CN101625175A - Multifunctional air-condition heat pump device of single-double level compression and capable of free switch - Google Patents
Multifunctional air-condition heat pump device of single-double level compression and capable of free switch Download PDFInfo
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- CN101625175A CN101625175A CN200910023490A CN200910023490A CN101625175A CN 101625175 A CN101625175 A CN 101625175A CN 200910023490 A CN200910023490 A CN 200910023490A CN 200910023490 A CN200910023490 A CN 200910023490A CN 101625175 A CN101625175 A CN 101625175A
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Abstract
The invention comprises a multifunctional air-condition heat pump device which comprises a compressing mechanism, a hot source side heat exchanger, a user side heat exchanger, a second heat exchanger, a first throttling mechanism, a second throttling mechanism, a first four-way reversing device, a second four-way reversing device, a first flow direction control valve, a second flow direction control valve, and a ninth flow direction control valve; the multifunctional air-condition heat pump device is characterized in that the compressing mechanism comprises a low-pressure compression engine, a high-pressure compression engine, a first one-way valve and a second one-way valve; when in operation, the heat pump device can realize the free switching of the single-double level compression according to requirements, can implement more accurate control on heating amount and cooling amount or cooled medium and heated medium, has simple structure and low cost, is reliable in work and particularly suitable for civil small and medium size occasions with life hot-water requirements.
Description
Technical field
The present invention relates to a kind of multifunctional air-condition heat pump device, belong to refrigeration technology field.
Background technology
Application number is respectively five patents of invention of 200710162570.0,200710305376.3,200810100059.2,200810175176.5,200810177703.6, all relate to a kind of multifunctional air-condition heat pump device, the condensation heat when this device can be realized refrigeration, heating, productive life hot water, refrigeration according to user's needs in the whole year operation process reclaims, summer freezes simultaneously by user's needs and productive life hot water, winter heat simultaneously by user's needs and multiple function such as productive life hot water.When said apparatus realizes needing simultaneously refrigeration and productive life hot water function by the user in summer, owing to need control heating load and refrigerating capacity simultaneously by customer requirements, or by customer requirements simultaneously to the medium temperature that is cooled (for example: indoor air temperature or chilled water temperature) with the heated medium temperature (for example: the domestic hot-water) control, therefore, said apparatus is when adopting single-stage compressor, because influencing each other between heating load and the refrigerating capacity is simultaneously to heating load and refrigerating capacity, or can't accomplish very accurate to be cooled medium temperature and heated medium temperature controlling.In addition, above-mentioned multifunctional air-condition heat pump device is in order to realize above-mentioned all functions, its compressor will be worked in a very wide compression ratio range, for example: with outdoor air during as low-temperature heat source, when summer, outside air temperature was higher, when said apparatus is used for productive life hot water, its compression ratio is with less, and when winter, outside air temperature was low, said apparatus is when productive life hot water, its compression ratio will be bigger, when said apparatus adopts the twin-stage compression, though can solve the higher problem of bringing of winter operation compression ratio, when summer operation is used for productive life hot water, because compression ratio was just less originally, after said apparatus adopted the twin-stage compression, its hiigh pressure stage compressor and the low-pressure stage compressor compression ratio when work will be littler, therefore, said apparatus adopts twin-stage compression back can propose higher requirement to the performance of compressor, requires each stage compressor to want to keep operate as normal under lower compression ratio.
Summary of the invention
The purpose of this invention is to provide a kind of simple in structure, reliable operation, can realize the multifunctional air-condition heat pump device that single twin-stage compression is freely switched.
In order to overcome the problem that above-mentioned technology exists, the technical scheme of technical solution problem of the present invention is:
1, a kind of multifunctional air-condition heat pump device comprises compressing mechanism, heat source side heat exchanger, user side heat exchanger, second heat exchanger, first throttle mechanism, second throttle mechanism, the first four-way reversing arrangement, the second four-way reversing arrangement, first flow direction control valve, second flow direction control valve, the 9th flow direction control valve; It is characterized in that: described compressing mechanism is made of low pressure compressor, high pressure compressor, first check valve and second check valve; Described low pressure compressor input is connected with the described first four-way reversing arrangement low pressure node by the 63 pipeline, described low pressure compressor output is successively by described high pressure compressor input, the high pressure compressor output, the described second check valve arrival end, the second check valve port of export is connected with the described first four-way reversing arrangement high pressure node, the described first check valve arrival end is connected with pipeline between described low pressure compressor output and the described high pressure compressor input, and the described first check valve port of export is connected with the 60 pipeline between the described second check valve port of export and the described first four-way reversing arrangement high pressure node.
