CN201138110Y

CN201138110Y - Refrigerant direction changing device and application thereof

Info

Publication number: CN201138110Y
Application number: CNU200720302694XU
Authority: CN
Inventors: 刘雄
Original assignee: Xian University of Architecture and Technology
Current assignee: Xian University of Architecture and Technology
Priority date: 2007-12-24
Filing date: 2007-12-24
Publication date: 2008-10-22
Anticipated expiration: 2017-12-24

Abstract

The utility model discloses a refrigerant flow-direction changeover device and the application of the device. The device comprises a first one-way valve, a second one-way valve, a third one-way valve and a fourth one-way valve, and four connection end points; a four-way valve high-pressure joint is connected with the outlet end of the one-way valve; the inlet end of the one-way valve is connected with the first connection end point; the low-pressure joint of the four-way valve is connected with the inlet end of the one-way valve; the outlet end of the one-way valve is connected with the second connection end point; the outlet end of the one-way valve is connected with a pipeline between the first connection end point and the second connection end point; the inlet end of the one-way valve is connected with a pipeline that is arranged between the four-way valve low-pressure joint and the inlet end of the third one-way valve; the inlet end of the one-way valve is connected with a pipeline that is arranged between the second connection end point and the third one-way valve outlet end; the outlet end of the one-way valve is connected with a pipeline that is arranged between the four-way valve high-pressure joint and the outlet end of the first one-way valve; the third connection end point is connected with either of the changeover joints of the four-way valve; the fourth connection end point is connected with the other changeover joint of the four-way valve. The device has simple structure, reliable operation and low cost.

Description

The application of refrigerant flow direction converting and device

Technical field

The utility model relates to the application of two kinds of refrigerant flow direction convertings and device, belongs to refrigeration technology field.

Background technology

Nanjing TianJia Air Conditioner Equipment Co., Ltd obtained the authorization on October 3rd, 2007, the patent No. is 200620068218.1 utility model patent, and by Xi'an University of Architecture and Technology on June 6th, 2007, applied for October 11, application number is respectively 200710018006.1,200710018005.7,200710162570.0 three utility model patents, all relate to a kind of by compressor and two refrigerant flow direction convertings that cross valve is formed, in this device, if cross valve adopts known air conditioner refrigerating cross valve at present, so when realizing some function, that cross valve that directly links to each other with compressor (is not called as second cross valve in application number is 200710162570.0 utility application file.), the pressure at its low pressure node place can surpass the pressure at high pressure node place, therefore, can cause cross valve inside to be used to control the fixedly poorly sealed between the contact-making surface of the movable slider of refrigerant flow direction and valve, make between cross valve internal high pressure side and the low-pressure side, the leakage of cold-producing medium takes place, thereby causes cross valve can't finish the task of refrigerant flow direction conversion correctly, effectively.

The utility model content

The purpose of this utility model provides two kinds of low costs, simple in structure, reliable operation, can realize the refrigerant flow direction converting of multiple translation function, and heat pump and the aircondition of using these two kinds of refrigerant flow direction convertings.

In order to overcome the problem that above-mentioned technology exists, the technical scheme of the utility model technical solution problem is: a kind of refrigerant flow direction converting, comprise cross valve, its special character is: it also comprises four check valves, i.e. first check valve, second check valve, the 3rd check valve and the 4th check valve, four connection end points are arranged, i.e. first connection end point, second connection end point, the 3rd connection end point and the 4th connection end point, the high pressure node of described cross valve links to each other with the first check valve port of export, the first check valve arrival end links to each other with first connection end point, the low pressure node of cross valve links to each other with the 3rd check valve arrival end, the 3rd check valve port of export links to each other with second connection end point, the second check valve port of export links to each other with pipeline between first connection end point and the first check valve arrival end, the second check valve arrival end links to each other with the low pressure node of cross valve and the pipeline between the 3rd check valve arrival end, the 4th check valve arrival end links to each other with pipeline between second connection end point and the 3rd check valve port of export, the 4th check valve port of export links to each other with the high pressure node of cross valve and the pipeline between the first check valve port of export, any one of two commutations of the 3rd connection end point and cross valve node links to each other, and the 4th connection end point links to each other with another commutation node of cross valve.

A kind of refrigerant flow direction converting, comprise compressor, cross valve, its special character is: it also comprises four check valves, i.e. first check valve, second check valve, the 3rd check valve and the 4th check valve, four connection end points are arranged, i.e. first connection end point, second connection end point, high pressure connection end point and low pressure connection end point, the high pressure node of described cross valve links to each other with compressor outlet by pipeline, the low pressure node of cross valve links to each other with the suction port of compressor end by pipeline, any one of two commutations of cross valve node links to each other with first connection end point, another commutation node of cross valve links to each other with the first check valve arrival end by pipeline, the first check valve port of export links to each other with the 4th check valve port of export, the 4th check valve arrival end links to each other with second connection end point, the second check valve port of export links to each other with pipeline between the cross valve and the first check valve arrival end, second check valve (92) arrival end links to each other with the 3rd check valve arrival end, the 3rd check valve port of export links to each other with pipeline between the 4th check valve arrival end and second connection end point, the high pressure connection end point links to each other with pipeline between the first check valve port of export and the 4th check valve port of export, and the low pressure connection end point links to each other with pipeline between the second check valve arrival end and the 3rd check valve arrival end.

The application of the described refrigerant flow direction converting of a kind of claim 1, comprise compressor, second cross valve, heat source side heat exchanger, the user side heat exchanger, throttle mechanism, its special character is: it also comprises second throttle mechanism, second heat exchanger, first flow direction control valve, second flow direction control valve, the 9th flow direction control valve, first check valve, second check valve, the 3rd check valve, the 4th check valve and cross valve, the high pressure node of described cross valve links to each other with the first check valve port of export, the first check valve arrival end links to each other with first connection end point, the low pressure node of cross valve links to each other with the 3rd check valve arrival end, the 3rd check valve port of export links to each other with second connection end point, the second check valve port of export links to each other with pipeline between first connection end point and the first check valve arrival end, the second check valve arrival end links to each other with the low pressure node of cross valve and the pipeline between the 3rd check valve arrival end, the 4th check valve arrival end links to each other with pipeline between second connection end point and the 3rd check valve port of export, the 4th check valve port of export links to each other with the high pressure node of cross valve and the pipeline between the first check valve port of export, any one of two commutations of the 3rd connection end point and cross valve node links to each other, the 4th connection end point links to each other with another commutation node of cross valve, described the 3rd connection end point links to each other with second heat exchanger, one end, the second heat exchanger other end links to each other with heat source side heat exchanger one end by second throttle mechanism, the heat source side heat exchanger other end links to each other with the 4th connection end point, described first connection end point links to each other by any one of two commutations of the pipeline and second cross valve node, the high pressure node of second cross valve links to each other with compressor outlet by pipeline, the low pressure node of second cross valve links to each other with the suction port of compressor end by pipeline, another commutation node of second cross valve links to each other with user side heat exchanger one end by pipeline, the user side heat exchanger other end passes through throttle mechanism successively, second flow direction control valve, pipeline links to each other with described second connection end point, first flow direction control valve, one end links to each other with pipeline between second cross valve and the user side heat exchanger, the first flow direction control valve other end links to each other with pipeline between second connection end point and second flow direction control valve, the 9th flow direction control valve one end links to each other with pipeline between the throttle mechanism and second flow direction control valve, and the 9th flow direction control valve other end links to each other with pipeline between second throttle mechanism and second heat exchanger;

Or described the 3rd connection end point links to each other with heat source side heat exchanger one end, and the heat source side heat exchanger other end links to each other with second heat exchanger, one end by second throttle mechanism, and the second heat exchanger other end links to each other with the 4th connection end point.

The application of the described refrigerant flow direction converting of a kind of claim 3, it comprises compressor, heat source side heat exchanger, the user side heat exchanger, throttle mechanism and cross valve, its special character is: it also comprises second throttle mechanism, second heat exchanger, first flow direction control valve, second flow direction control valve, the 9th flow direction control valve, first check valve, second check valve, the 3rd check valve and the 4th check valve, the high pressure node of described cross valve links to each other with compressor outlet by pipeline, the low pressure node of cross valve links to each other with the suction port of compressor end by pipeline, any one of two commutations of cross valve node links to each other with first connection end point, another commutation node of cross valve links to each other with the first check valve arrival end by pipeline, the first check valve port of export links to each other with the 4th check valve port of export, the 4th check valve arrival end links to each other with second connection end point, the second check valve port of export links to each other with pipeline between the cross valve and the first check valve arrival end, the second check valve arrival end links to each other with the 3rd check valve arrival end, the 3rd check valve port of export links to each other with pipeline between the 4th check valve arrival end and second connection end point, the high pressure connection end point links to each other with pipeline between the first check valve port of export and the 4th check valve port of export, the low pressure connection end point links to each other with pipeline between the second check valve arrival end and the 3rd check valve arrival end, described first connection end point links to each other with user side heat exchanger one end by pipeline, the user side heat exchanger other end passes through throttle mechanism successively, second flow direction control valve, pipeline links to each other with second connection end point, the high pressure connection end point links to each other with second heat exchanger, one end by pipeline, the second heat exchanger other end links to each other with second throttle mechanism, one end, the second throttle mechanism other end links to each other with heat source side heat exchanger one end by pipeline, the heat source side heat exchanger other end links to each other with the low pressure connection end point by pipeline, first flow direction control valve, one end links to each other with pipeline between first connection end point and the user side heat exchanger, the first flow direction control valve other end links to each other with pipeline between second connection end point and second flow direction control valve, the 9th flow direction control valve one end links to each other with pipeline between the throttle mechanism and second flow direction control valve, and the 9th flow direction control valve other end links to each other with pipeline between second throttle mechanism and second heat exchanger;

Or set up the tenth flow direction control valve, and the tenth flow direction control valve one end links to each other with pipeline between the high pressure connection end point and second heat exchanger, and the tenth flow direction control valve other end links to each other with pipeline between second throttle mechanism and second heat exchanger.

