阅读说明：本技术 一种跨临界二氧化碳热风机及其性能优化控制方法 (Transcritical carbon dioxide air heater and performance optimization control method thereof ) 是由 曹锋 叶祖樑 宋昱龙 殷翔 于 2020-03-09 设计创作，主要内容包括：本发明公开了一种跨临界二氧化碳热风机及其性能优化控制方法,热风机采用两级气体冷却器和中间回热器的结构配置,第二级气体冷却器的热负荷为第一级气体冷却器的三分之一,利用高压侧的热量提高压缩机的排气温度,从而在满足换热需要的情况下,实现在高环境温度高出风温度的工况下生产热风,并且同时降低了相应的排气压力,增强了系统的可靠性。所提出的性能优化控制方法,考虑了环境空气温度、设定出风温度和回热器效率,可以满足不同运行工况和变工况下的需要,适用性广。(The invention discloses a transcritical carbon dioxide air heater and a performance optimization control method thereof, wherein the air heater adopts the structural configuration of a two-stage gas cooler and an intermediate heat regenerator, the heat load of a second-stage gas cooler is one third of that of a first-stage gas cooler, and the exhaust temperature of a compressor is improved by using the heat of a high-pressure side, so that the hot air is produced under the working conditions of high environmental temperature and high air-out temperature under the condition of meeting the heat exchange requirement, the corresponding exhaust pressure is reduced, and the reliability of the system is enhanced. The performance optimization control method considers the ambient air temperature, the set air outlet temperature and the efficiency of the heat regenerator, can meet the requirements of different operation working conditions and variable working conditions, and has wide applicability.)

1. A transcritical carbon dioxide air heater is characterized in that a two-stage gas cooler and an intermediate heat regenerator are structurally configured, the heat load of a second-stage gas cooler is one third of that of a first-stage gas cooler, the exhaust temperature of a compressor is improved by using the heat of a high-pressure side, and hot air is produced under the working conditions of high environment temperature and high air outlet temperature.

2. The transcritical carbon dioxide air heater according to claim 1, comprising: the system comprises a compressor, a first-stage gas cooler, a second-stage gas cooler, an electronic expansion valve, an evaporator, a heat regenerator, a gas-liquid separator, a variable frequency fan and a fixed frequency fan;

the refrigerant side circuit is as follows: an exhaust port of the compressor is connected to a first heat exchange channel inlet of the first-stage gas cooler, a first heat exchange channel outlet of the first-stage gas cooler is connected to a high-pressure side inlet of the heat regenerator, a high-pressure side outlet of the heat regenerator is connected to a first heat exchange channel inlet of the second-stage gas cooler, a first heat exchange channel outlet of the second-stage gas cooler is connected to an electronic expansion valve inlet, an electronic expansion valve outlet is connected to an evaporator inlet, an evaporator outlet is connected to a low-pressure side inlet of the heat regenerator, a low-pressure side outlet of the heat regenerator is connected to a gas-liquid separator, and an outlet of the gas-liquid separator;

the hot air side loop is as follows: the fresh air of the environment enters the second heat exchange channel inlet of the second-stage gas cooler from the air inlet A to be heated, the air discharged from the second heat exchange channel of the second-stage gas cooler passes through the variable frequency fan, enters the second heat exchange channel inlet of the first-stage gas cooler to be heated again, and finally obtained hot air is discharged from the second heat exchange channel air outlet B of the first-stage gas cooler.

3. The transcritical carbon dioxide air heater according to claim 1, wherein the ambient temperature is in the range of 10-40 ℃; the air outlet temperature range is 60-90 ℃.

4. The transcritical carbon dioxide air heater of claim 1, wherein said transcritical carbon dioxide air heater uses carbon dioxide R744 refrigerant.

5. The transcritical carbon dioxide air heater of claim 2, wherein said evaporator is equipped with a constant frequency fan to absorb heat from ambient air.

6. The transcritical carbon dioxide air heater of claim 2, wherein said evaporator, first stage gas cooler and second stage gas cooler are finned tube or micro-channel heat exchangers.

7. The transcritical carbon dioxide air heater according to claim 2, wherein the regenerator is a plate heat exchanger or a double pipe heat exchanger.