2, a kind of multifunctional air-condition heat pump device comprises compressing mechanism, heat source side heat exchanger, user side heat exchanger, second heat exchanger, first throttle mechanism, second throttle mechanism, the first four-way reversing arrangement, the second four-way reversing arrangement, first flow direction control valve, second flow direction control valve, the 9th flow direction control valve; It is characterized in that: described compressing mechanism is made of low pressure compressor, high pressure compressor, first check valve and second check valve; Described low pressure compressor input is connected with the described first four-way reversing arrangement low pressure node by the 63 pipeline, described low pressure compressor output is connected with the described first four-way reversing arrangement high pressure node by the described second check valve arrival end, the second check valve port of export, described high pressure compressor input, high pressure compressor output successively, the described first check valve arrival end is connected with described low pressure compressor input, and the described first check valve port of export is connected with pipeline between the described second check valve port of export and the described high pressure compressor input.
The present invention compared with prior art, its beneficial effect is:
1. can realize freely switching of single twin-stage compression as required;
2. when summer operation, can implement more accurate control to refrigerating capacity and heating load or to the temperature of be cooled medium and heated medium;
3. simple in structure, reliable operation, with low cost;
4. the present invention is applicable to industry and civilian multifunctional air-condition heat pump device, is specially adapted to the air-condition heat pump device of the civilian middle-size and small-size domestic hot-water's of having demand.
Description of drawings
Fig. 1 is the embodiment of the invention 1 structural representation;
Fig. 2 is the embodiment of the invention 2 structural representations;
Fig. 3 is the embodiment of the invention 1 an improvement project structural representation;
Fig. 4 is the embodiment of the invention 1 an improvement project structural representation;
Fig. 5 is the embodiment of the invention 1 an improvement project structural representation;
Fig. 6 is the embodiment of the invention 2 improvement project structural representations;
Fig. 7 is the embodiment of the invention 2 improvement project structural representations;
Fig. 8 is the embodiment of the invention 2 improvement project structural representations;
Fig. 9 is the embodiment of the invention 3 structural representations;
Figure 10 is the embodiment of the invention 4 structural representations;
Figure 11 is the embodiment of the invention 5 structural representations;
Figure 12 is the improvement project structural representation of the present invention's scheme shown in Figure 4;
Figure 13 is the improvement project structural representation of the present invention's scheme shown in Figure 5;
Figure 14 is the embodiment of the invention 6 structural representations;
Figure 15 is the improvement project structural representation of the present invention's scheme shown in Figure 7;
Figure 16 is the improvement project structural representation of the present invention's scheme shown in Figure 8.
The specific embodiment
Below in conjunction with accompanying drawing content of the present invention is described in further detail.
As shown in Figure 1, whole device comprises following equipment: compressing mechanism 1, heat source side heat exchanger 2, user side heat exchanger 3, second heat exchanger 6, first throttle mechanism 4, second throttle mechanism 5, the first four-way reversing arrangement 110, the second four-way reversing arrangement 120, the first flow direction control valve 7-1, the second flow direction control valve 7-2, the 9th flow direction control valve 7-9; Described compressing mechanism 1 is made up of low pressure compressor 1-1, high pressure compressor 1-2, the first check valve 9A and the second check valve 9B; The first four-way reversing arrangement 110 is that a cross valve 100, the second four-way reversing arrangements 120 are made up of four check valves, and they are respectively the 3rd check valve 91, the 4th check valve 92, the 5th check valve 93 and the 6th check valve 94.
Whole device can be realized freezing merely summer, summer refrigeration reclaims condensation heat productive life hot water simultaneously, summer quick productive life hot water, summer need simultaneously refrigeration by the user and heat merely in productive life hot water, winter, heat supply in winter reclaims high temperature refrigerant liquid sensible heat simultaneously, winter quick productive life hot water, winter need heating simultaneously and productive life hot water, nine kinds of functions of winter frost removing by the user.
Realize freezing merely summer, when summer, refrigeration reclaimed the quick productive life hot water function of condensation heat productive life hot water, summer simultaneously, because compression ratio is less relatively, high pressure compressor 1-2 does not work, low pressure compressor 1-1 isolated operation, independently bear the compression work of cold-producing medium, constitute the single stage compress circulation, therefore, low pressure compressor 1-1 can move under a more moderate relatively compression ratio.During work, the high-temperature high-pressure refrigerant superheated vapor that comes out from low pressure compressor 1-1 output directly enters the 60 pipeline 60 by the first check valve 9A and finishes whole working cycles, and does not enter high pressure compressor 1-2;
Under other function, because compression ratio is relatively large, high pressure compressor 1-2 and low pressure compressor 1-1 work simultaneously, constitute the twin-stage compression cycle, so each stage compressor can move under a more moderate compression ratio.During work, cold-producing medium is without the first check valve 9A, finishes whole working cycles but order enters the 60 pipeline 60 from low pressure compressor 1-1 through high pressure compressor 1-2 and the second check valve 9B.