The application of the described refrigerant flow direction converting of a kind of claim 3, it comprises compressor, evaporimeter, throttle mechanism, direct heat exchanger, working medium pump, evaporative heat exchanger, solution cooler, regenerator, dehumidifier and heater, above-mentioned said evaporative heat exchanger is made up of one group of cooling heat exchanger and one group of condensing heat exchanger, its special character is: it also comprises cross valve, first check valve, second check valve, the 3rd check valve and the 4th check valve, the high pressure node of described cross valve links to each other with compressor outlet by pipeline, the low pressure node of cross valve links to each other with the suction port of compressor end by pipeline, any one of two commutations of cross valve node links to each other with first connection end point, another commutation node of cross valve links to each other with the first check valve arrival end by pipeline, the first check valve port of export links to each other with the 4th check valve port of export, the 4th check valve arrival end links to each other with second connection end point, the second check valve port of export links to each other with pipeline between the cross valve and the first check valve arrival end, the second check valve arrival end links to each other with the 3rd check valve arrival end, the 3rd check valve port of export links to each other with pipeline between the 4th check valve arrival end and second connection end point, the high pressure connection end point links to each other with pipeline between the first check valve port of export and the 4th check valve port of export, the low pressure connection end point links to each other with pipeline between the second check valve arrival end and the 3rd check valve arrival end, described first connection end point links to each other with evaporimeter one end by pipeline, the evaporimeter other end links to each other with second connection end point with pipeline by throttle mechanism, described high pressure connection end point links to each other with condensing heat exchanger one end of evaporative heat exchanger by pipeline, the condensing heat exchanger other end of evaporative heat exchanger links to each other with direct heat exchanger by pipeline, direct heat exchanger passes through pipeline successively, working medium pump links to each other with cooling heat exchanger one end of evaporative heat exchanger, the cooling heat exchanger other end of evaporative heat exchanger links to each other with pipeline, pipeline is divided into three the tunnel: the pipeline of leading up to links to each other with described low pressure connection end point, another road links to each other with direct heat exchanger by pipeline, and Third Road passes through pipeline successively, solution cooler, pipeline links to each other with direct heat exchanger;

Except that said structure, also can change over other structure kinds by the conversion of following structure:

Or the 3rd flow direction control valve is set and working medium pump is connected in parallel;

Or set up second throttle mechanism, second throttle mechanism is arranged on direct heat exchanger and the pipeline that the condensing heat exchanger of evaporative heat exchanger links to each other;

Or set up second throttle mechanism and the 5th flow direction control valve, second throttle mechanism is arranged on the pipeline between the cooling heat exchanger three of direct heat exchanger, working medium pump and evaporative heat exchanger, the 5th flow direction control valve one end is connected with pipeline, and the 5th flow direction control valve other end is connected with pipeline;

Or set up the 3rd flow direction control valve and second throttle mechanism, and the 3rd flow direction control valve and working medium pump are connected in parallel, and second throttle mechanism is arranged on direct heat exchanger and the pipeline that the condensing heat exchanger of evaporative heat exchanger links to each other;

Or set up the 3rd flow direction control valve, second throttle mechanism and the 5th flow direction control valve, the 3rd flow direction control valve and working medium pump are connected in parallel, second throttle mechanism is arranged on the pipeline between the cooling heat exchanger three of direct heat exchanger, the 3rd flow direction control valve and evaporative heat exchanger, the 5th flow direction control valve one end is connected with pipeline, and the 5th flow direction control valve other end is connected with pipeline;

Or described throttle mechanism is arranged on low pressure connection end point and the pipeline that pipeline links to each other, sets up second throttle mechanism, and second throttle mechanism is arranged on direct heat exchanger and the pipeline that the condensing heat exchanger of evaporative heat exchanger links to each other;

Or described throttle mechanism is arranged on low pressure connection end point and the pipeline that pipeline links to each other, set up the 3rd flow direction control valve and second throttle mechanism, the 3rd flow direction control valve and working medium pump are connected in parallel, and second throttle mechanism is arranged on direct heat exchanger and the pipeline that the condensing heat exchanger of evaporative heat exchanger links to each other;

Or described throttle mechanism is arranged on low pressure connection end point and the pipeline that pipeline links to each other, set up second throttle mechanism and the 5th flow direction control valve, second throttle mechanism is arranged on the pipeline between the cooling heat exchanger three of direct heat exchanger, working medium pump and evaporative heat exchanger, the 5th flow direction control valve one end links to each other with pipeline, and the 5th flow direction control valve other end links to each other with pipeline;

Or described throttle mechanism is arranged on low pressure connection end point and the pipeline that pipeline links to each other, set up the 3rd flow direction control valve, second throttle mechanism and the 5th flow direction control valve, the 3rd flow direction control valve and working medium pump are connected in parallel, second throttle mechanism is arranged on the pipeline between the cooling heat exchanger three of direct heat exchanger, the 3rd flow direction control valve and evaporative heat exchanger, the 5th flow direction control valve one end is connected with pipeline, and the 5th flow direction control valve other end is connected with pipeline.

The utility model compared with prior art, its beneficial effect is:

1. can realize multiple refrigerant flow direction translation function as required.

2. use the heat pump of these flow direction convertings, can realize freezing, the waste heat in the heating, recovery operation process, make that cold-producing medium is cold excessively, productive life hot water, freeze simultaneously and productive life hot water, heat simultaneously and the function of productive life hot water according to user's needs according to user's needs; Can also utilize the waste heat defrosting of recovery for air source heat pump.

3. when working, can guarantee that the on high-tension side pressure of cross valve is all the time greater than low-pressure side.

4. simple in structure, reliable operation, with low cost.

5. the utility model is applicable to industry and civilian Winter-summer dual purpose heat pump, is specially adapted to the Winter-summer dual purpose heat pump of the civilian middle-size and small-size domestic hot-water's of having demand.

Description of drawings

Fig. 1 is first kind of refrigerant flow direction converting structural representation of the utility model;

Fig. 2 is second kind of refrigerant flow direction converting structural representation of the utility model;

Fig. 3 is to use the heat pump structural representation of first kind of refrigerant flow direction converting;

Fig. 4 is to use the heat pump structural representation of first kind of refrigerant flow direction converting;

Fig. 5 is to use the heat pump structural representation of second kind of refrigerant flow direction converting;

Fig. 6 is to use the air condition by dehumidifying, evaporative cooling solution apparatus structure schematic diagram of second kind of refrigerant flow direction converting.

The specific embodiment

Accompanying drawing embodiment of the present utility model

Below in conjunction with accompanying drawing the utility model content is described in further detail.

With reference to Figure 1 shows that first kind of refrigerant flow direction converting structural representation, it comprises: cross valve 80, the first check valve 9A, the second check valve 9B, the 3rd check valve 9C and the 4th check valve 9D; Four connection end points are arranged, that is: the first connection end point a, the second connection end point b, the 3rd connection end point c and the 4th connection end point d; Cross valve 80 comprises: the high pressure node 81 that links to each other with pressure duct, the low pressure node that links to each other with low pressure line 83, the first commutation node 82 and the second commutation node 84.

The high pressure node 81 of cross valve 80 links to each other with the first check valve 9A port of export, the first check valve 9A arrival end links to each other with the first connection end point a, the low pressure node 83 of cross valve 80 links to each other with the 3rd check valve 9C arrival end, the 3rd check valve 9C port of export links to each other with the second connection end point b, the second check valve 9B port of export links to each other with pipeline between the first connection end point a and the first check valve 9A arrival end, the second check valve 9B arrival end links to each other with the low pressure node 83 of cross valve 80 and the pipeline between the 3rd check valve 9C arrival end, the 4th check valve 9D arrival end links to each other with pipeline between the second connection end point b and the 3rd check valve 9C port of export, the 4th check valve 9D port of export links to each other with the high pressure node 81 of cross valve 80 and the pipeline between the first check valve 9A port of export, the first commutation node 82 of cross valve 80 links to each other with the 3rd connection end point c, and the second commutation node 84 of cross valve 80 links to each other with the 4th connection end point d.

