat exchanger 15, the 3rd reservoir 18, the 8th check valve 17, second throttling arrangement 19, the second air side fins formula heat exchanger 21, the 4th cross valve 20, S4 port, second gas-liquid separator 25, second compressor 24 is connected successively.

When the energising of the 3rd cross valve 23 and during the 4th cross valve 20 no powers, the suction side of the E4 of the D4 of the D3 of the outlet side of second compressor 24 and the 3rd cross valve 23, E3 port, part heat recovering heat exchanger 27, the 9th check valve 26, the 4th cross valve 20, C4 port, the second air side fins formula heat exchanger 21, second throttling arrangement 19, the 7th check valve 16, air-conditioning side heat exchanger 15, the 4th cross valve 20, S4 port, second gas-liquid separator 25, second compressor 24 joins successively.

When the 3rd cross valve 23 and the 4th cross valve 20 were all switched on, the suction side of the C4 of the D4 of the D3 of the outlet side of second compressor 24 and the 3rd cross valve 23, E3 port, part heat recovering heat exchanger 27, the 9th check valve 26, the 4th cross valve 20, E4 port, air-conditioning side heat exchanger 15, the 3rd reservoir 18, the 8th check valve 17, second throttling arrangement 19, the second air side fins formula heat exchanger 21, the 4th cross valve 20, S4 port, second gas-liquid separator 25, second compressor 24 was connected successively.

Concrete, second throttling arrangement 19 is capillary, heating power expansion valve or electric expansion valve.

Concrete, a side of the first air side fins formula heat exchanger 3 is provided with first blower fan.

Concrete, a side of the second air side fins formula heat exchanger 21 is provided with second blower fan.

Recovery type heat Air-Cooled Heat Pump Unit of the present utility model has four kinds of operational modes: air conditioner refrigerating pattern, air-conditioning heating mode, air conditioner refrigerating and heat recovery mode and domestic hot-water's pattern.

During the air conditioner refrigerating mode operation, open first refrigerant-cycle systems 100 and second refrigerant-cycle systems 200 simultaneously.The refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2, then through second cross valve 4 (this moment first cross valve 2 and second cross valve 4 all no power), flow to the first air side fins formula heat exchanger 3 again, carry out heat exchange with outdoor air, simultaneously, first blower fan of the first air side fins formula heat exchanger 3 is opened, make cold-producing medium in the first air side fins formula heat exchanger 3, be condensed in the liquid of warm high pressure, again through first check valve 6, second electric expansion valve 10 becomes the liquid of low-temp low-pressure, again through second check valve 14, enter air-conditioning side heat exchanger 15, carry out heat exchange with air conditioner water, and air conditioner water become the temperature of setting, the liquid of low-temp low-pressure flashes to the gas of low-temp low-pressure simultaneously, flows to second cross valve 4, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish whole kind of refrigeration cycle; The refrigerant vapour of the low-temp low-pressure of second refrigerant-cycle systems 200 is compressed into the superheated vapor of HTHP through second compressor 24, flow to the 3rd cross valve 23, through the 6th check valve 22, flow to the 4th cross valve 20 (this moment the 3rd cross valve 23 and the 4th cross valve 20 all no power) then, flow to the second air side fins formula heat exchanger 21 again, carry out heat exchange with outdoor air, simultaneously, second blower fan of the second air side fins formula heat exchanger 21 is opened, make cold-producing medium in the second air side fins formula heat exchanger 21, be condensed in the liquid of warm high pressure, become the liquid of low-temp low-pressure again through second throttling arrangement 19, again through the 7th check valve 16, enter air-conditioning side heat exchanger 15, carry out heat exchange, and air conditioner water is become the temperature of setting with air conditioner water, the liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to the 4th cross valve 20, flow back to second compressor 24 through second gas-liquid separator 25 at last, finish whole kind of refrigeration cycle.To the refrigerating capacity demand when little, can by unloading running time the output of long system held air conditioner load reach the purpose of energy savings.

