CN205245614U - Wind heat exchanger structures of modular air cooled heat pump unit - Google Patents

Abstract

The utility model provides a wind heat exchanger structures of modular air cooled heat pump unit, relates to cooler air -conditioner technical field. The utility model discloses among the heat exchanger a, two way refrigerant runner interval arrangements is connected with collector no. 1 and collector no. 2 respectively, among the heat exchanger b, two way refrigerant runner interval arrangements be connected with collector no. 3 and collector no. 4 respectively. The bottom of collector no. 1 and collector no. 3 is through a tee bend connection, and the bottom of collector no. 2 and collector no. 4 is through two connections of tee bend. Manage a liquid separation head no. 1 who is connected to subsystem no. 1 with a collector communicating refrigerant runner through a plurality of minutes liquid among the heat exchanger a, manage a liquid separation head no. 1 who is connected to subsystem no. 1 with three communicating refrigerant runners of collector through a plurality of minutes liquid among the heat exchanger b. The utility model discloses can, the part utilize the wind heat exchanger area that leaves unused originally in the modular air cooled heat pump unit when loading to improve the operation efficiency of modular air cooled heat pump unit system, reduce operating power consumption.

Description

A kind of wind heat exchanger structure of air cooled heat pump modular chiller

Technical field

The utility model relates to the wind heat exchanger structure of air conditioner refrigerating technical field, particularly air cooled heat pump modular chiller.

Background technology

The advantages such as air cooled heat pump modular chiller is with its clean and effective, easy to install, and load range is wide occupy larger share in the air-conditioner host market of the small and medium constructions such as office building, hotel, dining room, hospital always. According to the difference of wind heat exchanger structure form, air cooled heat pump modular chiller can be divided into V-type, U-shaped waits type.

In prior art, as shown in Figure 1, V-type air cooled heat pump modular chiller is general adopt two covers identical and independently subsystem form. Each subsystem comprises the parts such as compressor separately, expansion valve, air cooling heat exchanger, water cooling heat exchanger. Each subsystem can independent operating, especially when load hour, single system work can reduce the start and stop frequency of compressor, extends its service life, reduces fluctuating temperature amplitude simultaneously, improves end comfortableness. But because the blower fan (conventionally having two Fans) of V-type air cooled heat pump modular chiller is shared by two cover subsystems, when single system operation, blower fan needs standard-sized sheet. Therefore when single system moves, refrigeration (heat) amount and compressor horsepower reduce by half, and power of fan remains unchanged, and the energy efficiency coefficient (COP) of system is less than dual system operation. Because another set of subsystem does not move, its air cooling heat exchanger, in idle state, has caused the wasting of resources simultaneously.

Because building load is along with the variation of the indoor thermal source of outer gentleness is in annual wide variation, in addition safe clearance when design of air conditioning, in fact most of the time air-conditioning system, all in operation at part load state, causes air cooled heat pump modular chiller more in the time of single system operation. Thereby cause air cooling heat exchanger not make full use of, operational energy efficiency cannot improve. Special in the system that has adopted the parallel running of many pack modules formula Air-Cooled Heat Pump Unit, the wasting phenomenon of this resource and the energy is even more serious. In addition, when the parallel running of many pack modules machine, under sub-load, certain module is closed, but water route do not turn-off, and has occurred bypass phenomenon, causes cold and hot losses by mixture, has further limited the raising of entire system operational energy efficiency under sub-load.

Summary of the invention

In order to overcome above-mentioned the deficiencies in the prior art, the purpose of this utility model is to provide a kind of wind heat exchanger structure of air cooled heat pump modular chiller. It can, in the time of sub-load, be used the idle wind heat exchanger area of script in air cooled heat pump modular chiller, thereby improves the operational energy efficiency of air cooled heat pump modular chiller system, reduces operation energy consumption.

