Air source heat pump heating system based on solar frequency heat-electricity combined utilization and control method

Abstract

The application provides a kind of air source heat pump heating system and control method based on solar frequency division heat-electricity combined utilization, belong to solar heat pump heating technical field.To solve how to effectively combine solar energy and air source heat pump, realize all-weather clean heating in severe cold area, achieve the problem of self-production and self-sale.The system includes solar light condensation frequency division utilization photovoltaic power generation and heat collection subsystem and low-temperature air source heat pump subsystem, solar light condensation frequency division utilization photovoltaic power generation and heat collection subsystem generates electric energy and makes the circulating medium in heat collection tube warm, at the same time, the surplus electric energy is stored;Low-temperature air source heat pump subsystem is coupled by two-stage system, the first stage is conventional compression heat pump cycle, the second stage can switch conventional compression, low compression ratio compression, conventional injection, compression-injection coupled heat pump cycle according to different working condition requirements.Only relying on solar energy can realize the function of solar air source heat pump heating in severe cold area, effectively reduce energy consumption.

Description

Technical Field

[0001] This invention relates to the field of solar heat pump heating technology, and more specifically, to an air source heat pump heating system and control method based on the combined utilization of solar energy frequency division heat and electricity. Background Technology

[0002] Heat pumps are a new energy technology characterized by cleanliness, energy saving, and renewability, making them an ideal alternative. Air source heat pumps, aside from being affected by ambient temperature, are virtually unaffected by other conditions, offering better adaptability. However, in the entire air source heat pump cycle, as the ambient temperature decreases, the evaporation temperature also decreases; while the required heating temperature (condensation temperature) remains constant. This results in a large temperature difference between the evaporation and condensation temperatures. To achieve heating under these conditions, the compression ratio becomes excessively high, leading to an increase in exhaust temperature. Consequently, the heat pump's heating efficiency decreases, the heat exchanger's heat transfer effect deteriorates, and the system cannot function properly. This limits the use of air source heat pumps in extremely cold regions. In my country's extremely cold regions, the average winter temperature approaches -30°C, while the required condensation temperature is above 70°C. The temperature difference between the evaporation and condensation of the heat pump exceeds 100°C, a requirement that traditional single-stage compression cycles struggle to meet. This necessitates new demands on the system design.

[0003] In addition, solar energy, as the renewable energy source with the greatest development potential and the most readily available, has good energy substitution properties. Therefore, how to combine solar thermal power utilization with new system forms of air source heat pumps is of great significance for solving the heating problem in northern regions, and its research value is even higher for heating in frigid regions. Summary of the Invention

[0004] The technical problem to be solved by this invention is:

[0005] To address the issue of how to effectively combine solar energy and air source heat pumps to achieve clean heating in frigid regions around the clock and realize self-production and self-sales.

[0006] The technical solution adopted by the present invention to solve the above-mentioned technical problems is as follows:

[0007] This invention provides an air-source heat pump heating system based on solar energy frequency division combined heat and electricity utilization.

[0008] It includes a trough-type solar collector, photovoltaic panels, frequency divider, collector tubes, oil tank, oil circulation pump, generator, energy storage converter, first ejector, first compressor, condenser, liquid receiver, first expansion valve, evaporator-condenser, refrigerant circulation pump, second expansion valve, evaporator, second compressor, first regulating valve, second regulating valve, third regulating valve, and fourth regulating valve.

[0009] The oil outlet of the solar collector tube is connected to the oil inlet of the oil tank; the oil outlet of the oil tank is connected to the oil inlet of the oil circulation pump; the oil outlet of the oil circulation pump is connected to the oil inlet of the generator; and the oil outlet of the generator is connected to the oil inlet of the solar collector tube.

[0010] The generator's outlet is connected to the high-pressure inlet of the first ejector. A second regulating valve is installed on the low-pressure inlet pipe of the first ejector, and a first regulating valve is installed on the outlet pipe of the first ejector. The outlet of the first ejector is connected to both the inlet of the condenser and the inlet of the first compressor. A third regulating valve is installed on the inlet pipe of the first compressor, and a fourth regulating valve is installed on the outlet pipe of the first compressor. The condenser's outlet is connected to the inlet of the receiver tank, and the receiver tank's outlet is connected to the inlet of the first throttle valve. The first throttle valve's outlet is connected to the inlet of the secondary side of the evaporator-condenser. The outlets of the secondary side of the evaporator-condenser are connected to both the outlet of the first compressor and the low-pressure inlet of the first ejector. The other outlet of the receiver tank is connected to the inlet of the refrigerant circulation pump, and the refrigerant circulation pump's outlet is connected to the generator's inlet.

[0011] The liquid outlet on the primary side of the evaporator-condenser is connected to the liquid inlet of the second expansion valve. The liquid outlet of the second expansion valve is connected to the liquid inlet of the evaporator. The liquid outlet of the evaporator is connected to the liquid inlet of the second compressor. The liquid outlet of the second compressor is connected to the liquid inlet on the primary side of the evaporator-condenser.

[0012] The condenser has an inlet and an outlet on the other side.

[0013] The number of parabolic trough collectors is at least one. When the number of parabolic trough collectors is at least two, the parabolic trough collectors are evenly distributed. Each parabolic trough collector includes a collector tube, and multiple collector tubes are connected in series. At least one parabolic trough collector is connected to a photovoltaic panel. The photovoltaic panel is connected to an energy storage converter. The electrical energy generated by the photovoltaic panel can be stored in the energy storage converter and simultaneously undergoes DC-AC conversion. The energy storage converter is connected to a first compressor, an oil circulation pump, a refrigerant circulation pump, and a second compressor.

[0014] Furthermore, the oil tank can be a thermal storage tank.

[0015] A control method for an air source heat pump heating system based on solar frequency-division heat-electricity combined utilization.

[0016] During the daytime, open the first and second regulating valves, and close the third and fourth regulating valves;

[0017] The parabolic trough collector concentrates sunlight and reflects it to a frequency divider. After frequency division, short-wave radiation is reflected onto the photovoltaic panels to generate electricity, which is then stored in an energy storage converter. This electricity is converted from DC to AC for nighttime use. The electricity in the energy storage converter directly drives the oil circulation pump, refrigerant circulation pump, and second compressor to drive a primary compression heat pump cycle that uses low-temperature air as a low-grade heat source. The heat generated on the condenser side of the primary compression heat pump cycle acts on the evaporator side of the secondary heat pump cycle. Long-wave radiation is transmitted through the collector tubes to heat the heat transfer oil. This heat acts on the generator as the driving heat source for the jet heat pump. At the same time, the heat from the primary condenser side acts as a low-grade heat source to drive the jet heat pump cycle, realizing a compression-jet cascade solar air source heat pump cycle to ensure heating during the day.

[0018] At night, open the third and fourth regulating valves, and close the first and second regulating valves;

[0019] At night, the stored electrical energy in the energy storage converter is used as the power source for the first and second compressors. The first-stage compression heat pump cycle directly uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as a low-grade heat source, thus realizing a cascaded solar air source heat pump cycle and ensuring nighttime heating conditions.

[0020] A control method for an air source heat pump heating system based on solar frequency-division heat-electricity combined utilization.

[0021] During the daytime, open the first and second regulating valves, and close the third and fourth regulating valves;

[0022] The parabolic trough collector concentrates sunlight and reflects it to a frequency divider. After frequency division, short-wave radiation is reflected onto the photovoltaic panels, generating electricity which is then stored in an energy storage converter. This electricity is converted from DC to AC for nighttime use. The electricity in the energy storage converter directly drives the oil circulation pump, refrigerant circulation pump, and second compressor, driving a primary compression heat pump cycle that uses low-temperature air as a low-grade heat source. The heat generated on the condenser side of this cycle acts on the evaporator side of the secondary heat pump cycle. Long-wave radiation is transmitted through the collector tubes to heat the heat transfer oil. Part of this heat is stored in the heat storage tank for nighttime use, while the other part acts on the generator as the driving heat source for the jet heat pump. Simultaneously, the heat from the primary condenser side acts as a low-grade heat source to drive the jet heat pump cycle, realizing a compression-jet cascade solar air source heat pump cycle to ensure heating during the day.

[0023] At night, the first and second regulating valves are opened first, while the third and fourth regulating valves are closed; when the heating supply is insufficient, the third and fourth regulating valves are opened, while the first and second regulating valves are closed.

[0024] At night, the stored electrical energy in the energy storage inverter is used first to drive the oil circulation pump and the second compressor, driving the first-stage compression heat pump cycle with low-temperature air as the low-grade heat source. At the same time, the heat in the heat storage tank is used to act on the generator as the driving heat source for the jet heat pump. The heat on the first-stage condenser side is used as the low-grade heat source to drive the jet heat pump cycle, realizing a compression-jet cascade solar air source heat pump cycle. When the heat load demand is large and the driving heat of the heat storage tank is insufficient, the stored electrical energy in the energy storage inverter is used as the power source for the first and second compressors. The first-stage compression heat pump cycle directly uses low-temperature air as the low-grade heat source, and the heat generated on its condenser side is used as the low-grade heat source for the second-stage compression heat pump cycle, directly driving the second-stage compression heat pump cycle, realizing a cascade solar air source heat pump cycle, ensuring heating conditions at night.

