CN115789980A - Cascade parallel heat pump system - Google Patents
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- CN115789980A CN115789980A CN202211614412.5A CN202211614412A CN115789980A CN 115789980 A CN115789980 A CN 115789980A CN 202211614412 A CN202211614412 A CN 202211614412A CN 115789980 A CN115789980 A CN 115789980A
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Abstract
The invention discloses a cascade parallel heat pump system, comprising: a fresh air channel; the first heat exchange system comprises a first heat exchanger, a second heat exchanger and a third heat exchanger which are arranged in parallel, and the first heat exchanger is positioned in the fresh air channel; the second heat exchange system comprises a fourth heat exchanger arranged in the fresh air channel, and the second heat exchange system realizes heat exchange with the first heat exchange system through the second heat exchanger; the third heat exchange system comprises a fifth heat exchanger arranged in the fresh air channel, and the third heat exchange system realizes heat exchange with the first heat exchange system through the third heat exchanger; the first heat exchanger, the fourth heat exchanger and the fifth heat exchanger are sequentially arranged in the fresh air channel; the cascade parallel heat pump system can achieve the purpose of heating fresh air from medium-low temperature to high temperature with lower energy efficiency ratio, saves energy and is timely regulated and controlled.
Description
Technical Field
The invention relates to the technical field of heat pumps, in particular to a cascade parallel heat pump system.
Background
The cascade heat pump system generally comprises a high-pressure refrigerant circulation loop and a low-pressure refrigerant circulation loop, wherein the high-pressure refrigerant circulation loop and the low-pressure refrigerant circulation loop exchange heat through a shared intermediate heat exchanger so as to achieve the purpose of providing high-temperature hot water or hot air. However, the existing cascade heat pump system usually heats the fresh air in one step, and in this case, the load and energy consumption of the compressor are high, and the desired temperature may not be reached, and it is difficult to adjust the temperature of the hot air in real time.
Disclosure of Invention
The invention aims to overcome one or more defects in the prior art and provide an improved cascade parallel heat pump system which can achieve the aim of heating fresh air from a medium-low temperature to a high temperature with a lower energy efficiency ratio.
In order to achieve the purpose, the invention adopts the technical scheme that: a cascade parallel heat pump system, comprising:
a fresh air channel;
the first heat exchange system comprises a first heat exchanger, a second heat exchanger and a third heat exchanger which are arranged in parallel, and the first heat exchanger is positioned in the fresh air channel;
the second heat exchange system comprises a fourth heat exchanger arranged in the fresh air channel, and the second heat exchange system realizes heat exchange with the first heat exchange system through the second heat exchanger;
the third heat exchange system comprises a fifth heat exchanger arranged in the fresh air channel, and the third heat exchange system realizes heat exchange with the first heat exchange system through the third heat exchanger;
the first heat exchanger, the fourth heat exchanger and the fifth heat exchanger are sequentially arranged in the fresh air channel.
According to some preferred aspects of the present invention, the first heat exchanger, the fourth heat exchanger, and the fifth heat exchanger are fin type heat exchangers, respectively.
According to some preferred aspects of the invention, the second heat exchanger and the third heat exchanger are evaporative condensers, respectively.
According to some preferred aspects of the present invention, the cascade parallel heat pump system further comprises a fan, and the fan is disposed at the air inlet of the fresh air channel.
Furthermore, the fan is a variable frequency fan and is used for regulating and controlling fresh air volume.
According to some preferred aspects of the invention, the refrigerant medium adopted by the first heat exchange system is R410A refrigerant.
According to some preferred aspects of the present invention, the refrigerant medium used in the second heat exchange system and the refrigerant medium used in the third heat exchange system are R245fa refrigerants respectively.
According to some preferable aspects of the invention, the first heat exchange system comprises a first compressor, an oil separator, the first heat exchanger, the second heat exchanger, the third heat exchanger, a reservoir, a first expansion valve and a gas-liquid separator, the first compressor, the oil separator, the first heat exchanger, the reservoir, the first expansion valve and the gas-liquid separator are sequentially communicated in a circulating manner, and the second heat exchanger and the third heat exchanger are respectively arranged on the first heat exchanger in parallel.