In order to reach foregoing invention object, the technical solution of the utility model realizes as follows:

A wind heat exchanger structure for air cooled heat pump modular chiller, every pack module formula Air-Cooled Heat Pump Unit adopts two cover subsystems to form, and is respectively subsystem unification and subsystem two, between each pack module formula Air-Cooled Heat Pump Unit, is connected in parallel. Its design feature is, every pack module formula Air-Cooled Heat Pump Unit comprises heat exchanger a that subsystem is unified and the heat exchanger b of subsystem two. In heat exchanger a, the two-way refrigerant channel interval layout being connected with collector one and collector two respectively, in heat exchanger b, the two-way refrigerant channel interval being connected with collector three and collector four is respectively arranged. The bottom of collector one and collector three is connected by threeway one, and the bottom of collector two and collector four is connected by threeway two. It is first that the refrigerant channel communicating with collector one in heat exchanger a is connected to by multiple separating tubes one separatory that subsystem is unified, and it is first that the refrigerant channel communicating with collector three in heat exchanger b is connected to by multiple separating tubes one separatory that subsystem is unified. The refrigerant channel communicating with collector two in heat exchanger a is connected to the liquid-dividing head two of subsystem two by multiple separating tubes two, the refrigerant channel communicating with collector four in heat exchanger b is connected to the liquid-dividing head two of subsystem two by multiple separating tubes two.

The utility model is owing to having adopted said structure, identical with conventional air cooled heat pump modular chiller property retention of the same type in the time that Dyon System moves simultaneously. And in the time that list system is moved, the heat exchange area of air side is identical while still keeping moving with Dyon System, compare conventional system, the heat exchange area increasing of air side is twice. Therefore refrigeration, heating capacity and energy efficiency coefficient when, the utility model list system is moved all improves greatly. When the parallel running of many pack modules of the utility model formula Air-Cooled Heat Pump Unit, can in the time of sub-load, make full use of every pack module formula Air-Cooled Heat Pump Unit single system operational energy efficiency than high feature, reduce idle heat exchange area, improve the operational energy efficiency of whole system, reduce energy consumption. Meanwhile, under sub-load, can reduce the cold and hot losses by mixture that causes because of water route bypass, thereby under cooling condition, improve unit leaving water temperature, heating condition reduces unit leaving water temperature, further improves unit operation efficiency. Below in conjunction with the drawings and specific embodiments, the utility model is described in further detail.

Brief description of the drawings

Fig. 1 is V-type air cooled heat pump modular chiller structural representation in prior art;

Fig. 2 is structural representation of the present utility model;

Fig. 3 is the system architecture schematic diagram in the utility model embodiment;

Fig. 4 is the heat exchange situation map of prior art in embodiment;

Fig. 5 is the heat exchange situation map of the utility model application in embodiment;

Fig. 6 is the connection diagram of many pack modules of the utility model formula Air-Cooled Heat Pump Unit parallel running.