As shown in Figure 2, be that the connected mode of compressing mechanism 1 is different with the difference of embodiment 1.Realize freezing merely summer, when summer, refrigeration reclaimed the quick productive life hot water function of condensation heat productive life hot water, summer simultaneously, low pressure compressor 1-1 does not work, the compression work of cold-producing medium is independently born in high pressure compressor 1-2 isolated operation, constitutes the single stage compress circulation.During work, directly enter high pressure compressor 1-2 from the low-temperature low-pressure refrigerant steam of the 63 pipeline 63 and be compressed, and do not enter low pressure compressor 1-1 by the first check valve 9A;
Under other function, high pressure compressor 1-2 and low pressure compressor 1-1 work simultaneously, constitute the twin-stage compression cycle.During operation, being introduced into low pressure compressor 1-1 from the low-temperature low-pressure refrigerant steam of the 63 pipeline 63 is compressed, then, entering high pressure compressor 1-2 through the second check valve 9B is again compressed once more, after meeting the requirements of pressure, enter the 60 pipeline 60 and finish whole working cycles, in the course of work, refrigerant vapour is without the first check valve 9A.
Fig. 3 is improvement to scheme shown in the embodiment 1 to scheme shown in Figure 5, Fig. 6 to scheme shown in Figure 8 be improvement to scheme shown in the embodiment 2.After the improvement, can make refrigerant liquid quilt before throttling cold excessively, reduce restriction loss, in addition, under high low temperature operating temperature, can also improve the working environment of air-condition heat pump device, further improve its operating efficiency.
In scheme shown in Figure 3, the economizer 11 low-pressure side ports of export can be connected with the 63 pipeline 63 any places between pipeline between high pressure compressor 1-2 input and the low pressure compressor 1-1 output, low pressure compressor 1-1 compressing mechanism middle part gas supplementing opening, low pressure compressor 1-1 input and the first four-way reversing arrangement, the 110 low pressure nodes 103 by the 7th flow direction control valve 7-7.
In scheme shown in Figure 4, flash vessel 50 can be connected with the 63 pipeline 63 any places between pipeline between high pressure compressor 1-2 input and the low pressure compressor 1-1 output, low pressure compressor 1-1 compressing mechanism middle part gas supplementing opening, low pressure compressor 1-1 input and the first four-way reversing arrangement, the 110 low pressure nodes 103 by the 3rd flow direction control valve 7-3.
In Fig. 5 and scheme shown in Figure 8, low pressure compressor 1-1 input is connected with the low pressure node 103 of the first four-way reversing arrangement 110 by the regenerator 9 low-pressure side ports of export, regenerator 9 low-pressure side arrival ends, the 63 pipeline 63 successively.
In scheme shown in Figure 6, the economizer 11 low-pressure side ports of export can be connected with pipeline, any place of gas supplementing opening, high pressure compressor 1-2 compressing mechanism middle part between pipeline, the second check valve 9B port of export and the high pressure compressor 1-2 input between low pressure compressor 1-1 input, low pressure compressor 1-1 output and the second check valve 9B arrival end by the 7th flow direction control valve 7-7.In Fig. 3 and scheme shown in Figure 6, when the 3rd throttle mechanism 8 has turn-off function, when for example using electric expansion valve, can not establish the 7th flow direction control valve 7-7.
In scheme shown in Figure 7, flash vessel 50 can be connected with pipeline, any place of gas supplementing opening, high pressure compressor 1-2 compressing mechanism middle part between pipeline, the second check valve 9B port of export and the high pressure compressor 1-2 input between low pressure compressor 1-1 input, low pressure compressor 1-1 output and the second check valve 9B arrival end by the 3rd flow direction control valve 7-3.
Embodiment 3
As shown in Figure 9, the difference of it and embodiment 1 is to have increased by one the 6th flow direction control valve 7-6, the 6th flow direction control valve 7-6 one end is connected with pipeline between low pressure compressor 1-1 output and the high pressure compressor 1-2 input, the 6th flow direction control valve 7-6 other end can with the 62 pipeline 62, heat source side heat exchanger 2 and the second four-way reversing arrangement 120 between the first flow direction control valve 7-1 and the second four-way reversing arrangement 120 between the 41 pipeline 41 any one be connected.
Summer, multifunctional air-condition heat pump device of the present invention is when realizing needing simultaneously refrigeration and productive life hot water function by the user, heat source side heat exchanger 2 and user side heat exchanger 3 all become evaporimeter, user side heat exchanger 3 is used for cooling off the medium (for example: room air or chilled water) that is cooled, heat source side heat exchanger 2 is used for from the low-temperature heat source draw heat, the heat that obtains from both places is used for productive life hot water at second heat exchanger 6, when low-temperature heat source is outdoor air, because summer, outside air temperature was high more a lot of than indoor air temperature or chilled water temperature, therefore can adopt different evaporating temperatures, constitute the two stages of compression circulation of the middle tonifying Qi of a band.In this circulation, condensation temperature depends on domestic hot-water's temperature of being produced, evaporating temperature depends on the temperature of the medium that is cooled, and the evaporating temperature at heat source side heat exchanger 2 places depends on outside air temperature, and its corresponding pressure is the middle tonifying Qi pressure of two stages of compression circulation.