Further, the first heat exchange system further comprises a sixth heat exchanger, and the sixth heat exchanger is used for exchanging heat with outside waste heat and is connected with the first heat exchanger in the first heat exchange system in series.
According to some preferred aspects of the present invention, the first heat exchange system further comprises a first regulating valve, a second regulating valve and a third regulating valve which are arranged in parallel, the first regulating valve and the first heat exchanger are connected in series in the first heat exchange system, the second regulating valve and the second heat exchanger are connected in series in the first heat exchange system, and the third regulating valve and the third heat exchanger are connected in series in the first heat exchange system.
According to some preferred aspects of the present invention, the second heat exchange system includes a second compressor, a second expansion valve, and the fourth heat exchanger, and one of the refrigerant passages of the second compressor, the fourth heat exchanger, the second expansion valve, and the second heat exchanger is sequentially communicated in a circulating manner.
According to some preferred aspects of the present invention, the third heat exchange system includes a third compressor, a third expansion valve, and a fifth heat exchanger, and one of refrigerant passages of the third compressor, the fifth heat exchanger, the third expansion valve, and the third heat exchanger is sequentially communicated in a circulating manner.
According to some preferred aspects of the present invention, the heating capacity Q of the first compressor at 50HZ is 1 And input power P 1 Satisfies the following formula (I):
(I) in the formula, a 0 、a 1 、a 2 、a 3 、a 4 、a 5 、a 6 、a 7 、a 8 、a 9 Respectively, a constant, T, associated with said first compressor r1 Is the evaporation temperature, T, of the first compressor s1 Is the condensing temperature of the first compressor and is a fixed value;
heating capacity Q of the second compressor 2 And input power P 2 Satisfies the following formula (II):
(II) in the formula, b 0 、b 1 、b 2 、b 3 、b 4 、b 5 、b 6 、b 7 、b 8 、b 9 Respectively, a constant, T, associated with said second compressor r3 Is the evaporation temperature, T, of the second compressor s2 Is the condensing temperature of the second compressor;
heating capacity Q of the third compressor 3 And input power P 3 Satisfies the following formula (III):
(III) in the formula, C 0 、C 1 、C 2 、C 3 、C 4 、C 5 、C 6 、C 7 、C 8 、C 9 Respectively, a constant, T, associated with said third compressor r5 Is the evaporation temperature, T, of the third compressor s3 Is the condensing temperature of the third compressor and is a fixed value;
the initial temperature of the fresh air is T a1 Initial humidity is RH and wind speed is V a The target temperature of the fresh air is T as Calculating to obtain the required total heat quantity Q all ；
At the same time, Q all ＝Q 1 -P 1 +P 2 +P 3 ；
COP＝(Q 1 -P 1 +P 2 +P 3 )/(P 1 +P 2 +P 3 ) COP is the ratio of the energy conversion efficiency to the operating frequency HZ of the first compressor 1 And the condensation temperature T of the second compressor s2 Correlation;
by simultaneous erection again
And
can obtain the optimal operating frequency HZ of the first compressor 1s And the condensation temperature T of the second compressor s2 According to the HZ 1s Adjusting the operating frequency HZ of the first compressor 1 According to said T s2 And adjusting the fresh air quantity.
Further, T s1 At a temperature of 55-60 ℃ and T s3 Is 100-120 ℃.
According to some specific aspects of the present invention, the first compressor is an inverter compressor.
Due to the application of the technical scheme, compared with the prior art, the invention has the following advantages:
according to the invention, through the structural design of the heat pump system, the heat pump system can achieve the purpose of heating fresh air to high temperature with lower energy efficiency ratio, and can dynamically adjust in real time, feed back in time and save energy.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without inventive exercise.
