CN115031445A

CN115031445A - Air source heat pump high-temperature heating device and operation method thereof

Info

Publication number: CN115031445A
Application number: CN202210679853.7A
Authority: CN
Inventors: 黄永年
Original assignee: Jiangsu Huayang Solar Energy Co ltd
Current assignee: Jiangsu Huayang New Energy Co ltd
Priority date: 2022-06-16
Filing date: 2022-06-16
Publication date: 2022-09-09
Anticipated expiration: 2042-06-16
Also published as: CN115031445B

Abstract

The invention discloses an air source heat pump high-temperature heating device and an operation method thereof in the technical field of thermal engineering.A compressor is sequentially connected with a condenser, a throttling element and an evaporator, the evaporator comprises at least three heat exchange units, each heat exchange unit comprises at least three heat exchange pipe sets, the heat exchange pipe sets positioned at the central position are connected in a special connection mode, and the rest heat exchange pipe sets are connected in parallel to form a total outlet and a total inlet of the evaporator; one end of the heat exchange tube set at the center is divided into two paths, one path is connected to a general outlet of the evaporator through the control valve, the other path is connected to a second access point on a pipeline between an outlet of the compressor and an inlet of the water tank heat exchanger through the control valve, the other end of the heat exchange tube set is also divided into two paths, one path is connected to the general inlet of the evaporator through the control valve, and the other path is connected to a first access point on a pipeline between the outlet of the water tank heat exchanger and the throttling element through the control valve. The invention is suitable for high-temperature hot water and drying equipment, supplies heat uninterruptedly during defrosting, and can normally operate in an ultralow temperature environment.

Description

Air source heat pump high-temperature heating device and operation method thereof

Technical Field

The invention relates to a thermal device, in particular to a high-temperature heating device and a heating method for an air source heat pump.

Background

In the prior art, hot water and hot air produced by an air source heat pump water heater and an air source heat pump drying device are not high in temperature, generally only 45-55 ℃, and cannot meet user requirements in many application scenes. When the evaporator is operated in winter for defrosting, the temperature of output hot water and hot air is reduced, and a heat pump system adopting only one common compressor cannot normally operate in an ultralow temperature environment below 15 ℃ below zero.

Disclosure of Invention

The present invention is to overcome the above disadvantages, and an object of the present invention is to provide an air source heat pump high temperature heating apparatus and an operation method thereof, which has a shorter defrosting time and a lower energy consumption, a heat pump system heats hot water and hot air without interruption during defrosting, an average COP value of the heat pump system in the whole process of operation is increased, and the purpose of outputting hot air or hot water with a high temperature of 80 ℃ or higher can be realized at a low cost by only using one common compressor, and the apparatus can be operated normally in an ultra low temperature environment of-15 ℃ or lower.

The purpose of the invention is realized as follows: the utility model provides an air source heat pump high temperature heating device, includes compressor, evaporimeter, heat exchanger and throttling element, the export of compressor is connected to the import of compressor through condenser, throttling element and evaporimeter in proper order, its characterized in that: the evaporator comprises at least three heat exchange units, each heat exchange unit comprises at least three heat exchange pipe sets, and each heat exchange pipe set is formed by connecting a plurality of heat exchange pipes in series; the heat exchange tube group positioned at the center in each heat exchange tube group of each heat exchange unit is a heat exchange tube group connected according to a special mode, and the rest heat exchange tube groups in each heat exchange unit are all connected in parallel to form a main outlet and a main inlet of the evaporator; one end of the heat exchange tube group connected in a special way is divided into two paths, one path is connected to the general outlet of the evaporator through a control valve, and the other path is connected to a second access point on a pipeline between the outlet of the compressor and the inlet of the water tank heat exchanger through the control valve; the other end of the heat exchange tube group connected in a special mode is also divided into two paths, one path is connected to the general inlet of the evaporator through a control valve, and the other path is connected to a first access point on a pipeline between the outlet of the water tank heat exchanger and the throttling element through the control valve.

The heat exchange tube sets connected in a special mode and all other heat exchange tube sets in the unit are provided with common heat exchange fins. The shared heat exchange fins are arranged according to the affiliated units in different areas, so that the heat transfer distance is short, the heat transfer efficiency is high, redundant heat energy is not transferred to the fins of other heat exchange units to enable the temperature of the fins to be higher than the atmospheric temperature, the fins absorb atmospheric energy, and the function of the evaporator is reduced.

The invention adopts the heat exchange tube group at the central position to transfer heat to the heat exchange tube groups at the two sides of the heat exchange tube group when the defrosting is generated, and the manufacturing cost is the most saved.

Further, a flow regulating valve is provided at the beginning or end of the branch line connected between the second access point via the group of heat exchange tubes connected in the special manner at the access point. The arrangement of the flow regulating valve can regulate the flow according to the requirement so as to regulate the proportion of the heat energy of the shunted defrosting, the proper proportion can ensure that the COP value of the system is optimal under the existing condition, and the COP value of the system is adversely affected by over-high proportion and over-low proportion.

Further, when the number of the heat exchange tube groups in each heat exchange unit is odd, the heat exchange tube groups connected in a special manner are one group at the central position; when the number of the heat exchange tube groups in each heat exchange unit is even, the heat exchange tube groups connected in a special mode are two groups at the central position or any one of the two groups. The arrangement ensures that the heat is transferred from the central position to the symmetrical two sides, and the heat transfer effect is good.

Further, the condenser is a water tank heat exchanger.

Furthermore, the water tank heat exchanger is a built-in coil heat exchanger, can also be a coil heat exchanger tightly attached to the outer surface of the inner container of the hot water tank, and can also be a microchannel heat exchanger tightly attached to the outer surface of the inner container of the hot water tank; or the water tank heat exchanger is a micro-channel heat exchanger tightly attached to the outer surface of the inner container of the hot water tank, and can also be a coil pipe heat exchanger or a plate heat exchanger with a cold water inlet and a hot water outlet.

Further, the condenser is a finned tube heat exchanger.

Further, the evaporator comprises at least four heat exchange units, and each heat exchange unit comprises at least five heat exchange tube sets.

