Comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency improvement

Abstract

The invention discloses a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency improvement. The comprehensive energy supply device comprises a waste heat utilization adsorption type dehumidification system, a heat pump air conditioning system and an air duct system. The adsorption type dehumidification system utilizing the waste heat comprises a cooling liquid pump, a first heat exchanger, a third heat exchanger, a first adsorption type heat exchanger, a second adsorption type heat exchanger and first to eighth three-way valves. The heat pump air conditioning system comprises a second heat exchanger, a compressor, a fourth heat exchanger and an expansion valve; the air duct system comprises a first fan, a second fan, first to fourth air doors, left openings of the first to fourth air doors and right openings of the first to fourth air doors; the invention relates to a comprehensive energy supply device capable of recycling waste heat of a fuel cell for treating sensible heat and latent heat loads in civil, commercial and industrial buildings. The comprehensive energy supply device is further provided with an air conditioner air duct for achieving switching among the functions of refrigeration, heating, adsorption dehumidification and desorption.

Description

Technical Field

[0001] The present invention belongs to the technical field of user-side dehumidification and heating and cooling technology, and in particular relates to a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement. Background Art

[0002] With social progress and economic development, people's demand for energy is growing stronger. The large-scale use of traditional fossil fuels such as oil and coal has played a huge role in promoting the development of human society, but it has also caused the practical problems of environmental pollution and shrinking storage. In recent years, the "dual carbon" concept of carbon peak and carbon neutrality has inspired China's determination to promote the use of renewable energy and reduce carbon emissions. Therefore, it is necessary to vigorously develop a variety of efficient clean energy utilization systems and strive to achieve the "carbon peak" policy goal in 2030.

[0003] At present, air conditioning in civil, commercial and industrial buildings mainly uses vapor compression refrigeration system (VCS) to control temperature and provide dehumidification function. However, this process is inefficient and the dehumidification effect is not obvious in humid weather in southern my country. To solve this problem, adsorption heat exchanger technology has been developed as an alternative. In the context of dual carbon, proton exchange membrane fuel cells (PEMFC) have good development prospects, and nearly half of the energy of PEMFC will be dissipated in the form of low-grade heat energy (70-100℃) during operation. Therefore, it is promising to use fuel cells to generate electricity and desorb the adsorption heat exchanger through the remaining heat to realize the combined heat, cooling and power supply of buildings.

[0004] However, the main function of the current adsorption heat exchanger circulation system is to dehumidify in summer, and the multi-mode response plan according to different seasons is not perfect enough. Therefore, combining the heat pump system with the adsorption dehumidification system for waste heat utilization can achieve the cascade utilization of energy in different seasons, which is of great significance. It is necessary to propose a comprehensive energy supply device that combines fuel cell waste heat dehumidification and heat pump efficiency enhancement, so that it can use fuel cell waste heat to meet the multiple load requirements of cooling, heating, dehumidification, etc. in civil, commercial and industrial buildings in different seasons. Summary of the invention

[0005] The present invention provides a comprehensive energy supply device that combines fuel cell waste heat dehumidification and heat pump efficiency enhancement. The comprehensive energy supply device can utilize the heat generated by the existing fuel cell while outputting electrical energy, and use the heat to desorb the adsorption heat exchanger. Compared with traditional dehumidifiers and steam compression refrigeration dehumidification, the comprehensive energy supply device can effectively reduce the power consumption of dehumidification. At the same time, compared with a simple adsorption heat exchanger system, the comprehensive energy supply device can also switch modes to help the heat pump system reduce energy consumption in winter to achieve environmental protection purposes.

[0006] To solve the above problems, the technical solution provided by the present invention is as follows:

[0007] The embodiment of the present invention provides a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement, including an adsorption dehumidification system for waste heat utilization and a heat pump air conditioning system;

[0008] The waste heat utilization adsorption dehumidification system comprises a coolant pump (1), a first heat exchanger (2), a first three-way valve (3), a second three-way valve (4), a third three-way valve (5), a fourth three-way valve (6), a fifth three-way valve (7), a first adsorption heat exchanger (8), a second adsorption heat exchanger (9), a sixth three-way valve (10), a seventh three-way valve (12), an eighth three-way valve (13) and a third heat exchanger (14);

[0009] Wherein, in the mode in which the first adsorption heat exchanger (8) performs a desorption cycle, the outlet end of the coolant pump (1) is connected to the inlet end of the first heat exchanger (2) through a coolant pipeline. After waste heat recovery, the outlet end of the first heat exchanger (2) is connected to the inlet end of the first three-way valve (3) through a coolant pipeline. The outlet end of the first three-way valve (3) is connected to the inlet end of the third three-way valve (5) through a coolant pipeline. The outlet end of the third three-way valve (5) is connected to the inlet end of the first adsorption heat exchanger (8) through a coolant pipeline. After heat absorption and desorption, the first adsorption heat exchanger (8) is connected to the inlet end of the fifth three-way valve (7) through a coolant pipeline. The outlet end of the fifth three-way valve (7) is connected to the inlet end of the second three-way valve (4) through a coolant pipeline. The outlet end of the second three-way valve (4) is connected to the inlet end of the coolant pump (1) through a coolant pipeline, thereby completing the desorption cycle of the first adsorption heat exchanger (8);

[0010] In the mode in which the second adsorption heat exchanger (9) performs a desorption cycle, the outlet end of the coolant pump (1) is connected to the inlet end of the first heat exchanger (2) through a coolant pipeline. After waste heat recovery, the outlet end of the first heat exchanger (2) is connected to the inlet end of the first three-way valve (3) through a coolant pipeline. The outlet end of the first three-way valve (3) is connected to the inlet end of the sixth three-way valve (10) through a coolant pipeline. The outlet end of the sixth three-way valve (10) is connected to the inlet end of the second adsorption heat exchanger (9) through a coolant pipeline. After endothermic desorption, the second adsorption heat exchanger (9) is connected to the inlet end of the fourth three-way valve (6) through a coolant pipeline. The outlet end of the fourth three-way valve (6) is connected to the inlet end of the second three-way valve (4) through a coolant pipeline. The outlet end of the second three-way valve (4) is connected to the inlet end of the coolant pump (1) through a coolant pipeline, thereby completing the desorption cycle of the second adsorption heat exchanger (9).