In actual application, also can be that the first commutation node 82 of cross valve 80 links to each other with the 4th connection end point d, the second commutation node 84 of cross valve 80 links to each other with the 3rd connection end point c.

Its special character is: during work, the pressure that can make high pressure node 81 places is all the time greater than the pressure at low pressure node 83 places; Cross valve 80 can be present known air conditioner refrigerating cross valve.

Figure 2 shows that second kind of refrigerant flow direction converting structural representation, it comprises: compressor 1, cross valve 70, first check valve 91, second check valve 92, the 3rd check valve 93 and the 4th check valve 94; Four connection end points are arranged, that is: the first connection end point g, the second connection end point h, high pressure connection end point f and low pressure connection end point e; Cross valve 70 comprises: high pressure node 71, low pressure node 73, the first commutation node 72 and the second commutation node 74.

The high pressure node 71 of cross valve 70 links to each other with compressor 1 port of export by pipeline 60, the low pressure node 73 of cross valve 70 links to each other with compressor 1 arrival end by pipeline 63, the first commutation node 72 of cross valve 70 links to each other with the first connection end point g of flow direction converting, the second commutation node 74 of cross valve 70 links to each other with first check valve, 91 arrival ends by pipeline 61, first check valve, 91 ports of export link to each other with the 4th check valve 94 ports of export, the 4th check valve 94 arrival ends link to each other with the second connection end point h of flow direction converting, second check valve, 92 ports of export link to each other with pipeline 61 between cross valve 70 and first check valve, 91 arrival ends, second check valve, 92 arrival ends link to each other with the 3rd check valve 93 arrival ends, pipeline between the second connection end point h of the 3rd check valve 93 ports of export and the 4th check valve 94 arrival ends and flow direction converting links to each other, the high pressure connection end point f of flow direction converting links to each other with pipeline between first check valve, 91 ports of export and the 4th check valve 94 ports of export, and the low pressure connection end point e of flow direction converting links to each other with pipeline between second check valve, 92 arrival ends and the 3rd check valve 93 arrival ends.

Its special character is: any one links to each other first check valve, 91 arrival ends and second check valve, 92 ports of export two commutation nodes by pipeline and cross valve 70 and (Figure 2 shows that with second node 74 that commutates and link to each other.); Cross valve 70 can be present known air conditioner refrigerating cross valve; Constitute the circulation loop of an one-way flow between high pressure connection end point f and the low pressure connection end point e; Constitute between the first connection end point g and the second connection end point h one can switch as required, the circulation loop of two-way flow.

The described check valve of Fig. 1 and Fig. 2 can be a magnetic valve.

Embodiment 1

Be the heat pump of first kind of refrigerant flow direction converting of a kind of use as shown in Figure 3, it comprises: compressor 1, heat source side heat exchanger 2, user side heat exchanger 3, throttle mechanism 4, second throttle mechanism 5, second heat exchanger 6, second cross valve 100, the first flow direction control valve 7-1, the second flow direction control valve 7-2, the 9th flow direction control valve 7-9 and described first kind of refrigerant flow direction converting.

User side heat exchanger 3, heat source side heat exchanger 2 are cold-producing medium-air heat exchangers, and second heat exchanger 6 is cold-producing medium-water-to-water heat exchangers, normally storage heat exchanger.Heat pump can be realized freezing merely summer, summer, refrigeration reclaimed condensation heat productive life hot water and cold excessively to cold-producing medium simultaneously, summer quick productive life hot water, need simultaneously refrigeration and productive life hot water by the user summer, heat winter merely, heat supply in winter reclaims high temperature refrigerant liquid sensible heat and cold excessively to cold-producing medium simultaneously, winter quick productive life hot water, need simultaneously heating and productive life hot water by the user winter, utilize the nine kinds of functions of high temperature refrigerant liquid sensible heat defrost that reclaim winter.Their workflow is as described below respectively:

(1) freezes merely summer

The first flow direction control valve 7-1 and the second flow direction control valve 7-2 close, and the 9th flow direction control valve 7-9 opens, throttle mechanism 4 operate as normal, second throttle mechanism, 5 standard-sized sheets.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, the second commutation node 104, pipeline 61, the first connection end point a of flow direction converting, the first check valve 9A, the high pressure node 81 of cross valve 80, the second commutation node 84, the 4th connection end point d of flow direction converting, pipeline 41 enters heat source side heat exchanger 2 and carries out indirect heat exchange with outdoor air, become refrigerant liquid after emitting heat, refrigerant liquid is again through piping 42, second throttle mechanism 5 and the 9th flow direction control valve 7-9 enter throttle mechanism 4 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter user side heat exchanger 3, absorb user's heat therein by indirect heat exchange, be user's cooling, after cold-producing medium absorbs user's heat, become the low-temperature low-pressure refrigerant steam, through piping 64, the first commutation node 102 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, and so far finishes once simple kind of refrigeration cycle.

(2) summer, refrigeration reclaimed condensation heat productive life hot water and cold excessively to cold-producing medium simultaneously

The first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 close, and the second flow direction control valve 7-2 opens, throttle mechanism 4 operate as normal, second throttle mechanism, 5 standard-sized sheets.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, the second commutation node 104, pipeline 61, the first connection end point a of flow direction converting, the first check valve 9A, the high pressure node 81 of cross valve 80, the first commutation node 82, the 3rd connection end point c of flow direction converting, pipeline 31 enters second heat exchanger 6 and carries out indirect heat exchange with water, reclaim condensation of refrigerant heat and produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, refrigerant liquid is through piping 32, second throttle mechanism 5 and pipeline 42 enter heat source side heat exchanger 2 and carry out indirect heat exchange again with outdoor air or indoor exhaust wind, by cold excessively, cross refrigerant liquid after cold through piping 41, the 4th connection end point d of flow direction converting, the second commutation node 84 of cross valve 80, low pressure node 83, the 3rd check valve 9C, the second connection end point b of flow direction converting, pipeline 62, the second flow direction control valve 7-2 enters throttle mechanism 4 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter user side heat exchanger 3, absorb user's heat therein by indirect heat exchange, be user's cooling, after cold-producing medium absorbs user's heat, become the low-temperature low-pressure refrigerant steam, through piping 64, the first commutation node 102 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, and so far finishing freezes a summer reclaims condensation heat productive life hot water simultaneously and cold-producing medium was carried out cold circulation.

(3) summer quick productive life hot water

The second flow direction control valve 7-2 and the 9th flow direction control valve 7-9 close, and the first flow direction control valve 7-1 opens, and throttle mechanism 4 is not worked, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, the second commutation node 104, pipeline 61, the first connection end point a of flow direction converting, the first check valve 9A, the high pressure node 81 of cross valve 80, the first commutation node 82, the 3rd connection end point c of flow direction converting, pipeline 31 enters second heat exchanger 6 and carries out indirect heat exchange with water, produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, enter second throttle mechanism 5 again by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 and carry out indirect heat exchange with outdoor air or indoor exhaust wind, after absorbing the heat of air by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the 4th connection end point d of flow direction converting, the second commutation node 84 of cross valve 80, low pressure node 83, the 3rd check valve 9C, the second connection end point b of flow direction converting, pipeline 62, the first flow direction control valve 7-1, pipeline 64, the first commutation node 102 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, so far finish one time summer quick productive life hot water circulation.

(4) need refrigeration and productive life hot water simultaneously by the user summer

The first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 open, and the second flow direction control valve 7-2 closes, and the throttle mechanism 4 and second throttle mechanism 5 be operate as normal all.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, the second commutation node 104, pipeline 61, the first connection end point a of flow direction converting, the first check valve 9A, the high pressure node 81 of cross valve 80, the first commutation node 82, the 3rd connection end point c of flow direction converting, pipeline 31 enters second heat exchanger 6 and carries out indirect heat exchange with water, produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, after coming out from second heat exchanger 6, be divided into two-way; One the tunnel enters second throttle mechanism 5 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through piping 42 and carry out indirect heat exchange with outdoor air or indoor exhaust wind, after absorbing the heat of air by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, more successively through piping 41, the 4th connection end point d of flow direction converting, the second commutation node 84 of cross valve 80, low pressure node 83, the 3rd check valve 9C, the second connection end point b of flow direction converting, pipeline 62, the first flow direction control valve 7-1 enters pipeline 64; Another road enters throttle mechanism 4 by throttling through the 9th flow direction control valve 7-9, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter user side heat exchanger 3, absorb user's heat therein by indirect heat exchange, be user's cooling, after cold-producing medium absorbs user's heat, become the low-temperature low-pressure refrigerant steam, also enter pipeline 64, after first via refrigerant mixed, again through piping 64, the first commutation node 102 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, and so far finishing summer needs the circulation of refrigeration and productive life hot water simultaneously by the user.