Further, the operation method of the air source heat pump high-temperature heating device is characterized by comprising the following operation procedures:

the number of the heat exchange units adopted by the evaporator is n, wherein n is more than or equal to 3,

the conventional heating operation is defined as the case when the heat exchange tube groups connected in the special manner are all connected in parallel between the main inlets and outlets a and B of the evaporator, and the case when the conventional heating operation is performed is as follows:

the number of the heat exchange units in which the heat exchange tube groups connected between the first access point and the second access point in a special mode are located and connected through the control valve is S, S =1, 2, 3 … … (n-2), (n-1),

let the number of heat exchange units in which the heat exchange tubes connected in a particular manner between the general outlet and the general inlet of the evaporator are connected via the control valve be R, R =1, 2, 3 … … (n-3), (n-2), (n-1),

r = (n-1) when S =1, R = (n-2) when S =2, R = (n-3) when S =3, R =2 when … … S = (n-2), R =1 when S = (n-1),

S+R=n，

the ratio of S/R to R is as follows:

1/ (n-1) 、2/（n-2）、3/（n-3）、…… (n-2) /2,（n-1）,

these ratios correspond to S values 1, 2, 3 … … (n-2), (n-1) and are defined as 1-gear heating, 2-gear heating, 3-gear heating … … (n-2) gear heating, and (n-1) gear heating, respectively,

1/( n-1) ＜ 2/（n-2）＜3/（n-3）＜…… ＜(n-2) /2＜（n-1）,

the minimum value of S/R is 1/(n-1), and the maximum value of S/R is (n-1);

testing and adjusting at a certain ambient temperature:

(1) the number n of the heat exchange units adopted by the evaporator is called as n value, and when the n value is determined as designed and whether the COP value of the system is good or bad is not considered, the larger the S/R ratio is, the higher the temperature of the hot water or hot air output by the system is; when S/R = (n-1) maximum value, the temperature of the hot water or hot air output by the system is maximum compared with the temperature increased during normal heating operation, namely the heat increasing intensity, and the temperature of the hot water or hot air output by the system is maximum; when S/R = 1/(n-1) is the minimum value, the temperature of the hot water or the hot air output by the system is the minimum value of the increased temperature when the system is in the normal heating operation, namely the 'heating intensity', and the temperature of the hot water or the hot air output by the system is only slightly higher than the temperature when the system is in the normal heating operation;

(2) if the n value is determined and the COP value of the system is required to be ensured to be higher than the set value, the larger the S/R ratio is, the larger the temperature value of the hot water or the hot air output by the system is, the largest ratio of the S/R ratios with the COP value higher than the set value is, the best gear is the first gear, namely the best gear, of the temperature value of the hot water or the hot air output by the system, and in the operation of the best gear, the opening of the flow regulating valve is adjusted to enable the COP value of the system to be higher than the set value and the system output temperature to reach the best value in the best gear, namely the highest output temperature value;

(3) if the n value is determined and the system output temperature is required to be ensured to be higher than the set value, the smaller the S/R ratio is, the better the system COP value is, the smallest of the S/R ratios is the optimal stage of the system COP value on the premise that the system output temperature is higher than the set value, and in the operation of the optimal stage, the opening degree of the flow regulating valve is adjusted to ensure that the system output temperature is higher than the set value and the COP value reaches the optimal value in the optimal stage;

(II) testing and adjusting at a certain range of ultralow temperature environment temperature:

(1) if the n value is determined as designed and whether the COP value of the system is good or bad is not considered, the larger the S/R ratio is, the lower the temperature value of the ultralow temperature environment in which the system can normally operate is;

(2) if the n value is determined and on the premise that the COP value of the system is required to be higher than the set value, the ultralow-temperature environment temperature value at which the system can normally operate is lower as the S/R ratio is larger, the largest ratio of the S/R ratios at which the COP value of the system is higher than the set value is the lowest ultralow-temperature environment temperature value at which the system can normally operate and is the best gear, and in the operation of the best gear, the opening size of the flow regulating valve is adjusted to enable the COP value of the system to be higher than the set value and enable the environment temperature at which the system normally operates to reach the best value in the best gear, namely the lowest environment temperature value;

(3) if the n value is determined and the ultralow temperature environment temperature value which can normally run by the system is required to be ensured to be lower than the target value, the COP value of the system is better as the S/R ratio is smaller, the first gear with the smallest ratio in a plurality of S/R ratios with the ultralow temperature environment temperature value which can normally run by the system being lower than the target value is the best gear with the best COP value, and in the operation of the best gear, the opening degree of the flow regulating valve is adjusted, the ultralow temperature environment temperature value which can normally run by the system is lower than the target value, and the COP value is enabled to reach the best value in the best gear.

The value of n is small and suitable for a low-power heat pump heating system, the value of n is large and suitable for a high-power heat pump heating system, the larger the value of n is, the higher the maximum output temperature value which can be obtained on the premise that the COP value of the test system is higher than a certain standard under the same environmental temperature, the lower the ultralow temperature environmental temperature value which can normally run is, but the larger the value of n is, the more control valves need to be arranged, and the value of n is determined by considering the product power and the number of the arranged control valves.

The various parameters obtained by the test according to the method are input into the automatic control instrument, and the work belongs to the work required by product design and manufacture, so that a user can easily operate the device by selecting the parameters suitable for the working environment and the use requirement of the device according to the specification. Many prior art techniques allow the manufacture of control instruments and are not overrepresented here.

When the device works, the following working modes are provided:

1. normal heating mode of operation: through the conversion of control valve, make whole heat exchange tube group in the whole heat exchange unit of evaporimeter parallelly connected, compressor during operation high temperature high pressure refrigerant is discharged from the compressor export, get into water tank heat exchanger and carry out the heat transfer or finned tube heat exchanger, make the water in the water tank heated or let finned tube heat exchanger export hot air, the refrigerant is condensed, then behind the refrigerant through throttling element, evaporate in the evaporimeter, absorb the heat in the air, reentrant compressor import, accomplish a duty cycle, so relapse constantly, make the water in the water tank by continuous heating, reach the operation requirement.

2. Heating and defrosting operation mode: when the evaporator frosts, the heat exchange tube group at the central position in each heat exchange unit of the evaporator is alternately separated from the state of being connected with the evaporator in parallel through the conversion of the control valve. When most of high-temperature and high-pressure refrigerant at the outlet of the compressor flows into the water tank heat exchanger or the finned tube heat exchanger, part of the refrigerant bypasses the water tank heat exchanger or the finned tube heat exchanger and passes through the heat exchange tube group connected in the special mode, then reaches the outlet of the water tank heat exchanger or the finned tube heat exchanger to form a shunt connected with the water tank heat exchanger or the finned tube heat exchanger in parallel, and when the high-temperature and high-pressure refrigerant flows through the heat exchange tube group connected in the special mode, frost on the common heat exchange fins of the high-temperature and high-pressure refrigerant is quickly melted and removed.

When the evaporator comprises three or more heat exchange units, each heat exchange unit is enabled to perform defrosting operation in turn through opening and closing of the control valve, the heat exchange units always play a role of the evaporator, the heat energy of the atmosphere is still absorbed to maintain the operation of the heat pump, and the heat energy output by the condenser is not interrupted, so that the defrosting does not cause output temperature fluctuation.