8. The performance optimization control method for the transcritical carbon dioxide air heater of any one of claims 1 to 7, comprising the following steps:

firstly, after a transcritical carbon dioxide air heater is started, calculating an exhaust pressure optimization value according to a set air outlet temperature and an exhaust pressure optimization formula;

when the outlet air temperature T_air,outWhen the temperature is less than 75 ℃, the exhaust pressure optimization formula is as follows:

P_opt＝(0.189T_amb+60.118)(0.014T_air,out+14.819)(-0.007η_IHX+0.342)-254.546

when the outlet air temperature T_air,outWhen the temperature is more than or equal to 75 ℃, the exhaust pressure optimization formula is as follows:

P_opt＝(0.312T_amb+14.531)(2.082T_air,out+7.153)(-0.008η_IHX+0.022)+25.752

wherein, P_optThe exhaust pressure is an optimized value in bar; t is_ambIs ambient air temperature in units; t is_air,outη representing the set value of the air-out temperature in unit ℃_IHXFor the efficiency of the heat regenerator, the calculation formula is as follows:

wherein, T_L,inAnd T_L,outThe inlet and outlet refrigerant temperatures, in units, for the low pressure side of the regenerator; t is_H,inThe refrigerant inlet temperature on the high-pressure side of the heat regenerator is unit ℃;

secondly, controlling the opening degree of the electronic expansion valve based on the calculated exhaust pressure optimization value and the real-time measured exhaust pressure;

and thirdly, controlling the variable frequency fan by adopting PID (proportion integration differentiation) to enable the air outlet temperature to reach a set value.

9. The performance optimization control method according to claim 8, wherein in the third step, the outlet air temperature PID control is controlled by a differential PID method, and the calculation formula is as follows:

wherein F (n) is the frequency of the variable frequency fan, Δ T is the difference between the current outlet air temperature and the set outlet air temperature, n is the number of operations, K_P、K_IAnd K_DRespectively a proportional regulation coefficient, an integral regulation coefficient and a differential regulation coefficient, and the values are respectively K_P＝10，K_I＝0.5，K_D＝3。

10. The performance optimization control method of claim 8, further comprising the steps of:

step four, when the system is not stopped, delaying, then returning to the step one, and entering the next operation control cycle; the performance optimization control method continuously and circularly operates until the transcritical carbon dioxide air heater is stopped.

Technical Field

The invention belongs to the technical field of heat pumps, and particularly relates to a trans-critical carbon dioxide air heater and a performance optimization control method thereof.

Background

Due to the increasing greenhouse effect, the public, research institutions and government departments have been concerned more and more about the global warming, which is a major problem in recent years. In the field of refrigeration and heat pumps, HFC refrigerants having no ozone layer destruction effect are now being widely used. However, since HFC refrigerants have a high Global Warming Potential (GWP) and have a certain influence on global warming, further research and replacement work for environmentally friendly refrigerants is being actively conducted. Carbon dioxide (CO)₂) As a natural working medium, the ozone layer destruction potential value ODP is 0, the global warming potential value GWP is 1, and the natural working medium has outstanding environment-friendly performance. CO 2₂As an inorganic compound naturally existing in the environment, the environment-friendly flame-retardant coating is safe, nontoxic, non-flammable, chemically stable and free of environmental pollution in production, transportation and use. At the same time as the refrigerant, CO₂The unit volume heating capacity is 3-5 times of that of the traditional refrigerant, so that CO is generated₂The heat pump requires a smaller compressor displacement, less unit charge and a smaller unit volume at the same capacity. Lorentzen proposed transcritical CO in the president of the International society for refrigeration₂After recycling, CO₂Attention has been increasingly paid to the field of refrigeration and heat pump systems.

In transcritical CO₂In the circulation, due to the temperature slippage phenomenon existing when heat is released at the high-pressure side, the heat pump is particularly suitable for being applied to heating scenes needing large temperature rise, such as primary direct-current heating of water and air. When applied to the production of hot water, trans-critical CO₂The heat pump can directly produce hot water with the temperature of more than 90 ℃ at low water inlet temperature, which is incomparable with the heat pump adopting the traditional refrigerant. Similarly, in a hot air blower system, transcritical CO₂The circulation can also generate outlet air with higher temperature than that of the traditional refrigerant heat pump, so that the applicable process field is greatly expanded, the traditional heat supply methods such as coal burning, gas burning, electric heating and the like can be replaced, and the energy conservation and the environmental protection are realized.