[0025] This invention provides an air-source heat pump heating system based on solar energy frequency division combined heat and electricity utilization.

[0026] It includes a trough-type solar collector, photovoltaic panels, frequency divider, collector tubes, oil tank, oil circulation pump, generator, energy storage converter, first ejector, first compressor, condenser, liquid receiver, first expansion valve, evaporator-condenser, refrigerant circulation pump, second expansion valve, evaporator, second compressor, first regulating valve, second regulating valve, third regulating valve, and fourth regulating valve.

[0027] The oil outlet of the solar collector tube is connected to the oil inlet of the oil tank; the oil outlet of the oil tank is connected to the oil inlet of the oil circulation pump; the oil outlet of the oil circulation pump is connected to the oil inlet of the generator; and the oil outlet of the generator is connected to the oil inlet of the solar collector tube.

[0028] The generator's outlet is connected to the high-pressure inlet of the first ejector. A second regulating valve is installed on the low-pressure inlet pipe of the first ejector, and a first regulating valve is installed on the outlet pipe of the first ejector. The outlet of the first ejector is connected to both the condenser's inlet and a pipe for merging with the outlet of the first compressor. This pipe, after merging with the outlet of the first compressor, connects to the low-pressure inlet of the first ejector. A third regulating valve is installed on the pipe connecting the condenser's inlet to the first compressor's outlet. A fourth regulating valve is installed on the first compressor's inlet pipe. The condenser's outlet is connected to the inlet of the receiver tank. The receiver tank's outlet is connected to the inlet of the first throttle valve. The first throttle valve's outlet is connected to the inlet of the secondary side of the evaporator-condenser. The secondary side outlet of the evaporator-condenser is connected to the inlet of the first compressor. The other outlet of the receiver tank is connected to the inlet of the refrigerant circulation pump, and the refrigerant circulation pump's outlet is connected to the generator's inlet.

[0029] The liquid outlet on the primary side of the evaporator-condenser is connected to the liquid inlet of the second expansion valve. The liquid outlet of the second expansion valve is connected to the liquid inlet of the evaporator. The liquid outlet of the evaporator is connected to the liquid inlet of the second compressor. The liquid outlet of the second compressor is connected to the liquid inlet on the primary side of the evaporator-condenser.

[0030] The condenser has an inlet and an outlet on the other side.

[0031] The number of parabolic trough collectors is at least one. When the number of parabolic trough collectors is at least two, the parabolic trough collectors are evenly distributed. Each parabolic trough collector includes a collector tube, and multiple collector tubes are connected in series. At least one parabolic trough collector is connected to a photovoltaic panel. The photovoltaic panel is connected to an energy storage converter. The electrical energy generated by the photovoltaic panel can be stored in the energy storage converter and simultaneously undergoes DC-AC conversion. The energy storage converter is connected to a first compressor, an oil circulation pump, a refrigerant circulation pump, and a second compressor.

[0032] Furthermore, it also includes a second injector, a gas-liquid separator, a fifth regulating valve, a sixth regulating valve, a seventh regulating valve, an eighth regulating valve, a ninth regulating valve, a tenth regulating valve, an eleventh regulating valve, a twelfth regulating valve, a fifth working refrigerant line, a third mixed refrigerant line, a fourth mixed refrigerant line, and an eighth gaseous refrigerant line.

[0033] The liquid outlet of the condenser merges with the liquid outlet on one side of the liquid storage tank and is then connected to the high-pressure liquid inlet of the second ejector. A ninth regulating valve is installed on the high-pressure liquid inlet pipe of the second ejector. The liquid outlet of the second ejector is connected to the liquid inlet of the gas-liquid separator. The gas outlet of the gas-liquid separator merges with the gas outlet of the second ejector refrigerant line 82 and is then connected to the low-pressure gas inlet of the first ejector. A fifth regulating valve is installed on the gas outlet pipe of the gas-liquid separator. The gas outlet of the first ejector is connected to the gas inlets of the fourth and third mixed refrigerant lines. A sixth regulating valve is installed on the third mixed refrigerant line. The first regulating valve is located on the fourth mixed refrigerant line. The liquid outlet on the primary side of the evaporator-condenser is connected to the low-pressure liquid inlet of the second ejector. The gas outlet on the primary side of the evaporator-condenser is connected to the gas inlet of the eighth gaseous refrigerant line. A fourth regulating valve is installed on the eighth gaseous refrigerant line. The second ejector... A seventh regulating valve is installed on the low-pressure liquid inlet pipeline. The outlet of the eighth gaseous refrigerant pipeline and the outlet of the third mixed refrigerant pipeline merge and are connected to the inlet of the first compressor. The outlet of the first compressor is connected to the liquid inlet of the second ejector refrigerant pipeline and the liquid inlet of the sixth gaseous refrigerant pipeline. The outlet of the sixth gaseous refrigerant pipeline and the outlet of the fourth mixed refrigerant pipeline merge and are connected to the inlet of the fifth working refrigerant pipeline and the inlet of the condenser. An eighth regulating valve is installed on the fifth working refrigerant pipeline. The outlet of the fifth working refrigerant pipeline and the outlet of the generator merge and are connected to the high-pressure inlet of the first ejector. The outlet of the gas-liquid separator is connected to the inlet of the liquid storage tank and the inlet of the first throttle valve. A twelfth regulating valve is installed on the outlet pipeline of the gas-liquid separator. An eleventh regulating valve is installed on the inlet pipeline of the liquid storage tank. A tenth regulating valve is installed on the outlet pipeline on one side of the liquid storage tank.

[0034] Furthermore, the oil tank can be a thermal storage tank.

[0035] A control method for an air source heat pump heating system based on solar frequency-division heat-electricity combined utilization.

[0036] During the daytime, open the first regulating valve, the second regulating valve, and the fourth regulating valve, and close the third regulating valve;

[0037] The parabolic trough collector concentrates sunlight and reflects it to a frequency divider. After frequency division, short-wave radiation is reflected onto the photovoltaic panels, generating electricity which is then stored in an energy storage converter. This electricity is converted from DC to AC for nighttime use. The electricity in the energy storage converter directly drives the oil circulation pump, refrigerant circulation pump, first compressor, and second compressor to operate, driving a first-stage compression heat pump cycle that uses low-temperature air as a low-grade heat source. The heat generated on the condenser side of the first-stage compression heat pump cycle acts on the evaporator side of the second-stage heat pump cycle. Long-wave radiation is transmitted through the collector tubes to heat the heat transfer oil, and this heat acts on the generator as the driving heat source for the jet heat pump. At the same time, the heat from the first-stage condenser side serves as a low-grade heat source, and the first compressor acts as an auxiliary device for the jet heat pump to pressurize the ejector fluid, driving the jet heat pump cycle. This achieves a compression-jet coupled solar air source heat pump cycle, ensuring heating during the day.

[0038] At night, open the third and fourth regulating valves, and close the first and second regulating valves;

[0039] At night, the stored electrical energy in the energy storage converter is used as the power source for the first and second compressors. The first-stage compression heat pump cycle directly uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as a low-grade heat source, thus realizing a cascaded solar air source heat pump cycle and ensuring nighttime heating conditions.

[0040] A control method for an air-source heat pump heating system based on solar frequency-division heat-electricity combined utilization includes a conventional heat pump operation mode and a low-compression-ratio compression heat pump operation mode.

[0041] When in normal heat pump operation mode

[0042] During the day, open the first, second, fourth, tenth, and eleventh regulating valves, and close the third, fifth, sixth, seventh, eighth, ninth, and twelfth regulating valves.

[0043] The parabolic trough collector concentrates sunlight and reflects it to a frequency divider. After frequency division, short-wave radiation is reflected onto the photovoltaic panels to generate electricity, which is then stored in an energy storage converter. The electricity in the energy storage converter directly drives the oil circulation pump, refrigerant circulation pump, first compressor, and second compressor to operate, driving a first-stage compression heat pump cycle with low-temperature air as the low-grade heat source. The heat generated on the condenser side acts on the evaporator side of the second-stage heat pump cycle. Long-wave radiation is transmitted through the collector tubes to heat the heat transfer oil, and the heat acts on the generator as the driving heat source for the jet heat pump. At the same time, the heat from the first-stage condenser side serves as the low-grade heat source, and the compressor acts as an auxiliary device for the jet heat pump to pressurize the ejector fluid, driving the jet heat pump cycle. This realizes a compression-jet coupled solar air source heat pump cycle, ensuring heating during the day.

[0044] At night, open the third, fourth, tenth, and eleventh regulating valves, and close the first, second, fifth, sixth, seventh, eighth, ninth, and twelfth regulating valves.