[0011] In the mode in which the third heat exchanger (14) is used for heating, the outlet end of the coolant pump (1) is connected to the inlet end of the first heat exchanger (2) through a coolant pipeline. After waste heat recovery, the outlet end of the first heat exchanger (2) is connected to the inlet end of the first three-way valve (3) through a coolant pipeline. The outlet end of the first three-way valve (3) is connected to the inlet end of the sixth three-way valve (10) through a coolant pipeline. The outlet end of the sixth three-way valve (10) is connected to the inlet end of the seventh three-way valve (12) through a coolant pipeline. The outlet end of the seventh three-way valve (12) is connected to the inlet end of the third heat exchanger (14) through a coolant pipeline. After heat release, the outlet end of the third heat exchanger (14) is connected to the inlet end of the eighth three-way valve (12) through a coolant pipeline. The inlet end of the three-way valve (13) is connected, the outlet end of the eighth three-way valve (13) is connected to the inlet end of the fifth three-way valve (7) through a coolant pipeline, the outlet end of the fifth three-way valve (7) is connected to the inlet end of the second three-way valve (4) through a coolant pipeline, and the outlet end of the second three-way valve (4) is connected to the inlet end of the coolant pump (1) through a coolant pipeline, thereby completing the heating cycle of the third heat exchanger (14); in the heating mode, the third heat exchanger (14) selects whether to heat with the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) at the same time according to the size of the heat load in the civil, commercial and industrial buildings; the third heat exchanger (14) can be started to dissipate heat when there is too much waste heat in the fuel cell;

[0012] The heat pump air conditioning system comprises a second heat exchanger (11), a compressor (15), a fourth heat exchanger (16) and an expansion valve (17); in a cooling mode, the outlet end of the second heat exchanger (11) is connected to the inlet end of the compressor (15) via a refrigerant pipeline, the outlet end of the compressor (15) is connected to the inlet end of the fourth heat exchanger (16) via a refrigerant pipeline, the outlet end of the fourth heat exchanger (16) is connected to the inlet end of the expansion valve (17) via a refrigerant pipeline, and the outlet end of the expansion valve (17) is connected to the inlet end of the second heat exchanger (11) via a refrigerant pipeline. The outlet end of the second heat exchanger (11) is connected to the inlet end of the expansion valve (17) through a refrigerant pipe, thereby completing the connection of the heat pump air conditioning system in the cooling mode; in the heating mode, the outlet end of the second heat exchanger (11) is connected to the inlet end of the expansion valve (17) through a refrigerant pipe, the outlet end of the expansion valve (17) is connected to the inlet end of the fourth heat exchanger (16) through a refrigerant pipe, the outlet end of the fourth heat exchanger (16) is connected to the inlet end of the compressor (15) through a refrigerant pipe, and the outlet end of the compressor (15) is connected to the inlet end of the second heat exchanger (11) through a refrigerant pipe, thereby completing the connection of the heat pump air conditioning system in the heating mode.

[0013] According to an optional embodiment of the present invention, the integrated energy supply device also includes an air duct system, wherein the air duct system includes a first fan (18), a second fan (19), a first damper (20), a first damper left opening (20a), a first damper right opening (20b), a second damper (21), a second damper left opening (21a), a second damper right opening (21b), a third damper (22), a third damper left opening (22a), a third damper right opening (22b), a fourth damper (23), a fourth damper left opening (23a), a fourth damper right opening (23b), a fourth damper left opening (23b), a second damper right opening (23b), a third damper left opening (23a), a third damper right opening (23b), a first damper left opening (23b), a second damper right opening (23b), a second damper left opening (23a), a second damper right opening (23b), a third damper left opening (23b), a second damper right opening (23b), a second damper left opening (23a), a second damper right opening (23b), a third damper left opening (23b), a second damper left opening (23b), a second damper right opening (23b), a second damper left opening (23a), a second damper right opening (23b), a third damper left opening (23b), a second damper left opening (23b), a second damper left opening (23b), a second damper left opening (23b), a second damper right opening (23b), a second damper left ... The first air door (20) is located at the fork of the air duct passage passing through the fourth heat exchanger (16), the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9), and controls the flow rate of the indoor return air according to the distance between the first air door left opening (20a) and the first air door right opening (20b) and the heat exchange amount. The ratio of outdoor fresh air flowing through the fourth heat exchanger (16), the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) is controlled; the second damper (21) is at the fork of the air duct passages flowing through the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9), and controls the ratio of air flowing through the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) according to the distance between the second damper left opening (21a) and the second damper right opening (21b) and the heat exchange capacity; the third damper (22 ) at the fork of the air duct passage between the outside and the second heat exchanger (11), the direction of air flow is controlled according to the third damper left opening (22a), the third damper right opening (22b) and the working mode of the first adsorption heat exchanger (8); the fourth damper (23) at the fork of the air duct passage between the outside and the second heat exchanger (11), the direction of air flow is controlled according to the fourth damper left opening (23a), the fourth damper right opening (23b) and the working mode of the second adsorption heat exchanger (9).

[0014] According to an optional embodiment of the present invention, the coolant in the coolant pipeline is a 50% propylene glycol aqueous solution, and the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) are coated parallel flow heat exchangers.

[0015] According to an optional embodiment of the present invention, under summer conditions when the first adsorption heat exchanger (8) performs a desorption cycle, the coolant pump (1) pressurizes the coolant and delivers it to the first heat exchanger (2) for heat exchange. After the waste heat of the first heat exchanger (2) is recovered, the coolant flows through the first three-way valve (3), and then flows through the third three-way valve (5). The first adsorption heat exchanger (8) desorbs the heat of the coolant by absorbing it. After releasing the heat, the coolant flows through the fifth three-way valve (7), then flows through the second three-way valve (4), and finally returns to the coolant pump (1), thereby completing the first adsorption heat exchanger. The desorption cycle of the exchanger (8); the compressor (15) pressurizes the refrigerant and transports it to the fourth heat exchanger (16) for heat dissipation. The refrigerant dissipates heat to a supercooled state through the fourth heat exchanger (16) and then is throttled and cooled through the expansion valve (17). The cooled refrigerant absorbs heat through the second heat exchanger (11) and becomes a superheated state, and finally returns to the compressor (15) to be re-pressurized to complete the cycle. Under this working condition, the air is dehumidified through the second adsorption heat exchanger (9) and then cooled through the second heat exchanger (11), thereby achieving dehumidification and cooling in summer.