During the operation of air-conditioning heating mode, open first refrigerant-cycle systems 100 and second refrigerant-cycle systems 200 simultaneously.The refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2, then through (second cross valve, 4 energisings this moment of second cross valve 4, first cross valve, 2 no powers), flow to air-conditioning side heat exchanger 15 again, carry out heat exchange with air conditioner water, and air conditioner water is heated into the temperature of setting, the liquid of warm high pressure during cold-producing medium is condensed in air-conditioning side heat exchanger 15, again respectively successively through first reservoir 13, the 3rd check valve 12, the 4th check valve 11, first electric expansion valve 5 becomes the liquid of low-temp low-pressure, enter the first air side fins formula heat exchanger 3, carry out heat exchange with air, the liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to second cross valve 4, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish the whole circulation that heats.The refrigerant vapour of the low-temp low-pressure of second refrigerant-cycle systems 200 is compressed into the superheated vapor of HTHP through second compressor 24, flow to the 3rd cross valve 23, through the 6th check valve 22, flowing through then, the 4th cross valve 20 (this moment the 4th, switched on by cross valve 20, the 3rd cross valve 23 no powers), flow to air-conditioning side heat exchanger 15 again, carry out heat exchange with air conditioner water, and air conditioner water is heated into the temperature of setting with first refrigerant-cycle systems 100, the liquid of warm high pressure during cold-producing medium is condensed in air-conditioning side heat exchanger 15, again respectively successively through the 3rd reservoir 18, the 8th check valve 17, second throttling arrangement 19 becomes the liquid of low-temp low-pressure, enter the 4th air side fins formula heat exchanger, carry out heat exchange with air, the liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to the 4th cross valve 20, flow back to second compressor 24 through second gas-liquid separator 25 at last, finish the whole circulation that heats.To the heating capacity demand when little, can by unloading running time the output of long system held air conditioner load reach the purpose of energy savings.

When air conditioner refrigerating and heat recovery mode operation, open first refrigerant-cycle systems 100 and second refrigerant-cycle systems 200 simultaneously.The refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2 (first cross valve, 2 energisings this moment, second cross valve, 4 no powers), flow to full heat recovering heat exchanger 30 again, carry out heat exchange with the domestic water of attemperater 28, and domestic water heated, the liquid of warm high pressure during cold-producing medium is condensed in full heat recovering heat exchanger 30, again respectively successively through second reservoir 31, the 5th check valve 8, second electric expansion valve 10 becomes the liquid of low-temp low-pressure, through second check valve 14, enter air-conditioning side heat exchanger 15, carry out heat exchange with air conditioner water, and air conditioner water is become the temperature of setting, the refrigerant liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to second cross valve 4, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish whole refrigeration and recuperation of heat circulation, domestic water is heated to releases this pattern under the temperature of first compressor, 1 safe operation and transfer the air conditioner refrigerating pattern to.The refrigerant vapour of the low-temp low-pressure of second refrigerant-cycle systems 200 is compressed into the superheated vapor of HTHP through second compressor 24, flow to the 3rd cross valve 23 (the 3rd cross valve 23 energisings this moment the 4th cross valve 20 no powers), flow to part heat recovering heat exchanger 27 again, carry out heat exchange with the domestic water of attemperater 28, and domestic water heated, again respectively successively through the 9th check valve 26, the 4th cross valve 20, the second air side fins formula heat exchanger 21, carry out heat exchange with outdoor air, second blower fan of the second air side fins formula heat exchanger 21 is opened, make cold-producing medium in the second air side fins formula heat exchanger 21, be condensed in the liquid of warm high pressure, become the liquid of low-temp low-pressure through second throttling arrangement 19, through the 7th check valve 16, enter air-conditioning side heat exchanger 15, carry out heat exchange with air conditioner water, and air conditioner water is become the temperature of setting, the refrigerant liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to the 4th cross valve 20, flow back to second compressor 24 through second gas-liquid separator 25 at last, finish whole refrigeration and recuperation of heat circulation, release this pattern when the domestic water heating is provided with temperature and transfer the air conditioner refrigerating pattern to.But the controller by unit is to the operation of air-conditioning and hot water load's calculating Based Intelligent Control unit.

During domestic hot-water's mode operation, open first refrigerant-cycle systems 100, the refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2 (this moment, first cross valve 2 and second cross valve 4 were all switched on), flow to full heat recovering heat exchanger 30 again, carry out heat exchange with the domestic water of attemperater 28, and domestic water heated, the liquid of warm high pressure during cold-producing medium is condensed in full heat recovering heat exchanger 30, again respectively successively through second reservoir 31, the 5th check valve 8, first electric expansion valve 5 becomes the liquid of low-temp low-pressure, enter the first air side fins formula heat exchanger 3 then, carry out heat exchange with outdoor air, the liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to second cross valve 4, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish whole domestic hot-water's circulation.