During work, the first flow direction control valve 7-1, the second flow direction control valve 7-2, the 11 flow to control valve 7-11 and close, the 6th flow direction control valve 7-6, the 9th flow direction control valve 7-9 open, and low pressure compressor 1-1, high pressure compressor 1-2, first throttle mechanism 4, second throttle mechanism 5 be operate as normal all.
The course of work is as follows: the low-temperature low-pressure refrigerant steam enters low pressure compressor 1-1 through the 63 pipeline 63, be compressed into refrigerant superheat steam under the intermediate pressure, with from after refrigerant vapour mixes under the intermediate pressure of the 6th flow direction control valve 7-6, enter high pressure compressor 1-2 again and be compressed into the high-temperature high-pressure refrigerant superheated vapor, then successively through the second check valve 9B, the 60 pipeline 60, cross valve 100 high pressure nodes 101, commutation node 104, the 61 pipeline 61, the 3rd check valve 91, the 31 pipeline 31 enters second heat exchanger 6 and carries out indirect heat exchange with water, productive life hot water, and refrigerant vapour becomes refrigerant liquid after emitting heat, enter the 32 pipeline 32 again and be divided into two the tunnel, one the tunnel enters first 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 again, absorb the heat of the medium that is cooled therein by indirect heat exchange, be user's cooling, after cold-producing medium absorbs heat, become the low-temperature low-pressure refrigerant steam, through the 64 pipeline 64, another commutation node 102 of cross valve 100, low pressure node 103 enters the 63 pipeline 63, another road enters second throttle mechanism 5 by throttling, cold-producing medium after the throttling becomes the intermediate pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through the 42 pipeline 42 and carry out indirect heat exchange with outdoor air, behind the cold-producing medium absorption chamber outer air heat, become the intermediate pressure refrigerant steam, again successively through the 41 pipeline 41, the 5th check valve 93, the 62 pipeline 62 enters the 6th flow direction control valve 7-6, and so far finishing needs refrigeration and productive life hot water circuit simultaneously by the user summer.
Compare with embodiment 1,, therefore can improve the operational efficiency of whole device owing to reduced low pressure compressor 1-1 input low-temperature low-pressure refrigerant vapor flow rate.
Present embodiment is when realizing other function, and the 6th flow direction control valve 7-6 closes.In actual applications, the 6th flow direction control valve 7-6 can use magnetic valve, also can use throttling arrangement.Described throttling arrangement can be used to control the intermediate pressure between low pressure compressor 1-1 output and the high pressure compressor 1-2 input as required, this throttling arrangement can use electric expansion valve, also can use the combined type throttling arrangement that is in series by fixed restriction element and magnetic valve.
In the present embodiment, when low pressure compressor 1-1 and high pressure compressor 1-2 are the variable-displacement compressor, during summer operation, the low pressure compressor 1-1 of this device can implement control to the refrigerating capacity or the medium temperature that is cooled as required, simultaneously, high pressure compressor 1-2 can implement control to heating load or heated medium temperature as required, therefore can improve the operating efficiency of whole device.
The described scheme of present embodiment also can be used in Fig. 3 to scheme shown in Figure 5.During application, in these schemes, the link position of described the 6th flow direction control valve 7-6 in system is identical with present embodiment, that is: the 6th flow direction control valve 7-6 one end is connected with pipeline between low pressure compressor 1-1 output and the high pressure compressor 1-2 input, between the 62 pipeline 62, heat source side heat exchanger 2 and the second four-way reversing arrangement 120 between the 6th flow direction control valve 7-6 other end and the first flow direction control valve 7-1 and the second four-way reversing arrangement 120 the 41 pipeline 41 any one be connected.
As shown in figure 10, the difference of it and embodiment 2 is to have increased by one the 6th flow direction control valve 7-6.The 6th flow direction control valve 7-6 one end is connected with pipeline between the second check valve 9B port of export and the high pressure compressor 1-2 input, the 6th flow direction control valve 7-6 other end can with the 62 pipeline 62, heat source side heat exchanger 2 and the second four-way reversing arrangement 120 between the first flow direction control valve 7-1 and the second four-way reversing arrangement 120 between the 41 pipeline 41 any one be connected.
The 6th effect of flow direction control valve 7-6 in system, and the function that present embodiment had is identical with embodiment 3.Summer, when realizing needing simultaneously refrigeration and productive life hot water function by the user, the first flow direction control valve 7-1, the second flow direction control valve 7-2, the 11 flow to control valve 7-11 and close, the 6th flow direction control valve 7-6, the 9th flow direction control valve 7-9 open, and low pressure compressor 1-1, high pressure compressor 1-2, first throttle mechanism 4, second throttle mechanism 5 be operate as normal all.