[0016] According to an optional embodiment of the present invention, in the summer working condition when the second adsorption heat exchanger (9) performs a desorption cycle, the coolant pump (1) pressurizes the coolant and delivers it to the first heat exchanger (2) for heat exchange. After the waste heat of the first heat exchanger (2) is recovered, the coolant flows through the first three-way valve (3), and then flows through the sixth three-way valve (10). The second adsorption heat exchanger (9) desorbs the heat of the coolant by absorbing it. After releasing the heat, the coolant flows through the fourth three-way valve (6), then flows through the second three-way valve (4), and finally returns to the coolant pump (1), thereby completing the second adsorption heat exchanger. The desorption cycle of the exchanger (9); the compressor (15) pressurizes the refrigerant and transports it to the fourth heat exchanger (16) for heat dissipation. The refrigerant dissipates heat to a supercooled state through the fourth heat exchanger (16) and then is throttled and cooled by the expansion valve (17). The cooled refrigerant absorbs heat through the second heat exchanger (11) and becomes a superheated state, and finally returns to the compressor (15) to be re-pressurized to complete the cycle. Under this working condition, the air is dehumidified through the first adsorption heat exchanger (8) and then cooled through the second heat exchanger (11), thereby achieving dehumidification and cooling in summer.

[0017] According to an optional embodiment of the present invention, under the winter waste heat matching condition, the coolant pump (1) pressurizes and delivers the coolant to the first heat exchanger (2) for heat exchange. After the waste heat of the coolant is recovered by the first heat exchanger (2), it flows through the first three-way valve (3) for diversion. The first part of the coolant flows through the third three-way valve (5) through the first adsorption heat exchanger (8) to release heat. After releasing heat, this part of the coolant flows through the fifth three-way valve (7) and then flows through the second three-way valve (4); the second part of the coolant flows through the sixth three-way valve (10) through the second adsorption heat exchanger (9) to release heat. After releasing heat, this part of the coolant flows through the fourth three-way valve (6) and then flows through the second three-way valve (4) to merge with the first part of the coolant. The merged coolant flows through the second three-way valve (4) and returns to the coolant pump (1), thereby completing heating under the winter waste heat matching condition.

[0018] According to an optional embodiment of the present invention, under the working condition of insufficient residual heat in winter, the coolant pump (1) pressurizes and delivers the coolant to the first heat exchanger (2) for heat exchange. After the residual heat of the coolant is recovered by the first heat exchanger (2), it flows through the first three-way valve (3), and then flows through the sixth three-way valve (10) and the seventh three-way valve (12) in sequence. After passing through the seventh three-way valve (12), the coolant flows through the third heat exchanger (14) to release heat, and then flows through the eighth three-way valve (13), the fifth three-way valve (7) and the second three-way valve (4) in sequence, and finally returns to the coolant pump (1) to complete the cycle; the compressor (15) The refrigerant is pressurized and transported to the second heat exchanger (11) for heat dissipation. After the refrigerant dissipates heat to a supercooled state through the second heat exchanger (11), it is throttled and cooled through the expansion valve (17). The cooled refrigerant absorbs heat through the fourth heat exchanger (16) to become a superheated state, and finally returns to the compressor (15) to be re-pressurized to complete the cycle. Under this working condition, the first part of the air first passes through the third heat exchanger (14) to transfer heat to the fourth heat exchanger (16) to improve the performance of the heat pump, and the second part of the air is heated through the second heat exchanger (11) to achieve winter heating.

[0019] According to an optional embodiment of the present invention, under the condition of excessive waste heat in winter, the coolant pump (1) pressurizes the coolant and delivers it to the first heat exchanger (2) for heat exchange. After the waste heat of the coolant is recovered by the first heat exchanger (2), it flows through the first three-way valve (3) for diversion. The first part of the coolant flows through the third three-way valve (5) through the first adsorption heat exchanger (8) to release heat. After releasing heat, this part of the coolant flows through the fifth three-way valve (7) and then flows through the second three-way valve (4); the second part of the coolant flows through the sixth three-way valve (10) through the second adsorption heat exchanger (9) to release heat. This part of the coolant flows through the After releasing heat, the coolant flows through the fourth three-way valve (6) and then through the second three-way valve (4) to merge with the first part of the coolant. The merged coolant flows through the second three-way valve 4 and returns to the coolant pump (1), thereby completing the heating under the winter waste heat matching working condition. In addition, the second part of the coolant is divided into a third part of the coolant at the sixth three-way valve (10). The third part of the coolant flows through the seventh three-way valve (12) and the third heat exchanger (14) to release heat, and then flows through the eighth three-way valve (13), the fifth three-way valve (7) and the second three-way valve (4) in sequence, and finally returns to the coolant pump (1) to complete the heat dissipation of excess heat.

[0020] Beneficial effects: The present invention is a comprehensive energy supply device that combines fuel cell waste heat dehumidification and heat pump efficiency enhancement. Compared with the dehumidification and heat pump system, the comprehensive energy supply device can utilize the waste heat generated by fuel cell power generation for desorption, thereby continuously achieving low-power dehumidification. In addition, the spatial position of the adsorption dehumidification system for waste heat utilization and the heat pump system are coupled with each other. In summer, the two systems can first dehumidify and then cool through the same air duct. In winter, when the waste heat is insufficient, the coupling system can improve the energy efficiency of the heat pump system by switching modes, thereby achieving the purpose of comprehensive fuel cell energy supply and maximum energy utilization. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the technical solutions in the embodiments or the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0022] Figure 1 A schematic diagram of summer operation of a system of a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement provided in an embodiment of the present application when the first adsorption heat exchanger is dehumidified.

[0023] Figure 2 A schematic diagram of summer operation of a system of a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement provided in an embodiment of the present application when the second adsorption heat exchanger is dehumidified.

[0024] Figure 3 A schematic diagram of winter operation of a system of a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement when waste heat is matched is provided in an embodiment of the present application.

[0025] Figure 4 A schematic diagram of the winter operation of a comprehensive energy supply device that combines fuel cell waste heat dehumidification and heat pump efficiency enhancement when waste heat is insufficient is provided in an embodiment of the present application.

[0026] Figure 5 A schematic diagram of the winter operation of a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement when there is excessive waste heat provided in an embodiment of the present application.

[0027] Figure 6 A schematic diagram of the summer wind duct of a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement provided in an embodiment of the present application during dehumidification in the first adsorption heat exchanger.

[0028] Figure 7 A schematic diagram of the summer wind duct of a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement provided in an embodiment of the present application during dehumidification in the second adsorption heat exchanger.

[0029] Figure 8 A schematic diagram of the winter wind duct during waste heat matching of a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement provided in an embodiment of the present application.

[0030] Fig. 9 A schematic diagram of the winter wind duct when the waste heat is insufficient for a comprehensive energy supply device that combines fuel cell waste heat dehumidification and heat pump efficiency enhancement provided in an embodiment of the present application.

[0031] Fig.10 A schematic diagram of the winter wind duct when there is too much waste heat in a comprehensive energy supply device that combines fuel cell waste heat dehumidification and heat pump efficiency enhancement provided in an embodiment of the present application.