However, for transcritical CO₂In the case of a heat pump cycle, when the ambient temperature is high,the evaporation temperature rises correspondingly, and the pressure ratio of the compressor is smaller even if the refrigerant CO₂The degree of superheat at the evaporator outlet is large and the exhaust temperature cannot reach a high level. If hot air with higher temperature needs to be produced at the moment, for example, the temperature is more than 80 ℃, the lower exhaust temperature cannot meet the heat exchange temperature difference required by heat release at the high-pressure side, so that the air outlet temperature is insufficient, and the requirement of a hot air process cannot be met. Moreover, since at present transcritical CO is used₂The pressure resistance of system components such as a compressor, a heat exchanger, a valve and the like is all at an upper limit value, so that the exhaust temperature is ensured to have application limitation by simply increasing the exhaust pressure of the compressor, and the requirements cannot be met.

Disclosure of Invention

The invention aims to provide a transcritical carbon dioxide air heater and a performance optimization control method thereof, which are used for solving the problem that the exhaust temperature of the transcritical carbon dioxide air heater is insufficient under the working conditions of high environmental temperature (10-40 ℃) and high air-out temperature (60-90 ℃) and simultaneously performing performance optimization control.

In order to achieve the purpose, the invention adopts the following technical scheme:

a transcritical carbon dioxide air heater adopts the structural configuration of a two-stage gas cooler and an intermediate heat regenerator, the heat load of a second-stage gas cooler is one third of that of a first-stage gas cooler, the exhaust temperature of a compressor is improved by utilizing the heat of a high-pressure side, and the hot air is produced under the working conditions of high environmental temperature and high air outlet temperature.

Further, the method comprises the following steps: the system comprises a compressor, a first-stage gas cooler, a second-stage gas cooler, an electronic expansion valve, an evaporator, a heat regenerator, a gas-liquid separator, a variable frequency fan and a fixed frequency fan;

the refrigerant side circuit is as follows: an exhaust port of the compressor is connected to a first heat exchange channel inlet of the first-stage gas cooler, a first heat exchange channel outlet of the first-stage gas cooler is connected to a high-pressure side inlet of the heat regenerator, a high-pressure side outlet of the heat regenerator is connected to a first heat exchange channel inlet of the second-stage gas cooler, a first heat exchange channel outlet of the second-stage gas cooler is connected to an electronic expansion valve inlet, an electronic expansion valve outlet is connected to an evaporator inlet, an evaporator outlet is connected to a low-pressure side inlet of the heat regenerator, a low-pressure side outlet of the heat regenerator is connected to a gas-liquid separator, and an outlet of the gas-liquid separator;

the hot air side loop is as follows: the fresh air of the environment enters the second heat exchange channel inlet of the second-stage gas cooler from the air inlet A to be heated, the air discharged from the second heat exchange channel of the second-stage gas cooler passes through the variable frequency fan, enters the second heat exchange channel inlet of the first-stage gas cooler to be heated again, and finally obtained hot air is discharged from the second heat exchange channel air outlet B of the first-stage gas cooler.

Further, the high ambient temperature is 10-40 ℃; the high air outlet temperature is 60-90 ℃.

Further, the transcritical carbon dioxide air heater uses carbon dioxide R744 refrigerant.

Further, the evaporator is provided with a fixed frequency fan to absorb heat from ambient air.

Further, the evaporator, the first stage gas cooler and the second stage gas cooler are fin tube type or micro-channel type heat exchangers.

Further, the heat regenerator is a plate heat exchanger or a double-pipe heat exchanger.

A performance optimization control method of a trans-critical carbon dioxide air heater comprises the following steps:

firstly, after a transcritical carbon dioxide air heater is started, calculating an exhaust pressure optimization value according to a set air outlet temperature and an exhaust pressure optimization formula;

when the outlet air temperature T_air,outWhen the temperature is less than 75 ℃, the exhaust pressure optimization formula is as follows:

P_opt＝(0.189T_amb+60.118)(0.014T_air,out+14.819)(-0.007η_IHX+0.342)-254.546

when the outlet air temperature T_air,outWhen the temperature is more than or equal to 75 ℃, the exhaust pressure optimization formula is as follows:

P_opt＝(0.312T_amb+14.531)(2.082T_air,out+7.153)(-0.008η_IHX+0.022)+25.752

wherein, P_optThe exhaust pressure is an optimized value in bar; t is_ambIs ambient air temperature in units; t is_air,outη representing the set value of the air-out temperature in unit ℃_IHXFor the efficiency of the heat regenerator, the calculation formula is as follows:

wherein, T_L,inAnd T_L,outThe inlet and outlet refrigerant temperatures, in units, for the low pressure side of the regenerator; t is_H,inThe refrigerant inlet temperature on the high-pressure side of the heat regenerator is unit ℃;

secondly, controlling the opening degree of the electronic expansion valve based on the calculated exhaust pressure optimization value and the real-time measured exhaust pressure;

and thirdly, controlling the variable frequency fan by adopting PID (proportion integration differentiation) to enable the air outlet temperature to reach a set value.