The user can be according to the different operational mode of selecting air-conditioning system different seasons, such as: when the summer, when the existing air-conditioning demand of user has the hot water demand again, can move air conditioner refrigerating and recuperation of heat operational mode, can between air conditioner refrigerating pattern, air conditioner refrigerating and heat recovery mode and domestic hot-water's pattern, carry out intelligent operation according to the air-conditioner temperature of setting and the demand of domestic hot-water's temperature by microcomputer controller, thereby realize the effect of energy savings.During winter, the user can adopt air-conditioning to heat and domestic hot-water's automatic mode, switches by microcomputer controller intelligence between air-conditioning heating mode and domestic hot-water's pattern, moves at times, satisfies the demand of air-conditioning and hot water.

The full recovery type heat wind-cooling type heat pump unit of present embodiment has a kind of Defrost operation pattern: air-conditioning heating mode Defrost operation pattern.

During air-conditioning heating mode Defrost operation, open first refrigerant-cycle systems 100 or second refrigerant-cycle systems 200.The refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2, then through second cross valve 4 (this moment first cross valve 2 and second cross valve 4 all no power), flow to the first air side fins formula heat exchanger 3 again, carry out heat exchange with outdoor air, simultaneously, first blower fan of the first air side fins formula heat exchanger 3 is not opened, make cold-producing medium in the first air side fins formula heat exchanger 3, be condensed in the liquid of warm high pressure, again through first check valve 6, second electric expansion valve 10 becomes the liquid of low-temp low-pressure, again through second check valve 14, enter air-conditioning side heat exchanger 15, carry out heat exchange with air conditioner water, and air conditioner water become the temperature of setting, the liquid of low-temp low-pressure flashes to the gas of low-temp low-pressure simultaneously, flows to second cross valve 4, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish the cold-producing medium circulation of whole air-conditioning heating mode Defrost operation; The refrigerant vapour of the low-temp low-pressure of second refrigerant-cycle systems 200 is compressed into the superheated vapor of HTHP through second compressor 24, flow to the 3rd cross valve 23, through the 6th check valve 22, flow to the 4th cross valve 20 (this moment the 3rd cross valve 23 and the 4th cross valve 20 all no power) then, flow to the second air side fins formula heat exchanger 21 again, carry out heat exchange with outdoor air, simultaneously, second blower fan of the second air side fins formula heat exchanger 21 is not opened, make cold-producing medium in the second air side fins formula heat exchanger 21, be condensed in the liquid of warm high pressure, become the liquid of low-temp low-pressure again through second throttling arrangement 19, again through the 7th check valve 16, enter air-conditioning side heat exchanger 15, carry out heat exchange, and air conditioner water is become the temperature of setting with air conditioner water, the liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to the 4th cross valve 20, flow back to second compressor 24 through second gas-liquid separator 25 at last, finish the cold-producing medium circulation of whole air-conditioning heating mode Defrost operation.

Embodiment 2

Two of the specific embodiment of a kind of recovery type heat Air-Cooled Heat Pump Unit of the present utility model, as shown in Figure 2, the main technical schemes of present embodiment is identical with embodiment 1, unaccounted in the present embodiment feature, adopt the explanation among the embodiment 1, no longer give unnecessary details at this, and the parts identical with Fig. 1 adopt identical label in Fig. 2.The difference of present embodiment and embodiment 1 is, the part heat recovering heat exchanger 27 in second refrigerant-cycle systems 200 is positioned over the outside of attemperater 28.

Concrete, second refrigerant-cycle systems 200 includes second compressor 24, the 3rd cross valve 23, the 4th cross valve 20, the second air side fins formula heat exchanger 21, second throttling arrangement 19, the 6th check valve 22, the 7th check valve 16, the 8th check valve 17, the 9th check valve 26, air-conditioning side heat exchanger 15, the 3rd reservoir 18, second gas-liquid separator 25, part heat recovering heat exchanger 27 and attemperater 28; The delivery port of part heat recovering heat exchanger 27 is connected with the water inlet of attemperater 28, and the water inlet of part heat recovering heat exchanger 27 is connected with the delivery port of full heat recovering heat exchanger 30.