3. A heating operation mode: the operation process is the same as that of the defrosting mode, except that the operation process is not carried out when the evaporator frosts, but is adopted when the temperature of hot water in a water tank needs to be further increased or the finned tube heat exchanger needs to output hot air with higher temperature, or the mode can not be normally operated when the external temperature is too low. At the moment, the evaporator is not frosted and needs to be removed, the heat exchange tube group at the central position in each heat exchange unit is separated from the state of being connected with the evaporator in parallel through opening and closing of a related control valve, a small part of high-temperature refrigerants bypass the water tank heat exchanger or the finned tube heat exchanger, the high-temperature refrigerants directly pass through the heat exchange tube group at the central position without being condensed to release condensation heat, are transferred by the common heat exchange fins and absorbed by the refrigerants in other heat exchange tube groups at two sides of the central position in the same unit, the temperature of the refrigerants is increased and then is converged with the refrigerants in most heat exchange tube groups which are connected in parallel to form the evaporator, the temperature of the converged refrigerants is increased compared with that in the conventional operation, and the temperature of the refrigerants in the water tank heat exchanger or the finned tube heat exchanger is further increased after being compressed by the compressor. This is the heat increasing mode of operation.

Compared with the prior art, the invention has the following beneficial effects: high-temperature hot water or high-temperature hot air can be output only by utilizing one common compressor to operate according to a heat increasing mode, and output temperature far beyond the prior art can be obtained. The invention can also be operated in a heat increasing mode below-15 ℃ to realize normal use in an ultralow temperature environment. The device also has the function of rapid defrosting, the defrosting energy consumption is low, the energy loss is extremely low, and the heat energy output by the heat pump system is uninterrupted during defrosting.

Drawings

Fig. 1 is a schematic diagram of the operation of one configuration of the present invention.

Fig. 2 is a schematic diagram of the operation of another configuration of the present invention.

In the figure, 1 is a compressor, 2 is a water tank heat exchanger, 3 is a throttling element, 4 is an evaporator, 5 is a heat exchange fin, 6 is a fin-tube heat exchanger, F1 is a first control valve, F2 is a second control valve, F3 is a third control valve, F4 is a fourth control valve, F5 is a fifth control valve, F6 is a sixth control valve, F7 is a seventh control valve, F8 is an eighth control valve, F9 is a ninth control valve, F10 is a tenth control valve, F11 is a eleventh control valve, F12 is a twelfth control valve, F13 is a thirteenth control valve, F14 is a fourteenth control valve, F15 is a fifteenth control valve, F16 is a sixteenth control valve, F0 is a flow regulating valve, 101 is a first heat exchange tube group, 102 is a second heat exchange tube group, 103 is a third heat exchange tube group, 104 is a fifth heat exchange tube group, 201 is a sixth heat exchange tube group, 202 is a heat exchange tube group, 203 is an eighth heat exchange tube group, 204 is a ninth heat exchange tube group, 205 is a eleventh heat exchange tube group, 301 is a twelfth group, 302 is a thirteenth group, 303, 305 is a fourteenth heat exchange tube group, the heat exchange tube group comprises a 401 heat exchange tube group sixteen, a 402 heat exchange tube group seventeen, a 403 heat exchange tube group eighteen, a 404 heat exchange tube group nineteen, a 405 heat exchange tube group twenty, a main outlet A, a main inlet B, a first access point C and a second access point D.

Detailed Description

Example 1

As shown in fig. 1, the air source heat pump high-temperature heating device comprises a compressor 1, a water tank heat exchanger 2, a throttling element 3 and an evaporator 4, wherein an outlet of the compressor 1 sequentially passes through the water tank heat exchanger 2, the throttling element 3 and the evaporator 4 and is then connected to an inlet of the compressor 1, the evaporator 4 comprises four heat exchange units, each heat exchange unit comprises five heat exchange tube sets, each heat exchange unit comprises a first heat exchange tube set 101, a second heat exchange tube set 102, a third heat exchange tube set 103, a fourth heat exchange tube set 104 and a fifth heat exchange tube set 105, and the third heat exchange tube set 103 is centered; the second heat exchange unit consists of a heat exchange tube group six 201, a heat exchange tube group seven 202, a heat exchange tube group eight 203, a heat exchange tube group nine 204 and a heat exchange tube group ten 205, wherein the heat exchange tube group eight 203 is positioned at the central position; the heat exchange unit III is composed of a heat exchange tube group eleven 301, a heat exchange tube group twelve 302, a heat exchange tube group thirteen 303, a heat exchange tube group fourteen 304 and a heat exchange tube group fifteen 305, wherein the heat exchange tube group thirteen 303 is positioned at the central position; the heat exchange unit IV consists of a sixteen heat exchange tube group 401, a seventeenth heat exchange tube group 402, an eighteen heat exchange tube group 403, a nineteen heat exchange tube group 404 and a twenty 405, wherein the eighteen heat exchange tube group 403 is positioned in the center; the heat exchange tube groups positioned at the center in each heat exchange tube group in each heat exchange unit are connected in a special connection mode, and the other heat exchange tube groups in each heat exchange unit are connected in parallel to form a main outlet A and a main inlet B of the evaporator 4.

One end of the heat exchange tube group III 103 is divided into two paths, one path is connected to the general outlet A of the evaporator 4 through a control valve I F1, and the other path is connected to a second access point D on a pipeline between the outlet of the compressor 1 and the inlet of the water tank heat exchanger 2 through a control valve II F2; the other end of the heat exchange tube set three 103 is also divided into two paths, one path is connected to the general inlet B of the evaporator 4 through a control valve three F3, and the other path is connected to a first access point C on the pipeline between the outlet of the water tank heat exchanger 2 and the throttling element 3 through a control valve four F4.

One end of the heat exchange tube group eight 203 is divided into two paths, one path is connected to the general outlet A of the evaporator 4 through a control valve five F5, and the other path is connected to an access point two D through a control valve six F6; the other end of the heat exchange tube set eight 203 is also split into two paths, one path is connected to the general inlet B of the evaporator 4 via the control valve seven F7, and the other path is connected to the first access point C via the control valve eight F8.

One end of the heat exchange tube group thirteen 303 is divided into two paths, one path is connected to the general outlet A of the evaporator 4 through a control valve nine F9, and the other path is connected to the access point two D through a control valve ten F10; the other end of the thirteen 303 heat exchange tube sets is also split into two paths, one path is connected to the general inlet B of the evaporator 4 via the control valve eleven F11, and the other path is connected to the first C access point via the control valve twelve F12.