The course of work is as follows: the low-temperature low-pressure refrigerant steam enters low pressure compressor 1-1 through the 63 pipeline 63, be compressed into refrigerant superheat steam under the intermediate pressure, again through the second check valve 9B with from after refrigerant vapour mixes under the intermediate pressure of the 6th flow direction control valve 7-6, enter high pressure compressor 1-2 and be compressed into the high-temperature high-pressure refrigerant superheated vapor, then successively through the 60 pipeline 60, cross valve 100 high pressure nodes 101, commutation node 104, the 61 pipeline 61, the 3rd check valve 91, the 31 pipeline 31 enters second heat exchanger 6 and carries out indirect heat exchange with water, productive life hot water, refrigerant vapour becomes refrigerant liquid after emitting heat, enter the 32 pipeline 32 again and be divided into two the tunnel, one the tunnel enters first 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 again, absorb the heat of the medium that is cooled therein by indirect heat exchange, be user's cooling, after cold-producing medium absorbs heat, become the low-temperature low-pressure refrigerant steam, through the 64 pipeline 64, another commutation node 102 of cross valve 100, low pressure node 103 enters the 63 pipeline 63, another road enters second throttle mechanism 5 by throttling, cold-producing medium after the throttling becomes the intermediate pressure gas-fluid two-phase mixture, enter heat source side heat exchanger 2 through the 42 pipeline 42 and carry out indirect heat exchange with outdoor air, behind the cold-producing medium absorption chamber outer air heat, become the intermediate pressure refrigerant steam, again successively through the 41 pipeline 41, the 5th check valve 93, the 62 pipeline 62 enters the 6th flow direction control valve 7-6, and so far finishing needs refrigeration and productive life hot water circuit simultaneously by the user summer.
Compare with embodiment 2,, therefore can improve the operational efficiency of whole device owing to reduced low pressure compressor 1-1 input low-temperature low-pressure refrigerant vapor flow rate.
The described scheme of present embodiment also can be used in Fig. 6 to scheme shown in Figure 8.During application, in these schemes, the link position of described the 6th flow direction control valve 7-6 in system is identical with present embodiment, that is: the 6th flow direction control valve 7-6 one end is connected with pipeline between the second check valve 9B port of export and the high pressure compressor 1-2 input, between the 62 pipeline 62, heat source side heat exchanger 2 and the second four-way reversing arrangement 120 between the 6th flow direction control valve 7-6 other end and the first flow direction control valve 7-1 and the second four-way reversing arrangement 120 the 41 pipeline 41 any one be connected.
As shown in figure 11, the difference of it and scheme shown in Figure 3 is to have increased a triple valve 13, the seven check valves 95 to use the 8th flow direction control valve 7-8 instead, and described the 8th flow direction control valve 7-8 should have turn-off function.The node A3 that often opens of described triple valve 13 is connected with heat source side heat exchanger 2 by the 49 pipeline 49, any one B3 in 13 2 on the triple valve commutation node is connected with the second four-way reversing arrangement 120 by the 33 pipeline 33, and another node C3 that commutates is connected with the 42 pipeline 42 between second heat exchanger 6 and the 8th flow direction control valve 7-8.
When the second four-way reversing arrangement 120 is the four-way reversing arrangement that is made of the 3rd check valve 91, the 4th check valve 92, the 5th check valve 93 and the 6th check valve 94, present embodiment scheme shown in Figure 11 is compared with scheme shown in Figure 3, can improve freeze merely summer, summer refrigeration reclaims the operating efficiency under the condensation heat productive life hot water function simultaneously.
Present embodiment scheme shown in Figure 11 can be done further improvement by increasing by one the 6th flow direction control valve 7-6, the connectivity scenario of the 6th flow direction control valve 7-6 in system is as follows: the 6th flow direction control valve 7-6 one end is connected with pipeline between low pressure compressor 1-1 output and the high pressure compressor 1-2 input, the 6th flow direction control valve 7-6 other end can and the first flow direction control valve 7-1 and the second four-way reversing arrangement 120 between the 62 pipeline 62, the 33 pipeline 33 between the second four-way reversing arrangement 120 and the triple valve 13 commutation Node B 3, triple valve 13 often open between node A3 and the heat source side heat exchanger 2 the 49 pipeline 49 any one be connected.The 6th effect of flow direction control valve 7-6 in system, and the function that present embodiment had is identical with embodiment 3.
Figure 12 and scheme shown in Figure 13 are respectively the variation schemes of Fig. 4 and scheme shown in Figure 5, and the difference between they are mutual is: 1) triple valve 13 is in the link position difference in system; 2) in Figure 12 and scheme shown in Figure 13, the 7th check valve 95 is used the 8th flow direction control valve 7-8 instead, and described the 8th flow direction control valve 7-8 should have turn-off function.