Embodiment 3

Three of the specific embodiment of a kind of recovery type heat Air-Cooled Heat Pump Unit of the present utility model, as shown in Figure 3, the main technical schemes of present embodiment is identical with embodiment 1, unaccounted in the present embodiment feature, adopt the explanation among the embodiment 1, no longer give unnecessary details at this, and the parts identical with Fig. 1 adopt identical label in Fig. 3.The difference of present embodiment and embodiment 1 is that first refrigerant-cycle systems 100 is provided with magnetic valve 7 and first throttle device 9, with magnetic valve 7 with first throttle device 9 is connected in series and be connected in parallel with the 5th check valve 8.Set up magnetic valve 7 and throttling arrangement 9 and can realize that domestic hot-water's pattern Defrost operation pattern of removing air-conditioning heating mode Defrost operation can supply the user to select.

Concrete, first throttle device 9 is capillary, heating power expansion valve or electric expansion valve.

The full recovery type heat wind-cooling type heat pump unit of present embodiment has two kinds of Defrost operation patterns: air-conditioning heating mode Defrost operation pattern and domestic hot-water's pattern Defrost operation.

During air-conditioning heating mode Defrost operation, open first refrigerant-cycle systems 100 or second refrigerant-cycle systems 200.The refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2, then through second cross valve 4 (this moment first cross valve 2 and second cross valve 4 all no power), flow to the first air side fins formula heat exchanger 3 again, carry out heat exchange with outdoor air, simultaneously, first blower fan of the first air side fins formula heat exchanger 3 is not opened, make cold-producing medium in the first air side fins formula heat exchanger 3, be condensed in the liquid of warm high pressure, again through first check valve 6, second electric expansion valve 10 becomes the liquid of low-temp low-pressure, again through second check valve 14, enter air-conditioning side heat exchanger 15, carry out heat exchange with air conditioner water, and air conditioner water become the temperature of setting, the liquid of low-temp low-pressure flashes to the gas of low-temp low-pressure simultaneously, flows to second cross valve 4, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish the cold-producing medium circulation of whole air-conditioning heating mode Defrost operation; The refrigerant vapour of the low-temp low-pressure of second refrigerant-cycle systems 200 is compressed into the superheated vapor of HTHP through second compressor 24, flow to the 3rd cross valve 23, through the 6th check valve 22, flow to the 4th cross valve 20 (this moment the 3rd cross valve 23 and the 4th cross valve 20 all no power) then, flow to the second air side fins formula heat exchanger 21 again, carry out heat exchange with outdoor air, simultaneously, second blower fan of the second air side fins formula heat exchanger 21 is not opened, make cold-producing medium in the second air side fins formula heat exchanger 21, be condensed in the liquid of warm high pressure, become the liquid of low-temp low-pressure again through second throttling arrangement 19, again through the 7th check valve 16, enter air-conditioning side heat exchanger 15, carry out heat exchange, and air conditioner water is become the temperature of setting with air conditioner water, the liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to the 4th cross valve 20, flow back to second compressor 24 through second gas-liquid separator 25 at last, finish the cold-producing medium circulation of whole air-conditioning heating mode Defrost operation.

During domestic hot-water's pattern Defrost operation, the refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2, then through second cross valve 4 (this moment first cross valve 2 and second cross valve 4 all no power), flow to the first air side fins formula heat exchanger 3 again, carry out heat exchange with outdoor air, simultaneously, first blower fan of the first air side fins formula heat exchanger 3 is not opened, make cold-producing medium in the first air side fins formula heat exchanger 3, be condensed in the liquid of warm high pressure, through first check valve 6, pass through magnetic valve 7 again, first throttle device 9 becomes the liquid of low-temp low-pressure, again through second reservoir 31, enter the full heat regenerator 30 of domestic hot-water's side, carry out heat exchange with the domestic hot-water, the liquid of low-temp low-pressure flashes to the gas of low-temp low-pressure simultaneously, flow to first cross valve 2, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish the cold-producing medium circulation of whole domestic hot-water's pattern Defrost operation.

Embodiment 4

Four of the specific embodiment of a kind of recovery type heat Air-Cooled Heat Pump Unit of the present utility model, as shown in Figure 4, the main technical schemes of present embodiment is identical with embodiment 2, unaccounted in the present embodiment feature, adopt the explanation among the embodiment 2, no longer give unnecessary details at this, and the parts identical with Fig. 2 adopt identical label in Fig. 4.The difference of present embodiment and embodiment 2 is that first refrigerant-cycle systems 100 is provided with magnetic valve 7 and first throttle device 9, with magnetic valve 7 with first throttle device 9 is connected in series and be connected in parallel with the 5th check valve 8.Set up magnetic valve 7 and throttling arrangement 9 and can realize that domestic hot-water's pattern Defrost operation pattern of removing air-conditioning heating mode Defrost operation can supply the user to select.