[0032] Reference numerals: coolant pump 1, first heat exchanger 2, first three-way valve 3, second three-way valve 4, third three-way valve 5, fourth three-way valve 6, fifth three-way valve 7, first adsorption heat exchanger 8, second adsorption heat exchanger 9, sixth three-way valve 10, second heat exchanger 11, seventh three-way valve 12, eighth three-way valve 13, third heat exchanger 14, compressor 15, fourth heat exchanger 16, expansion valve 17, first fan 18, second fan 19, first damper 20, first damper left opening 20a, first damper right opening 20b, second damper 21, second damper left opening 21a, second damper right opening 21b, third damper 22, third damper left opening 22a, third damper right opening 22b, fourth damper 23, fourth damper left opening 23a, fourth damper right opening 23b. DETAILED DESCRIPTION

[0033] The technical solutions in the embodiments of the present application will be described clearly and completely below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work are within the scope of protection of the present application.

[0034] like Figures 1 to 10 As shown, an embodiment of the present invention provides a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement, including an adsorption dehumidification system for waste heat utilization and a heat pump air conditioning system.

[0035] The adsorption dehumidification system for waste heat utilization includes a coolant pump 1, a first heat exchanger 2, a first three-way valve 3, a second three-way valve 4, a third three-way valve 5, a fourth three-way valve 6, a fifth three-way valve 7, a first adsorption heat exchanger 8, a second adsorption heat exchanger 9, a sixth three-way valve 10, a seventh three-way valve 12, an eighth three-way valve 13 and a third heat exchanger 14.

[0036] Among them, Figure 1 As shown, in the mode in which the first adsorption heat exchanger 8 performs a desorption cycle, the outlet end of the coolant pump 1 is connected to the inlet end of the first heat exchanger 2 through a coolant pipeline, and after waste heat recovery, the outlet end of the first heat exchanger 2 is connected to the inlet end of the first three-way valve 3 through a coolant pipeline, and the outlet end of the first three-way valve 3 is connected to the inlet end of the third three-way valve 5 through a coolant pipeline, and the outlet end of the third three-way valve 5 is connected to the inlet end of the first adsorption heat exchanger 8 through a coolant pipeline. After endothermic desorption, the first adsorption heat exchanger 8 is connected to the inlet end of the fifth three-way valve 7 through a coolant pipeline; the outlet end of the fifth three-way valve 7 is connected to the inlet end of the second three-way valve 4 through a coolant pipeline, and the outlet end of the second three-way valve 4 is connected to the inlet end of the coolant pump 1 through a coolant pipeline, thereby completing the desorption cycle of the first adsorption heat exchanger 8.

[0037] like Figure 2As shown, in the mode in which the second adsorption heat exchanger 9 performs a desorption cycle, the outlet end of the coolant pump 1 is connected to the inlet end of the first heat exchanger 2 through a coolant pipeline, and after waste heat recovery, the outlet end of the first heat exchanger 2 is connected to the inlet end of the first three-way valve 3 through a coolant pipeline, and the outlet end of the first three-way valve 3 is connected to the inlet end of the sixth three-way valve 10 through a coolant pipeline, and the outlet end of the sixth three-way valve 10 is connected to the inlet end of the second adsorption heat exchanger 9 through a coolant pipeline. After endothermic desorption, the second adsorption heat exchanger 9 is connected to the inlet end of the fourth three-way valve 6 through a coolant pipeline, and the outlet end of the fourth three-way valve 6 is connected to the inlet end of the second three-way valve 4 through a coolant pipeline, and the outlet end of the second three-way valve 4 is connected to the inlet end of the coolant pump 1 through a coolant pipeline, thereby completing the desorption cycle of the second adsorption heat exchanger 9.

[0038] like Figure 4 As shown, in the mode in which the third heat exchanger 14 is used for heating, the outlet end of the coolant pump 1 is connected to the inlet end of the first heat exchanger 2 through the coolant pipeline, and after the waste heat is recovered, the outlet end of the first heat exchanger 2 is connected to the inlet end of the first three-way valve 3 through the coolant pipeline, and the outlet end of the first three-way valve 3 is connected to the inlet end of the sixth three-way valve 10 through the coolant pipeline, and the outlet end of the sixth three-way valve 10 is connected to the inlet end of the seventh three-way valve 12 through the coolant pipeline, and the outlet end of the seventh three-way valve 12 is connected to the inlet end of the third heat exchanger 14 through the coolant pipeline, and after heat release, the outlet end of the third heat exchanger 14 is connected to the inlet end of the eighth three-way valve 12 through the coolant pipeline. The inlet end of the eighth three-way valve 13 is connected, the outlet end of the eighth three-way valve 13 is connected to the inlet end of the fifth three-way valve 7 through the coolant pipeline, the outlet end of the fifth three-way valve 7 is connected to the inlet end of the second three-way valve 4 through the coolant pipeline, and the outlet end of the second three-way valve 4 is connected to the inlet end of the coolant pump 1 through the coolant pipeline, thereby completing the heating cycle of the third heat exchanger 14; the third heat exchanger 14 chooses whether to heat with the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 at the same time according to the size of the heat load in civil, commercial and industrial buildings in the heating mode; the third heat exchanger 14 can be started for heat dissipation when there is too much waste heat in the fuel cell.

[0039] like Figure 1 , Figure 2 , Figure 4 and Figure 5As shown, the heat pump air-conditioning system includes a second heat exchanger 11, a compressor 15, a fourth heat exchanger 16 and an expansion valve 17; in the cooling mode, the outlet end of the second heat exchanger 11 is connected to the inlet end of the compressor 15 through a refrigerant pipe, the outlet end of the compressor 15 is connected to the inlet end of the fourth heat exchanger 16 through a refrigerant pipe, the outlet end of the fourth heat exchanger 16 is connected to the inlet end of the expansion valve 17 through a refrigerant pipe, and the outlet end of the expansion valve 17 is connected to the inlet end of the second heat exchanger 11 through a refrigerant pipe, thereby completing the connection of the heat pump air-conditioning system in the cooling mode; in the heating mode, the outlet end of the second heat exchanger 11 is connected to the inlet end of the expansion valve 17 through a refrigerant pipe, the outlet end of the expansion valve 17 is connected to the inlet end of the fourth heat exchanger 16 through a refrigerant pipe, the outlet end of the fourth heat exchanger 16 is connected to the inlet end of the compressor 15 through a refrigerant pipe, and the outlet end of the compressor 15 is connected to the inlet end of the second heat exchanger 11 through a refrigerant pipe, thereby completing the connection of the heat pump air-conditioning system in the heating mode.