Fig. 1 is a schematic structural diagram of a cascade parallel heat pump system in an embodiment of the invention;
in the reference symbols: 1. a fresh air channel; 2. a first heat exchanger; 3. a second heat exchanger; 4. a third heat exchanger; 5. a fourth heat exchanger; 6. a fifth heat exchanger; 7. a first compressor; 8. an oil separator; 9. a reservoir; 10. a first expansion valve; 11. a gas-liquid separator; 12. a sixth heat exchanger; 13. a first regulating valve; 14. a second regulating valve; 15. a third regulating valve; 16. a second compressor; 17. a second expansion valve; 18. a third compressor; 19. a third expansion valve; 20. a fan; 21. and (4) a water pump.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein.
In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless explicitly specified otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be interconnected within two elements or in a relationship where two elements interact with each other unless otherwise specifically limited. The specific meanings of the above terms in the present invention can be understood according to specific situations by those of ordinary skill in the art.
In the present invention, unless otherwise explicitly specified or limited, a first feature "on" or "under" a second feature may be directly contacted with the first and second features, or indirectly contacted with the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.
It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present.
Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
As shown in fig. 1, the present example provides a cascade parallel heat pump system, which includes a fresh air channel 1, a first heat exchange system, a second heat exchange system, a third heat exchange system, and a fan 20, where the first heat exchange system includes a first heat exchanger 2, a second heat exchanger 3, and a third heat exchanger 4 that are arranged in parallel, and the first heat exchanger 2 is located in the fresh air channel 1; the second heat exchange system comprises a fourth heat exchanger 5 arranged in the fresh air channel 1, and the second heat exchange system realizes heat exchange with the first heat exchange system through a second heat exchanger 3; the third heat exchange system comprises a fifth heat exchanger 6 arranged in the fresh air channel 1, and the third heat exchange system realizes heat exchange with the first heat exchange system through a third heat exchanger 4; the first heat exchanger 2, the fourth heat exchanger 5 and the fifth heat exchanger 6 are sequentially arranged in the fresh air channel 1, and the fan 20 is arranged at an air inlet of the fresh air channel 1.
Specifically, the first heat exchange system comprises a first compressor 7, an oil separator 8, a first heat exchanger 2, a second heat exchanger 3, a third heat exchanger 4, a liquid storage device 9, a first expansion valve 10 and a gas-liquid separator 11, wherein the first compressor 7, the oil separator 8, the first heat exchanger 2, the liquid storage device 9, the first expansion valve 10 and the gas-liquid separator 11 are sequentially communicated in a circulating manner, and the second heat exchanger 3 and the third heat exchanger 4 are respectively arranged on the first heat exchanger 2 in parallel. Further, in this example, the first heat exchange system further includes a sixth heat exchanger 12, and a first regulating valve 13, a second regulating valve 14, and a third regulating valve 15 that are arranged in parallel, where the sixth heat exchanger 12 is used for exchanging heat with outside waste heat and is connected in series with the first heat exchanger 2 in the first heat exchange system, the first regulating valve 13 and the first heat exchanger 2 are connected in series in the first heat exchange system, the second regulating valve 14 and the second heat exchanger 3 are connected in series in the first heat exchange system, and the third regulating valve 15 and the third heat exchanger 4 are connected in series in the first heat exchange system; in the actual operation process, the water pump 21 may be used to pump the sewage to exchange heat with the refrigerant in the first heat exchange system in the sixth heat exchanger 12.
Specifically, the second heat exchange system comprises a second compressor 16, a second expansion valve 17 and a fourth heat exchanger 5, wherein one refrigerant passage of the second compressor 16, the fourth heat exchanger 5, the second expansion valve 17 and the second heat exchanger 3 is sequentially communicated in a circulating manner; the third heat exchange system comprises a third compressor 18, a third expansion valve 19 and a fifth heat exchanger 6, wherein one refrigerant passage of the third compressor 18, the fifth heat exchanger 6, the third expansion valve 19 and the third heat exchanger 4 is sequentially communicated in a circulating manner
As an optional embodiment, the first heat exchanger 2, the fourth heat exchanger 5, and the fifth heat exchanger 6 are fin heat exchangers, and the second heat exchanger 3 and the third heat exchanger 4 are evaporative condensers, respectively.