Concrete, second throttling arrangement 19 is capillary, heating power expansion valve or electric expansion valve.

The full recovery type heat wind-cooling type heat pump unit of present embodiment has two kinds of Defrost operation patterns: air-conditioning heating mode Defrost operation pattern and domestic hot-water's pattern Defrost operation.

During air-conditioning heating mode Defrost operation, open first refrigerant-cycle systems 100 or second refrigerant-cycle systems 200.The refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2, then through second cross valve 4 (this moment first cross valve 2 and second cross valve 4 all no power), flow to the first air side fins formula heat exchanger 3 again, carry out heat exchange with outdoor air, simultaneously, first blower fan of the first air side fins formula heat exchanger 3 is not opened, make cold-producing medium in the first air side fins formula heat exchanger 3, be condensed in the liquid of warm high pressure, again through first check valve 6, second electric expansion valve 10 becomes the liquid of low-temp low-pressure, again through second check valve 14, enter air-conditioning side heat exchanger 15, carry out heat exchange with air conditioner water, and air conditioner water become the temperature of setting, the liquid of low-temp low-pressure flashes to the gas of low-temp low-pressure simultaneously, flows to second cross valve 4, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish the cold-producing medium circulation of whole air-conditioning heating mode Defrost operation; The refrigerant vapour of the low-temp low-pressure of second refrigerant-cycle systems 200 is compressed into the superheated vapor of HTHP through second compressor 24, flow to the 3rd cross valve 23, through the 6th check valve 22, flow to the 4th cross valve 20 (this moment the 3rd cross valve 23 and the 4th cross valve 20 all no power) then, flow to the second air side fins formula heat exchanger 21 again, carry out heat exchange with outdoor air, simultaneously, second blower fan of the second air side fins formula heat exchanger 21 is not opened, make cold-producing medium in the second air side fins formula heat exchanger 21, be condensed in the liquid of warm high pressure, become the liquid of low-temp low-pressure again through second throttling arrangement 19, again through the 7th check valve 16, enter air-conditioning side heat exchanger 15, carry out heat exchange, and air conditioner water is become the temperature of setting with air conditioner water, the liquid of low-temp low-pressure flashes to low-temp low-pressure gas simultaneously, flow to the 4th cross valve 20, flow back to second compressor 24 through second gas-liquid separator 25 at last, finish the cold-producing medium circulation of whole air-conditioning heating mode Defrost operation.

During domestic hot-water's pattern Defrost operation, the refrigerant vapour of the low-temp low-pressure of first refrigerant-cycle systems 100 is compressed into the superheated vapor of HTHP through first compressor 1, flow to first cross valve 2, then through second cross valve 4 (this moment first cross valve 2 and second cross valve 4 all no power), flow to the first air side fins formula heat exchanger 3 again, carry out heat exchange with outdoor air, simultaneously, first blower fan of the first air side fins formula heat exchanger 3 is not opened, make cold-producing medium in the first air side fins formula heat exchanger 3, be condensed in the liquid of warm high pressure, through first check valve 6, pass through magnetic valve 7 again, first throttle device 9 becomes the liquid of low-temp low-pressure, again through second reservoir 31, enter the full heat regenerator 30 of domestic hot-water's side, carry out heat exchange with the domestic hot-water, the liquid of low-temp low-pressure flashes to the gas of low-temp low-pressure simultaneously, flow to first cross valve 2, flow back to first compressor 1 through first gas-liquid separator 32 at last, finish the cold-producing medium circulation of whole domestic hot-water's pattern Defrost operation.

Should be noted that at last; above embodiment is only in order to the explanation the technical solution of the utility model; but not to the restriction of the utility model protection domain; although the utility model has been done to explain with reference to preferred embodiment; those of ordinary skill in the art is to be understood that; can make amendment or be equal to replacement the technical solution of the utility model, and not break away from the essence and the scope of technical solutions of the utility model.