(5) heat merely winter

The 9th flow direction control valve 7-9 opens, and the first flow direction control valve 7-1 and the second flow direction control valve 7-2 close, throttle mechanism 4 standard-sized sheets, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, the first commutation node 102, pipeline 64 laggard access customer side heat exchangers 3, emit heat by indirect heat exchange therein, be user's heat supply, after cold-producing medium is emitted heat, become high-temperature high-pressure refrigerant liquid, refrigerant liquid passes through throttle mechanism 4 again, the 9th flow direction control valve 7-9 enters second throttle mechanism 5 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 again and carry out indirect heat exchange with outdoor air or indoor exhaust wind, after absorbing the heat of air by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the 4th connection end point d of flow direction converting, the second commutation node 84 of cross valve 80, low pressure node 83, the second check valve 9B, the first connection end point a of flow direction converting, the second commutation node 104 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, and so far finishes the circulation of a simple heating in winter.

(6) heat supply in winter reclaims high temperature refrigerant liquid sensible heat and cold excessively to cold-producing medium simultaneously

The first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 close, and the second flow direction control valve 7-2 opens, throttle mechanism 4 standard-sized sheets, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, the first commutation node 102, pipeline 64 laggard access customer side heat exchangers 3, emit heat by indirect heat exchange therein, be user's heat supply, after cold-producing medium is emitted heat, become high-temperature high-pressure refrigerant liquid, refrigerant liquid passes through throttle mechanism 4 again, the second flow direction control valve 7-2, pipeline 62, the second connection end point b of flow direction converting, the 4th check valve 9D, the high pressure node 81 of cross valve 80, the first commutation node 82, behind the 3rd connection end point c and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, reclaim the sensible heat of high temperature refrigerant liquid and produce low-temperature water heating, and cold-producing medium is emitted behind the heat by cold excessively, the cold-producing medium of crossing after cold enters second throttle mechanism 5 by throttling through piping 32, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through piping 42 again, carry out indirect heat exchange with outdoor air or indoor exhaust wind, after absorbing the heat of air by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the 4th connection end point d of flow direction converting, the second commutation node 84 of cross valve 80, low pressure node 83, the second check valve 9B, the first connection end point a of flow direction converting, pipeline 61, the second commutation node 104 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, and so far finishes a heat supply in winter and reclaims high temperature refrigerant liquid sensible heat simultaneously and cold-producing medium was carried out cold circulation.

(7) winter quick productive life hot water

The first flow direction control valve 7-1 opens, and the second flow direction control valve 7-2 and the 9th flow direction control valve 7-9 close, and throttle mechanism 4 is not worked, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, the first commutation node 102, pipeline 64, the first flow direction control valve 7-1, pipeline 62, the second connection end point b of flow direction converting, the 4th check valve 9D, the high pressure node 81 of cross valve 80, the first commutation node 82, behind the 3rd connection end point c and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, enter second throttle mechanism 5 by throttling through piping 32 again, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through piping 42 and carry out indirect heat exchange with outdoor air or indoor exhaust wind, after absorbing the heat of air by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the 4th connection end point d of flow direction converting, the second commutation node 84 of cross valve 80, low pressure node 83, the second check valve 9B, the first connection end point a of flow direction converting, pipeline 61, the second commutation node 104 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, so far finish one time winter quick productive life hot water circulation.

(8) need heating and productive life hot water simultaneously by the user winter

The first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 open, and the second flow direction control valve 7-2 closes, throttle mechanism 4 standard-sized sheets, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, be divided into two the tunnel: the one tunnel through the first flow direction control valve 7-1 behind the first commutation node 102 and the pipeline 64, pipeline 62, the second connection end point b of flow direction converting, the 4th check valve 9D, the high pressure node 81 of cross valve 80, the first commutation node 82, behind the 3rd connection end point c and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, enters pipeline 32 after second heat exchanger 6 comes out; Another road enters user side heat exchanger 3, emit heat by indirect heat exchange therein, be user's heat supply, after cold-producing medium is emitted heat, become high-temperature high-pressure refrigerant liquid, refrigerant liquid passes through throttle mechanism 4 again, the 9th flow direction control valve 7-9 also enters pipeline 32, after first via refrigerant liquid mixes, enter second throttle mechanism 5 again by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 and carry out indirect heat exchange with outdoor air or indoor exhaust wind, after absorbing the heat of air by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the 4th connection end point d of flow direction converting, the second commutation node 84 of cross valve 80, low pressure node 83, the second check valve 9B, the first connection end point a of flow direction converting, pipeline 61, the second commutation node 104 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, and so far finishes the circulation that a time need heating simultaneously and productive life hot water winter by the user.

(9) utilize the high temperature refrigerant liquid sensible heat defrost of reclaiming winter

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 101 of second cross valve 100, the first commutation node 102, pipeline 64, the first flow direction control valve 7-1, pipeline 62, the second connection end point b of flow direction converting, the 4th check valve 9D, the high pressure node 81 of cross valve 80, the second commutation node 84, behind the 4th connection end point d and pipeline 41 of flow direction converting, entering heat source side heat exchanger 2 defrosts to it, refrigerant vapour becomes refrigerant liquid after emitting heat, refrigerant liquid enters second throttle mechanism 5 by throttling through piping 42 again, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter second heat exchanger 6 through piping 32 and carry out indirect heat exchange with low-temperature water heating, after absorbing the heat of water, become the low-temperature low-pressure refrigerant steam, again through piping 31, the 3rd connection end point c of flow direction converting, the first commutation node 82 of cross valve 80, low pressure node 83, the second check valve 9B, the first connection end point a of flow direction converting, pipeline 61, the second commutation node 104 of second cross valve 100, low pressure node 103, pipeline 63 enters compressor 1 and is compressed, and so far finishes the circulation that a time utilize the high temperature refrigerant liquid sensible heat of recovery to defrost winter.

When the shortage of heat of low-temperature water heating in second heat exchanger 6 during with defrosting, also can defrost by traditional Defrost method, promptly utilize the heat of room air to defrost, its workflow with summer simple kind of refrigeration cycle identical.

When using, also has another scheme, as shown in Figure 4, that is: heat source side heat exchanger 2 one ends link to each other with the 3rd connection end point c of flow direction converting by pipeline 31, heat source side heat exchanger 2 other ends link to each other with second heat exchanger, 6 one ends by pipeline 32, second throttle mechanism 5, pipeline 42, second heat exchanger, 6 other ends link to each other with the 4th connection end point d of flow direction converting by pipeline 41, and the connected mode of miscellaneous equipment is identical with embodiment 1.This scheme has the 1 identical function with embodiment, is when realizing same function, the path difference that cold-producing medium is walked in cross valve 80.

In addition, when practical application, the role of the heat source side heat exchanger 2 and second heat exchanger 6 can exchange, that is: heat source side heat exchanger 2 is cold-producing medium-water-to-water heat exchangers, be used to produce low-temperature water heating, and second heat exchanger 6 is cold-producing medium-air heat exchangers, utilizes outdoor air as Cooling and Heat Source.At this moment, the connected mode of the 9th flow direction control valve 7-9 is slightly different with embodiment 1, should change to: the end of the 9th flow direction control valve 7-9 links to each other with pipeline between the throttle mechanism 4 and the second flow direction control valve 7-2, the other end links to each other with pipeline between throttle mechanism 5 and the heat source side heat exchanger 2, and the connected mode of miscellaneous equipment is identical with embodiment 1.This scheme has the 1 identical function with embodiment.

Embodiment 2

Shown in Figure 5 is the heat pump of second kind of refrigerant flow direction converting of a kind of use.It comprises: heat source side heat exchanger 2, user side heat exchanger 3, throttle mechanism 4, second throttle mechanism 5, second heat exchanger 6, the first flow direction control valve 7-1, the second flow direction control valve 7-2, the 9th flow direction control valve 7-9, the tenth flow direction control valve 7-10 and described second kind of refrigerant flow direction converting.

User side heat exchanger 3 and heat source side heat exchanger 2 are cold-producing medium-air heat exchangers, and second heat exchanger 6 is cold-producing medium-water-to-water heat exchangers.Embodiment 2 also has nine kinds of functions, but during winter frost removing, can not as embodiment 1, utilize the high temperature refrigerant liquid sensible heat of recovery to defrost, and can only adopt traditional Defrost method, for example: contrary circulation hot gas defrosting, that is: be that outdoor heat source side heat exchanger 2 defrosts from user's draw heat, other eight functions is identical with embodiment 1.The workflow of these nine kinds of functions is as described below respectively:

(1) freezes merely summer

The first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 close, and the second flow direction control valve 7-2 and the tenth flow direction control valve 7-10 open, throttle mechanism 4 operate as normal, second throttle mechanism, 5 standard-sized sheets.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the second commutation node 74, pipeline 61, first check valve 91, the high pressure connection end point f of flow direction converting, pipeline 31, the tenth flow direction control valve 7-10, behind second throttle mechanism 5 and the pipeline 42, enter heat source side heat exchanger 2 and carry out indirect heat exchange, refrigerant vapour becomes refrigerant liquid after emitting heat, refrigerant liquid is again through piping 41, the low pressure connection end point e of flow direction converting, the 3rd check valve 93, the second connection end point h of flow direction converting, pipeline 62, the second flow direction control valve 7-2 enters throttle mechanism 4 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter user side heat exchanger 3, absorb user's heat therein by indirect heat exchange, be user's cooling, after cold-producing medium absorbs user's heat, become the low-temperature low-pressure refrigerant steam, through piping 64, the first connection end point g of flow direction converting, the first commutation node 72 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, and so far finishes once simple kind of refrigeration cycle.