Further, the fan 20 is a variable frequency fan for regulating and controlling fresh air volume; the first compressor 7 is an inverter compressor.
In this example, the refrigerant medium used in the first heat exchange system is a low-temperature refrigerant, and may be, but is not limited to, an R410A refrigerant, and the refrigerant medium used in the second heat exchange system and the refrigerant medium used in the third heat exchange system are high-temperature refrigerants, respectively, and may be, but is not limited to, an R245fa refrigerant.
In this example, the fan 20 arranged at the inlet of the fresh air channel 1 generates power to drive the fresh air to circulate along the fresh air channel 1, and primarily exchanges heat at the first heat exchanger 2 to achieve primary heating, then continuously advances to the fourth heat exchanger 5 to exchange heat again to be heated, and finally exchanges heat at the fifth heat exchanger 6 to be heated to a target temperature, in this example, the fresh air is heated by stages to achieve the target temperature, and the condition that the fresh air is heated by a single compressor is avoided: not only may the desired temperature not be reached, but also the load requirement on the compressor may be too great to be easily realized.
In this example, the cascade parallel heat pump system further comprises: a pressure sensor a, a pressure sensor b, a pressure sensor c, a temperature sensor a, a temperature sensor b, a temperature sensor c, a temperature sensor d, a temperature sensor e, a temperature sensor f, a temperature sensor g, and a temperature sensor h, wherein the pressure sensor a is disposed at an exhaust port of the first compressor 7, the pressure sensor b is disposed at an exhaust port of the second compressor 16, the pressure sensor c is disposed at an exhaust port of the third compressor 18, the temperature sensor a is disposed at an outlet of the first expansion valve 10, the temperature sensor b is disposed at an intake port of the first compressor 7, the temperature sensor c is disposed at an outlet of the second expansion valve 17, the temperature sensor d is disposed at an intake port of the second compressor 16, the temperature sensor e is disposed at an outlet of the third expansion valve 19, the temperature sensor f is disposed at an intake port of the third compressor 18, the temperature sensor g is disposed at an outlet of the water pump 21, and the temperature sensor h is disposed at a heat source side outlet of the sixth heat exchanger 12.
In this example, the cascade parallel heat pump system further comprises: the dry bulb temperature sensor a, the dry bulb temperature sensor b, the dry bulb temperature sensor c, the dry bulb temperature sensor d, the relative humidity sensor, the wind speed sensor and the atmospheric pressure sensor are arranged between the fan 20 and the first heat exchanger 2, the dry bulb temperature sensor b is arranged between the fourth heat exchanger 5 and the first heat exchanger 2, the dry bulb temperature sensor c is arranged between the fifth heat exchanger 6 and the fourth heat exchanger 5, and the dry bulb temperature sensor d is arranged behind the fifth heat exchanger 6 and measures the fresh air temperature after final complete heating.