Claims (10)

1. a recovery type heat Air-Cooled Heat Pump Unit is characterized in that: include first refrigerant-cycle systems and second refrigerant-cycle systems;
Described first refrigerant-cycle systems includes first compressor, first cross valve, second cross valve, the first air side fins formula heat exchanger, first electric expansion valve, second electric expansion valve, first check valve, second check valve, the 3rd check valve, the 4th check valve, the 5th check valve, air-conditioning side heat exchanger, first reservoir, second reservoir, first gas-liquid separator, full heat recovering heat exchanger, hot-water circulating pump and attemperater; The water inlet of described full heat recovering heat exchanger is connected with the delivery port of described attemperater by described hot-water circulating pump, and the delivery port of described full heat recovering heat exchanger is connected with the water inlet of described attemperater;
When described second cross valve and described first cross valve all during no power, the suction side of the E2 of the D2 of the D1 of the outlet side of described first compressor and described first cross valve, C1 port, described second cross valve, C2 port, the described first air side fins formula heat exchanger, described first check valve, described second electric expansion valve, described second check valve, described air-conditioning side heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor joins successively; When the energising of described second cross valve and during the described first cross valve no power, the suction side of the C2 of the D2 of the D1 of the outlet side of described first compressor and described first cross valve, C1 port, described second cross valve, E2 port, described air-conditioning side heat exchanger, described first reservoir, described the 3rd check valve, described the 4th check valve, described first electric expansion valve, the described first air side fins formula heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor is connected successively; When the energising of described first cross valve and during the described second cross valve no power, the suction side of the E2 of the D1 of the outlet side of described first compressor and described first cross valve, e1 port, described full heat recovering heat exchanger, described second reservoir, described the 5th check valve, described second electric expansion valve, described second check valve, described air-conditioning side heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor is connected successively; When described second cross valve and described first cross valve were all switched on, the suction side of the C2 of the D1 of the outlet side of described first compressor and described first cross valve, e1 port, described full heat recovering heat exchanger, described second reservoir, described the 5th check valve, described first electric expansion valve, the described first air side fins formula heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor was connected successively;
Described second refrigerant-cycle systems includes second compressor, the 3rd cross valve, the 4th cross valve, the second air side fins formula heat exchanger, second throttling arrangement, the 6th check valve, the 7th check valve, the 8th check valve, the 9th check valve, air-conditioning side heat exchanger, the 3rd reservoir, second gas-liquid separator, part heat recovering heat exchanger and attemperater; Described part heat recovering heat exchanger is arranged in the described attemperater;
When described the 3rd cross valve and described the 4th cross valve all during no power, the suction side of the E4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, C3 port, described the 6th check valve, described the 4th cross valve, C4 port, the described second air side fins formula heat exchanger, described second throttling arrangement, described the 7th check valve, described air-conditioning side heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor joins successively; When the energising of described the 4th cross valve and during described the 3rd cross valve no power, the suction side of the C4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, C3 port, described the 6th check valve, described the 4th cross valve, E4 port, described air-conditioning side heat exchanger, described the 3rd reservoir, described the 8th check valve, described second throttling arrangement, the described second air side fins formula heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor is connected successively; When the energising of described the 3rd cross valve and during described the 4th cross valve no power, the suction side of the E4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, E3 port, described part heat recovering heat exchanger, described the 9th check valve, described the 4th cross valve, C4 port, the described second air side fins formula heat exchanger, described second throttling arrangement, described the 7th check valve, described air-conditioning side heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor joins successively; When described the 3rd cross valve and described the 4th cross valve were all switched on, the suction side of the C4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, E3 port, described part heat recovering heat exchanger, described the 9th check valve, described the 4th cross valve, E4 port, described air-conditioning side heat exchanger, described the 3rd reservoir, described the 8th check valve, described second throttling arrangement, the described second air side fins formula heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor was connected successively.
2. recovery type heat Air-Cooled Heat Pump Unit according to claim 1, it is characterized in that: described first refrigerant-cycle systems is provided with magnetic valve and first throttle device, and described magnetic valve and described first throttle device are connected in series and are connected in parallel with described the 5th check valve.
3. recovery type heat Air-Cooled Heat Pump Unit according to claim 2 is characterized in that: described first throttle device is capillary, heating power expansion valve or electric expansion valve.
4. according to claim 1 or 2 or 3 described recovery type heat Air-Cooled Heat Pump Unit, it is characterized in that: described second throttling arrangement is capillary, heating power expansion valve or electric expansion valve.
5. recovery type heat Air-Cooled Heat Pump Unit according to claim 1 is characterized in that: a side of the described first air side fins formula heat exchanger is provided with first blower fan, and a side of the described second air side fins formula heat exchanger is provided with second blower fan.
6. a recovery type heat Air-Cooled Heat Pump Unit is characterized in that: include first refrigerant-cycle systems and second refrigerant-cycle systems;