The first flow direction control valve 7-1, the 9th flow direction control valve 7-9 and the tenth flow direction control valve 7-10 close, and the second flow direction control valve 7-2 opens, throttle mechanism 4 operate as normal, second throttle mechanism, 5 standard-sized sheets.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the second commutation node 74, pipeline 61, first check valve 91, behind the high pressure connection end point f and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, reclaim condensation of refrigerant heat and produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, refrigerant liquid is through piping 32, second throttle mechanism 5 and pipeline 42, enter heat source side heat exchanger 2 and carry out indirect heat exchange again by cold excessively, cross refrigerant liquid after cold through piping 41, the low pressure connection end point e of flow direction converting, the 3rd check valve 93, the second connection end point h of flow direction converting, pipeline 62, the second flow direction control valve 7-2 enters throttle mechanism 4 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter user side heat exchanger 3, absorb user's heat therein by indirect heat exchange, be user's cooling, after cold-producing medium absorbs user's heat, become the low-temperature low-pressure refrigerant steam, through piping 64, the first connection end point g of flow direction converting, the first commutation node 72 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, and so far finishing freezes a summer reclaims condensation heat productive life hot water simultaneously and cold-producing medium was carried out cold circulation.

(3) summer quick productive life hot water

The second flow direction control valve 7-2, the 9th flow direction control valve 7-9 and the tenth flow direction control valve 7-10 close, and the first flow direction control valve 7-1 opens, and throttle mechanism 4 is not worked, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the second commutation node 74, pipeline 61, first check valve 91, behind the high pressure connection end point f and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, enter second throttle mechanism 5 by throttling through piping 32 again, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through piping 42 and carry out indirect heat exchange, after absorbing heat by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the low pressure connection end point e of flow direction converting, the 3rd check valve 93, the second connection end point h of flow direction converting, pipeline 62, the first flow direction control valve 7-1, pipeline 64, the first connection end point g of flow direction converting, the first commutation node 72 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, so far finish one time summer quick productive life hot water circulation.

The second flow direction control valve 7-2 and the tenth flow direction control valve 7-10 close, and the first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 open, and the throttle mechanism 4 and second throttle mechanism 5 be operate as normal all.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the second commutation node 74, pipeline 61, first check valve 91, behind the high pressure connection end point f and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, entering pipeline 32 again is divided into two the tunnel: the one tunnel and enters second throttle mechanism 5 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through piping 42 and carry out indirect heat exchange, after absorbing heat by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, more successively through piping 41, the low pressure connection end point e of flow direction converting, the 3rd check valve 93, the second connection end point h of flow direction converting, pipeline 62, the first flow direction control valve 7-1 enters pipeline 64; Another road enters throttle mechanism 4 by throttling through the 9th flow direction control valve 7-9, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter user side heat exchanger 3, absorb user's heat therein by indirect heat exchange, be user's cooling, after cold-producing medium absorbs user's heat, become the low-temperature low-pressure refrigerant steam, also enter pipeline 64, after first via refrigerant mixed, again through piping 64, the first connection end point g of flow direction converting, the first commutation node 72 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, and so far finishing summer needs the circulation of refrigeration and productive life hot water simultaneously by the user.

(5) heat merely winter

The first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 close, and the second flow direction control valve 7-2 and the tenth flow direction control valve 7-10 open, throttle mechanism 4 standard-sized sheets, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the first commutation node 72, the first connection end point g of flow direction converting, pipeline 64 laggard access customer side heat exchangers 3, emit heat by indirect heat exchange therein, be user's heat supply, after cold-producing medium is emitted heat, become high-temperature high-pressure refrigerant liquid, refrigerant liquid passes through throttle mechanism 4 again, the second flow direction control valve 7-2, pipeline 62, the second connection end point h of flow direction converting, the 4th check valve 94, the high pressure connection end point f of flow direction converting, pipeline 31, the tenth flow direction control valve 7-10 enters second throttle mechanism 5 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 again and carry out indirect heat exchange, after absorbing heat by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the low pressure connection end point e of flow direction converting, second check valve 92, pipeline 61, the second commutation node 74 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, and so far finishes a simple heating circulation in winter.

Winter, simple heating also had alternative plan, that is: the first flow direction control valve 7-1 and the second flow direction control valve 7-2 close, the 9th flow direction control valve 7-9 opens, the tenth flow direction control valve 7-10 does not work, throttle mechanism 4 standard-sized sheets, second throttle mechanism, 5 operate as normal also can realize simple heating circulation in winter.Its course of work is no longer carefully stated.

The first flow direction control valve 7-1, the 9th flow direction control valve 7-9 and the tenth flow direction control valve 7-10 close, and the second flow direction control valve 7-2 opens, throttle mechanism 4 standard-sized sheets, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the first commutation node 72, the first connection end point g of flow direction converting, pipeline 64 laggard access customer side heat exchangers 3, emit heat by indirect heat exchange therein, be user's heat supply, after cold-producing medium is emitted heat, become high-temperature high-pressure refrigerant liquid, refrigerant liquid passes through throttle mechanism 4 again, the second flow direction control valve 7-2, pipeline 62, the second connection end point h of flow direction converting, the 4th check valve 94, behind the high pressure connection end point f and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, reclaim the sensible heat of high temperature refrigerant liquid, and cold-producing medium is emitted behind the heat by cold excessively, the cold-producing medium of crossing after cold enters second throttle mechanism 5 by throttling through piping 32, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through piping 42 again and carry out indirect heat exchange, after absorbing heat by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the low pressure connection end point e of flow direction converting, second check valve 92, pipeline 61, the second commutation node 74 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, and so far finishes a heat supply in winter and reclaims high temperature refrigerant liquid sensible heat simultaneously and cold-producing medium was carried out cold circulation.

(7) winter quick productive life hot water

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the first commutation node 72, the first connection end point g of flow direction converting, pipeline 64, the first flow direction control valve 7-1, pipeline 62, the second connection end point h of flow direction converting, the 4th check valve 94, behind the high pressure connection end point f and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, enter second throttle mechanism 5 by throttling through piping 32 again, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through piping 42 and carry out indirect heat exchange, after absorbing heat by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the low pressure connection end point e of flow direction converting, second check valve 92, pipeline 61, the second commutation node 74 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, so far finish one time winter quick productive life hot water circulation.

The second flow direction control valve 7-2 and the tenth flow direction control valve 7-10 close, and the first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 open, throttle mechanism 4 standard-sized sheets, second throttle mechanism, 5 operate as normal.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the first commutation node 72, behind the first connection end point g and pipeline 64 of flow direction converting, be divided into two the tunnel: lead up to the first flow direction control valve 7-1, pipeline 62, the second connection end point h of flow direction converting, the 4th check valve 94, behind the high pressure connection end point f and pipeline 31 of flow direction converting, enter second heat exchanger 6 and carry out indirect heat exchange with water, produce low-temperature water heating, and refrigerant vapour becomes refrigerant liquid after emitting heat, enters pipeline 32; Another road enters user side heat exchanger 3, emit heat by indirect heat exchange therein, be user's heat supply, after cold-producing medium is emitted heat, become high-temperature high-pressure refrigerant liquid, refrigerant liquid also enters pipeline 32 through throttle mechanism 4 and the 9th flow direction control valve 7-9 again, after first via refrigerant liquid mixes, enter second throttle mechanism 5 again by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through piping 42 and carry out indirect heat exchange, after absorbing heat by indirect heat exchange therein, become the low-temperature low-pressure refrigerant steam, again successively through piping 41, the low pressure connection end point e of flow direction converting, second check valve 92, pipeline 61, the second commutation node 74 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, and so far finishes the circulation that a time need heating simultaneously and productive life hot water winter by the user.

(9) defrost from user's draw heat winter

The first flow direction control valve 7-1 and the 9th flow direction control valve 7-9 close, and the second flow direction control valve 7-2 and the tenth flow direction control valve 7-10 open, throttle mechanism 4 operate as normal, second throttle mechanism, 5 standard-sized sheets.Its workflow with summer simple kind of refrigeration cycle identical.

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the second commutation node 74, pipeline 61, first check valve 91, the high pressure connection end point f of flow direction converting, pipeline 31, the tenth flow direction control valve 7-10, behind second throttle mechanism 5 and the pipeline 42, entering heat source side heat exchanger 2 defrosts, refrigerant vapour becomes refrigerant liquid after emitting heat, refrigerant liquid is again through piping 41, the low pressure connection end point e of flow direction converting, the 3rd check valve 93, the second connection end point h of flow direction converting, pipeline 62, the second flow direction control valve 7-2 enters throttle mechanism 4 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter user side heat exchanger 3, draw user's heat therein by indirect heat exchange, after cold-producing medium is drawn user's heat, become the low-temperature low-pressure refrigerant steam, through piping 64, the first connection end point g of flow direction converting, the first commutation node 72 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1 and is compressed, and so far finishes the circulation that a time defrost from user's draw heat winter.