[0045] At night, the stored electrical energy in the energy storage converter is used as the power source for the first and second compressors. The first-stage compression heat pump cycle uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as a low-grade heat source, thus realizing a cascade solar air source heat pump cycle and ensuring nighttime heating conditions.

[0046] When operating in low compression ratio compression heat pump mode

[0047] Open the third, fourth, fifth, sixth, seventh, eighth, ninth, and twelfth regulating valves; close the first, second, tenth, and eleventh regulating valves; and operate the low-compression ratio compression heat pump cycle with the first and second ejectors.

[0048] The stored electrical energy in the energy storage converter serves as the power source for the first and second compressors. The first-stage compression heat pump cycle directly uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side serves as the low-grade heat source for the second-stage low-compression ratio compression heat pump cycle, directly driving the second-stage low-compression ratio compression heat pump cycle. The second ejector serves as an auxiliary device for the second-stage compression refrigeration.

[0049] Furthermore, the trough-type solar collector includes an arc-shaped secondary reflector, a parabolic primary reflector, and a solar collector tube. The central axis of the solar collector tube coincides with the focal line of the parabolic primary reflector. The cross-sections of the parabolic primary reflector and the arc-shaped secondary reflector are both arc-shaped. The arc-shaped secondary reflector is located above the solar collector tube, and the openings of the parabolic primary reflector and the parabolic secondary reflector are arranged facing each other.

[0050] The radius r of the circular arc secondary reflector is...

[0051]

[0052] In the formula, a is the length of OB; b1 is the coefficient between OO′ and radius r; The edge angle of a parabolic primary reflector;

[0053] The width W of the arc-shaped secondary reflector is...

[0054]

[0055] In the formula, α is the tracking error angle; OB is the distance from the intersection point B of the most divergent ray of the parabolic primary mirror and the edge line on the other side to the intersection point O of the parabolic primary mirror surface;

[0056] The position d of the circular arc secondary reflector is...

[0057]

[0058] The arc-shaped secondary reflector is a circular arc structure with point O′ on the vertical line of the heat collection tube as the center, radius r, relative position d from the center of the heat collection tube, and width W.

[0059] Compared with the prior art, the beneficial effects of the present invention are:

[0060] This invention discloses an air-source heat pump heating system and control method based on solar frequency-division combined heat and electricity utilization, comprising a solar concentrating frequency-division photovoltaic power generation and heat collection subsystem and a low-temperature air-source heat pump subsystem. The solar concentrating frequency-division photovoltaic power generation and heat collection subsystem generates electricity and heats the circulating medium in the heat collection tube, while storing excess electricity. The low-temperature air-source heat pump subsystem consists of two coupled systems: the first stage is a compression heat pump cycle, and the second stage can switch between compression and jet heat pump cycles as needed.

[0061] This invention discloses an air-source heat pump heating system and control method based on solar energy frequency division and combined heat and electricity utilization. It employs a technology of first concentrating sunlight and then dividing the frequency to increase the energy flux density of the total solar beam, thereby improving solar energy utilization. Simultaneously, it reduces the area required for solar photovoltaic panels and frequency division films, simplifying tracking control. By setting a parabolic and discrete frequency division technique that satisfies the concentricity of the primary reflection after concentration and the collector, it reduces the dispersion of sunlight and the heating of photovoltaic panels after frequency division, effectively improving the power generation efficiency of photovoltaic modules. This maximizes the full-spectrum solar thermal and photoelectric cascade utilization, improving the utilization rate of solar energy across the entire wavelength range.

[0062] This invention discloses an air source heat pump heating system and control method based on solar frequency-division heat-electric combined utilization. It matches solar thermal and photovoltaic elements with a jet-compression coupled air source heat pump system to realize a solar air source heat pump. In the conventional heat pump operation mode, the first stage uses photovoltaic compression and the second stage uses solar thermal jet air source for heating during the day, while the first and second stages use both photovoltaic compression and air source for heating at night, achieving all-weather heating. In addition, it can be switched to a low compression ratio heat pump operation mode. By adding a steam ejector, the compressor inlet pressure is increased, the compression ratio of the entire two-stage compression heat pump cycle is reduced, the compressor stability is improved, and the cascade heat pump cycle operation is made more stable and safer.

[0063] Air source heat pumps can provide heating by relying solely on solar energy, without requiring any external energy input.

[0064] This invention discloses an air source heat pump heating system and control method based on solar energy frequency division heat-electric combined utilization. It solves the problem of reduced heating efficiency of air source heat pumps caused by increased compression ratio and excessively high exhaust temperature due to low outdoor temperature in extremely cold regions. At the same time, it uses free energy sources such as solar energy and air energy to achieve heating, effectively reducing energy consumption.

[0065] This invention discloses an air source heat pump heating system and control method based on solar energy frequency division heat-electric combined utilization. The first ejector and compressor adopt a parallel structure, and the two heat pump systems share a set of evaporators and condensers, which makes the structure simpler and reduces costs. The use of an electric compression heat pump system as the first-stage cycle provides higher safety assurance. Attached Figure Description

[0066] Figure 1 The structure of the air source heat pump heating system based on solar frequency division heat-electric combined utilization in this embodiment of the invention is shown below. Figure 1 ;

[0067] Figure 2 The structure of the air source heat pump heating system based on solar frequency division heat-electric combined utilization in this embodiment of the invention is shown below. Figure 2 ;

[0068] Figure 3 The structure of the air source heat pump heating system based on solar frequency division heat-electric combined utilization in this embodiment of the invention is shown below. Figure 3 ;

[0069] Figure 4 The structure of the air source heat pump heating system based on solar frequency division heat-electric combined utilization in this embodiment of the invention is shown below. Figure 4 ;

[0070] Figure 5 The structure of the air source heat pump heating system based on solar frequency division heat-electric combined utilization in this embodiment of the invention is shown below. Figure 5 ;

[0071] Figure 6 The structure of the air source heat pump heating system based on solar frequency division heat-electric combined utilization in this embodiment of the invention is shown below. Figure 6 ;

[0072] Figure 7 This is a solar radiation path diagram of the slotted laser in an embodiment of the present invention;

[0073] Figure 8 This is a schematic diagram of the arc-shaped secondary reflector system in an embodiment of the present invention;

[0074] Figure 9 This is step one of the design method for the arc-shaped secondary reflector in this embodiment of the invention;

[0075] Figure 10 This is step two of the design method for the arc-shaped secondary reflector in this embodiment of the invention;

[0076] Figure 11 This is step three of the design method for the arc-shaped secondary reflector in this embodiment of the invention;

[0077] Figure 12 This is a diagram illustrating the design method of the arc-shaped secondary reflector for a trough-type concentrating solar collector system with the collector tubes offset vertically upwards, as described in this invention.

[0078] Figure 13 This is a diagram illustrating the design method of the arc-shaped secondary reflector for a trough-type concentrating solar collector system with the collector tube offset vertically downward, as described in this invention.

[0079] Figure 14 This is a schematic diagram of the offset direction when the heat collection tube is offset vertically in an embodiment of the present invention.

[0080] Explanation of reference numerals in the attached figures:

[0081] 1. Parabolic trough collector; 2. Photovoltaic panel; 3. Frequency divider; 4. Collector tube; 5. Oil tank; 6. Oil circulation pump; 7. Generator; 8. Energy storage converter; 9. First ejector; 10. First compressor; 11. Condenser; 12. Liquid receiver; 13. First throttle valve; 14. Evaporator-condenser; 15. Refrigerant circulation pump; 16. Second throttle valve; 17. Evaporator; 18. Second compressor; 19. Energy storage tank; 20. Second ejector; 21. Gas-liquid separator; 30. First regulating valve; 31. Second regulating valve; 32. Third regulating valve; 33. Fourth regulating valve; 34. Fifth... 35. Regulating valve; 36. Sixth regulating valve; 37. Seventh regulating valve; 38. Eighth regulating valve; 39. Ninth regulating valve; 40. Tenth regulating valve; 41. Eleventh regulating valve; 60. Twelfth regulating valve; 61. First oil line; 62. Second oil line; 63. Third oil line; 64. Fourth oil line; 65. First working refrigerant line; 66. First ejector refrigerant line; 67. First refrigerant line; 68. Second liquid refrigerant line; 69. First liquid refrigerant line; 70. Second gaseous refrigerant line; 71. First mixed refrigerant line; 72. First gaseous refrigerant line; 73. Third gaseous refrigerant line; 74. Second working refrigerant line; 75. Third working refrigerant line; 76. Fourth gaseous refrigerant line; 77. Fifth gaseous refrigerant line; 78. Third refrigerant line; 79. Third liquid refrigerant line; 80. First heat transfer medium line; 81. Second heat transfer medium line; 82. Second ejector refrigerant line; 83. Sixth gaseous refrigerant line; 84. Fourth refrigerant line; 85. Fifth refrigerant line; 86. Fourth working refrigerant line; 87. Third ejector refrigerant line; 88. Second 89. Mixed refrigerant line; 90. Fourth ejector refrigerant line; 91. Fifth ejector refrigerant line; 92. Sixth working refrigerant line; 93. Third mixed refrigerant line; 94. Fourth mixed refrigerant line; 95. Seventh gaseous refrigerant line; 96. Eighth gaseous refrigerant line; 97. Fourth liquid refrigerant line; 98. Fifth liquid refrigerant line; 99. Sixth liquid refrigerant line; 120. First power line; 121. Second power line; 122. Third power line; 123. Fourth power line; 124. Fifth power line. Detailed Implementation

[0082] In the description of this invention, it should be noted that the terms used in the various embodiments, such as "upper," "lower," "front," "rear," "left," and "right," which indicate orientation, are only used to simplify the description of the positional relationships based on the accompanying drawings and do not mean that the components and devices referred to must be operated in accordance with the specific orientations and defined operations, methods, and structures in the specification. Such directional terms do not constitute a limitation of this invention.