Furthermore, in the third step, the air outlet temperature PID control adopts a differential method PID for control, and the calculation formula is as follows:

wherein F (n) is the frequency of the variable frequency fan, Δ T is the difference between the current outlet air temperature and the set outlet air temperature, n is the number of operations, K_P、K_IAnd K_DRespectively a proportional regulation coefficient, an integral regulation coefficient and a differential regulation coefficient, and the values are respectively K_P＝10，K_I＝0.5，K_D＝3。

Further, the method also comprises the following steps:

step four, when the system is not stopped, delaying, then returning to the step one, and entering the next operation control cycle; the performance optimization control method continuously and circularly operates until the transcritical carbon dioxide air heater is stopped.

Compared with the prior art, the invention has the following beneficial effects:

1. the hot air blower provided by the invention adopts the structures of the heat regenerator and the two-stage gas cooler, and utilizes the heat of the high-pressure side to improve the suction superheat degree of the compressor, so that the exhaust temperature is increased, and hot air is produced under the working conditions of higher environmental temperature (10-40 ℃) and high air-out temperature (60-90 ℃). Solves the problem of common transcritical CO₂The problem that the exhaust temperature of the heat pump circulation is insufficient under the working conditions and high-temperature hot air cannot be prepared is solved. Meanwhile, the required exhaust pressure value is reduced while the exhaust temperature is increased, so that the system has higher reliability in operation and can meet the requirement of the existing CO₂Pressure resistance of the compressor product.

2. Compared with the common configuration that the heat regenerator is arranged in front of the electronic expansion valve, the heat regenerator is arranged between the two stages of gas coolers by calculation design, so that the heat is absorbed from the refrigerant with higher temperature, and the exhaust temperature is increased. Meanwhile, the heat load of the two stages of gas coolers is reasonably distributed, so that the proper heat exchange temperature difference of the heat exchange between the refrigerant and the air in the two gas coolers is ensured, and the matching performance of the system is improved.

3. The performance optimization method provided by the invention combines the optimization control of the exhaust pressure and the PID control of the air outlet temperature, and realizes the optimization of the system performance under the condition of ensuring the air outlet temperature. The proposed exhaust pressure optimization value takes the ambient air temperature, the set outlet air temperature and the efficiency of the heat regenerator into consideration, so that the requirements under different heat regenerator heat exchange efficiencies, different operating temperature working conditions and different operating working conditions can be met, and the applicability is wide.

Drawings

Fig. 1 is a schematic structural diagram of a transcritical carbon dioxide air heater according to the present invention.

The reference numbers in the figures are: the air conditioner comprises a compressor 1, a first-stage gas cooler 2, a second-stage gas cooler 3, an electronic expansion valve 4, an evaporator 5, a heat regenerator 6, a gas-liquid separator 7, a variable frequency fan 8, a fixed frequency fan 9, an air inlet A and an air outlet B.

Fig. 2 is a flowchart of a performance optimization control method according to the present invention.

FIG. 3 shows the present inventionExtraction of air heater and common transcritical CO₂And (5) comparing the performance of the circulating system (air outlet is 90 ℃).

Detailed Description

Referring to fig. 1, the present invention provides a transcritical carbon dioxide air heater, including: the system comprises a compressor 1, a first-stage gas cooler 2, a second-stage gas cooler 3, an electronic expansion valve 4, an evaporator 5, a heat regenerator 6, a gas-liquid separator 7, a variable frequency fan 8 and a fixed frequency fan 9.

The refrigerant side circuit is as follows: an exhaust port of the compressor 1 is connected to a first heat exchange channel inlet of the first-stage gas cooler 2, a first heat exchange channel outlet of the first-stage gas cooler 2 is connected to a high-pressure side inlet of the heat regenerator 6, a high-pressure side outlet of the heat regenerator 6 is connected to a first heat exchange channel inlet of the second-stage gas cooler 3, a first heat exchange channel outlet of the second-stage gas cooler 3 is connected to an inlet of the electronic expansion valve 4, an outlet of the electronic expansion valve 4 is connected to an inlet of the evaporator 5, an outlet of the evaporator 5 is connected to a low-pressure side inlet of the heat regenerator 6, a low-pressure side outlet of the heat regenerator 6 is connected to the gas-liquid separator 7, and an outlet.