Detailed description of the invention

Referring to Fig. 2, the wind heat exchanger structure of the utility model air cooled heat pump modular chiller, every pack module formula Air-Cooled Heat Pump Unit adopts two cover subsystems to form, and is respectively subsystem unification and subsystem two, between each pack module formula Air-Cooled Heat Pump Unit, is connected in parallel. Every pack module formula Air-Cooled Heat Pump Unit comprises heat exchanger a1 that subsystem is unified and the heat exchanger b2 of subsystem two, in heat exchanger a1, the two-way refrigerant channel interval being connected with collector 1 and collector 24 is respectively arranged, in heat exchanger b2, the two-way refrigerant channel interval being connected with collector 35 and collector 46 is respectively arranged. The bottom of collector 1 and collector 35 is connected by threeway 1, and the bottom of collector 24 and collector 46 is connected by threeway 28. It is first 10 that the refrigerant channel communicating with collector 1 in heat exchanger a1 is connected to by multiple separating tubes 1 separatory that subsystem is unified, and the refrigerant channel communicating with collector 35 in heat exchanger b2 is connected to separatory first 10 by multiple separating tubes 1. The refrigerant channel communicating with collector 24 in heat exchanger a1 is connected to the liquid-dividing head 2 12 of subsystem two by multiple separating tubes 2 11, the refrigerant channel communicating with collector 46 in heat exchanger b2 is connected to liquid-dividing head 2 12 by multiple separating tubes 2 11. Referring to Fig. 3, when the utility model is applied in air cooled heat pump modular chiller, heat exchanger a1 is connected with compressor, water cooling heat exchanger and the expansion valve of subsystem two with subsystem is unified respectively with heat exchanger b2. In the time that subsystem one and subsystem two are all opened, the operation of this unit is identical with conventional unit of the prior art. In the time only moving a set of subsystem in this embodiment, unit of the prior art only has 1 wind heat exchanger to come into operation, and the heat exchange area of each heat transfer unit as shown in Figure 4. And the utility model is in the time that single system moves, suppose the only unified operation of subsystem, under refrigerating state, the refrigerant that subsystem is unified evenly enters collector 1 and collector 35 by threeway 1, condensation in heat exchanger a1 and heat exchanger b2 simultaneously; Heating under state, refrigerant, by separatory first 10 and separating tube 1, evenly enters heat exchanger a1 and heat exchanger b2 evaporation. Subsystem refrigerant channel interval unified and subsystem two is arranged simultaneously. Therefore subsystem unification, except the heat exchange area of self, also can be used the idle heat exchange area of adjacent subsystem two, and the heat exchange area of each heat transfer unit increases and is twice than prior art unit, as shown in Figure 5. If subsystem two isolated operations are also identical conclusions. Therefore based on wind heat exchanger structure of the present utility model, when the operation of module machine single system, wind heat exchanger area is a times of conventional module machine, and the performance parameter of unit improves greatly.

Referring to Fig. 6, when many pack modules formula Air-Cooled Heat Pump Unit cooperation, be assumed to be n platform unit, every unit all has subsystem unification and 2 two systems of subsystem. The control method of prior art is as follows: in the time that load increases gradually from 0, open successively each module, wherein two cover system opening sequences in same module are adjacent, for example opening sequence is as follows: module 1 subsystem is unified, module 1 subsystem two, and module 2 subsystems are unified, module 2 subsystems two,, module n subsystem is unified, module n subsystem two; When load is when reducing gradually at full capacity, close successively modules, wherein two cover system closing sequences in same module are adjacent, for example closing sequence is as follows: module 1 subsystem is unified, module 1 subsystem two, and module 2 subsystems are unified, module 2 subsystems two,, module n subsystem is unified, module n subsystem two. The dual system operational energy efficiency coefficient of supposing every module is x, and the energy efficiency coefficient of single system operation is y, due to machine unit characteristic, and y < x, under this control method, the total energy efficiency coefficient of system is between y and x.

Control method of the present utility model is as follows: in the time that load increases gradually from 0, open successively the arbitrary cover system in every unit, until n platform unit is single system operation, if now also do not meet burden requirement, open gradually more remaining another set of system in n platform module, until n platform module is dual system operation. For example opening sequence is as follows: module 1 subsystem is unified, and module 2 subsystems are unified ... module n subsystem is unified, module 1 subsystem two, and module 2 subsystems two ... module n subsystem two. When load is when reducing gradually at full capacity, close successively arbitrary cover system of n module, until being single system, n platform module moves, if now also do not meet burden requirement, close gradually more remaining another set of system in n platform module, until n platform module is all closed. For example closing sequence is as follows: module 1 subsystem is unified, and module 2 subsystems are unified ... module n subsystem is unified, module 1 subsystem two, and module 2 subsystems two ... module n subsystem two. While operation due to dual system, the utility model unit is identical with conventional system, and energy efficiency coefficient is x, and because the wind heat exchanger area of single system operation doubles, its energy efficiency coefficient is z, and z > x. This control method can be under sub-load, keeps as far as possible total system to move with high energy efficiency. In the time that load increases, system first allows a set of subsystem of every module open, and energy efficiency coefficient remains on z, until n platform module is while being single system operation, energy efficiency coefficient also remains on z, higher than prior art. Along with load further improves, the another set of system of n platform module remainder is opened in succession, and module switches to dual system from single system operation gradually and moves simultaneously, total energy efficiency coefficient declines from z gradually, but still higher than x, until all modules are dual system operation, energy efficiency coefficient becomes x. When load is when reducing at full capacity, it is also identical principle. Therefore, adopt wind heat exchanger structure of the present utility model and control method, idle wind heat exchanger area can make full use of sub-load time, improve the efficiency of module machine single system operation, thereby improve the energy efficiency coefficient of total system operation, allow the energy efficiency coefficient of total system of many module machine parallel connections between x and z, higher than prior art.