[0083] In the description of this invention, it should be noted that the terms "first," "second," "third," "fourth," and "fifth" mentioned in the embodiments of this invention are for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined with "first," "second," "third," "fourth," and "fifth" may explicitly or implicitly include one or more of that feature.

[0084] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0085] Specific Implementation Plan 1: Combining Figure 1 As shown, this invention provides an air-source heat pump heating system based on the combined utilization of solar energy for frequency division of heat and electricity.

[0086] The system includes a trough-type solar collector 1, photovoltaic panels 2, a frequency divider 3, collector tubes 4, an oil tank 5, an oil circulation pump 6, a generator 7, an energy storage converter 8, a first ejector 9, a first compressor 10, a condenser 11, a liquid receiver 12, a first throttle valve 13, an evaporator-condenser 14, a refrigerant circulation pump 15, a second throttle valve 16, an evaporator 17, a second compressor 18, a first regulating valve 30, a second regulating valve 31, a third regulating valve 32, a fourth regulating valve 33, a first oil line 60, a second oil line 61, a third oil line 62, a fourth oil line 63, a first working refrigerant line 64, a first ejector refrigerant line 65, and a first mixed refrigerant line 71. First gaseous refrigerant line 72, second gaseous refrigerant line 70, first liquid refrigerant line 69, second liquid refrigerant line 68, first refrigerant line 67, second refrigerant line 66, third gaseous refrigerant line 73, second working refrigerant line 74, third working refrigerant line 75, fourth gaseous refrigerant line 76, third liquid refrigerant line 79, third refrigerant line 78, fifth gaseous refrigerant line 77, first heat transfer medium line 80, second heat transfer medium line 81, first power line 120, second power line 121, third power line 122, fourth power line 123, and fifth power line 124.

[0087] The oil outlet of the collector tube 4 is connected to the oil inlet of the first oil pipeline 60. The oil outlet of the first oil pipeline 60 is connected to the oil inlet of the oil tank 5. The oil outlet of the oil tank 5 is connected to the oil inlet of the second oil pipeline 61. The oil outlet of the second oil pipeline 61 is connected to the oil inlet of the oil circulation pump 6. The oil outlet of the oil circulation pump 6 is connected to the oil inlet of the third oil pipeline 62. The oil outlet of the third oil pipeline 62 is connected to the oil inlet of the generator 7. The oil outlet of the generator 7 is connected to the oil inlet of the fourth oil pipeline 63. The oil outlet of the fourth oil pipeline 63 is connected to the oil inlet of the collector tube 4.

[0088] The liquid outlet of generator 7 is connected to the liquid inlet of the first working refrigerant line 64. The liquid outlet of the first working refrigerant line 64 is connected to the high-pressure liquid inlet of the first ejector 9. The low-pressure liquid inlet of the first ejector 9 is connected to the liquid outlet of the first ejector refrigerant line 65. A second regulating valve 31 is provided on the first ejector refrigerant line 65. The liquid inlet of the first ejector refrigerant line 65 is connected to the liquid outlet of the second refrigerant line 66 and the liquid inlet of the third gaseous refrigerant line 73. A fourth regulating valve is provided on the third gaseous refrigerant line 73. Valve 33, the outlet of the third gaseous refrigerant line 73 is connected to the inlet of the first compressor 10, the outlet of the first compressor 10 is connected to the inlet of the first gaseous refrigerant line 72, the first gaseous refrigerant line 72 is equipped with a third regulating valve 32, the outlet of the first ejector 9 is connected to the inlet of the first mixed refrigerant line 71, the first mixed refrigerant line 71 is equipped with a first regulating valve 30, the outlet of the first mixed refrigerant line 71 is connected to the outlet of the first gaseous refrigerant line 72 and the inlet of the second gaseous refrigerant line 70. The liquid outlet of the second gaseous refrigerant line 70 is connected to the liquid inlet of the condenser 11. The liquid outlet of the condenser 11 is connected to the liquid inlet of the first liquid refrigerant line 69. The liquid outlet of the first liquid refrigerant line 69 is connected to the liquid inlet of the liquid storage tank 12. The liquid outlet of the liquid storage tank 12 is connected to the liquid inlet of the second liquid refrigerant line 68. The liquid outlet of the second liquid refrigerant line 68 is connected to the liquid inlet of the first throttle valve 13. The liquid outlet of the first throttle valve 13 is connected to the liquid inlet of the first refrigerant line 67. The liquid outlet of pipe 67 is connected to the liquid inlet on the secondary side of evaporator-condenser 14. The liquid outlet on the secondary side of evaporator-condenser 14 is connected to the liquid inlet of the second refrigerant pipe 66. The liquid outlet on the other side of the liquid storage tank 12 is connected to the liquid inlet of the second working refrigerant pipe 74. The liquid outlet of the second working refrigerant pipe 74 is connected to the liquid inlet of refrigerant circulation pump 15. The liquid outlet of refrigerant circulation pump 15 is connected to the liquid inlet of the third working refrigerant pipe 75. The liquid outlet of the third working refrigerant pipe 75 is connected to the liquid inlet of generator 7.

[0089] The liquid outlet on the primary side of the evaporator-condenser 14 is connected to the liquid inlet of the third liquid refrigerant line 79. The liquid outlet of the third liquid refrigerant line 79 is connected to the liquid inlet of the second throttle valve 16. The liquid outlet of the second throttle valve 16 is connected to the liquid inlet of the third refrigerant line 78. The liquid outlet of the third refrigerant line 78 is connected to the liquid inlet of the evaporator 17. The liquid outlet of the evaporator 17 is connected to the liquid inlet of the fifth gaseous refrigerant line 77. The liquid outlet of the fifth gaseous refrigerant line 77 is connected to the liquid inlet of the second compressor 18. The liquid outlet of the second compressor 18 is connected to the liquid inlet of the fourth gaseous refrigerant line 76. The liquid outlet of the fourth gaseous refrigerant line 76 is connected to the liquid inlet on the primary side of the evaporator-condenser 14.

[0090] The outlet of the first heat transfer medium pipeline 80 is connected to the inlet on the other side of the condenser 11, and the outlet on the other side of the condenser 11 is connected to the inlet of the second heat transfer medium pipeline 81.

[0091] The number of parabolic trough collectors 1 is at least one. When the number of parabolic trough collectors 1 is at least two, the parabolic trough collectors 1 are evenly distributed. Each parabolic trough collector 1 includes a collector tube 4, and multiple collector tubes 4 are connected in series. At least one parabolic trough collector 1 is connected to a photovoltaic panel 2. The photovoltaic panel 2 is connected to an energy storage converter 8. The electrical energy generated by the photovoltaic panel 2 can be stored in the energy storage converter 8, and DC-AC conversion is performed simultaneously. The energy storage converter 8 is connected to a first compressor 10, an oil circulation pump 6, a refrigerant circulation pump 15, and a second compressor 18 as a power source.

[0092] The power outlet of the energy storage converter 8 is connected to the power inlet of the first power line 120. The power outlet of the first power line 120 is connected to the power inlets of the second power line 121, the third power line 122, the fourth power line 123, and the fifth power line 124. The power outlet of the second power line 121 is connected to the power inlet of the oil circulation pump 6. The power outlet of the third power line 122 is connected to the power inlet of the first compressor 10. The power outlet of the fourth power line 123 is connected to the power inlet of the refrigerant circulation pump 15. The power outlet of the fifth power line 124 is connected to the power inlet of the second compressor 18.

[0093] The operating principle of this implementation plan is as follows:

[0094] During the day, open the first regulating valve 30 and the second regulating valve 31, and close the third regulating valve 32 and the fourth regulating valve 33.

[0095] The parabolic trough collector 1 concentrates sunlight to increase its energy flux density and simultaneously reflects it once to the frequency divider 3. After frequency division by the frequency divider 3, the short-wave reflection acts on the photovoltaic panel 2 to generate electricity, which is then stored in the energy storage converter 8. It undergoes DC-AC conversion for nighttime use. A portion of the electricity directly drives the oil circulation pump 6, the refrigerant circulation pump 15, and the second compressor 18 to drive the first-stage compression heat pump cycle, which uses low-temperature air as a low-grade heat source. The heat generated on the condenser side acts on the evaporator side of the second-stage heat pump cycle.