In this example, the heating capacity Q of the first compressor 7 at 50HZ is preferably set 1 And input power P 1 Satisfies the following formula (I):
(I) in the formula, a 0 、a 1 、a 2 、a 3 、a 4 、a 5 、a 6 、a 7 、a 8 、a 9 Respectively, a constant, T, associated with the first compressor 7 r1 Is the evaporation temperature, T, of the first compressor 7 s1 Is the condensation temperature of the first compressor 7 and is a fixed value;
heating capacity Q of the second compressor 16 2 And input power P 2 Satisfies the following formula (II):
(II) in the formula, b 0 、b 1 、b 2 、b 3 、b 4 、b 5 、b 6 、b 7 、b 8 、b 9 Respectively, a constant, T, associated with the second compressor 16 r3 Is the evaporating temperature, T, of the second compressor 16 s2 Is the condensing temperature of the second compressor 16;
heating capacity Q of the third compressor 18 3 And input power P 3 Satisfies the following formula (III):
(III) in the formula, C 0 、C 1 、C 2 、C 3 、C 4 、C 5 、C 6 、C 7 、C 8 、C 9 Respectively, a constant, T, associated with the third compressor 18 r5 Is the evaporating temperature, T, of the third compressor 18 s3 Is the condensing temperature of the third compressor 18 and is a fixed value;
further, T s1 At a temperature of 55-60 ℃ and T s3 Is 100-120 ℃;
the initial temperature of the fresh air is T a1 Initial humidity is RH and wind speed is V a The target temperature of the fresh air is T as Calculating to obtain the required total heat quantity Q all ；
At the same time, Q all ＝Q 1 -P 1 +P 2 +P 3 ；
COP＝(Q 1 -P 1 +P 2 +P 3 )/(P 1 +P 2 +P 3 ) COP is the ratio of the energy conversion efficiency to the operating frequency HZ of the first compressor 7 1 And the condensing temperature T of the second compressor 16 s2 Correlation;
by connecting together again
And
can be solved to obtain the optimum operating frequency HZ of the first compressor 7 1s And the condensing temperature T of the second compressor 16 s2 According to HZ 1s Adjusting the operating frequency HZ of the first compressor 7 1 According to T s2 The fresh air quantity is adjusted, and the regulation and control of the air quantity can be realized by controlling the frequency of the fan 20.
Further, in one case, when the compressor used above is selected to be a Danfoss compressor:
the formula (I) is:
the formula (II) is:
the formula (III) is:
when the unit is operating normally, the fan 20 is turned on to detect the parameters of the wind side, and the required heating amount can be calculated because the outlet air temperature is the set target value. T is r1 Is the post-valve temperature, T, of the first compressor 7 r3 Is the post-valve temperature, T, of the second compressor 16 r5 Is the post-valve temperature, T, of the third compressor 18 s1 Is the condensation temperature, T, of the first compressor 7 s2 Is the condensing temperature and T of the second compressor 16 s3 The post-valve temperature is the corresponding evaporating temperature for the condensing temperature of the third compressor 18, based on the evaporating temperature andthe condensing temperature can calculate the input power of the heating quantity of the corresponding system. Because the evaporation temperature of the first compressor 7 is related to the temperature of the waste heat recovery side, such as sewage, and the condensation temperature of the first compressor 7 is determined, the temperature is controlled to be about 55 ℃, the operation frequency of the first compressor 7 is adjusted, the heating output of the first compressor 7 is controlled, on one hand, the heat generated by the first heat exchange system meets the requirement of first heating of fresh air, and on the other hand, the heat source is also provided for the second heat exchange system and the third heat exchange system.
The first expansion valve 10, the second expansion valve 17 and the third expansion valve 19 are used to control the degree of superheat, i.e., the suction temperature-post-valve temperature, of the respective systems to be in a certain range, e.g., 2-3K.
The first regulating valve 13 is used for controlling the outlet air temperature corresponding to the first compressor 7, the second regulating valve 14 is used for controlling the post-valve temperature of the second compressor 16, and the third regulating valve 15 is used for controlling the post-valve temperature of the third compressor 18.
In this example, the heating temperature of the first heat exchange system is stable, and the heating temperature of the third heat exchange system is also constant, so that the optimal intermediate heating temperature can be T by adjusting the heating temperature of the second heat exchange system s2 To achieve a target heating temperature for the fresh air and since the first heat exchange system also provides a heat source for the second and third heat exchange systems, the optimum operating frequency of the first compressor 7 and the optimum intermediate temperature T of the second compressor 16 s2 Can be calculated according to the above-mentioned manner. The fan 20 frequency is controlled according to the calculated optimal intermediate heating temperature.
In this example, the opening degree of each expansion valve and/or each regulating valve can be effectively regulated according to the temperature difference and the like of each position in the system, so that real-time regulation and control are realized, energy is saved while the requirement of heating the fresh air temperature is met, and the energy efficiency ratio is improved.