[0040] like Figure 6 to Figure 10 As shown, the integrated energy supply device also includes an air duct system, which includes a first fan 18, a second fan 19, a first damper 20, a first damper left opening 20a, a first damper right opening 20b, a second damper 21, a second damper left opening 21a, a second damper right opening 21b, a third damper 22, a third damper left opening 22a, a third damper right opening 22b, a fourth damper 23, a fourth damper left opening 23a and a fourth damper right opening 23b; wherein the first fan 18 controls the flow rate of outdoor fresh air at the outdoor fresh air duct outlet; the second fan 19 controls the flow rate of indoor return air at the indoor return air duct outlet; the first damper 20 controls the flow rate of outdoor fresh air through the fourth heat exchanger 16, the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 at the fork of the air duct channel passing through the fourth heat exchanger 16, the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 according to the distance between the first damper left opening 20a and the first damper right opening 20b and the heat exchange amount. the ratio of the four heat exchangers 16, the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9; the second damper 21 controls the ratio of air flowing through the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 according to the distance and heat exchange rate of the second damper left opening 21a and the second damper right opening 21b at the bifurcation of the air duct channel flowing through the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9; the third damper 22 controls the direction of air flow according to the third damper left opening 22a, the third damper right opening 22b and the working mode of the first adsorption heat exchanger 8 at the bifurcation of the air duct channel flowing through the outdoor and the second heat exchanger 11; the fourth damper 23 controls the direction of air flow according to the fourth damper left opening 23a, the fourth damper right opening 23b and the working mode of the second adsorption heat exchanger 9 at the bifurcation of the air duct channel flowing through the outdoor and the second heat exchanger 11.

[0041] The coolant in the coolant pipeline in this embodiment is a 50% propylene glycol aqueous solution, and the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 are coated parallel flow heat exchangers.

[0042] like Figure 1 As shown, in the summer working condition when the first adsorption heat exchanger 8 performs a desorption cycle, the coolant pump 1 pressurizes the coolant and delivers it to the first heat exchanger 2 for heat exchange. After the waste heat of the first heat exchanger 2 is recovered, the coolant flows through the first three-way valve 3 and then flows through the third three-way valve 5. The first adsorption heat exchanger 8 desorbs by absorbing the heat of the coolant. After releasing heat, the coolant flows through the fifth three-way valve 7 and then flows through the second three-way valve 4, and finally returns to the coolant pump 1, thereby completing the desorption cycle of the first adsorption heat exchanger 8; the compressor 15 pressurizes the refrigerant and delivers it to the fourth heat exchanger 16 for heat dissipation. After the refrigerant dissipates heat to a supercooled state through the fourth heat exchanger 16, it is throttled and cooled by the expansion valve 17. The cooled refrigerant absorbs heat through the second heat exchanger 11 to become a superheated state, and finally returns to the compressor 15 for re-pressurization to complete the cycle; under this working condition, the air is dehumidified after passing through the second adsorption heat exchanger 9 and then cooled after passing through the second heat exchanger 11, thereby achieving dehumidification and cooling in summer.

[0043] like Figure 2 As shown, in the summer working condition when the second adsorption heat exchanger 9 performs a desorption cycle, the coolant pump 1 pressurizes the coolant and delivers it to the first heat exchanger 2 for heat exchange. After the waste heat of the first heat exchanger 2 is recovered, the coolant flows through the first three-way valve 3 and then flows through the sixth three-way valve 10. The second adsorption heat exchanger 9 desorbs by absorbing the heat of the coolant. After releasing heat, the coolant flows through the fourth three-way valve 6 and then flows through the second three-way valve 4, and finally returns to the coolant pump 1, thereby completing the desorption cycle of the second adsorption heat exchanger 9; the compressor 15 pressurizes the refrigerant and delivers it to the fourth heat exchanger 16 for heat dissipation. After the refrigerant dissipates heat to a supercooled state through the fourth heat exchanger 16, it is throttled and cooled by the expansion valve 17. The cooled refrigerant absorbs heat through the second heat exchanger 11 to become a superheated state, and finally returns to the compressor 15 for re-pressurization to complete the cycle; under this working condition, the air is dehumidified after passing through the first adsorption heat exchanger 8 and then cooled after passing through the second heat exchanger 11, thereby achieving dehumidification and cooling in summer.

[0044] like Figure 3As shown, under the winter waste heat matching condition, the coolant pump 1 pressurizes and delivers the coolant to the first heat exchanger 2 for heat exchange. After the waste heat of the coolant is recovered by the first heat exchanger 2, it flows through the first three-way valve 3 for diversion. The first part of the coolant flows through the third three-way valve 5 through the first adsorption heat exchanger 8 to release heat. After heat release, this part of the coolant flows through the fifth three-way valve 7 and then flows through the second three-way valve 4; the second part of the coolant flows through the sixth three-way valve 10 through the second adsorption heat exchanger 9 to release heat. After heat release, this part of the coolant flows through the fourth three-way valve 6 and then flows through the second three-way valve 4 to merge with the first part of the coolant. The merged coolant flows through the second three-way valve 4 back to the coolant pump 1, thereby completing the heating under the winter waste heat matching condition.

[0045] like Figure 4 As shown, in the working condition of insufficient residual heat in winter, the coolant pump 1 pressurizes the coolant and delivers it to the first heat exchanger 2 for heat exchange. After the residual heat of the first heat exchanger 2 is recovered, the coolant flows through the first three-way valve 3, and then flows through the sixth three-way valve 10 and the seventh three-way valve 12 in sequence. After passing through the seventh three-way valve 12, the coolant flows through the third heat exchanger 14 to release heat, and then flows through the eighth three-way valve 13, the fifth three-way valve 7 and the second three-way valve 4 in sequence, and finally returns to the coolant pump 1 to complete the cycle. The compressor 15 pressurizes the refrigerant and delivers it to the second heat exchanger 11 for heat dissipation. After the refrigerant dissipates heat to a supercooled state through the second heat exchanger 11, it is throttled and cooled by the expansion valve 17. The cooled refrigerant absorbs heat through the fourth heat exchanger 16 to become a superheated state, and finally returns to the compressor 15 to be re-pressurized to complete the cycle. Under this working condition, the first part of the air first passes through the third heat exchanger 14 to transfer heat to the fourth heat exchanger 16 to improve the heat pump performance, and the second part of the air passes through the second heat exchanger 11 to be heated to achieve winter heating.