One end of the heat exchange tube group eighteen 403 is divided into two paths, one path is connected to the general outlet A of the evaporator 4 through a control valve thirteen F13, and the other path is connected to an access point II D through a control valve fourteen F14; the other end of the heat exchange tube set eighteen 403 is also split into two paths, one path is connected to the general inlet B of the evaporator 4 via the control valve fifteen F15, and the other path is connected to the first access point C via the control valve sixteen F16.

And a flow regulating valve is arranged at the starting end or the tail end of a branch pipeline connected between the second access point D and the first access point C through the third heat exchange pipe set 103, the eighth heat exchange pipe set 203, the thirteenth heat exchange pipe set 303 and the eighteen heat exchange pipe set 403, and the flow regulating valve F0 is arranged at a position close to the tail end of the branch pipeline, namely close to the first access point C, the opening degree of the flow regulating valve is adjustable, and the flow regulating valve F0 is arranged to control and regulate the flow according to the requirement.

The present embodiment has the following operation modes:

1. the normal heating operation mode comprises the following steps: all the heat exchange tube groups in all the heat exchange units are connected in parallel to work as the evaporator 4 through switching on and off of the control valve, specifically, a first control valve F1, a third control valve F3, a fifth control valve F5, a seventh control valve F7, a ninth control valve F9, a tenth control valve F11, a thirteenth control valve F13 and a fifteenth control valve F15 are opened, a second control valve F2, a fourth control valve F4, a sixth control valve F6, an eighth control valve F8, a tenth control valve F10, a twelfth control valve F12, a fourteenth control valve F14 and a sixteenth control valve F16 are closed, the compressor 1 works, high-temperature and high-pressure refrigerant is discharged from an outlet of the compressor 1 and enters the water tank heat exchanger 2 for heat exchange, so that water in the water tank is heated, the refrigerant is condensed, then the refrigerant passes through the throttling element 3 and is evaporated in the evaporator 4, absorbs heat in the air and then enters an inlet of the compressor 1 to complete a working cycle repeatedly, so that the water in the water tank is continuously heated to meet the use requirement.

2. Defrosting operation mode: the flow regulating valve F0 is in an open state. When the evaporator 4 frosts, the heat exchange tube group at the central position in each heat exchange unit is separated from the state of being connected with the evaporator 4 in parallel by switching the control valve, part of the refrigerant bypasses the water tank heat exchanger 2 and flows through the heat exchange tube group at the central position without being condensed to release heat for defrosting, for example, the first heat exchange unit is firstly defrosted, and the second heat exchange unit, the third heat exchange unit and the fourth heat exchange unit still play the role of the evaporator. Firstly, a control valve F2, a control valve F4, a control valve F5, a control valve F7, a control valve F9, a control valve F11, a control valve F13 and a control valve F15 are opened, the control valve F1, a control valve F3, a control valve F6, a control valve F8, a control valve F10, a control valve F12, a control valve F14 and a control valve F16 are closed, most of high-temperature refrigerant at the outlet of the compressor flows through a water tank heat exchanger, the refrigerant releases hot water in the phase-change heat tank, and enters 5 heat exchange tube groups of a second heat exchange unit, 5 heat exchange tube groups of a third heat exchange unit and 5 heat exchange tube groups of a fourth heat exchange unit in the outdoor heat exchanger through a throttling element to evaporate and absorb heat, so as to absorb heat energy of air, and enter the inlet of the compressor to complete a working cycle, and the cycle is the cycle of a main loop. A small part of high-temperature refrigerant at the outlet of the compressor flows through a control valve F2, the heat exchange tube group 103 of the first heat exchange unit, a control valve F4, a flow regulating valve F0 and an access point C and is merged with the refrigerant of the main loop; when a small part of the high-temperature refrigerant flows through the heat exchange tube set 103, frost formed on the heat exchange tube set 103 and the common heat exchange fins 5 arranged on the heat exchange tube set 101, the heat exchange tube set 102, the heat exchange tube set 104 and the heat exchange tube set 105 is melted and removed.

Then, the second heat exchange unit is defrosted, and the first heat exchange unit, the third heat exchange unit and the fourth heat exchange unit function as evaporators. Closing a control valve F5, a control valve F7, a control valve F2, a control valve F4, a control valve F10, a control valve F12, a control valve F14 and a control valve F16, opening the control valve F6, a control valve F8, a control valve F1, a control valve F3, a control valve F9, a control valve F11, a control valve F13 and a control valve F15, enabling most of high-temperature refrigerant at the outlet of the compressor to flow through the water tank heat exchanger, releasing phase-change heat by the refrigerant to heat hot water in the water tank, and enabling the refrigerant to enter a first heat exchange tube group 5 heat exchange tube groups in the outdoor heat exchanger, a third heat exchange tube group 5 heat exchange tube groups in the outdoor heat exchanger and a fourth heat exchange tube group 5 heat exchange tube groups in the outdoor heat exchanger through a throttling element to evaporate and absorb heat energy of air, and enter the inlet of the compressor to complete a working cycle, wherein the cycle is the cycle of the main loop. A small part of high-temperature refrigerant at the outlet of the compressor flows through a control valve F6, the heat exchange tube group 203 of the second heat exchange unit, a control valve F8, a flow regulating valve F0 and an access point C and is merged with the refrigerant of the main loop; when a small part of the high-temperature refrigerant flows through the heat exchange tube set 203, frost formed on the common heat exchange fins 5 arranged on the heat exchange tube set 203, the heat exchange tube set 201, the heat exchange tube set 202, the heat exchange tube set 204 and the heat exchange tube set 205 is melted and removed.

Then, the third heat exchange unit is defrosted, and the first heat exchange unit, the second heat exchange unit and the fourth heat exchange unit play the role of an evaporator. Closing a control valve F2, a control valve F4, a control valve F6, a control valve F8, a control valve F9 and a control valve F11, opening a control valve F10, a control valve F12 and a control valve F14, controlling a valve F16, a control valve F1, a control valve F3, a control valve F5 and a control valve F7, wherein most of high-temperature refrigerant at the outlet of the compressor flows through the water tank heat exchanger, the refrigerant releases phase-change heat to heat water in the water tank, and enters 5 heat exchange tube groups of the first heat exchange unit, 5 heat exchange tube groups of the second heat exchange unit and 5 heat exchange tube groups of the fourth heat exchange unit in the outdoor heat exchanger through a throttling element to evaporate and absorb heat, so that the heat energy of air is absorbed and enters the inlet of the compressor to complete a working cycle, which is the circulation of a main loop. A small part of high-temperature refrigerant at the outlet of the compressor flows through a control valve F10, a heat exchange tube group thirteen 303 of a third heat exchange unit, a control valve F12, a flow regulating valve F0 and an access point C and is merged with the refrigerant of a main loop; when a small part of the high-temperature refrigerant flows through the heat exchange tube set 303, frost formed on the heat exchange tube set 303 and the common heat exchange fins 5 arranged on the heat exchange tube set 301, the heat exchange tube set 302, the heat exchange tube set 304 and the heat exchange tube set 305 is melted and removed.