Scheme shown in Figure 12 and scheme shown in Figure 4, scheme shown in Figure 13 and scheme shown in Figure 5 all have identical functions.By in system, increasing by one the 6th flow direction control valve 7-6, Figure 12 and scheme shown in Figure 13 can be done further improvement, the 6th flow direction control valve 7-6 is identical with present embodiment with link position in the scheme shown in Figure 13 at Figure 12, that is: the 6th flow direction control valve 7-6 one end is connected the 62 pipeline 62 between the 6th flow direction control valve 7-6 other end and the first flow direction control valve 7-1 and the second four-way reversing arrangement 120 with pipeline between low pressure compressor 1-1 output and the high pressure compressor 1-2 input, the 33 pipeline 33 between the second four-way reversing arrangement 120 and the triple valve 13 commutation Node B 3, triple valve 13 often open between node A3 and the heat source side heat exchanger 2 the 49 pipeline 49 any one be connected.The 6th effect of flow direction control valve 7-6 in system, and the function that is had is identical with embodiment 3.
As shown in figure 14, the difference of it and scheme shown in Figure 6 is to have increased a triple valve 13, the seven check valves 95 to use the 8th flow direction control valve 7-8 instead, and described the 8th flow direction control valve 7-8 should have turn-off function.The node A3 that often opens of described triple valve 13 is connected with heat source side heat exchanger 2 by the 49 pipeline 49, any one B3 in 13 2 on the triple valve commutation node is connected with the second four-way reversing arrangement 120 by the 33 pipeline 33, and another node C3 that commutates is connected with the 42 pipeline 42 between second heat exchanger 6 and the 8th flow direction control valve 7-8.
When the second four-way reversing arrangement 120 is the four-way reversing arrangement that is made of the 3rd check valve 91, the 4th check valve 92, the 5th check valve 93 and the 6th check valve 94, present embodiment scheme shown in Figure 14 is compared with scheme shown in Figure 6, can improve freeze merely summer, summer refrigeration reclaims the operating efficiency under the condensation heat productive life hot water function simultaneously.
Present embodiment scheme shown in Figure 14 can be done further improvement by increasing by one the 6th flow direction control valve 7-6, the connectivity scenario of the 6th flow direction control valve 7-6 in system is as follows: the 6th flow direction control valve 7-6 one end is connected with pipeline between the second check valve 9B port of export and the high pressure compressor 1-2 input, the 6th flow direction control valve 7-6 other end can and the first flow direction control valve 7-1 and the second four-way reversing arrangement 120 between the 62 pipeline 62, the 33 pipeline 33 between the second four-way reversing arrangement 120 and the triple valve 13 commutation Node B 3, triple valve 13 often open between node A3 and the heat source side heat exchanger 2 the 49 pipeline 49 any one be connected.The 6th effect of flow direction control valve 7-6 in system, and the function that is had is identical with embodiment 4.
Figure 15 and scheme shown in Figure 16 are respectively the variation schemes of Fig. 7 and scheme shown in Figure 8, and the difference between they are mutual is: 1) triple valve 13 is in the link position difference in system; 2) in Figure 15 and scheme shown in Figure 16, the 7th check valve 95 is used the 8th flow direction control valve 7-8 instead, and described the 8th flow direction control valve 7-8 should have turn-off function.
Scheme shown in Figure 15 and scheme shown in Figure 7, scheme shown in Figure 16 and scheme shown in Figure 8 all have identical functions.By in system, increasing by one the 6th flow direction control valve 7-6, Figure 15 and scheme shown in Figure 16 can be done further improvement, the 6th flow direction control valve 7-6 is identical with present embodiment with link position in the scheme shown in Figure 16 at Figure 15, that is: the 6th flow direction control valve 7-6 one end is connected the 62 pipeline 62 between the 6th flow direction control valve 7-6 other end and the first flow direction control valve 7-1 and the second four-way reversing arrangement 120 with pipeline between the second check valve 9B port of export and the high pressure compressor 1-2 input, the 33 pipeline 33 between the second four-way reversing arrangement 120 and the triple valve 13 commutation Node B 3, triple valve 13 often open between node A3 and the heat source side heat exchanger 2 the 49 pipeline 49 any one be connected.Effect and the function that had of the 6th flow direction control valve 7-6 in system is identical with embodiment 4.
In the above embodiment, what the first four-way reversing arrangement 110 used is cross valve, an operational version of the second four-way reversing arrangement 120 is cross valves, the four-way reversing arrangement that another operational version is made up of four check valves, but it is fully aware of, in actual applications, the first four-way reversing arrangement 110 and the second four-way reversing arrangement 120 can also use other four-way reversing arrangement.
In above embodiment, the first check valve 9A and the second check valve 9B also can use magnetic valve.Other check valve B also can use magnetic valve.