In running, the tenth flow direction control valve 7-10 can also utilize it that the water temperature of second heat exchanger 6 is controlled except the function that helps realization simple refrigeration in summer and winter frost removing.In when control, do not enter second heat exchanger 6 fully in order to make cold-producing medium, also can establish a flow direction control valve and second heat exchanger 6 is connected in series, the tenth flow direction control valve 7-10 and they are connected in parallel.

When practical application,, also can not establish the tenth flow direction control valve 7-10 when heat pump does not need simple refrigeration the and during function of winter frost removing in summer.

When practical application, first check valve 91, second check valve 92, the 3rd check valve 93 and the 4th check valve 94 also can be magnetic valves.At this moment, scheme shown in Figure 5 can not established the tenth flow direction control valve 7-10, also can realize embodiment 1 described all functions.

In the above-mentioned technical scheme of embodiment 1 and embodiment 2, when during as low-temperature heat source, during winter operation, defrosting with indoor exhaust wind, soil, water or solar energy etc.;

User side heat exchanger 3 can be cold-producing medium-air heat exchanger, also can be the heat exchanger of cold-producing medium-water-to-water heat exchanger or other kind;

When second heat exchanger 6 is cold-producing medium-water-to-water heat exchangers, when being used to produce low-temperature water heating, heat source side heat exchanger 2 can be cold-producing medium-soil heat exchange device, cold-producing medium-water-to-water heat exchanger, also can be evaporating heat exchanger, can also be solar thermal collector, in addition, also can be the heat exchanger of cold-producing medium-air heat exchanger or other kind;

In addition, in application process, second heat exchanger 6 can be heat exchangers of other kind according to the needs that use also..

Embodiment 3

Shown in Figure 6 is the air condition by dehumidifying, evaporative cooling solution device of second kind of refrigerant flow direction converting of a kind of use.It comprises: evaporimeter 8, throttle mechanism 4, second throttle mechanism 5, direct heat exchanger 24, working medium pump 26, evaporative heat exchanger 27, solution cooler 11, regenerator 13, concentrated solution pump 14, solution heat exchanger 15, dehumidifier 17, weak solution pump 18 and heater 21, in addition, also comprise second kind of refrigerant flow direction converting.

Two groups of heat exchangers are arranged in the evaporative heat exchanger 27, and one group is cooling heat exchanger 43, and another group is condensing heat exchanger 44; When practical application, evaporative heat exchanger 27 also may be split into two evaporative heat exchangers, and cooling heat exchanger 43 and condensing heat exchanger 44 are located at respectively in these two evaporative heat exchangers.

During summer operation, throttle mechanism 4 operate as normal, second throttle mechanism, 5 standard-sized sheets, the 5th flow direction control valve 53-1 standard-sized sheet, the 3rd flow direction control valve 53-3 closes.Its workflow is:

The refrigerant liquid that comes out from direct heat exchanger 24, it is pressurized to enter working medium pump 26 through piping 46, refrigerant liquid after the pressurization enters the cooling heat exchanger 43 of evaporative heat exchanger 27 through second throttle mechanism 5, carry out indirect heat exchange with indoor exhaust wind and recirculated cooling water, after cold-producing medium is emitted heat, by cold excessively, after crossing refrigerant liquid after cold and coming out from the cooling heat exchanger 43 of evaporative heat exchanger 27, be divided into three the tunnel through piping 28: first via refrigerant liquid is through piping 31, the low pressure connection end point e of flow direction converting, the 3rd check valve 93, behind the second connection end point h and pipeline 62 of flow direction converting, enter throttle mechanism 4 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter evaporimeter 8 again, carried out heat exchange with dehumidifier 17 comes out by dehumidified air therein, the temperature that makes it be cooled to require, and behind the heat of cold-producing medium absorption air, become the low-temperature low-pressure refrigerant steam, again through piping 64, the first connection end point g of flow direction converting, the first commutation node 72 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor. after the refrigerant superheat steam comes out from compressor 1, successively through piping 60, the high pressure node 71 of cross valve 70, the second commutation node 74, pipeline 61, first check valve 91, behind the high pressure connection end point f and pipeline 41 of flow direction converting, enter the condensing heat exchanger 44 of evaporative heat exchanger 27, carry out indirect heat exchange with air and recirculated cooling water, after the refrigerant superheat steam is emitted heat, be condensed into liquid, refrigerant liquid is got back to direct heat exchanger 24 again through piping 42 after coming out from condensing heat exchanger 44 again; The second road refrigerant liquid enters solution cooler 11 through the 5th flow direction control valve 53-1 and pipeline 30, carry out indirect heat exchange with solution, the heat of absorbent solution makes its cooling, after the heat absorption of refrigerant liquid level pressure, partly or all vaporize, get back to direct heat exchanger 24 again through piping 32; The Third Road refrigerant liquid is also got back to direct heat exchanger 24 through the 5th flow direction control valve 53-1, pipeline 29, control valve 25, the cold-producing medium of getting back to direct heat exchanger 24 with the first via and the second tunnel directly contacts mixing, carry out heat exchange, make them be condensed into saturated liquid, himself is because of absorbing heat, also become saturated liquid, so far cold-producing medium is finished once simultaneously the refrigeration cool cycles to air, solution and cold-producing medium self.

During winter operation, throttle mechanism 4 standard-sized sheets, second throttle mechanism, 5 operate as normal, the 5th flow direction control valve 53-1 closes, the 3rd flow direction control valve 53-3 standard-sized sheet.Its workflow is:

During work, the low-temperature low-pressure refrigerant steam is after piping 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, superheated vapor is successively through piping 60, the high pressure node 71 of cross valve 70, the first commutation node 72, behind the first connection end point g and pipeline 64 of flow direction converting, enter evaporimeter 8, carry out heat exchange with the air behind being heated of coming out of dehumidifier 17 and the humidification, its temperature is further raise, after meeting the requirements of temperature, send into air-conditioned room, after the refrigerant superheat steam is emitted its heat, become refrigerant liquid, after refrigerant liquid comes out from evaporimeter 8, through throttle mechanism 4, pipeline 62, the second connection end point h of flow direction converting, the 4th check valve 94, behind the high pressure connection end point f and pipeline 41 of flow direction converting, enter the condensing heat exchanger 44 of evaporative heat exchanger 27, carry out indirect heat exchange with air, quilt is cold excessively after emitting its heat, the refrigerant liquid of crossing after cold enters direct heat exchanger 24 through piping 42, after crossing cold refrigerant liquid and coming out from direct heat exchanger 24, through piping 46, pipeline 45, the 3rd flow direction control valve 53-3 enters second throttle mechanism 5 by throttling, cold-producing medium after the throttling becomes the low-temp low-pressure gas-fluid two-phase mixture, enter the cooling heat exchanger 43 of evaporative heat exchanger 27, carry out heat exchange with indoor exhaust wind, after absorbing the heat of air, become the low-temperature low-pressure refrigerant steam, after refrigerant vapour comes out from the cooling heat exchanger 43 of evaporative heat exchanger 27, through piping 28, pipeline 31, the low pressure connection end point e of flow direction converting, second check valve 92, pipeline 61, the second commutation node 74 of cross valve 70, low pressure node 73, pipeline 63 enters compressor 1, be compressed into the high-temperature high-pressure refrigerant superheated vapor, so far cold-producing medium is finished recuperation of heat circulation.

In native system, the effect of control valve 25 is for better assignment system cryogen fluid flow, prevents the refrigerant liquid short circuit, and most of direct heat exchanger 24 that flows into makes solution cooler 11 can not get required flow.

The 5th flow direction control valve 53-1 and the 3rd flow direction control valve 53-3 can be check valves.

In actual application, second throttle mechanism 5 also can be arranged on direct heat exchanger 24 and the pipeline 46 that working medium pump 26 links to each other; Can also be arranged on direct heat exchanger 24 and the pipeline 42 that the condensing heat exchanger 44 of evaporative heat exchanger 27 links to each other, at this moment, the 5th flow direction control valve 53-1 can be set.In above scheme, on the low pressure connection end point e that throttle mechanism 4 also can be arranged on flow direction converting and the pipeline 31 that pipeline 28 links to each other.

In system, working medium pump 26 suction sides and to extrude the purpose of establishing by-pass line 45 and the 3rd flow direction control valve 53-3 between the end be in the cyclic process in the winter time reduce the flow resistance of cold-producing medium in pipeline.For above scheme, also can not establish the 3rd flow direction control valve 53-3.

For embodiment 3 described schemes, second throttle mechanism 5, the 5th flow direction control valve 53-1 and the 3rd flow direction control valve 53-3 also can be set, throttle mechanism 4 operate as normal all in summer in the winter course of work.Circulation time in the winter time, the condensing heat exchanger 44 of evaporative heat exchanger 27 and cooling heat exchanger 43 all become and are evaporimeter, low-temperature low-pressure refrigerant gas-fluid two-phase mixture and indoor exhaust wind or outdoor air or both mixing airs carry out indirect heat exchange therein, absorb the heat of air.In this scheme, throttle mechanism 4 can only be arranged on the second connection end point h and the pipeline 62 between the evaporimeter 8 of flow direction converting.