[0046] like Figure 5As shown, under the working condition of excessive waste heat in winter, the coolant pump 1 pressurizes the coolant and delivers it to the first heat exchanger 2 for heat exchange. After the waste heat of the coolant is recovered by the first heat exchanger 2, it flows through the first three-way valve 3 for diversion. The first part of the coolant flows through the third three-way valve 5 through the first adsorption heat exchanger 8 for heat release. After heat release, this part of the coolant flows through the fifth three-way valve 7 and then flows through the second three-way valve 4. The second part of the coolant flows through the sixth three-way valve 10 through the second adsorption heat exchanger 9 for heat release. After heat release, this part of the coolant flows The coolant flows through the fourth three-way valve 6 and then through the second three-way valve 4 to merge with the first part of the coolant. The merged coolant flows through the second three-way valve 4 and returns to the coolant pump 1, thereby completing the heating under the winter waste heat matching condition; in addition, the second part of the coolant is divided into a third part of the coolant at the sixth three-way valve 10, and the third part of the coolant flows through the third heat exchanger 14 through the seventh three-way valve 12 to release heat, and then flows through the eighth three-way valve 13, the fifth three-way valve 7 and the second three-way valve 4 in sequence, and finally returns to the coolant pump 1 to complete the heat dissipation of excess heat.

[0047] like Figure 6 As shown, in the air duct operation mode under the summer working condition when the first adsorption heat exchanger 8 performs a desorption cycle: the first fan 18 controls the flow rate of outdoor fresh air at the outdoor fresh air duct outlet, and the second fan 19 controls the flow rate of indoor return air at the indoor return air duct outlet; the first damper 20 controls the ratio of outdoor fresh air flowing through the fourth heat exchanger 16, the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 according to the distance from the first damper left opening 20a and the first damper right opening 20b and the heat exchange amount; the second damper 21 controls the ratio of outdoor fresh air flowing through the fourth heat exchanger 16, the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 according to the distance from the first damper left opening 20a and the first damper right opening 20b at the bifurcation of the air duct channel flowing through the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 The distance between the right opening 21b of the second damper and the heat exchange amount are used to control the ratio of air flowing through the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9; since the first adsorption heat exchanger 8 needs to be heated and desorbed, the third damper 22 is at the left opening 22a of the third damper at this time, and the air is directly discharged to the outside after passing through the first adsorption heat exchanger 8; while the second adsorption heat exchanger 9 adsorbs and dehumidifies the air, and the fourth damper 23 is at the left opening 23a of the fourth damper at this time, and the air passes through the second adsorption heat exchanger 9 and then through the second heat exchanger 11 for cooling and then transported to the room, thereby realizing dehumidification and cooling in civil, commercial and industrial buildings in summer.

[0048] like Figure 7As shown, in the air duct operation mode under the summer working condition when the second adsorption heat exchanger 9 performs a desorption cycle: the first fan 18 and the second fan 19 respectively control the flow rate of outdoor fresh air and indoor return air, and the first damper 20 and the second damper 21 control the ratio of the two air duct bifurcations; because the second adsorption heat exchanger 9 needs to be heated and desorbed, the fourth damper 23 is at the right opening 23b of the fourth damper at this time, and the air is directly discharged to the outside after passing through the second adsorption heat exchanger 9; while the first adsorption heat exchanger 8 performs adsorption and dehumidification on the air, and the third damper 22 is at the right opening 22b of the third damper at this time, and the air passes through the first adsorption heat exchanger 8 and then through the second heat exchanger 11 for cooling and then transported to the room, thereby realizing dehumidification and cooling in civil, commercial and industrial buildings in summer.

[0049] like Figure 8 As shown, the duct operation mode under winter conditions when the waste heat is matched: since there is no need to dissipate heat to the outdoors and there is no need to activate the heat pump, the first damper 20 is adjusted to the right opening 20b of the first damper to allow all outdoor fresh air to merge with the indoor return air; the first fan 18 and the second fan 19 respectively control the flow rates of outdoor fresh air and indoor return air, and the first damper 20 and the second damper 21 control the ratio of the two air duct bifurcations; since there is no need to perform dehumidification in turn through the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 in winter, the third damper 22 and the fourth damper 23 are respectively located at the right opening 22b of the third damper and the left opening 23a of the fourth damper, and the air is heated by the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 and then transported to the room through the non-working second heat exchanger 11, thereby realizing heating in civil, commercial and industrial buildings in winter.

[0050] like Fig. 9 As shown, the duct operation mode under winter conditions when the residual heat is insufficient is as follows: the first fan 18 and the second fan 19 control the flow of outdoor fresh air and indoor return air respectively, and the first damper 20 and the second damper 21 control the ratio of the two duct bifurcations; due to insufficient residual heat, all the heat is dissipated through the third heat exchanger 14, and the outdoor fresh air transfers the heat of the third heat exchanger 14 to the fourth heat exchanger 16, thereby improving the performance of the heat pump; the third damper 22 and the fourth damper 23 are respectively located at the third damper right opening 22b and the fourth damper left opening 23a, and the air passes through the non-operating first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 and then is heated by the second heat exchanger 11 and transferred to the room, thereby realizing heating in civil, commercial and industrial buildings in winter; in addition, when the residual heat is insufficient, it is necessary to decide whether to start the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 according to the amount of residual heat and the amount of heat exchange of the heat exchanger.

[0051] like Fig.10As shown, the duct operation mode under winter conditions when there is too much residual heat: the first fan 18 and the second fan 19 control the flow rate of outdoor fresh air and indoor return air respectively, and the first damper 20 and the second damper 21 control the ratio of the two duct bifurcations; due to the excessive residual heat, the first adsorption heat exchanger 8, the second adsorption heat exchanger 9 and the third heat exchanger 14 need to be started at the same time to dissipate heat, and the outdoor fresh air first passes through the third heat exchanger 14 and then passes through the non-working fourth heat exchanger 16 to take away the excess heat; the third damper 22 and the fourth damper 23 are respectively located at the third damper right opening 22b and the fourth damper left opening 23a, and the air is heated by the first adsorption heat exchanger 8 and the second adsorption heat exchanger 9 and then transported to the room through the non-working second heat exchanger 11, thereby realizing heating in civil, commercial and industrial buildings in winter.

[0052] In summary, although the present invention has been disclosed as above in terms of preferred embodiments, the above preferred embodiments are not intended to limit the present invention. A person skilled in the art may make various changes and modifications without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be based on the scope defined in the claims.