[0096] Long-wave transmission acts on the heat collector tube 4 to heat the heat transfer oil. The heat from this oil acts on the generator 7 as the driving heat source for the jet heat pump. At the same time, the heat from the first-stage condenser side is used as a low-grade heat source to drive the jet heat pump cycle, realizing the compression-jet cascade solar air source heat pump cycle to ensure heating during the day.

[0097] At night, open the third regulating valve 32 and the fourth regulating valve 33, and close the first regulating valve 30 and the second regulating valve 31.

[0098] At night, the stored electrical energy in the energy storage converter 8 is used as the power source for the first compressor 10 and the second compressor 18. The first-stage compression heat pump cycle directly uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as a low-grade heat source, thus realizing a cascaded solar air source heat pump cycle and ensuring nighttime heating conditions.

[0099] Preferably, the oil tank 5 can be a thermal storage tank 19.

[0100] Combination Figure 2 As shown, the operating principle is as follows:

[0101] During the day, open the first regulating valve 30 and the second regulating valve 31, and close the third regulating valve 32 and the fourth regulating valve 33.

[0102] The parabolic trough collector 1 concentrates sunlight to increase its energy flux density and simultaneously reflects it once to the frequency divider 3. After frequency division by the frequency divider 3, the short-wave reflection acts on the photovoltaic panel 2 to generate electricity, which is then stored in the energy storage converter 8. It undergoes DC-AC conversion for nighttime use. A portion of the electricity directly drives the oil circulation pump 6, the refrigerant circulation pump 15, and the second compressor 18 to drive the first-stage compression heat pump cycle, which uses low-temperature air as a low-grade heat source. The heat generated on the condenser side acts on the evaporator side of the second-stage heat pump cycle.

[0103] Long-wave transmission acts on the heat collector tube 4 to heat the heat transfer oil. Part of the heat is stored in the heat storage tank 19 for nighttime use, and another part of the heat acts on the generator 7 as the driving heat source for the jet heat pump. At the same time, the heat from the first-stage condenser side is used as a low-grade heat source to drive the jet heat pump cycle, realizing the compression-jet cascade solar air source heat pump cycle, ensuring heating conditions during the day.

[0104] At night, the first regulating valve 30 and the second regulating valve 31 are opened first, while the third regulating valve 32 and the fourth regulating valve 33 are closed. When the heating supply is insufficient, the third regulating valve 32 and the fourth regulating valve 33 are opened, while the first regulating valve 30 and the second regulating valve 31 are closed.

[0105] At night, the stored electrical energy in the energy storage converter 8 is used first to drive the oil circulation pump 6 and the second compressor 18 to drive the first-stage compression heat pump cycle with low-temperature air as the low-grade heat source. At the same time, the heat in the heat storage tank 19 is used to act on the generator 7 as the driving heat source of the jet heat pump. The heat on the first-stage condenser side is used as the low-grade heat source to drive the jet heat pump cycle, realizing the compression-jet cascade solar air source heat pump cycle.

[0106] When the heat load demand is large and the driving heat of the heat storage tank 19 is insufficient, the stored electrical energy in the energy storage converter 8 is used as the power source for the first compressor 10 and the second compressor 18. The first-stage compression heat pump cycle directly uses low-temperature air as the low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as the low-grade heat source, realizing a cascade solar air source heat pump cycle and ensuring nighttime heating conditions.

[0107] Specific Implementation Plan Two: Combining Figure 3 As shown, this invention provides an air-source heat pump heating system based on the combined utilization of solar energy for frequency division of heat and electricity.

[0108] The system includes: 1. Parabolic trough collector; 2. Photovoltaic panel; 3. Frequency divider; 4. Collector tube; 5. Oil tank; 6. Oil circulation pump; 7. Generator; 8. Energy storage converter; 9. First ejector; 10. First compressor; 11. Condenser; 12. Liquid receiver; 13. First throttle valve; 14. Evaporator-condenser; 15. Refrigerant circulation pump; 16. Second throttle valve; 17. Evaporator; 18. Second compressor; 30. First regulating valve; 31. Second regulating valve; 32. Third regulating valve; 33. Fourth regulating valve; 60. First oil line; 61. Second oil line; 62. Third oil line; 63. Fourth oil line; 64. First working refrigerant line; 71. First mixed refrigerant line; 70. Second gaseous refrigerant line. The following pipelines are listed: First liquid refrigerant pipeline 69, Second liquid refrigerant pipeline 68, First refrigerant pipeline 67, Second working refrigerant pipeline 74, Third working refrigerant pipeline 75, Fourth gaseous refrigerant pipeline 76, Third liquid refrigerant pipeline 79, Third refrigerant pipeline 78, Fifth gaseous refrigerant pipeline 77, First heat transfer medium pipeline 80, Second heat transfer medium pipeline 81, First power pipeline 120, Second power pipeline 121, Third power pipeline 122, Fourth power pipeline 123, Fifth power pipeline 124, Second ejector refrigerant pipeline 82, Sixth gaseous refrigerant pipeline 83, Fourth refrigerant pipeline 84, and Fifth refrigerant pipeline 85.

[0109] The oil outlet of the collector tube 4 is connected to the oil inlet of the first oil pipeline 60. The oil outlet of the first oil pipeline 60 is connected to the oil inlet of the oil tank 5. The oil outlet of the oil tank 5 is connected to the oil inlet of the second oil pipeline 61. The oil outlet of the second oil pipeline 61 is connected to the oil inlet of the oil circulation pump 6. The oil outlet of the oil circulation pump 6 is connected to the oil inlet of the third oil pipeline 62. The oil outlet of the third oil pipeline 62 is connected to the oil inlet of the generator 7. The oil outlet of the generator 7 is connected to the oil inlet of the fourth oil pipeline 63. The oil outlet of the fourth oil pipeline 63 is connected to the oil inlet of the collector tube 4.

[0110] The liquid outlet of generator 7 is connected to the liquid inlet of the first working refrigerant line 64. The liquid outlet of the first working refrigerant line 64 is connected to the high-pressure liquid inlet of the first ejector 9. The low-pressure liquid inlet of the first ejector 9 is connected to the liquid outlet of the second ejector refrigerant line 82. The liquid inlet of the second ejector refrigerant line 82 is connected to the liquid inlet of the sixth gaseous refrigerant line 83 and the liquid outlet of the fourth refrigerant line 84. A second regulating valve 31 is provided on the second ejector refrigerant line 82. The outlet of the sixth gaseous refrigerant line 83 is connected to the inlet of the second gaseous refrigerant line 70 and the outlet of the first mixed refrigerant line 71. A third regulating valve 32 is installed on the sixth gaseous refrigerant line 83. The outlet of the second gaseous refrigerant line 70 is connected to the inlet of the condenser 11. The outlet of the condenser 11 is connected to the inlet of the first liquid refrigerant line 69. The outlet of the first liquid refrigerant line 69 is connected to the inlet of the liquid storage tank 12. The liquid outlet of the second liquid refrigerant line 68 is connected to the liquid inlet of the second liquid refrigerant line 68. The liquid outlet of the second liquid refrigerant line 68 is connected to the liquid inlet of the first throttle valve 13. The liquid outlet of the first throttle valve 13 is connected to the liquid inlet of the first refrigerant line 67. The liquid outlet of the first refrigerant line 67 is connected to the liquid inlet of the secondary side of the evaporator-condenser 14. The liquid outlet of the secondary side of the evaporator-condenser 14 is connected to the liquid inlet of the fifth refrigerant line 85. The liquid outlet of the fifth refrigerant line 85 is connected to the liquid inlet of the first pressure... The liquid inlet of compressor 10 is connected to the liquid outlet of the first compressor 10, which is connected to the liquid inlet of the fourth refrigerant line 84. The liquid outlet on the other side of the liquid receiver 12 is connected to the liquid inlet of the second working refrigerant line 74. The liquid outlet of the second working refrigerant line 74 is connected to the liquid inlet of the refrigerant circulation pump 15. The liquid outlet of the refrigerant circulation pump 15 is connected to the liquid inlet of the third working refrigerant line 75. The liquid outlet of the third working refrigerant line 75 is connected to the liquid inlet of the generator 7.

[0111] The liquid outlet on the primary side of the evaporator-condenser 14 is connected to the liquid inlet of the third liquid refrigerant line 79. The liquid outlet of the third liquid refrigerant line 79 is connected to the liquid inlet of the second throttle valve 16. The liquid outlet of the second throttle valve 16 is connected to the liquid inlet of the third refrigerant line 78. The liquid outlet of the third refrigerant line 78 is connected to the liquid inlet of the evaporator 17. The liquid outlet of the evaporator 17 is connected to the liquid inlet of the fifth gaseous refrigerant line 77. The liquid outlet of the fifth gaseous refrigerant line 77 is connected to the liquid inlet of the second compressor 18. The liquid outlet of the second compressor 18 is connected to the liquid inlet of the fourth gaseous refrigerant line 76. The liquid outlet of the fourth gaseous refrigerant line 76 is connected to the liquid inlet on the primary side of the evaporator-condenser 14.