For the above scheme, solution cooler 11 also can be arranged on dehumidifier 17 inside, is combined into an integral body with dehumidifier 17, constitutes the internally cooled dehumidifier, and at this moment, solution cooler 11 becomes the internally cooled dehumidifier; For two-stage air condition by dehumidifying, evaporative cooling solution device, evaporimeter 8 can be the solution cooler of second dehumidifier, and evaporimeter 8 also can be the internally cooled dehumidifier in addition.

When evaporimeter 8 becomes the internally cooled dehumidifier, can realize two stage dehumidify, finish cooling simultaneously to air.Summer circulation time, in the internally cooled dehumidifier, low-temperature low-pressure refrigerant gas-fluid two-phase mixture and weak solution from choke valve 4 are carried out indirect heat exchange, cold-producing medium becomes refrigerant vapour after absorbing its heat, and weak solution is cooled after emitting heat, and simultaneously weak solution also directly contacts with the air that quilt from dehumidifier 17 dehumidifies, carry out the wet exchange of heat, air is dehumidified once more, and the temperature that makes air be cooled to require simultaneously is sent to air-conditioned room again.Winter circulation time, the solution of internally cooled dehumidifier is out of service, it becomes cold-producing medium-air heat exchanger, therein, from the high-temperature high-pressure refrigerant superheated vapor of compressor 1 with from dehumidifier 17 be heated with humidification after air carry out indirect heat exchange, air is heated once more, meet the requirements of temperature after, be sent to air-conditioned room again, and refrigerant vapour is condensed into liquid after emitting heat.

For two-stage air condition by dehumidifying, evaporative cooling solution device, the first order internally cooled dehumidifier that solution cooler 11 and dehumidifier 17 are formed, with the second level internally cooled dehumidifier that evaporimeter 8 is constituted, can be combined into an integral body, provide air by at least one air driven equipment.

In above-mentioned technical scheme: throttle mechanism can be an electric expansion valve; All flow direction control valves can be magnetic valves; Described check valve also can be a magnetic valve; Compressor 1 can be a frequency-changeable compressor.

Claims

1, a kind of refrigerant flow direction converting, comprise cross valve (80), it is characterized in that: further comprising four check valves, i.e. first check valve (9A), second check valve (9B), the 3rd check valve (9C) and the 4th check valve (9D), four connection end points are arranged, i.e. first connection end point (a), second connection end point (b), the 3rd connection end point (c) and the 4th connection end point (d), the high pressure node (81) of described cross valve (80) links to each other with first check valve (9A) port of export, first check valve (9A) arrival end links to each other with first connection end point (a), the low pressure node (83) of cross valve (80) links to each other with the 3rd check valve (9C) arrival end, the 3rd check valve (9C) port of export links to each other with second connection end point (b), second check valve (9B) port of export links to each other with pipeline between first connection end point (a) and first check valve (9A) arrival end, second check valve (9B) arrival end links to each other with the low pressure node (83) of cross valve (80) and the pipeline between the 3rd check valve (9C) arrival end, the 4th check valve (9D) arrival end links to each other with pipeline between second connection end point (b) and the 3rd check valve (9C) port of export, the 4th check valve (9D) port of export links to each other with the high pressure node (81) of cross valve (80) and the pipeline between first check valve (9A) port of export, any one of (80) two commutations of the 3rd connection end point (c) and cross valve node links to each other, and the 4th connection end point (d) links to each other with another commutation node of cross valve (80).

2, refrigerant flow direction converting according to claim 1 is characterized in that described cross valve (80) is meant the air conditioner refrigerating cross valve.

3, a kind of refrigerant flow direction converting, comprise compressor (1), cross valve (70), it is characterized in that: further comprising four check valves, i.e. first check valve (91), second check valve (92), the 3rd check valve (93) and the 4th check valve (94), four connection end points are arranged, i.e. first connection end point (g), second connection end point (h), high pressure connection end point (f) and low pressure connection end point (e), the high pressure node (71) of described cross valve (70) links to each other with compressor (1) port of export by pipeline (60), the low pressure node (73) of cross valve (70) links to each other with compressor (1) arrival end by pipeline (63), any one of (70) two commutations of cross valve node links to each other with first connection end point (g), another commutation node of cross valve (70) links to each other with first check valve (91) arrival end by pipeline (61), first check valve (91) port of export links to each other with the 4th check valve (94) port of export, the 4th check valve (94) arrival end links to each other with second connection end point (h), second check valve (92) port of export links to each other with pipeline (61) between cross valve (70) and first check valve (91) arrival end, second check valve (92) arrival end links to each other with the 3rd check valve (93) arrival end, the 3rd check valve (93) port of export links to each other with pipeline between the 4th check valve (94) arrival end and second connection end point (h), high pressure connection end point (f) links to each other with pipeline between first check valve (91) port of export and the 4th check valve (94) port of export, and low pressure connection end point (e) links to each other with pipeline between second check valve (92) arrival end and the 3rd check valve (93) arrival end.

4, refrigerant flow direction converting according to claim 3, it is characterized in that described cross valve (70) is meant the air conditioner refrigerating cross valve, first check valve (91) arrival end and second check valve (92) port of export link to each other with commutate any one of node of (70) two of cross valves by pipeline is common, constitute the circulation loop of an one-way flow between high pressure connection end point (f) and the low pressure connection end point (e), between first connection end point (g) and second connection end point (h) one of formation can switch as required, the circulation loop of two-way flow.

5, the application of the described refrigerant flow direction converting of a kind of claim 1, comprise compressor (1), second cross valve (100), heat source side heat exchanger (2), user side heat exchanger (3), throttle mechanism (4), it is characterized in that: further comprising second throttle mechanism (5), second heat exchanger (6), first flow direction control valve (7-1), second flow direction control valve (7-2), the 9th flow direction control valve (7-9), first check valve (9A), second check valve (9B), the 3rd check valve (9C), the 4th check valve (9D) and cross valve (80), the high pressure node (81) of described cross valve (80) links to each other with first check valve (9A) port of export, first check valve (9A) arrival end links to each other with first connection end point (a), the low pressure node (83) of cross valve (80) links to each other with the 3rd check valve (9C) arrival end, the 3rd check valve (9C) port of export links to each other with second connection end point (b), second check valve (9B) port of export links to each other with pipeline between first connection end point (a) and first check valve (9A) arrival end, second check valve (9B) arrival end links to each other with the low pressure node (83) of cross valve (80) and the pipeline between the 3rd check valve (9C) arrival end, the 4th check valve (9D) arrival end links to each other with pipeline between second connection end point (b) and the 3rd check valve (9C) port of export, the 4th check valve (9D) port of export links to each other with the high pressure node (81) of cross valve (80) and the pipeline between first check valve (9A) port of export, any one of (80) two commutations of the 3rd connection end point (c) and cross valve node links to each other, the 4th connection end point (d) links to each other with another commutation node of cross valve (80), described the 3rd connection end point (c) links to each other with second heat exchanger (6) one ends, second heat exchanger (6) other end links to each other with heat source side heat exchanger (2) one ends by second throttle mechanism (5), heat source side heat exchanger (2) other end links to each other with the 4th connection end point (d), described first connection end point (a) links to each other by any one of (100) two commutations of the pipeline (61) and second cross valve node, the high pressure node (101) of second cross valve (100) links to each other with compressor (1) port of export by pipeline (60), the low pressure node (103) of second cross valve (100) links to each other with compressor (1) arrival end by pipeline (63), another commutation node of second cross valve (100) links to each other with user side heat exchanger (3) one ends by pipeline (64), user side heat exchanger (3) other end is successively by throttle mechanism (4), second flow direction control valve (7-2), pipeline (62) links to each other with described second connection end point (b), first flow direction control valve (7-1) end links to each other with pipeline (64) between second cross valve (100) and the user side heat exchanger (3), first flow direction control valve (7-1) other end links to each other with pipeline (62) between second connection end point (b) and second flow direction control valve (7-2), the 9th flow direction control valve (7-9) end links to each other with pipeline between throttle mechanism (4) and second flow direction control valve (7-2), and the 9th flow direction control valve (7-9) other end links to each other with pipeline between second throttle mechanism (5) and second heat exchanger (6);

Or described the 3rd connection end point (c) links to each other with heat source side heat exchanger (2) one ends, heat source side heat exchanger (2) other end links to each other with second heat exchanger (6) one ends by second throttle mechanism (5), and second heat exchanger (6) other end links to each other with the 4th connection end point (d).