Claims

1. A comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement, characterized in that: Including adsorption dehumidification system and heat pump air conditioning system for waste heat utilization; The waste heat utilization adsorption dehumidification system comprises a coolant pump (1), a first heat exchanger (2), a first three-way valve (3), a second three-way valve (4), a third three-way valve (5), a fourth three-way valve (6), a fifth three-way valve (7), a first adsorption heat exchanger (8), a second adsorption heat exchanger (9), a sixth three-way valve (10), a seventh three-way valve (12), an eighth three-way valve (13) and a third heat exchanger (14); Wherein, in the mode in which the first adsorption heat exchanger (8) performs a desorption cycle, the outlet end of the coolant pump (1) is connected to the inlet end of the first heat exchanger (2) through a coolant pipeline. After waste heat recovery, the outlet end of the first heat exchanger (2) is connected to the inlet end of the first three-way valve (3) through a coolant pipeline. The outlet end of the first three-way valve (3) is connected to the inlet end of the third three-way valve (5) through a coolant pipeline. The outlet end of the third three-way valve (5) is connected to the inlet end of the first adsorption heat exchanger (8) through a coolant pipeline. After heat absorption and desorption, the first adsorption heat exchanger (8) is connected to the inlet end of the fifth three-way valve (7) through a coolant pipeline. The outlet end of the fifth three-way valve (7) is connected to the inlet end of the second three-way valve (4) through a coolant pipeline. The outlet end of the second three-way valve (4) is connected to the inlet end of the coolant pump (1) through a coolant pipeline, thereby completing the desorption cycle of the first adsorption heat exchanger (8); In the mode in which the second adsorption heat exchanger (9) performs a desorption cycle, the outlet end of the coolant pump (1) is connected to the inlet end of the first heat exchanger (2) through a coolant pipeline. After waste heat recovery, the outlet end of the first heat exchanger (2) is connected to the inlet end of the first three-way valve (3) through a coolant pipeline. The outlet end of the first three-way valve (3) is connected to the inlet end of the sixth three-way valve (10) through a coolant pipeline. The outlet end of the sixth three-way valve (10) is connected to the inlet end of the second adsorption heat exchanger (9) through a coolant pipeline. After endothermic desorption, the second adsorption heat exchanger (9) is connected to the inlet end of the fourth three-way valve (6) through a coolant pipeline. The outlet end of the fourth three-way valve (6) is connected to the inlet end of the second three-way valve (4) through a coolant pipeline. The outlet end of the second three-way valve (4) is connected to the inlet end of the coolant pump (1) through a coolant pipeline, thereby completing the desorption cycle of the second adsorption heat exchanger (9). In the mode in which the third heat exchanger (14) is used for heating, the outlet end of the coolant pump (1) is connected to the inlet end of the first heat exchanger (2) through a coolant pipeline. After waste heat recovery, the outlet end of the first heat exchanger (2) is connected to the inlet end of the first three-way valve (3) through a coolant pipeline. The outlet end of the first three-way valve (3) is connected to the inlet end of the sixth three-way valve (10) through a coolant pipeline. The outlet end of the sixth three-way valve (10) is connected to the inlet end of the seventh three-way valve (12) through a coolant pipeline. The outlet end of the seventh three-way valve (12) is connected to the inlet end of the third heat exchanger (14) through a coolant pipeline. After heat release, the outlet end of the third heat exchanger (14) is connected to the inlet end of the eighth three-way valve (12) through a coolant pipeline. The inlet end of the three-way valve (13) is connected, the outlet end of the eighth three-way valve (13) is connected to the inlet end of the fifth three-way valve (7) through a coolant pipeline, the outlet end of the fifth three-way valve (7) is connected to the inlet end of the second three-way valve (4) through a coolant pipeline, and the outlet end of the second three-way valve (4) is connected to the inlet end of the coolant pump (1) through a coolant pipeline, thereby completing the heating cycle of the third heat exchanger (14); in the heating mode, the third heat exchanger (14) selects whether to heat with the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) at the same time according to the size of the heat load in the civil, commercial and industrial buildings; the third heat exchanger (14) can be started to dissipate heat when there is too much waste heat in the fuel cell; The heat pump air conditioning system comprises a second heat exchanger (11), a compressor (15), a fourth heat exchanger (16) and an expansion valve (17); in a cooling mode, the outlet end of the second heat exchanger (11) is connected to the inlet end of the compressor (15) via a refrigerant pipeline, the outlet end of the compressor (15) is connected to the inlet end of the fourth heat exchanger (16) via a refrigerant pipeline, the outlet end of the fourth heat exchanger (16) is connected to the inlet end of the expansion valve (17) via a refrigerant pipeline, and the outlet end of the expansion valve (17) is connected to the inlet end of the second heat exchanger (11) via a refrigerant pipeline. The outlet end of the second heat exchanger (11) is connected to the inlet end of the expansion valve (17) through a refrigerant pipe, thereby completing the connection of the heat pump air conditioning system in the cooling mode; in the heating mode, the outlet end of the second heat exchanger (11) is connected to the inlet end of the expansion valve (17) through a refrigerant pipe, the outlet end of the expansion valve (17) is connected to the inlet end of the fourth heat exchanger (16) through a refrigerant pipe, the outlet end of the fourth heat exchanger (16) is connected to the inlet end of the compressor (15) through a refrigerant pipe, and the outlet end of the compressor (15) is connected to the inlet end of the second heat exchanger (11) through a refrigerant pipe, thereby completing the connection of the heat pump air conditioning system in the heating mode.

2. According to claim 1, a comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement is characterized in that: The integrated energy supply device also includes an air duct system, wherein the air duct system includes a first fan (18), a second fan (19), a first damper (20), a first damper left opening (20a), a first damper right opening (20b), a second damper (21), a second damper left opening (21a), a second damper right opening (21b), a third damper (22), a third damper left opening (22a), a third damper right opening (22b), a fourth damper (23), a fourth damper left opening (23a), and a fourth damper right opening (23b). The air door has a right opening (23b); wherein the first fan (18) controls the flow rate of outdoor fresh air at the outdoor fresh air pipe opening; the second fan (19) controls the flow rate of indoor return air at the indoor return air pipe opening; the first air door (20) controls the flow rate of outdoor fresh air at the bifurcation of the air duct passage passing through the fourth heat exchanger (16), the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) according to the distance between the first air door left opening (20a) and the first air door right opening (20b) and the heat exchange amount. The ratio of air passing through the fourth heat exchanger (16), the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9); the second damper (21) controls the ratio of air passing through the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) according to the distance between the second damper left opening (21a) and the second damper right opening (21b) and the heat exchange amount at the bifurcation of the air duct passages passing through the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9); the third damper (22) controls the ratio of air passing through the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) according to the distance between the second damper left opening (21a) and the second damper right opening (21b) and the heat exchange amount; At the fork of the air duct passage between the outdoor and the second heat exchanger (11), the direction of air flow is controlled according to the third air door left opening (22a), the third air door right opening (22b) and the working mode of the first adsorption heat exchanger (8); at the fork of the air duct passage between the outdoor and the second heat exchanger (11), the fourth air door (23) controls the direction of air flow according to the fourth air door left opening (23a), the fourth air door right opening (23b) and the working mode of the second adsorption heat exchanger (9).