[0112] The outlet of the first heat transfer medium pipeline 80 is connected to the inlet on the other side of the condenser 11, and the outlet on the other side of the condenser 11 is connected to the inlet of the second heat transfer medium pipeline 81.

[0113] The number of parabolic trough collectors 1 is at least one. When the number of parabolic trough collectors 1 is at least two, the parabolic trough collectors 1 are evenly distributed. Each parabolic trough collector 1 includes a collector tube 4, and multiple collector tubes 4 are connected in series. At least one parabolic trough collector 1 is connected to a photovoltaic panel 2. The photovoltaic panel 2 is connected to an energy storage converter 8. The electrical energy generated by the photovoltaic panel 2 can be stored in the energy storage converter 8, and DC-AC conversion is performed simultaneously. The energy storage converter 8 is connected to a first compressor 10, an oil circulation pump 6, a refrigerant circulation pump 15, and a second compressor 18 as a power source.

[0114] The power outlet of the energy storage converter 8 is connected to the power inlet of the first power line 120. The power outlet of the first power line 120 is connected to the power inlets of the second power line 121, the third power line 122, the fourth power line 123, and the fifth power line 124. The power outlet of the second power line 121 is connected to the power inlet of the oil circulation pump 6. The power outlet of the third power line 122 is connected to the power inlet of the first compressor 10. The power outlet of the fourth power line 123 is connected to the power inlet of the refrigerant circulation pump 15. The power outlet of the fifth power line 124 is connected to the power inlet of the second compressor 18.

[0115] The operating principle of this implementation plan is as follows:

[0116] During the day, open the first regulating valve 30, the second regulating valve 31 and the fourth regulating valve 33, and close the third regulating valve 32.

[0117] The parabolic trough collector 1 concentrates sunlight to increase its energy flux density and simultaneously reflects it once to the frequency divider 3. After frequency division by the frequency divider 3, the short-wave reflection acts on the photovoltaic panel 2 to generate electricity, which is then stored in the energy storage converter 8. It undergoes DC-AC conversion for nighttime use. A portion of the electricity directly drives the oil circulation pump 6, the refrigerant circulation pump 15, the first compressor 10, and the second compressor 18 to drive the first-stage compression heat pump cycle, which uses low-temperature air as a low-grade heat source. The heat generated on the condenser side acts on the evaporator side of the second-stage heat pump cycle.

[0118] Long-wave transmission acts on the heat collector tube 4 to heat the heat transfer oil. The heat from this oil acts on the generator 7 as the driving heat source for the jet heat pump. At the same time, the heat from the first-stage condenser side is used as a low-grade heat source. The first compressor 10 acts as an auxiliary device for the jet pump to pressurize the ejector fluid, drive the jet heat pump cycle, improve the efficiency of the jet heat pump cycle, realize the compression-jet coupled solar air source heat pump cycle, and ensure the heating conditions during the day.

[0119] At night, open the third regulating valve 32 and the fourth regulating valve 33, and close the first regulating valve 30 and the second regulating valve 31.

[0120] At night, the stored electrical energy in the energy storage converter 8 is used as the power source for the first compressor 10 and the second compressor 18. The first-stage compression heat pump cycle directly uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as a low-grade heat source, thus realizing a cascaded solar air source heat pump cycle and ensuring nighttime heating conditions.

[0121] The other combinations and connections in this implementation scheme are the same as in Specific Implementation Scheme 1.

[0122] Preferably, the oil tank 5 can be a thermal storage tank 19.

[0123] Combination Figure 4 As shown, the operating principle is as follows:

[0124] During the day, open the first regulating valve 30, the second regulating valve 31 and the fourth regulating valve 33, and close the third regulating valve 32.

[0125] The parabolic trough collector 1 concentrates sunlight to increase its energy flux density and simultaneously reflects it once to the frequency divider 3. After frequency division by the frequency divider 3, the short-wave reflection acts on the photovoltaic panel 2 to generate electricity, which is then stored in the energy storage converter 8. It undergoes DC-AC conversion for nighttime use. A portion of the electricity directly drives the oil circulation pump 6, the refrigerant circulation pump 15, and the second compressor 18 to drive the first-stage compression heat pump cycle, which uses low-temperature air as a low-grade heat source. The heat generated on the condenser side acts on the evaporator side of the second-stage heat pump cycle.

[0126] Long-wave transmission acts on the heat collector tube 4 to heat the heat transfer oil. Part of the heat is stored in the heat storage tank 19 for nighttime use, and another part of the heat acts on the generator 7 as the driving heat source for the jet heat pump. At the same time, the heat from the first-stage condenser side is used as a low-grade heat source. The first compressor 10, as an auxiliary device for the jet, pressurizes the ejector fluid to drive the jet heat pump cycle, improves the efficiency of the jet heat pump cycle, realizes the compression-jet coupled solar air source heat pump cycle, and ensures heating conditions during the day.

[0127] At night, the stored electrical energy in the energy storage converter 8 is used first to drive the oil circulation pump 6, the first compressor 10 and the second compressor 18 to drive the first-stage compression heat pump cycle with low-temperature air as the low-grade heat source. At the same time, the heat in the heat storage tank 19 is used to act on the generator 7 as the driving heat source of the jet heat pump. The heat on the first-stage condenser side is used as the low-grade heat source. The first compressor 10 is used as the jet auxiliary equipment to pressurize the ejector fluid and drive the jet heat pump cycle, thereby improving the efficiency of the jet heat pump cycle and realizing the compression-jet coupled solar air source heat pump cycle.

[0128] When the heat load demand is large and the driving heat of the heat storage tank 19 is insufficient, the stored electrical energy in the energy storage converter 8 is used as the power source for the first compressor 10 and the second compressor 18. The first-stage compression heat pump cycle directly uses low-temperature air as the low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as the low-grade heat source, realizing a cascade solar air source heat pump cycle and ensuring nighttime heating conditions.

[0129] Specific Implementation Plan III. Combination Figure 5 As shown, it also includes a second ejector 20, a gas-liquid separator 21, a fifth regulating valve 34, a sixth regulating valve 35, a seventh regulating valve 36, an eighth regulating valve 37, a ninth regulating valve 38, a tenth regulating valve 39, an eleventh regulating valve 40, a twelfth regulating valve 41, a fourth working refrigerant line 86, a third ejector refrigerant line 87, a second mixed refrigerant line 88, a fourth ejector refrigerant line 89, a fifth ejector refrigerant line 90, a fifth working refrigerant line 91, a sixth working refrigerant line 92, a third mixed refrigerant line 93, a fourth mixed refrigerant line 94, a seventh gaseous refrigerant line 95, an eighth gaseous refrigerant line 96, a fourth liquid refrigerant line 97, a fifth liquid refrigerant line 98, and a sixth liquid refrigerant line 99.

[0130] The outlet of the fourth working refrigerant line 86 is connected to the high-pressure inlet of the second ejector 20. A ninth regulating valve 38 is installed on the fourth working refrigerant line 86. The outlet of the third ejector refrigerant line 87 is connected to the low-pressure inlet of the second ejector 20. A seventh regulating valve 36 is installed on the third ejector refrigerant line 87. The inlet of the second mixing refrigerant line 88 is connected to the outlet of the second ejector 20. The outlet of the second mixing refrigerant line 88 is connected to the inlet of the gas-liquid separator 21. The outlet of the gas-liquid separator 21 is connected to the inlet of the fourth ejector refrigerant line 89. A fifth regulating valve 34 is installed on the fourth ejector refrigerant line 89. The outlet of the fourth ejector refrigerant line 89 is connected to the inlet of the second ejector refrigerant line 20. The outlets of the refrigerant injection lines 82 and 83 merge and connect to the inlet of the fifth refrigerant injection line 90. The outlet of the fifth refrigerant injection line 90 is connected to the low-pressure inlet of the first injector 9. The outlets of the sixth gaseous refrigerant line 83 and the fourth mixed refrigerant line 94 merge and connect to the inlets of the fifth working refrigerant line 91 and the second gaseous refrigerant line, respectively. The fifth working refrigerant line 91 is equipped with an eighth regulating valve 37, and the first regulating valve 30 is located on the fourth mixed refrigerant line 94. The outlets of the fifth working refrigerant line 91 and the first working refrigerant line 64 merge and connect to the inlet of the sixth working refrigerant line 92. The outlet of 92 is connected to the high-pressure inlet of the first ejector 9. The outlet of the first mixed refrigerant line 71 is connected to the inlet of the fourth mixed refrigerant line 94 and the inlet of the third mixed refrigerant line 93. The third mixed refrigerant line 93 is equipped with a sixth regulating valve 35. The outlet of the third mixed refrigerant line 93 and the outlet of the eighth gaseous refrigerant line 96 merge and are connected to the inlet of the seventh gaseous refrigerant line 95. The outlet of the seventh gaseous refrigerant line 95 is connected to the inlet of the first compressor 10. The outlet of the fifth refrigerant line 85 is connected to the inlet of the eighth gaseous refrigerant line 96 and the inlet of the third ejector refrigerant line 87, respectively. The eighth gaseous refrigerant line 96... A fourth regulating valve 33 is provided; a seventh regulating valve 36 is provided on the third ejector refrigerant line 87; the inlet of the fourth liquid refrigerant line 97 is connected to the outlet of the gas-liquid separator 21; a twelfth regulating valve 41 is provided on the fourth liquid refrigerant line 97; the outlet of the fourth liquid refrigerant line 97 is connected to the inlets of the second liquid refrigerant line 68 and the fifth liquid refrigerant line 98 respectively; an eleventh regulating valve 40 is provided on the fifth liquid refrigerant line 98; the outlet of the fifth liquid refrigerant line 98 is connected to the inlet of the liquid storage tank 12; the inlet of the sixth liquid refrigerant line 99 is connected to one side outlet of the liquid storage tank 12; and a tenth regulating valve 39 is provided on the sixth liquid refrigerant line 99.The outlet of the sixth liquid refrigerant line 99 and the outlet of the first liquid refrigerant line 69 merge and connect to the inlet of the fourth working refrigerant line 86. The fourth working refrigerant line 86 is equipped with a ninth regulating valve 38.