Described first refrigerant-cycle systems includes first compressor, first cross valve, second cross valve, the first air side fins formula heat exchanger, first electric expansion valve, second electric expansion valve, first check valve, second check valve, the 3rd check valve, the 4th check valve, the 5th check valve, air-conditioning side heat exchanger, first reservoir, second reservoir, first gas-liquid separator, full heat recovering heat exchanger, hot-water circulating pump and attemperater; The water inlet of described full heat recovering heat exchanger is connected with the delivery port of described attemperater by described hot-water circulating pump, and the delivery port of described full heat recovering heat exchanger is connected with the water inlet of described attemperater;
When described second cross valve and described first cross valve all during no power, the suction side of the E2 of the D2 of the D1 of the outlet side of described first compressor and described first cross valve, C1 port, described second cross valve, C2 port, the described first air side fins formula heat exchanger, described first check valve, described second electric expansion valve, described second check valve, described air-conditioning side heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor joins successively; When the energising of described second cross valve and during the described first cross valve no power, the suction side of the C2 of the D2 of the D1 of the outlet side of described first compressor and described first cross valve, C1 port, described second cross valve, E2 port, described air-conditioning side heat exchanger, described first reservoir, described the 3rd check valve, described the 4th check valve, described first electric expansion valve, the described first air side fins formula heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor is connected successively; When the energising of described first cross valve and during the described second cross valve no power, the suction side of the E2 of the D1 of the outlet side of described first compressor and described first cross valve, e1 port, described full heat recovering heat exchanger, described second reservoir, described the 5th check valve, described second electric expansion valve, described second check valve, described air-conditioning side heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor is connected successively; When described second cross valve and described first cross valve were all switched on, the suction side of the C2 of the D1 of the outlet side of described first compressor and described first cross valve, e1 port, described full heat recovering heat exchanger, described second reservoir, described the 5th check valve, described first electric expansion valve, the described first air side fins formula heat exchanger, described second cross valve, S2 port, described first gas-liquid separator, described first compressor was connected successively;
Described second refrigerant-cycle systems includes second compressor, the 3rd cross valve, the 4th cross valve, the second air side fins formula heat exchanger, second throttling arrangement, the 6th check valve, the 7th check valve, the 8th check valve, the 9th check valve, air-conditioning side heat exchanger, the 3rd reservoir, second gas-liquid separator, part heat recovering heat exchanger and attemperater; The delivery port of described part heat recovering heat exchanger is connected with the water inlet of described attemperater, and the water inlet of described part heat recovering heat exchanger is connected with the delivery port of described full heat recovering heat exchanger;
When described the 3rd cross valve and described the 4th cross valve all during no power, the suction side of the E4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, C3 port, described the 6th check valve, described the 4th cross valve, C4 port, the described second air side fins formula heat exchanger, described second throttling arrangement, described the 7th check valve, described air-conditioning side heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor joins successively; When the energising of described the 4th cross valve and during described the 3rd cross valve no power, the suction side of the C4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, C3 port, described the 6th check valve, described the 4th cross valve, E4 port, described air-conditioning side heat exchanger, described the 3rd reservoir, described the 8th check valve, described second throttling arrangement, the described second air side fins formula heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor is connected successively; When the energising of described the 3rd cross valve and during described the 4th cross valve no power, the suction side of the E4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, E3 port, described part heat recovering heat exchanger, described the 9th check valve, described the 4th cross valve, C4 port, the described second air side fins formula heat exchanger, described second throttling arrangement, described the 7th check valve, described air-conditioning side heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor joins successively; When described the 3rd cross valve and described the 4th cross valve were all switched on, the suction side of the C4 of the D4 of the D3 of the outlet side of described second compressor and described the 3rd cross valve, E3 port, described part heat recovering heat exchanger, described the 9th check valve, described the 4th cross valve, E4 port, described air-conditioning side heat exchanger, described the 3rd reservoir, described the 8th check valve, described second throttling arrangement, the described second air side fins formula heat exchanger, described the 4th cross valve, S4 port, described second gas-liquid separator, described second compressor was connected successively.
7. recovery type heat Air-Cooled Heat Pump Unit according to claim 6, it is characterized in that: described first refrigerant-cycle systems is provided with magnetic valve and first throttle device, and described magnetic valve and described first throttle device are connected in series and are connected in parallel with described the 5th check valve.
8. recovery type heat Air-Cooled Heat Pump Unit according to claim 7 is characterized in that: described first throttle device is capillary, heating power expansion valve or electric expansion valve.
9. according to claim 6 or 7 or 8 described recovery type heat Air-Cooled Heat Pump Unit, it is characterized in that: described second throttling arrangement is capillary, heating power expansion valve or electric expansion valve.
10. recovery type heat Air-Cooled Heat Pump Unit according to claim 6 is characterized in that: a side of the described first air side fins formula heat exchanger is provided with first blower fan, and a side of the described second air side fins formula heat exchanger is provided with second blower fan.
CN2010206340593U 2010-11-30 2010-11-30 Heat recovery type air-cooled heat pump unit CN201935476U (en)