3. The comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement according to claim 1 is characterized in that: The coolant in the coolant pipeline is a 50% propylene glycol aqueous solution, and the first adsorption heat exchanger (8) and the second adsorption heat exchanger (9) are coated parallel flow heat exchangers.

4. The comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement according to claim 2 is characterized in that: Under summer conditions when the first adsorption heat exchanger (8) performs a desorption cycle, the coolant pump (1) pressurizes and delivers the coolant to the first heat exchanger (2) for heat exchange. After the waste heat of the first heat exchanger (2) is recovered, the coolant flows through the first three-way valve (3) and then flows through the third three-way valve (5). The first adsorption heat exchanger (8) desorbs the heat of the coolant by absorbing it. After releasing the heat, the coolant flows through the fifth three-way valve (7) and then flows through the second three-way valve (4) and finally returns to the coolant pump (1), thereby completing the first adsorption heat exchanger (8). The compressor (15) pressurizes the refrigerant and transports it to the fourth heat exchanger (16) for heat dissipation. The refrigerant dissipates heat to a supercooled state through the fourth heat exchanger (16) and then is throttled and cooled through the expansion valve (17). The cooled refrigerant absorbs heat through the second heat exchanger (11) and becomes a superheated state, and finally returns to the compressor (15) for re-pressurization to complete the cycle. Under this working condition, the air is dehumidified through the second adsorption heat exchanger (9) and then cooled through the second heat exchanger (11), thereby achieving dehumidification and cooling in summer.

5. The comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement according to claim 2 is characterized in that: In summer conditions when the second adsorption heat exchanger (9) performs a desorption cycle, the coolant pump (1) pressurizes and delivers the coolant to the first heat exchanger (2) for heat exchange. After the waste heat of the first heat exchanger (2) is recovered, the coolant flows through the first three-way valve (3) and then flows through the sixth three-way valve (10). The second adsorption heat exchanger (9) desorbs the heat of the coolant. After releasing the heat, the coolant flows through the fourth three-way valve (6) and then flows through the second three-way valve (4), and finally returns to the coolant pump (1), thereby completing the second adsorption heat exchanger (9). The compressor (15) pressurizes the refrigerant and transports it to the fourth heat exchanger (16) for heat dissipation. The refrigerant dissipates heat to a supercooled state through the fourth heat exchanger (16) and is then throttled and cooled by the expansion valve (17). The cooled refrigerant absorbs heat to a superheated state through the second heat exchanger (11) and finally returns to the compressor (15) for re-pressurization to complete the cycle. Under this operating condition, the air is dehumidified through the first adsorption heat exchanger (8) and then cooled through the second heat exchanger (11), thereby achieving dehumidification and cooling in summer.

6. The comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement according to claim 2 is characterized in that: Under the winter waste heat matching condition, the coolant pump (1) pressurizes and delivers the coolant to the first heat exchanger (2) for heat exchange. After the waste heat of the coolant is recovered by the first heat exchanger (2), it flows through the first three-way valve (3) for diversion. The first part of the coolant flows through the third three-way valve (5) through the first adsorption heat exchanger (8) for heat release. After heat release, this part of the coolant flows through the fifth three-way valve (7) and then flows through the second three-way valve (4); the second part of the coolant flows through the sixth three-way valve (10) through the second adsorption heat exchanger (9) for heat release. After heat release, this part of the coolant flows through the fourth three-way valve (6) and then flows through the second three-way valve (4) to merge with the first part of the coolant. The merged coolant flows through the second three-way valve (4) and returns to the coolant pump (1), thereby completing heating under the winter waste heat matching condition.

7. The comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement according to claim 2 is characterized in that: In winter, when the residual heat is insufficient, the coolant pump (1) pressurizes the coolant and delivers it to the first heat exchanger (2) for heat exchange. After the residual heat is recovered by the first heat exchanger (2), the coolant flows through the first three-way valve (3), and then flows through the sixth three-way valve (10) and the seventh three-way valve (12) in sequence. After passing through the seventh three-way valve (12), the coolant flows through the third heat exchanger (14) to release heat, and then flows through the eighth three-way valve (13), the fifth three-way valve (7) and the second three-way valve (4) in sequence, and finally returns to the coolant pump (1) to complete the cycle. The compressor (15) The refrigerant is pressurized and transported to the second heat exchanger (11) for heat dissipation. After the refrigerant dissipates heat to a supercooled state through the second heat exchanger (11), it is throttled and cooled through the expansion valve (17). The cooled refrigerant absorbs heat through the fourth heat exchanger (16) to become a superheated state, and finally returns to the compressor (15) for re-pressurization to complete the cycle. Under this working condition, the first part of the air first passes through the third heat exchanger (14) to transfer heat to the fourth heat exchanger (16) to improve the performance of the heat pump, and the second part of the air is heated through the second heat exchanger (11) to achieve winter heating.

8. The comprehensive energy supply device combining fuel cell waste heat dehumidification and heat pump efficiency enhancement according to claim 2 is characterized in that: Under the condition of excessive waste heat in winter, the coolant pump (1) pressurizes and delivers the coolant to the first heat exchanger (2) for heat exchange. After the waste heat of the coolant is recovered by the first heat exchanger (2), it flows through the first three-way valve (3) for diversion. The first part of the coolant flows through the third three-way valve (5) through the first adsorption heat exchanger (8) for heat release. After heat release, this part of the coolant flows through the fifth three-way valve (7) and then flows through the second three-way valve (4). The second part of the coolant flows through the sixth three-way valve (10) through the second adsorption heat exchanger (9) for heat release. After heat release, this part of the coolant flows through the fourth three-way valve (5). The three-way valve (6) then flows through the second three-way valve (4) to merge with the first part of the coolant, and the merged coolant flows through the second three-way valve (4) and returns to the coolant pump (1), thereby completing the heating under the winter waste heat matching working condition; in addition, the second part of the coolant is divided into a third part of the coolant at the sixth three-way valve (10), and the third part of the coolant flows through the seventh three-way valve (12) and flows through the third heat exchanger (14) to release heat, and then flows through the eighth three-way valve (13), the fifth three-way valve (7) and the second three-way valve (4) in sequence, and finally returns to the coolant pump (1) to complete the heat dissipation of excess heat.

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