[0131] How this solution works:

[0132] Conventional heat pump operating mode:

[0133] During the day, open the first regulating valve 30, the second regulating valve 31, the fourth regulating valve 33, the tenth regulating valve 39, and the eleventh regulating valve 40, and close the third regulating valve 32, the fifth regulating valve 34, the sixth regulating valve 35, the seventh regulating valve 36, the eighth regulating valve 37, the ninth regulating valve 38, and the twelfth regulating valve 41.

[0134] The parabolic trough collector 1 concentrates sunlight to increase its energy flux density and simultaneously reflects it once to the frequency divider 3. After frequency division by the frequency divider 3, the short-wave reflection acts on the photovoltaic panel 2 to generate electricity, which is then stored in the energy storage converter 8. It undergoes DC-AC conversion for nighttime use. A portion of the electricity directly drives the oil circulation pump 6, the refrigerant circulation pump 15, the first compressor 10, and the second compressor 18 to drive the first-stage compression heat pump cycle, which uses low-temperature air as a low-grade heat source. The heat generated on the condenser side acts on the evaporator side of the second-stage heat pump cycle.

[0135] Long-wave transmission acts on the heat collector tube 4 to heat the heat transfer oil. The heat from this oil acts on the generator 7 as the driving heat source for the jet heat pump. At the same time, the heat from the first-stage condenser side is used as a low-grade heat source. The first compressor 10 acts as an auxiliary device for the jet pump to pressurize the ejector fluid, drive the jet heat pump cycle, improve the efficiency of the jet heat pump cycle, realize the compression-jet coupled solar air source heat pump cycle, and ensure the heating conditions during the day.

[0136] At night, open the third regulating valve 32, the fourth regulating valve 33, the tenth regulating valve 39 and the eleventh regulating valve 40, and close the first regulating valve 30, the second regulating valve 31, the fifth regulating valve 34, the sixth regulating valve 35, the seventh regulating valve 36, the eighth regulating valve 37, the ninth regulating valve 38 and the twelfth regulating valve 41.

[0137] At night, the stored electrical energy in the energy storage converter 8 is used as the power source for the first compressor 10 and the second compressor 18. The first-stage compression heat pump cycle directly uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as a low-grade heat source, thus realizing a cascaded solar air source heat pump cycle and ensuring nighttime heating conditions.

[0138] Low compression ratio compression heat pump operating mode:

[0139] Open the third regulating valve 32, the fourth regulating valve 33, the fifth regulating valve 34, the sixth regulating valve 35, the seventh regulating valve 36, the eighth regulating valve 37, the ninth regulating valve 38 and the twelfth regulating valve 41, and close the first regulating valve 30, the second regulating valve 31, the tenth regulating valve 39 and the eleventh regulating valve 40 to run a low compression ratio compression heat pump cycle with the first ejector 9 and the second ejector 20.

[0140] The stored electrical energy in the energy storage converter 8 serves as the power source for the first compressor 10 and the second compressor 18. The first-stage compression heat pump cycle directly uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side directly drives the second-stage low-compression ratio compression heat pump cycle as a low-grade heat source. The second ejector 20, as an auxiliary device for the second-stage compression refrigeration, reduces irreversible losses caused by the expansion device in the heat pump cycle and improves the cooling efficiency of the system. The first ejector 9 is driven by high pressure on the condenser side, which increases the inlet pressure of the first compressor 10, replacing the original form of directly connecting the inlet of the first compressor 10 from the gas-liquid separator 21. This reduces the compression ratio of the entire two-stage compression heat pump cycle, lowers the operating temperature of the first compressor 10, and improves the stability of the first compressor 10. This allows the entire cascade solar air source heat pump cycle to operate at a low compression ratio, making the operation more stable, safe, and efficient.

[0141] Preferably, the oil tank 5 can be a thermal storage tank 19.

[0142] Combination Figure 6 As shown, the operating principle is as follows:

[0143] Conventional heat pump operating mode:

[0144] During the day, open the first regulating valve 30, the second regulating valve 31, the fourth regulating valve 33, the tenth regulating valve 39, and the eleventh regulating valve 40, and close the third regulating valve 32, the fifth regulating valve 34, the sixth regulating valve 35, the seventh regulating valve 36, the eighth regulating valve 37, the ninth regulating valve 38, and the twelfth regulating valve 41.

[0145] The parabolic trough collector 1 concentrates sunlight to increase its energy flux density and simultaneously reflects it once to the frequency divider 3. After frequency division by the frequency divider 3, the short-wave reflection acts on the photovoltaic panel 2 to generate electricity, which is then stored in the energy storage converter 8. It undergoes DC-AC conversion for nighttime use. A portion of the electricity directly drives the oil circulation pump 6, the refrigerant circulation pump 15, and the second compressor 18 to drive the first-stage compression heat pump cycle, which uses low-temperature air as a low-grade heat source. The heat generated on the condenser side acts on the evaporator side of the second-stage heat pump cycle.

[0146] Long-wave transmission acts on the heat collector tube 4 to heat the heat transfer oil. Part of the heat is stored in the heat storage tank 19 for nighttime use, and another part of the heat acts on the generator 7 as the driving heat source for the jet heat pump. At the same time, the heat from the first-stage condenser side is used as a low-grade heat source. The first compressor 10, as an auxiliary device for the jet, pressurizes the ejector fluid to drive the jet heat pump cycle, improves the efficiency of the jet heat pump cycle, realizes the compression-jet coupled solar air source heat pump cycle, and ensures heating conditions during the day.

[0147] At night, the first regulating valve 30, the second regulating valve 31, the fourth regulating valve 33, the tenth regulating valve 39, and the eleventh regulating valve 40 are opened first, while the third regulating valve 32, the fifth regulating valve 34, the sixth regulating valve 35, the seventh regulating valve 36, the eighth regulating valve 37, the ninth regulating valve 38, and the twelfth regulating valve 41 are closed. When the heat load demand is large, the third regulating valve 32, the fourth regulating valve 33, the tenth regulating valve 39, and the eleventh regulating valve 40 are opened again, while the first regulating valve 30, the second regulating valve 31, the fifth regulating valve 34, the sixth regulating valve 35, the seventh regulating valve 36, the eighth regulating valve 37, the ninth regulating valve 38, and the twelfth regulating valve 41 are closed.

[0148] At night, the stored electrical energy in the energy storage converter 8 is used first to drive the oil circulation pump 6, the first compressor 10 and the second compressor 18 to drive the first-stage compression heat pump cycle with low-temperature air as the low-grade heat source. At the same time, the heat in the heat storage tank 19 is used to act on the generator 7 as the driving heat source of the jet heat pump. The heat on the first-stage condenser side is used as the low-grade heat source. The first compressor 10 is used as the jet auxiliary equipment to pressurize the ejector fluid and drive the jet heat pump cycle, thereby improving the efficiency of the jet heat pump cycle and realizing the compression-jet coupled solar air source heat pump cycle.

[0149] When the heat load demand is large and the driving heat of the heat storage tank 19 is insufficient, the stored electrical energy in the energy storage converter 8 is used as the power source for the first compressor 10 and the second compressor 18. The first-stage compression heat pump cycle directly uses low-temperature air as the low-grade heat source, and the heat generated on its condenser side directly drives the second-stage compression heat pump cycle as the low-grade heat source, realizing a cascade solar air source heat pump cycle and ensuring nighttime heating conditions.