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102022858A (en) * 2010-11-30 2011-04-20 广东欧科空调制冷有限公司 Heat recovery type air cooling heat pump unit
CN102563972A (en) * 2012-01-20 2012-07-11 淮安恒信水务科技有限公司 Dual-path input water heating system realizing gradient use of heat pump waste heat
CN102635977A (en) * 2011-12-31 2012-08-15 广东欧科空调制冷有限公司 Low-temperature full-heat recycling type air-cooling heat pump set
CN103673381A (en) * 2013-11-14 2014-03-26 浙江思科国祥制冷设备有限公司 Novel full-year heat recovery air-cooled heat pump unit
CN103791654A (en) * 2014-03-12 2014-05-14 无锡职业技术学院 Heat recovery refrigerating system and method of air-cooled heat pump unit
CN103940009A (en) * 2013-01-17 2014-07-23 上海交通大学 Air source heat pump air-conditioning system capable of providing domestic hot water
CN105206166A (en) * 2015-10-26 2015-12-30 天津商业大学 Two-stage throttling incomplete cooling carbon dioxide refrigeration/heat pump comprehensive experimental table
CN105206164A (en) * 2015-10-26 2015-12-30 天津商业大学 One-stage throttling incomplete cooling carbon dioxide two-stage refrigeration/heat pump integrated experiment table
CN105241220A (en) * 2015-11-20 2016-01-13 廖国栋 Multistage heat recovery air energy heat pump drier

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102022858A (en) * 2010-11-30 2011-04-20 广东欧科空调制冷有限公司 Heat recovery type air cooling heat pump unit
CN102022858B (en) * 2010-11-30 2012-02-29 广东欧科空调制冷有限公司 Heat recovery type air cooling heat pump unit
CN102635977A (en) * 2011-12-31 2012-08-15 广东欧科空调制冷有限公司 Low-temperature full-heat recycling type air-cooling heat pump set
CN102635977B (en) * 2011-12-31 2014-01-22 广东欧科空调制冷有限公司 Low-temperature full-heat recycling type air-cooling heat pump set
CN102563972A (en) * 2012-01-20 2012-07-11 淮安恒信水务科技有限公司 Dual-path input water heating system realizing gradient use of heat pump waste heat
CN102563972B (en) * 2012-01-20 2013-11-27 淮安恒信水务科技有限公司 Dual-path input water heating system realizing gradient use of heat pump waste heat
CN103940009A (en) * 2013-01-17 2014-07-23 上海交通大学 Air source heat pump air-conditioning system capable of providing domestic hot water
CN103940009B (en) * 2013-01-17 2017-02-08 上海交通大学 Air source heat pump air-conditioning system capable of providing domestic hot water
CN103673381A (en) * 2013-11-14 2014-03-26 浙江思科国祥制冷设备有限公司 Novel full-year heat recovery air-cooled heat pump unit
CN103673381B (en) * 2013-11-14 2015-07-22 浙江思科国祥制冷设备有限公司 Novel full-year heat recovery air-cooled heat pump unit
CN103791654B (en) * 2014-03-12 2015-12-02 无锡职业技术学院 A kind of Air-Cooled Heat Pump Unit heat recovery refrigerating system and recuperation of heat refrigerating method thereof
CN103791654A (en) * 2014-03-12 2014-05-14 无锡职业技术学院 Heat recovery refrigerating system and method of air-cooled heat pump unit
CN105206166A (en) * 2015-10-26 2015-12-30 天津商业大学 Two-stage throttling incomplete cooling carbon dioxide refrigeration/heat pump comprehensive experimental table
CN105206164A (en) * 2015-10-26 2015-12-30 天津商业大学 One-stage throttling incomplete cooling carbon dioxide two-stage refrigeration/heat pump integrated experiment table
CN105241220A (en) * 2015-11-20 2016-01-13 廖国栋 Multistage heat recovery air energy heat pump drier

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