On the one hand, though traditional control method, at not standard-sized sheet of sub-load lower module machine, is closed the water route of unit and cannot be turn-offed, in bypass mode, its leaving water temperature is identical with return water temperature in addition. The water-cooled of producing with operating unit mixes, and has caused energy loss. Be in particular in, in order to reach certain total leaving water temperature, owing to closing the cold and hot mixing of bypass of unit, under cooling condition, the leaving water temperature of operating unit need be lower than this temperature, and under heating condition, the leaving water temperature of operating unit need be higher than this temperature. Therefore the energy efficiency coefficient of actual motion unit cannot improve, and when rate of load condensate is lower, the unit of closing is more, and bypass phenomenon is more serious, and energy loss is higher. But the control method the utility model proposes can be opened all modules as early as possible under sub-load, reduce the generation of bypass phenomenon, make the leaving water temperature of unit approach even identical with the total leaving water temperature of system as far as possible, improve leaving water temperature at cooling condition, heating condition reduces leaving water temperature, thereby further improves the operational energy efficiency of each module. Illustrate taking cooling condition below: suppose that rate of load condensate is as 0.5, system only needs to open half unit, 12 DEG C of return water temperatures, total water outlet temperature setting is in 10 DEG C. For conventional system, n/2 platform module is closed, and water route is in bypass state, and leaving water temperature is all 12 DEG C mutually with return water temperature, and therefore the leaving water temperature of the n/2 platform module of all the other operations need reach 8 DEG C, could allow total leaving water temperature reach 10 DEG C. And while adopting control method of the present utility model, n platform module is all opened, in single system running status, there is not the cold and hot mixing phenomena of bypass in water route, and the leaving water temperature of n platform module is identical, is 10 DEG C. Due to the raising of leaving water temperature, unit has further improved operational energy efficiency, and energy-saving effect further increases.

Claims (1)

1. the wind heat exchanger structure of an air cooled heat pump modular chiller, every pack module formula Air-Cooled Heat Pump Unit adopts two cover subsystems to form, be respectively subsystem unification and subsystem two, between each pack module formula Air-Cooled Heat Pump Unit, be connected in parallel, it is characterized in that, every pack module formula Air-Cooled Heat Pump Unit comprises the heat exchanger a(1 that subsystem is unified) and the heat exchanger b(2 of subsystem two), heat exchanger a(1) in, the two-way refrigerant channel interval being connected with collector one (3) and collector two (4) is respectively arranged, heat exchanger b(2) in, the two-way refrigerant channel interval being connected with collector three (5) and collector four (6) is respectively arranged, the bottom of collector one (3) and collector three (5) is connected by threeway one (7), the bottom of collector two (4) and collector four (6) is connected by threeway two (8), heat exchanger a(1) in the refrigerant channel that communicates with collector one (3) be connected to the separatory that subsystem is unified first (10) by multiple separating tubes one (9), heat exchanger b(2) in the refrigerant channel that communicates with collector three (5) be connected to the separatory that subsystem is unified first (10) by multiple separating tubes one (9), heat exchanger a(1) in the refrigerant channel that communicates with collector two (4) be connected to the liquid-dividing head two (12) of subsystem two by multiple separating tubes two (11), heat exchanger b(2) in the refrigerant channel that communicates with collector four (6) be connected to the liquid-dividing head two (12) of subsystem two by multiple separating tubes two (11).