In conclusion, the heat pump system can achieve the purpose of heating fresh air to high temperature with lower energy efficiency ratio through the structural design of the heat pump system, and can dynamically adjust in real time, feed back in time and save energy.
The above embodiments are merely illustrative of the technical concept and features of the present invention, and the purpose thereof is to enable those skilled in the art to understand the content of the present invention and implement the invention, and not to limit the scope of the invention, and all equivalent changes or modifications made according to the spirit of the present invention should be covered by the scope of the present invention.
Claims (10)
1. A cascaded parallel heat pump system, comprising:
a fresh air channel;
the first heat exchange system comprises a first heat exchanger, a second heat exchanger and a third heat exchanger which are arranged in parallel, and the first heat exchanger is positioned in the fresh air channel;
the second heat exchange system comprises a fourth heat exchanger arranged in the fresh air channel, and the second heat exchange system realizes heat exchange with the first heat exchange system through the second heat exchanger;
the third heat exchange system comprises a fifth heat exchanger arranged in the fresh air channel, and the third heat exchange system realizes heat exchange with the first heat exchange system through the third heat exchanger;
the first heat exchanger, the fourth heat exchanger and the fifth heat exchanger are sequentially arranged in the fresh air channel.
2. The cascade parallel heat pump system according to claim 1, wherein the first heat exchanger, the fourth heat exchanger, the fifth heat exchanger are each finned heat exchangers; and/or the second heat exchanger and the third heat exchanger are respectively evaporative condensers.
3. The cascade parallel heat pump system according to claim 1, further comprising a blower disposed at an air inlet of the fresh air channel; and/or the cooling medium adopted by the first heat exchange system is R410A refrigerant, and the cooling medium adopted by the second heat exchange system and the cooling medium adopted by the third heat exchange system are R245fa refrigerant respectively.
4. The cascade parallel heat pump system according to claim 1, wherein the first heat exchange system comprises a first compressor, an oil separator, the first heat exchanger, the second heat exchanger, the third heat exchanger, a reservoir, a first expansion valve, and a gas-liquid separator, the first compressor, the oil separator, the first heat exchanger, the reservoir, the first expansion valve, and the gas-liquid separator are sequentially in circulation communication, and the second heat exchanger and the third heat exchanger are respectively disposed in parallel on the first heat exchanger.
5. The cascade parallel heat pump system according to claim 4, wherein the first heat exchange system further comprises a sixth heat exchanger for exchanging heat with waste ambient heat and connected in series with the first heat exchanger in the first heat exchange system.
6. The cascade parallel heat pump system of claim 4 wherein the first heat exchange system further comprises a first regulating valve, a second regulating valve, and a third regulating valve arranged in parallel, the first regulating valve being in series with the first heat exchanger in the first heat exchange system, the second regulating valve being in series with the second heat exchanger in the first heat exchange system, the third regulating valve being in series with the third heat exchanger in the first heat exchange system.
7. The cascade parallel heat pump system according to claim 4, wherein the second heat exchange system comprises a second compressor, a second expansion valve and the fourth heat exchanger, and one of the refrigerant passages of the second compressor, the fourth heat exchanger, the second expansion valve and the second heat exchanger is sequentially communicated in a circulating manner.
8. The cascade parallel heat pump system according to claim 7, wherein the third heat exchange system comprises a third compressor, a third expansion valve and the fifth heat exchanger, and one of the refrigerant passages of the third compressor, the fifth heat exchanger, the third expansion valve and the third heat exchanger is sequentially communicated in a circulating manner.