Claims (12)
1, a kind of multifunctional air-condition heat pump device comprises compressing mechanism (1), heat source side heat exchanger (2), user side heat exchanger (3), second heat exchanger (6), first throttle mechanism (4), second throttle mechanism (5), the first four-way reversing arrangement (110), the second four-way reversing arrangement (120), first flow direction control valve (7-1), second flow direction control valve (7-2), the 9th flow direction control valve (7-9); It is characterized in that: described compressing mechanism (1) is made of low pressure compressor (1-1), high pressure compressor (1-2), first check valve (9A) and second check valve (9B); Described low pressure compressor (1-1) input is connected with described first four-way reversing arrangement (110) the low pressure node (103) by the 63 pipeline (63), described low pressure compressor (1-1) output is successively by described high pressure compressor (1-2) input, high pressure compressor (1-2) output, described second check valve (9B) arrival end, second check valve (9B) port of export is connected with described first four-way reversing arrangement (110) the high pressure node (101), described first check valve (9A) arrival end is connected with pipeline between described low pressure compressor (1-1) output and described high pressure compressor (1-2) input, and described first check valve (9A) port of export is connected with the 60 pipeline (60) between described second check valve (9B) port of export and described first four-way reversing arrangement (110) the high pressure node (101).
2, a kind of multifunctional air-condition heat pump device comprises compressing mechanism (1), heat source side heat exchanger (2), user side heat exchanger (3), second heat exchanger (6), first throttle mechanism (4), second throttle mechanism (5), the first four-way reversing arrangement (110), the second four-way reversing arrangement (120), first flow direction control valve (7-1), second flow direction control valve (7-2), the 9th flow direction control valve (7-9); It is characterized in that: described compressing mechanism (1) is made of low pressure compressor (1-1), high pressure compressor (1-2), first check valve (9A) and second check valve (9B); Described low pressure compressor (1-1) input is connected with described first four-way reversing arrangement (110) the low pressure node (103) by the 63 pipeline (63), described low pressure compressor (1-1) output is successively by described second check valve (9B) arrival end, second check valve (9B) port of export, described high pressure compressor (1-2) input, high pressure compressor (1-2) output is connected with described first four-way reversing arrangement (110) the high pressure node (101), described first check valve (9A) arrival end is connected with described low pressure compressor (1-1) input, and described first check valve (9A) port of export is connected with pipeline between described second check valve (9B) port of export and described high pressure compressor (1-2) input.
3, multifunctional air-condition heat pump device according to claim 1 is characterized in that economizer (11) the low-pressure side port of export is connected by any place of the 63 pipeline (63) between the pipeline between pipeline and high pressure compressor (1-2) input and low pressure compressor (1-1) output, low pressure compressor (1-1) compressing mechanism middle part gas supplementing opening, low pressure compressor (1-1) input and first four-way reversing arrangement (110) the low pressure node (103).
4, multifunctional air-condition heat pump device according to claim 1 is characterized in that flash vessel (50) is connected by any place of the 63 pipeline (63) between the pipeline between the 3rd flow direction control valve (7-3) and high pressure compressor (1-2) input and low pressure compressor (1-1) output, low pressure compressor (1-1) compressing mechanism middle part gas supplementing opening, low pressure compressor (1-1) input and first four-way reversing arrangement (110) the low pressure node (103).
5, multifunctional air-condition heat pump device according to claim 1 is characterized in that described low pressure compressor (1-1) input is connected with described first four-way reversing arrangement (110) the low pressure node (103) by regenerator (9) the low-pressure side port of export, regenerator (9) low-pressure side arrival end, the 63 pipeline (63) successively.
6, multifunctional air-condition heat pump device according to claim 2 is characterized in that economizer (11) the low-pressure side port of export is connected by the pipeline between pipeline, second check valve (9B) port of export and high pressure compressor (1-2) input between pipeline and low pressure compressor (1-1) input, low pressure compressor (1-1) output and second check valve (9B) arrival end, any place of gas supplementing opening, high pressure compressor (1-2) compressing mechanism middle part.
7, multifunctional air-condition heat pump device according to claim 2 is characterized in that flash vessel (50) is connected by the pipeline between pipeline, second check valve (9B) port of export and high pressure compressor (1-2) input between the 3rd flow direction control valve (7-3) and low pressure compressor (1-1) input, low pressure compressor (1-1) output and second check valve (9B) arrival end, any place of gas supplementing opening, high pressure compressor (1-2) compressing mechanism middle part.
8, multifunctional air-condition heat pump device according to claim 2 is characterized in that described low pressure compressor (1-1) input is connected with described first four-way reversing arrangement (110) the low pressure node (103) by regenerator (9) the low-pressure side port of export, regenerator (9) low-pressure side arrival end, the 63 pipeline (63) successively.
9,, it is characterized in that the pipeline between described low pressure compressor (1-1) output and described high pressure compressor (1-2) input is connected with one the 6th flow direction control valve (7-6) according to claim 1 or 3 or 4 or 5 described multifunctional air-condition heat pump devices.