The hot air side loop is as follows: the fresh air of the environment enters the second heat exchange channel inlet of the second-stage gas cooler 3 from the air inlet A to be heated, the air discharged from the second heat exchange channel of the second-stage gas cooler 3 passes through the variable frequency fan 8, then enters the second heat exchange channel inlet of the first-stage gas cooler 2 to be heated again, and finally obtained hot air is discharged from the second heat exchange channel air outlet B of the first-stage gas cooler 2.

The transcritical carbon dioxide air heater uses a carbon dioxide R744 refrigerant. The evaporator 5 is equipped with a fixed frequency fan 9, which absorbs heat from the ambient air. The evaporator 5, the first-stage gas cooler 2 and the second-stage gas cooler 3 are fin tube type or micro-channel type heat exchangers. The heat regenerator 6 is a plate heat exchanger or a double-pipe heat exchanger. The heat duty of the second stage gas cooler 3 is one third of that of the first stage gas cooler 2.

Referring to fig. 2, the performance optimization control method provided by the invention for the transcritical carbon dioxide air heater comprises the following steps:

firstly, after the unit is started, calculating a corresponding compressor 1 exhaust pressure optimization value according to a set air outlet temperature and exhaust pressure optimization formula. When the set outlet air temperature T_air,outAt a temperature of less than 75 deg.C, the exhaust pressure P_optThe optimization formula is as follows:

P_opt＝(0.189T_amb+60.118)(0.014T_air,out+14.819)(-0.007η_IHX+0.342)-254.546

when the outlet air temperature T_air,outWhen the temperature is more than or equal to 75 ℃, the exhaust pressure optimization formula is as follows:

P_opt＝(0.312T_amb+14.531)(2.082T_air,out+7.153)(-0.008η_IHX+0.022)+25.752

wherein, P_optThe exhaust pressure is an optimized value in bar; t is_ambIs ambient air temperature in units; t is_air,outη representing the set value of the air-out temperature in unit ℃_IHXThe efficiency of the heat regenerator 6 is related to the heat exchanger structure and the heat exchange area of the heat regenerator, and can be obtained according to the parameters of the hot air blower in debugging and running, and the calculation formula is as follows:

wherein, T_L,inAnd T_L,outThe inlet and outlet refrigerant temperatures, in units, for the low pressure side of the regenerator; t is_H,inIs the refrigerant inlet temperature on the high pressure side of the regenerator in units of deg.c.

A second step of optimizing the value P based on the exhaust pressure obtained by calculation_optAnd measuring exhaust pressure P in real time_dThe opening degree of the electronic expansion valve 4 is controlled. When P is present_d>(P_optC, increasing the opening of the electronic expansion valve 4; when P is present_d<(P_opt-) the opening degree of the electronic expansion valve 4 is reduced; when (P)_opt-)≤P_d≤(P_optAnd (+) the opening degree of the electronic expansion valve 4 is kept unchanged. To allow for control errors, a value of 1bar is used.

And thirdly, controlling the variable frequency fan 8 by adopting PID (proportion integration differentiation) to enable the air outlet temperature to reach a set value. Considering the heat exchange delay of the air heater, a differential PID method is adopted for control, and the calculation formula is as follows:

wherein, f (n) is the frequency of the variable frequency fan 8, Δ T is the difference between the current outlet air temperature and the set outlet air temperature, n is the number of operations, K_P、K_IAnd K_DRespectively a proportional regulation coefficient, an integral regulation coefficient and a differential regulation coefficient, and the values are respectively K_P＝10，K_I＝0.5，K_D＝3。

And fourthly, delaying when the system is not stopped, then returning to the first step, and entering the next operation control cycle. And continuously circulating the performance optimization control until the system is stopped.

Referring to FIG. 3, according to the system simulation calculation result, the ratio of the sum of the heat dissipating capacity of the two gas coolers to the power consumption of the compressor is considered as the coefficient of performance of the system, and the common trans-critical CO₂Compared with a heat pump cycle, the hot air blower system provided by the invention has better performance coefficients within the range of 10-40 ℃ of the ambient temperature when the air outlet temperature is 90 ℃. Meanwhile, referring to the upper limit value of the exhaust pressure of a certain type of carbon dioxide compressor, the common transcritical CO is used₂The problem of exhaust pressure overrun exists when the circulation temperature is above 35 ℃, but the system provided by the invention ensures the reliability of the operation of the compressor because the exhaust pressure is lower than the upper limit value under the full working condition.