9. The cascade parallel heat pump system of claim 8, wherein the first compressor has a heating capacity Q at 50HZ 1 And input power P 1 Satisfies the following formula (I):
(I) in the formula, a 0 、a 1 、a 2 、a 3 、a 4 、a 5 、a 6 、a 7 、a 8 、a 9 Respectively, a constant, T, associated with said first compressor r1 Is the evaporating temperature, T, of the first compressor s1 Is the condensing temperature of the first compressor and is a fixed value;
heating capacity Q of the second compressor 2 And input power P 2 Satisfies the following formula (II):
(II) in the formula, b 0 、b 1 、b 2 、b 3 、b 4 、b 5 、b 6 、b 7 、b 8 、b 9 Respectively, a constant, T, associated with said second compressor r3 Is the evaporation temperature, T, of the second compressor s2 Is the condensing temperature of the second compressor;
heating capacity Q of the third compressor 3 And input power P 3 Satisfies the following formula (III):
(III) in the formula, C 0 、C 1 、C 2 、C 3 、C 4 、C 5 、C 6 、C 7 、C 8 、C 9 Respectively, a constant, T, associated with said third compressor r5 Is the evaporation temperature, T, of the third compressor s3 Is the condensing temperature of the third compressor and is a fixed value;
the initial temperature of the fresh air is T a1 Initial humidity is RH and wind speed is V a The target temperature of the fresh air is T as Calculating to obtain the required total heat quantity Q all ；
At the same time, Q all ＝Q 1 -P 1 +P 2 +P 3 ；
COP＝(Q 1 -P 1 +P 2 +P 3 )/(P 1 +P 2 +P 3 ) COP is the ratio of the energy conversion efficiency to the operating frequency HZ of the first compressor 1 And the condensation temperature T of the second compressor s2 Correlation;
by simultaneous erection again
And
can obtain the optimal operation frequency HZ of the first compressor 1s And the condensation temperature T of the second compressor s2 According to the HZ 1s Adjusting the operating frequency HZ of the first compressor 1 According to said T s2 And adjusting the fresh air quantity.
10. The cascaded parallel heat pump system of claim 9, wherein T is T s1 At a temperature of 55-60 ℃ and T s3 Is 100-120 ℃.
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|---|---|---|---|
| CN202211614412.5A CN115789980A (en) | 2022-12-15 | 2022-12-15 | Cascade parallel heat pump system |
| PCT/CN2023/103544 WO2024124863A1 (en) | 2022-12-15 | 2023-06-29 | Cascade parallel heat pump system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202211614412.5A CN115789980A (en) | 2022-12-15 | 2022-12-15 | Cascade parallel heat pump system |
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| CN115789980A true CN115789980A (en) | 2023-03-14 |
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| CN202211614412.5A Pending CN115789980A (en) | 2022-12-15 | 2022-12-15 | Cascade parallel heat pump system |
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| WO2024124863A1 (en) * | 2022-12-15 | 2024-06-20 | 江苏苏净集团有限公司 | Cascade parallel heat pump system |
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| KR100697087B1 (en) * | 2005-06-09 | 2007-03-20 | 엘지전자 주식회사 | Air-Condition |
| WO2018045507A1 (en) * | 2016-09-07 | 2018-03-15 | 徐生恒 | Air-source two-stage heat-pump air-conditioning system |
| CN109579338A (en) * | 2018-12-06 | 2019-04-05 | 青岛海尔空调电子有限公司 | Superposition type air conditioner |
| CN113939697A (en) * | 2019-06-12 | 2022-01-14 | 大金工业株式会社 | Refrigerant cycle system |
| DE102020201349A1 (en) * | 2020-02-04 | 2021-08-05 | Volkswagen Aktiengesellschaft | Refrigerant circuit arrangement and method for operating a refrigerant circuit arrangement |
| CN218993724U (en) * | 2022-12-15 | 2023-05-09 | 江苏苏净集团有限公司 | Overlapping type parallel heat pump system |
| CN115789980A (en) * | 2022-12-15 | 2023-03-14 | 江苏苏净集团有限公司 | Cascade parallel heat pump system |
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| WO2024124863A1 (en) * | 2022-12-15 | 2024-06-20 | 江苏苏净集团有限公司 | Cascade parallel heat pump system |
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