Then, the fourth heat exchange unit is defrosted, and the first heat exchange unit, the second heat exchange unit and the third heat exchange unit function as an evaporator. Closing a control valve F13, a control valve F15, a control valve F2, a control valve F4, a control valve F6, a control valve F8, a control valve F10 and a control valve F12, opening the control valve F14, a control valve F16, a control valve F1, a control valve F3, a control valve F5, a control valve F7, a control valve F9 and a control valve F11, flowing most of high-temperature refrigerant at the outlet of the compressor through a water tank heat exchanger, releasing the refrigerant to heat hot water in the water tank, and allowing the refrigerant to enter a first heat exchange tube group 5 heat exchange tubes in an outdoor heat exchanger, a second heat exchange tube group 5 heat exchange tubes in the second heat exchange unit and a fourth heat exchange tube group 5 heat exchange tubes in the fourth heat exchanger through a phase-change throttling element to evaporate and absorb heat energy of air, and then enter an inlet of the compressor to complete a working cycle, wherein the cycle is the circulation of a main loop. A small part of high-temperature refrigerant at the outlet of the compressor flows through a control valve F14, a heat exchange tube group eighteen 403 of the fourth heat exchange unit, a control valve F16, a flow regulating valve F0 and a first access point C and is merged with the refrigerant of the main loop; when a small part of the high-temperature refrigerant flows through the heat exchange tube group 403, frost formed on the heat exchange tube group 403 and the common heat exchange fins 5 arranged on the heat exchange tube group 401, the heat exchange tube group 402, the heat exchange tube group 404 and the heat exchange tube group 405 is melted and removed.

And after the work of defrosting in turn is finished, the conventional heating operation mode can be immediately recovered.

In the defrosting process of the embodiment, only 1 heat exchange unit of 4 heat exchange units of the evaporator is always defrosted, and the other 3 heat exchange units still play the role of the evaporator, namely, 75% of heat exchange fins 5 always absorb the heat energy of the atmosphere to maintain the heating operation without interrupting the output heat energy, only 25% of heat exchange fins 5 are defrosted, the heat energy required for defrosting is only a small part, the defrosting is fast, the energy consumption is low, and the influence on the stability of the system operation is reduced; according to the concept of the invention, if the number of the heat exchange units included in the evaporator is increased from 4 in the embodiment to 5 or more, the influence on the stability of the system operation during defrosting can be further reduced.

3. A heating operation mode: it is similar to the working process of defrosting by turns of a plurality of heat exchange units in the defrosting mode, except that it is not performed when the evaporator 4 is frosted, but is employed when the temperature of hot water in the water tank needs to be further increased or the temperature of hot air required for drying needs to be greatly increased, or the mode is employed when the external temperature is very low and cannot be normally operated, and this so-called defrosting is cyclically performed for a long time. During the heating operation, if some evaporator fins and finned tubes generate little frost in a short time, the frost is automatically melted and removed in the process of heating.

The working process of the heat increasing operation mode is as follows: the flow regulating valve F0 is in an open state, and the opening degree is adjustable. For example, the first heat exchange unit is heated for 10 minutes by so-called defrosting, and the second heat exchange unit, the second heat exchange unit and the fourth heat exchange unit still function as evaporators. Opening a control valve F2, a control valve F4, a control valve F5, a control valve F7, a control valve F9, a control valve F11, a control valve F13, a control valve F15, a closed control valve F1, a control valve F3, a control valve F6, a control valve F8, a control valve F10, a control valve F12, a control valve F14 and a control valve F16, wherein most of high-temperature refrigerant at the outlet of the compressor flows through the water tank heat exchanger, the refrigerant releases phase-change heat to heat hot water in the water tank, and the refrigerant enters 5 heat exchange tube groups of the second heat exchange unit and 5 heat exchange tube groups of the third heat exchange unit in the outdoor heat exchanger through a throttling element to evaporate and absorb heat, absorbs heat energy of air and enters the inlet of the compressor to complete a working cycle, which is the circulation of a main loop. A small part of high-temperature refrigerant at the outlet of the compressor flows through a control valve F2, the heat exchange tube group 103 of the first heat exchange unit, a control valve F4, a flow regulating valve F0 and an access point C and is merged with the refrigerant of the main loop; when a small part of high-temperature refrigerant flows through the heat exchange tube set 103, a large amount of heat energy is released, the refrigerant is rapidly transferred to the refrigerant in the heat exchange tube set 101, the heat exchange tube set 102, the heat exchange tube set 104 and the heat exchange tube set 105 adjacent to the refrigerant through the common heat exchange fin 5, the temperature of the refrigerant is rapidly increased, the refrigerant is converged with the refrigerant in all 5 heat exchange tube sets of the second heat exchange unit and all 5 heat exchange tube sets of the third heat exchange unit, the temperature of the converged refrigerant is greatly increased compared with the temperature in the conventional operation, and the temperature of the refrigerant after entering the compressor for compression is further increased, namely the first period of the heat increasing operation.

And in the next period of 10 minutes, the second heat exchange unit is heated, and the first heat exchange unit, the third heat exchange unit and the fourth heat exchange unit play the role of an evaporator. Closing a control valve F5, closing a control valve F7, closing a control valve F2, opening a control valve F4, opening a control valve F8, opening a control valve F1, opening a control valve F3, opening a control valve F10, opening a control valve F12, opening a control valve F14 and opening a control valve F16, opening a control valve F6, opening a control valve F8, opening a control valve F1, opening a control valve F3, opening a control valve F9, opening a control valve F11, opening a control valve F13 and opening a control valve F15, allowing most of high-temperature refrigerant at the outlet of the compressor to flow through a water tank heat exchanger, releasing phase-change heat to heat hot water in a water tank, and allowing the refrigerant to enter a first heat exchange unit 5 heat exchange tube groups, a third heat exchange unit 5 heat exchange tube groups and a fourth heat exchange tube groups in the evaporator 4 through a throttling element to evaporate and absorb heat, so as to absorb heat energy of air, and enter an inlet of the compressor to complete a working cycle, wherein the main loop. A small part of high-temperature refrigerant at the outlet of the compressor flows through a control valve F6, the heat exchange tube group 203 of the second heat exchange unit, a control valve F8, a flow regulating valve F0 and an access point C and is merged with the refrigerant of the main loop; when a small part of high-temperature refrigerant flows through the heat exchange tube set 203, a large amount of heat energy is released, the refrigerant is rapidly transferred by the common heat exchange fins, the temperature of the refrigerant in the heat exchange tube set 201, the heat exchange tube set 202, the heat exchange tube set 204 and the heat exchange tube set 205 adjacent to the refrigerant is increased, the refrigerant is converged with the refrigerant in all 5 heat exchange tube sets of the first heat exchange unit, all 15 heat exchange tube sets of the third heat exchange unit and all 15 heat exchange tube sets of the fourth heat exchange unit, the temperature of the converged refrigerant is greatly increased compared with the temperature in the conventional operation, the temperature of the refrigerant after entering the compressor for compression is further increased, and the cycle is another cycle of the heat increasing operation.