10,, it is characterized in that the pipeline between described second check valve (9B) port of export and described high pressure compressor (1-2) input is connected with one the 6th flow direction control valve (7-6) according to claim 2 or 6 or 7 or 8 described multifunctional air-condition heat pump devices.
11, multifunctional air-condition heat pump device according to claim 9 is characterized in that described low pressure compressor (1-1) and described high pressure compressor (1-2) can be simultaneously respectively to refrigerating capacity and heating load or be cooled medium temperature and heated medium temperature enforcement controls.
12, multifunctional air-condition heat pump device according to claim 10 is characterized in that described low pressure compressor (1-1) and described high pressure compressor (1-2) can be simultaneously respectively to refrigerating capacity and heating load or be cooled medium temperature and heated medium temperature enforcement controls.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910023490A CN101625175A (en) | 2009-08-04 | 2009-08-04 | Multifunctional air-condition heat pump device of single-double level compression and capable of free switch |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910023490A CN101625175A (en) | 2009-08-04 | 2009-08-04 | Multifunctional air-condition heat pump device of single-double level compression and capable of free switch |
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| Publication Number | Publication Date |
|---|---|
| CN101625175A true CN101625175A (en) | 2010-01-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN200910023490A Pending CN101625175A (en) | 2009-08-04 | 2009-08-04 | Multifunctional air-condition heat pump device of single-double level compression and capable of free switch |
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| CN (1) | CN101625175A (en) |
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| CN102418971A (en) * | 2011-04-04 | 2012-04-18 | 刘雄 | Dual heat source heat pump air conditioning equipment |
| CN102748900A (en) * | 2012-07-24 | 2012-10-24 | 上海伯涵热能科技有限公司 | Heat pump, heat pump air conditioner and heat pump water heating unit sequentially using single/double stage compression |
| CN102901262A (en) * | 2012-11-12 | 2013-01-30 | 天津商业大学 | Two-stage multiplex secondary throttling and intermediate incomplete cooling type refrigerating system |
| CN103453691A (en) * | 2013-08-06 | 2013-12-18 | 尹炯钜 | Three-in-one heating and cooling air conditioner and hot water supply device |
| CN104457047A (en) * | 2014-11-29 | 2015-03-25 | 刘雄 | Refrigeration equipment for air conditioner |
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| CN107514830A (en) * | 2016-06-18 | 2017-12-26 | 上海春至新能源科技有限公司 | A kind of single multi-stage compression automatic conversion Multifunctional heat pump system |
| CN108534356A (en) * | 2018-04-13 | 2018-09-14 | 佛山市美肯冷热节能设备有限公司 | A kind of heat pump unit that can generate high-temperature-hot-water |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102418971A (en) * | 2011-04-04 | 2012-04-18 | 刘雄 | Dual heat source heat pump air conditioning equipment |
| CN102418971B (en) * | 2011-04-04 | 2015-09-09 | 刘雄 | Dual heat source heat pump air conditioning equipment |
| CN102748900A (en) * | 2012-07-24 | 2012-10-24 | 上海伯涵热能科技有限公司 | Heat pump, heat pump air conditioner and heat pump water heating unit sequentially using single/double stage compression |
| CN102748900B (en) * | 2012-07-24 | 2015-03-11 | 上海伯涵热能科技有限公司 | Heat pump, heat pump air conditioner and heat pump water heating unit sequentially using single/double stage compression |
| CN102901262A (en) * | 2012-11-12 | 2013-01-30 | 天津商业大学 | Two-stage multiplex secondary throttling and intermediate incomplete cooling type refrigerating system |
| CN103453691B (en) * | 2013-08-06 | 2015-07-01 | 尹炯钜 | Three-in-one cold-warm air conditioner and hot water supply device |
| CN103453691A (en) * | 2013-08-06 | 2013-12-18 | 尹炯钜 | Three-in-one heating and cooling air conditioner and hot water supply device |
| CN104457047A (en) * | 2014-11-29 | 2015-03-25 | 刘雄 | Refrigeration equipment for air conditioner |
| CN104457047B (en) * | 2014-11-29 | 2017-11-24 | 刘雄 | Operation of air conditioning systems |
| CN107514830A (en) * | 2016-06-18 | 2017-12-26 | 上海春至新能源科技有限公司 | A kind of single multi-stage compression automatic conversion Multifunctional heat pump system |
| CN106247506A (en) * | 2016-08-23 | 2016-12-21 | 上海理工大学 | Flash distillation type Gas-supplying enthalpy-increasing heat pump and desiccant wheel combined air-conditioning system |
| CN106871385A (en) * | 2017-04-13 | 2017-06-20 | 青岛海尔空调器有限总公司 | A kind of air-conditioner and control method |
| CN108534356A (en) * | 2018-04-13 | 2018-09-14 | 佛山市美肯冷热节能设备有限公司 | A kind of heat pump unit that can generate high-temperature-hot-water |
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