6, the application of the described refrigerant flow direction converting of a kind of claim 3, it comprises compressor (1), heat source side heat exchanger (2), user side heat exchanger (3), throttle mechanism (4) and cross valve (70), it is characterized in that: further comprising second throttle mechanism (5), second heat exchanger (6), first flow direction control valve (7-1), second flow direction control valve (7-2), the 9th flow direction control valve (7-9), first check valve (91), second check valve (92), the 3rd check valve (93) and the 4th check valve (94), the high pressure node (71) of described cross valve (70) links to each other with compressor (1) port of export by pipeline (60), the low pressure node (73) of cross valve (70) links to each other with compressor (1) arrival end by pipeline (63), any one of (70) two commutations of cross valve node links to each other with first connection end point (g), another commutation node of cross valve (70) links to each other with first check valve (91) arrival end by pipeline (61), first check valve (91) port of export links to each other with the 4th check valve (94) port of export, the 4th check valve (94) arrival end links to each other with second connection end point (h), second check valve (92) port of export links to each other with pipeline (61) between cross valve (70) and first check valve (91) arrival end, second check valve (92) arrival end links to each other with the 3rd check valve (93) arrival end, the 3rd check valve (93) port of export links to each other with pipeline between the 4th check valve (94) arrival end and second connection end point (h), high pressure connection end point (f) links to each other with pipeline between first check valve (91) port of export and the 4th check valve (94) port of export, low pressure connection end point (e) links to each other with pipeline between second check valve (92) arrival end and the 3rd check valve (93) arrival end, described first connection end point (g) links to each other with user side heat exchanger (3) one ends by pipeline (64), user side heat exchanger (3) other end is successively by throttle mechanism (4), second flow direction control valve (7-2), pipeline (62) links to each other with second connection end point (h), high pressure connection end point (f) links to each other with second heat exchanger (6) one ends by pipeline (31), second heat exchanger (6) other end links to each other with second throttle mechanism (5) one ends, second throttle mechanism (5) other end links to each other with heat source side heat exchanger (2) one ends by pipeline (42), heat source side heat exchanger (2) other end links to each other with low pressure connection end point (e) by pipeline (41), first flow direction control valve (7-1) end links to each other with pipeline (64) between first connection end point (g) and the user side heat exchanger (3), first flow direction control valve (7-1) other end links to each other with pipeline (62) between second connection end point (h) and second flow direction control valve (7-2), the 9th flow direction control valve (7-9) end links to each other with pipeline between throttle mechanism (4) and second flow direction control valve (7-2), and the 9th flow direction control valve (7-9) other end links to each other with pipeline between second throttle mechanism (5) and second heat exchanger (6);

Or set up the tenth flow direction control valve (7-10), the tenth flow direction control valve (7-10) end links to each other with pipeline (31) between high pressure connection end point (f) and second heat exchanger (6), and the tenth flow direction control valve (7-10) other end links to each other with pipeline between second throttle mechanism (5) and second heat exchanger (6).

7, the application of refrigerant flow direction converting according to claim 6 is characterized in that described check valve is a magnetic valve.

8, the application of the described refrigerant flow direction converting of a kind of claim 3, it comprises compressor (1), evaporimeter (8), throttle mechanism (4), direct heat exchanger (24), working medium pump (26), evaporative heat exchanger (27), solution cooler (11), regenerator (13), dehumidifier (17) and heater (21), above-mentioned said evaporative heat exchanger (27) is made up of one group of cooling heat exchanger (43) and one group of condensing heat exchanger (44), it is characterized in that: further comprising cross valve (70), first check valve (91), second check valve (92), the 3rd check valve (93) and the 4th check valve (94), the high pressure node (71) of described cross valve (70) links to each other with compressor (1) port of export by pipeline (60), the low pressure node (73) of cross valve (70) links to each other with compressor (1) arrival end by pipeline (63), any one of (70) two commutations of cross valve node links to each other with first connection end point (g), another commutation node of cross valve (70) links to each other with first check valve (91) arrival end by pipeline (61), first check valve (91) port of export links to each other with the 4th check valve (94) port of export, the 4th check valve (94) arrival end links to each other with second connection end point (h), second check valve (92) port of export links to each other with pipeline (61) between cross valve (70) and first check valve (91) arrival end, second check valve (92) arrival end links to each other with the 3rd check valve (93) arrival end, the 3rd check valve (93) port of export links to each other with pipeline between the 4th check valve (94) arrival end and second connection end point (h), high pressure connection end point (f) links to each other with pipeline between first check valve (91) port of export and the 4th check valve (94) port of export, low pressure connection end point (e) links to each other with pipeline between second check valve (92) arrival end and the 3rd check valve (93) arrival end, described first connection end point (g) links to each other with evaporimeter (8) one ends by pipeline (64), evaporimeter (8) other end links to each other with second connection end point (h) with pipeline (62) by throttle mechanism (4), described high pressure connection end point (f) links to each other with condensing heat exchanger (44) one ends of evaporative heat exchanger (27) by pipeline (41), condensing heat exchanger (44) other end of evaporative heat exchanger (27) links to each other with direct heat exchanger (24) by pipeline (42), direct heat exchanger (24) is successively by pipeline (46), working medium pump (26) links to each other with cooling heat exchanger (43) one ends of evaporative heat exchanger (27), cooling heat exchanger (43) other end of evaporative heat exchanger (27) links to each other with pipeline (28), pipeline (28) is divided into three the tunnel: the pipeline (31) of leading up to links to each other with described low pressure connection end point (e), another road links to each other with direct heat exchanger (24) by pipeline (29), and Third Road is successively by pipeline (30), solution cooler (11), pipeline (32) links to each other with direct heat exchanger (24);

Or the 3rd flow direction control valve (53-3) and working medium pump (26) are set are connected in parallel;

Or set up second throttle mechanism (5), second throttle mechanism (5) is arranged on direct heat exchanger (24) and the pipeline (42) that the condensing heat exchanger (44) of evaporative heat exchanger (27) links to each other;

Or set up second throttle mechanism (5) and the 5th flow direction control valve (53-1), second throttle mechanism (5) is arranged on the pipeline between cooling heat exchanger (43) three of direct heat exchanger (24), working medium pump (26) and evaporative heat exchanger (27), the 5th flow direction control valve (53-1) end is connected with pipeline (28,31), and the 5th flow direction control valve (53-1) other end is connected with pipeline (29,30);

Or set up the 3rd flow direction control valve (53-3) and second throttle mechanism (5), the 3rd flow direction control valve (53-3) and working medium pump (26) are connected in parallel, and second throttle mechanism (5) is arranged on direct heat exchanger (24) and the pipeline (42) that the condensing heat exchanger (44) of evaporative heat exchanger (27) links to each other;

Or set up the 3rd flow direction control valve (53-3), second throttle mechanism (5) and the 5th flow direction control valve (53-1), the 3rd flow direction control valve (53-3) is connected in parallel with working medium pump (26), second throttle mechanism (5) is arranged on the pipeline between cooling heat exchanger (43) three of direct heat exchanger (24), the 3rd flow direction control valve (53-3) and evaporative heat exchanger (27), the 5th flow direction control valve (53-1) end is connected with pipeline (28,31), and the 5th flow direction control valve (53-1) other end is connected with pipeline (29,30);

Or described throttle mechanism (4) is arranged on low pressure connection end point (e) and the pipeline (31) that pipeline (28) links to each other, set up second throttle mechanism (5), second throttle mechanism (5) is arranged on direct heat exchanger (24) and the pipeline (42) that the condensing heat exchanger (44) of evaporative heat exchanger (27) links to each other;

Or described throttle mechanism (4) is arranged on low pressure connection end point (e) and the pipeline (31) that pipeline (28) links to each other, set up the 3rd flow direction control valve (53-3) and second throttle mechanism (5), the 3rd flow direction control valve (53-3) and working medium pump (26) are connected in parallel, and second throttle mechanism (5) is arranged on direct heat exchanger (24) and the pipeline (42) that the condensing heat exchanger (44) of evaporative heat exchanger (27) links to each other;

Or described throttle mechanism (4) is arranged on low pressure connection end point (e) and the pipeline (31) that pipeline (28) links to each other, set up second throttle mechanism (5) and the 5th flow direction control valve (53-1), second throttle mechanism (5) is arranged on the pipeline between cooling heat exchanger (43) three of direct heat exchanger (24), working medium pump (26) and evaporative heat exchanger (27), the 5th flow direction control valve (53-1) end links to each other with pipeline (28,31), and the 5th flow direction control valve (53-1) other end links to each other with pipeline (29,30);

Or described throttle mechanism (4) is arranged on low pressure connection end point (e) and the pipeline (31) that pipeline (28) links to each other, set up the 3rd flow direction control valve (53-3), second throttle mechanism (5) and the 5th flow direction control valve (53-1), the 3rd flow direction control valve (53-3) is connected in parallel with working medium pump (26), second throttle mechanism (5) is arranged at direct heat exchanger (24), on the pipeline between cooling heat exchanger (43) three of the 3rd flow direction control valve (53-3) and evaporative heat exchanger (27), the 5th flow direction control valve (53-1) end and pipeline (28,31) be connected the 5th flow direction control valve (53-1) other end and pipeline (29,30) be connected.

9, the application of refrigerant flow direction converting according to claim 8 is characterized in that described solution cooler (11) is the internally cooled dehumidifier.

10, the application of refrigerant flow direction converting according to claim 8 is characterized in that described evaporimeter (8) is solution cooler or internally cooled dehumidifier.

11,, it is characterized in that described second heat exchanger (6) is cold-producing medium-water-to-water heat exchanger according to the application of claim 5 or 6 described refrigerant flow direction convertings.