And in the next period of 10 minutes, the third heat exchange unit is heated, and the first heat exchange unit and the second heat exchange unit play the role of evaporators. Closing a control valve F2, a control valve F4, a control valve F6, a control valve F8, a control valve F9 and a control valve F11, opening a control valve F1, a control valve F3, a control valve F5, a control valve F7, a control valve F10 and a control valve F12, wherein most of high-temperature refrigerant at the outlet of the compressor flows through a water tank heat exchanger, the refrigerant releases phase-change heat to heat hot water in the water tank, the refrigerant enters a first heat exchange unit 5 heat exchange tube groups and a second heat exchange unit 5 heat exchange tube groups in the evaporator 4 through a throttling element to be evaporated and absorb heat, the heat energy of air is absorbed, and the heat energy enters the inlet of the compressor to complete a working cycle, which is the cycle of a main loop. A small part of high-temperature refrigerant at the outlet of the compressor flows through a control valve F10, a heat exchange tube group thirteen 303 of a third heat exchange unit, a control valve F12, a flow regulating valve F0 and an access point C and is merged with the refrigerant of a main loop; when a small part of high-temperature refrigerant flows through the heat exchange tube set 303, a large amount of heat energy is released, heat is rapidly transferred through the common heat exchange fins, the temperature of the refrigerant in the heat exchange tube set 301, the heat exchange tube set 302, the heat exchange tube set 304 and the heat exchange tube set 305 adjacent to the refrigerant is increased, the refrigerant is merged with the refrigerant in the 15 heat exchange tube sets of the first heat exchange unit, the second heat exchange unit and the fourth heat exchange unit, the temperature of the merged refrigerant is greatly increased compared with the temperature during normal operation, the temperature of the refrigerant is further increased after the refrigerant enters the compressor for compression, and the cycle is another cycle of heat increasing operation.

And in the next period of 10 minutes, the fourth heat exchange unit is heated, and the first heat exchange unit, the second heat exchange unit and the third heat exchange unit play the role of an evaporator. Closing a control valve F13, a control valve F15, a control valve F2, a control valve F4, a control valve F6, a control valve F8, a control valve F10 and a control valve F12, opening the control valve F14, a control valve F16, a control valve F1, a control valve F3, a control valve F5, a control valve F7, a control valve F9 and a control valve F11, flowing most of high-temperature refrigerant at the outlet of the compressor through a water tank heat exchanger, releasing the refrigerant to heat hot water in the water tank, and entering 15 heat exchange tube groups in the evaporator 4 through a phase change throttling element to evaporate and absorb heat, absorbing heat energy of air, and entering the inlet of the compressor to complete a working cycle, which is the circulation of a main loop. A small part of high-temperature refrigerant at the outlet of the compressor flows through a control valve F14, a heat exchange tube group eighteen 403 of the fourth heat exchange unit, a control valve F16, a flow regulating valve F0 and an access point C and is merged with the refrigerant of the main loop; when a small part of the high-temperature refrigerant flows through the heat exchange tube group 403, a large amount of heat energy is released, and the refrigerant is rapidly transferred through the common heat exchange fins, so that the temperature of the refrigerant in the heat exchange tube group 401, the heat exchange tube group 402, the heat exchange tube group 404 and the heat exchange tube group 405 adjacent to the refrigerant is increased, the refrigerant is merged with the refrigerants in the 15 heat exchange tube groups of the first heat exchange unit, the second heat exchange unit and the third heat exchange unit, the temperature of the merged refrigerant is greatly increased compared with the temperature in the conventional operation, the temperature of the refrigerant after entering the compressor for compression is further increased, and this is another cycle of the heat increasing operation.

Therefore, the long-time circulation is carried out, namely the whole process of the heat increasing operation mode.

In the above example, the number of the heat exchange units for each heat increment is 1, and the number of the heat exchange units for each heat increment can be three different choices of 2 and 3, the heat increment strength is respectively defined as 1 gear, 2 gears and 3 gears, the heat increment strength of the 3 gears is greater than 2 gears, the heat increment strength of the 2 gears is greater than 1 gear, and the heat increment of different gears can adapt to the requirements of outputting different high-temperature hot water or hot air. Taking the strength of 3 grades of heat increment as an example for analysis, in the process of operating under the heat increment working condition, 1 of 4 heat exchange units in the evaporator always absorbs heat energy from the atmosphere to maintain the heating operation of the system, and 3 of the 4 heat exchange units always shunt part of the heat energy of the high-temperature refrigerant from the air outlet of the compressor and feed back the heat energy of the high-temperature refrigerant to the input port of the compressor, so long as the opening of the regulating valve F0 is proper, the heat energy of the high-temperature refrigerant which is about 3 times of the maximum can be mixed with the heat energy of the low-temperature refrigerant which is 1 time of the maximum and then enters the air inlet of the compressor, so that the temperature of the refrigerant at the position is higher than that of the refrigerant in the conventional heating operation, the heat increment strength is very high, and the output temperature is very high.

The operation method of the air source heat pump high-temperature heating device in the embodiment comprises the following operation procedures:

the number of the heat exchange units adopted by the evaporator is n, n =4,

it is assumed that the number of groups of heat exchange tube groups connected in a special manner, which are connected between the main inlets and outlets a and B of the evaporator via the control valve, is n in total, n =4, and that the heat exchange tube groups connected in the special manner are all connected in parallel between the main inlets and outlets a and B of the evaporator to define a conventional heating operation, and in the conventional heating operation, the following is the case:

the number of heat exchange units, in which heat exchange tube groups connected in a special mode and connected between the first access point and the second access point through control valves are located, is S, S =1, 2 and 3, and 3 situations are set;

the number of heat exchange units in which heat exchange tube groups connected in a special mode are arranged and connected between a main outlet and a main inlet of an evaporator through a control valve is R, R =1, 2 and 3, and 3 situations exist in total;

r = (n-1) when S =1, R = (n-2) when S =2, R = (n-3) when S =3, where n =4, i.e., R =3 when S =1, R =2 when S =2, R =1 when S = 3;

S+R=n=4，

S/R is the ratio of S to R, and the following 3 cases exist:

1/(n-1), 2/(n-2), 3/(n-3), where n =4, and the ratio S/R is

1/3、1、3

The ratios correspond to S values 1, 2 and 3 respectively and are defined as 1-gear heating, 2-gear heating and 3-gear heating;

the S/R ratio of 1-gear heating is 1/3 as minimum, and the S/R ratio of 3-gear heating is 3 as maximum;

testing and adjusting at a certain ambient temperature:

(1) the number n of the heat exchange units adopted by the evaporator is called as n value =4, and when the n value is designed and determined without considering whether the COP value of the system is good or bad, the larger the S/R ratio is, the higher the temperature of the hot water or the hot air output by the system is; when S/R = maximum value of 3, the temperature of the hot water or hot air output by the system is the maximum compared with the temperature increased during the conventional heating operation, namely the 'heat increasing intensity', and the temperature of the hot water or hot air output by the system is the highest; when S/R = 1/(n-1) =1/3 minimum value, the temperature of the hot water or hot air output by the system is minimum compared with the temperature increased during normal heating operation, namely the 'heating intensity', and the temperature of the hot water or hot air output by the system is only slightly higher than the temperature during normal heating operation;

(2) n =4 is determined and it is required to ensure that the COP value of the system is higher than the set value, the larger the S/R ratio is, the larger the temperature value of the hot water or hot air output by the system is, the larger the ratio maximum one of the S/R ratios of which the COP value is higher than the set value is, the first gear that the temperature value of the hot water or hot air output by the system reaches the best is the best gear, if the ratio of 1-gear heating, 2-gear heating and 3-gear heating among the S/R ratios of which the COP value is higher than the set value in the test meets the requirement, the S/R ratio of 3-gear heating is 3, and 3-gear heating is the best gear, in the best operation, the opening degree of the flow regulating valve is adjusted to make the COP value of the system higher than the set value and the system output temperature reach the best value in the best gear, that is, that the highest output temperature value; on the premise that the COP value of the system is higher than the set value, the output temperature of the system reaches the maximum value.

(3) The n value =4 is determined and needs to ensure that the system output temperature is higher than the set value, the smaller the S/R ratio is, the better the system COP value is, the smallest ratio among a plurality of S/R ratios with the system output temperature higher than the set value is the optimal system COP grade, if the ratio of 2 grades of heat gain and 2 grades of 3 grades of heat gain among a plurality of S/R ratios with the system output temperature higher than the set value meets the requirement in the test, the smallest ratio is the S/R ratio of 2 grades of heat gain and is 1, and the 2 grades of heat gain is the optimal grade, and in the operation of the optimal grade, the opening degree of the flow regulating valve is adjusted to ensure that the system output temperature is higher than the set value and the COP value reaches the optimal value in the optimal grade; the COP value of the system reaches the optimal value on the premise that the output temperature of the system is higher than the set value.

(1) when the n value =4 is designed and determined without considering whether the COP value of the system is good or bad, the larger the S/R ratio is, the lower the temperature value of the ultralow temperature environment in which the system can normally operate is;

(2) the n value =4 is determined and on the premise that the COP value of the system is required to be ensured to be higher than a set value, the larger the S/R ratio is, the lower the ultralow-temperature environment temperature value which can be normally operated by the system is, the larger the S/R ratio is, the highest one of the S/R ratios in which the COP value of the system is higher than the set value is, the lowest ultralow-temperature environment temperature value which can be normally operated by the system is, if the ratio of 3 stages of 1-stage heating, 2-stage heating and 3-stage heating in the S/R ratios in which the COP value of the system is higher than the set value meets the requirement in the test, the S/R ratio of 3-stage heating which is the highest one is 3, and 3-stage heating is the best stage, in the operation of the optimal gear, the opening of the flow regulating valve is adjusted to ensure that the COP value of the system is higher than a set value and the environmental temperature in normal operation reaches the optimal value in the optimal gear, namely the lowest environmental temperature value; on the premise that the COP value of the system is higher than the set value, the temperature value of the ultralow temperature environment in which the system can normally operate reaches the lowest temperature value.

(3) The n value =4, on the premise that the ultralow temperature environment temperature value which is determined and needs to ensure that the system can normally operate is lower than the target value, the smaller the S/R ratio is, the better the COP value of the system is, if the ratio of 2-step heating and 2-step heating among a plurality of S/R ratios of which the ultralow-temperature environment temperature value capable of normally operating in the system is lower than the target value meets the requirement, the S/R ratio of 2-step heating is 1 for the minimum ratio, and the 2-step heating is the optimal ratio, during the operation of the optimal gear, the opening of the flow regulating valve is adjusted, the temperature value of the ultralow-temperature environment in normal operation of the system is lower than a target value, and the COP value reaches the optimal value in the optimal gear; the COP value of the system reaches the optimal value on the premise that the temperature value of the ultralow-temperature environment, which enables the system to normally operate, is lower than the target value.

The value of n is small and suitable for a low-power heat pump heating system, the value of n is large and suitable for a high-power heat pump heating system, the larger the value of n is, the higher the maximum output temperature value which can be obtained on the premise that the COP value of the system reaches a certain standard under the same environmental temperature is, the lower the ultralow-temperature environmental temperature value which can normally run is, but the larger the value of n is, the more control valves need to be arranged, and the value of n is determined by considering both the product power and the number of the arranged control valves.

Example 2

Referring to fig. 2, compared with embodiment 1, the condenser in embodiment 1 is a water tank heat exchanger, which is changed into a finned tube heat exchanger 6 in embodiment 2, and hot air is output for heating, drying and the like, and the heat exchanger is particularly suitable for the requirements of large-scale industrial drying, especially industrial high-temperature drying. The principle and the flow are similar to those of embodiment 1, and are not described in detail.

The overall beneficial effects that can be expected from the present invention are:

(1) all the heat exchange units are used as evaporators in the conventional heating and transporting process, and no spare parts are wasted;

(2) when in defrosting operation, the evaporator 4 can automatically defrost in time when the heat exchange assembly and the heat exchange fins of the evaporator 4 frost in partial areas, the system can still heat the hot water tank 6 in the defrosting process, 1 heat exchange unit in the 4 heat exchange units is defrosted in turn, 3 heat exchange units always still have the function of the evaporator to absorb atmospheric heat, the evaporator keeps 75% of the function of absorbing atmospheric heat, the process of heating hot water is uninterrupted, one fourth of the heat exchange fins of the evaporator is always defrosted in the defrosting process, the energy required for defrosting is less, the heat energy required for shunting is less, the influence on the output heat energy is small, the defrosting time is short, the energy consumption is low, the working stability of the system is high, the COP value of the system does not obviously fluctuate, the heat exchange tube group for defrosting can still work for the redundant evaporator 4 in the non-defrosting process, and no part is wasted, the equipment cost is saved, the average COP value in the whole process is greatly improved compared with the prior art, and the average COP value in the whole process is hopefully kept near the highest level which can be reached by the equipment. From the above analysis, it can be inferred that the number of the heat exchange units included in the evaporator 4 is 5 or 6, and the efficiency can be further improved compared with the present embodiment. The evaporator 4 includes only the minimum number of heat exchange units of 3, and is suitable for application to a small heat pump water heater, and even if the evaporator is used for a small water heater, the performance of the evaporator is lower than that of the embodiment in which the number of heat exchange units is 4.

(3) The invention can select multi-grade heating intensity during heating operation, and has low cost and high output temperature. The temperature of hot air output by a heat pump type dryer in the prior art is only 45-50 ℃, and the invention can produce hot air with the temperature of more than 90 ℃, and is particularly suitable for application of high-temperature large-scale heat pump type industrial drying equipment.

The intensity of the heat gain has different choices, and the heat gain device can also meet the requirement of realizing normal operation only by adopting a common compressor at low cost under different ultralow temperature environments without any auxiliary energy.

In patent implementation, a gas-liquid separator, a liquid storage tank and the like are additionally arranged under some conditions, throttling elements are various, the drawing is too complex when the drawing is exhausted under various conditions, and the drawing is not an innovation point and is not expressed in detail in the patent drawing. Those skilled in the art can make various alterations and modifications to the technical features of the invention without creative efforts based on the technical content disclosed, and the alterations and modifications are all within the protection scope of the invention.

Claims

1. The utility model provides an air source heat pump high temperature heating device, includes compressor, evaporimeter, condenser and throttling element, the export of compressor is connected to the import of compressor, its characterized in that through condenser, throttling element and evaporimeter in proper order: the evaporator comprises at least three heat exchange units, each heat exchange unit comprises at least three heat exchange pipe sets, and each heat exchange pipe set is formed by connecting a plurality of heat exchange pipes in series; the heat exchange tube group positioned at the center of each heat exchange tube group in each heat exchange unit is connected in a special way, and the other heat exchange tube groups in each heat exchange unit are all connected in parallel to form a main outlet and a main inlet of the evaporator; one end of the heat exchange tube group connected in a special way is divided into two paths, one path is connected to the general outlet of the evaporator through a control valve, and the other path is connected to a second access point on a pipeline between the outlet of the compressor and the inlet of the condenser through the control valve; the other end of the heat exchange tube group connected in a special way is also divided into two paths, one path is connected to the general inlet of the evaporator through a control valve, and the other path is connected to a first access point on a pipeline between the outlet of the condenser and the throttling element through the control valve;

the heat exchange tube sets connected in a special mode and all other heat exchange tube sets in the unit are provided with common heat exchange fins.

2. The air source heat pump high-temperature heating device according to claim 1, characterized in that: and a flow regulating valve is arranged at the starting end or the tail end of the branch pipeline, which is connected between the second access point and the second access point through the heat exchange tube group connected in the special mode.

3. The air source heat pump high-temperature heating device according to claim 1, characterized in that: when the number of the heat exchange tube groups in each heat exchange unit is odd, the heat exchange tube groups connected in a special mode are one group at the central position; when the number of the heat exchange tube groups in each heat exchange unit is even, the heat exchange tube groups connected in a special mode are two groups at the central position or any one of the two groups.

4. The air source heat pump high-temperature heating device according to any one of claims 1 to 3, characterized in that: the condenser is a water tank heat exchanger.

5. The air-source heat pump high-temperature heating device according to claim 4, characterized in that: the water tank heat exchanger is a built-in coil pipe heat exchanger, or a coil pipe heat exchanger tightly attached to the outer surface of the hot water tank inner container, or a micro-channel heat exchanger tightly attached to the outer surface of the hot water tank inner container, or a coil pipe heat exchanger with a cold water inlet and a hot water outlet, or a plate heat exchanger with a cold water inlet and a hot water outlet.

6. A high-temperature heating device of an air-source heat pump as claimed in any one of claims 1 to 3, characterized in that: the condenser is a finned tube heat exchanger.

7. The high-temperature heating device of the air-source heat pump as claimed in claim 1, wherein: the evaporator comprises at least four heat exchange units, and each heat exchange unit comprises at least five heat exchange tube sets.

8. An operation method of a high-temperature heating device of an air source heat pump is characterized by comprising the following operation procedures:

S+R=n，

the ratio of S/R to R is as follows:

1/ (n-1) 、2/（n-2）、3/（n-3）、…… (n-2) /2,（n-1）,

1/( n-1) ＜ 2/（n-2）＜3/（n-3）＜…… ＜(n-2) /2＜（n-1）,

the minimum value of S/R is 1/(n-1), and the maximum value of S/R is (n-1);

testing and adjusting at a certain ambient temperature:

(1) the number n of the heat exchange units adopted by the evaporator is called as n value, and when the n value is determined as designed and whether the COP value of the system is good or bad is not considered, the larger the S/R ratio is, the higher the temperature of the hot water or hot air output by the system is; when S/R = (n-1) maximum value, the temperature of the hot water or hot air output by the system is maximum compared with the temperature increased during normal heating operation, namely the heat increasing intensity, and the temperature of the hot water or hot air output by the system is maximum; when S/R = 1/(n-1) minimum value, the temperature of the hot water or hot air output by the system is minimum compared with the temperature increased during the normal heating operation, namely the 'heating intensity', and the temperature of the hot water or hot air output by the system is only slightly higher than the temperature during the normal heating operation;

(2) if the n value is determined and the COP value of the system is required to be ensured to be higher than the set value, the larger the S/R ratio is, the lower the ultralow temperature environment temperature value which can be normally operated by the system is, the larger the S/R ratio is, the largest ratio of the S/R ratios with the COP value higher than the set value is, the first gear with the lowest ultralow temperature environment temperature which can be normally operated by the system is the best gear, and in the operation of the best gear, the opening degree of the flow regulating valve is adjusted to enable the COP value of the system to be higher than the set value and enable the environment temperature which can be normally operated to reach the best value in the best gear, namely the lowest environment temperature value;

(3) if the n value is determined and the ultralow-temperature environment temperature value which can normally run by the system is required to be ensured to be lower than the target value, the COP value of the system is better when the S/R ratio is smaller, the first gear with the smallest ratio in a plurality of S/R ratios with ultralow-temperature environment temperature values which can normally run by the system being lower than the target value is the best gear with the best COP value, and in the operation of the best gear, the opening degree of the flow regulating valve is adjusted, the ultralow-temperature environment temperature value which can normally run by the system is lower than the target value, and the COP value is enabled to reach the best value in the best gear.