[0150] Low compression ratio compression heat pump operating mode:

[0151] Open the third regulating valve 32, the fourth regulating valve 33, the fifth regulating valve 34, the sixth regulating valve 35, the seventh regulating valve 36, the eighth regulating valve 37, the ninth regulating valve 38 and the twelfth regulating valve 41, and close the first regulating valve 30, the second regulating valve 31, the tenth regulating valve 39 and the eleventh regulating valve 40 to run a low compression ratio compression heat pump cycle with the first ejector 9 and the second ejector 20.

[0152] The stored electrical energy in the energy storage converter 8 serves as the power source for the first compressor 10 and the second compressor 18. The first-stage compression heat pump cycle directly uses low-temperature air as a low-grade heat source, and the heat generated on its condenser side directly drives the second-stage low-compression ratio compression heat pump cycle as a low-grade heat source. The second ejector 20, as an auxiliary device for the second-stage compression refrigeration, reduces irreversible losses caused by the expansion device in the heat pump cycle and improves the cooling efficiency of the system. The first ejector 9 is driven by high pressure on the condenser side, which increases the inlet pressure of the first compressor 10, replacing the original form of directly connecting the inlet of the first compressor 10 from the gas-liquid separator 21. This reduces the compression ratio of the entire two-stage compression heat pump cycle, lowers the operating temperature of the first compressor 10, and improves the stability of the first compressor 10. This allows the entire cascade solar air source heat pump cycle to operate at a low compression ratio, making the operation more stable, safe, and efficient.

[0153] Specific Implementation Plan IV. Combination Figures 8 to 14 As shown, the trough-type solar collector 1 includes an arc-shaped secondary reflector, a parabolic primary reflector, and a solar collector tube. The central axis of the solar collector tube coincides with the focal line of the parabolic primary reflector. The cross-sections of the parabolic primary reflector and the arc-shaped secondary reflector are both arc-shaped. The arc-shaped secondary reflector is located above the solar collector tube, and the openings of the parabolic primary reflector and the parabolic secondary reflector are arranged facing each other.

[0154] The other combinations and connections in this implementation scheme are the same as those in specific implementation schemes one, two, or three.

[0155] Specific Implementation Plan V. Combination Figures 8 to 14 As shown, the design method of the circular arc secondary reflector includes the following steps:

[0156] The parabolic equation of the primary reflector is x. 2 =4fy, the radius of the inner tube of the heat collector is r. a The angle between the reflected ray and the normal is called the position angle.

[0157] Step 1: Based on the structural parameters of the parabolic primary mirror and the tracking error angle α, determine the circle of tangency for the most divergent rays located at one edge corner of the parabolic primary mirror. The point of tangency is point A, and the intersection of the mirror surfaces is point O. At this point, the intersection of the parabolic primary mirror surfaces coincides with the center of the heat collection tube. The distance from point O to point A is OA. From the equation of the parabola, we have:

[0158]

[0159] In the formula, the height of the parabola is h; α is the tracking error angle; W ais the opening width of the parabolic primary mirror; f is the focal length of the parabolic primary mirror; when the edge angle When less than 90°,

[0160]

[0161] At the same time,

[0162]

[0163] In the formula, Let the edge angle of the parabolic primary reflector be defined as 0°, and the bottom position angle of the heat collection tube be defined as increasing counterclockwise. The maximum position angle is also called the edge angle of the parabolic primary reflector. We have:

[0164] Similarly, when For angles greater than or equal to 90°, the above formula still holds; RQ is a ray parallel to the principal axis, whose reflected ray OQ passes through the focal point, and its focal radius is OQ. At the edge, x0 = W a When the value is 2, OQ reaches its maximum value.

[0165]

[0166] Considering the existence of tracking errors and mirror shape processing errors, which cause light to defocus, the light divergence is most severe, that is, the maximum OA is corresponding to the edge of the parabola, and the maximum value is:

[0167]

[0168]

[0169]

[0170] Step 2: Determine the distance OB from the intersection point B of the most diverging ray of the parabolic primary mirror and the other edge line to the intersection point O of the parabolic primary mirror surface. Since the cross-section of the circular arc secondary mirror is axisymmetric, based on OB and the edge angle... Calculate the width BD of the secondary mirror.

[0171]

[0172]

[0173] Step 3: Based on the positional relationship OO′ between the arc-shaped secondary reflector and the heat collection tube, calculate the relative position OC of the arc-shaped secondary reflector, where OC is the vertical distance from the top of the arc-shaped secondary reflector to the center of the heat collection tube, i.e., the relative position of the arc-shaped secondary reflector; r is the radius of the arc-shaped secondary reflector; let OC = b*r, and obtain OC = 0.9226r - 0.0343 by simulation fitting using optical software. The optical software can be TracePro, which approximates OC ≈ 0.9r, OO′ = r - OC ≈ 0.1r, i.e., OO′ = b1*r. To simplify the calculation, let OB = a. In ΔOBO′, by the cosine theorem, we have: Substituting the values: Solving for the given information, we get:

[0174]

[0175] In the formula, a is the length of OB; b1 is the coefficient between OO′ and radius r.

[0176] The position d of the secondary reflector is,

[0177]

[0178] In summary, a circular arc-shaped secondary reflector for a trough-type concentrating solar collector is a circular arc structure with point O′ located on the vertical line of the collector tube as the center, radius r, relative position d from the center of the collector tube, and width W.

[0179] The placement, radius, and width of the arc-shaped secondary reflector are simulated and fitted using geometric optics principles and optical software to ensure that the reflected light from the secondary reflector illuminates the heat collection tube to the maximum extent, thereby improving optical efficiency. Considering the case where the heat collection tube is vertically offset from the focal point of the parabolic primary reflector due to installation errors, corrected fitting parameters are provided to improve the accuracy of the design method.

[0180] When the central axis of the heat collection tube shifts upward along the rod direction at the focal line of the parabolic primary reflector, when the shift amount... Unlike the above scheme, in step three, based on the positional relationship O1O′ between the focal points of the arc-shaped secondary reflector and the parabolic primary reflector, and the vertical offset l1 between the center O1 of the heat collection tube and the focal point of the parabolic primary reflector, the relative position O1C of the arc-shaped secondary reflector is calculated. Here, O1C is the vertical distance from the top of the secondary reflector to the center O1 of the heat collection tube, i.e., the relative position of the secondary reflector. Let O1C = b*r, where b is the coefficient between OC and radius r, with a recommended coefficient of 0.92 to 0.96. OO′ = r - OC = r - O1C - OO1, i.e., OO′ = b1*r - l1, where OO1 is the upward offset l1 along the rod direction between the center O1 of the heat collection tube and the focal point of the parabolic primary reflector. By the cosine theorem:

[0181]

[0182]

[0183] The position d of the secondary reflector is,

[0184]

[0185] When the central axis of the heat collection tube is offset vertically downwards from the focal line of the parabolic primary reflector, when the offset amount Unlike the above scheme, in step three, the relative position O2C of the arc-shaped secondary reflector is calculated based on the positional relationship O2O′ between the focal points of the arc-shaped secondary reflector and the parabolic primary reflector, and the vertical offset l2 between the center O2 of the heat collection tube and the focal point of the parabolic primary reflector.

[0186] Where O2C is the vertical distance from the top of the secondary reflector to the center O2 of the heat collection tube, i.e., the relative position of the secondary reflector. Let O2C = b*r, where b is the coefficient of OC and radius r. It is recommended that the coefficient b be 0.92 to 0.99. OO′ = r - OC = r - O2C + OO2, i.e., OO′ = b1*r + l2, ​​where OO2 is the vertical downward offset l2 between the center O2 of the heat collection tube and the focal point of the parabolic primary reflector. By the cosine theorem:

[0187]

[0188]

[0189] The position d of the secondary reflector is,

[0190]

[0191] It should be noted that, in combination Figure 14 As shown, in specific implementation methods three and four, only the vertical offset of the heat collection tube is considered. This is because: 1. Combining Figure 14 a. When the trough-type solar collector is in a vertical position, it is common for the collector tubes to shift in the vertical direction, for example, due to gravity, material expansion, or external mechanical vibration; 2. Combined with Figure 14 b. When the trough solar collector performs single-axis tracking of the sun, it is in an inclined state. At this time, the offset corresponding to the above calculation method is along the rod direction. It can be decomposed into horizontal and vertical offsets, so that both horizontal and vertical offsets can be considered.

[0192] Taking the downward displacement along the rod direction of a tilted trough solar collector as an example, as shown in the figure: Firstly, when the trough solar collector is tilted, the collector tubes are fixed by the rod, and if a certain displacement occurs, slippage along the rod direction is more likely to occur. To comprehensively consider the horizontal and vertical displacement of the collector tubes, the total displacement can be decomposed, such as... Figure 14 As shown,

[0193] OM = OO2 cos∠MOO2

[0194] ON = OO2 cos∠NOO2

[0195] Where ∠MOO2 is the angle between the rod and the horizontal direction; ∠NOO2 is the angle between the rod and the vertical direction; for scenarios where the horizontal offset is easy to measure, ∠MOO2 can be used. Right now Where x is the horizontal offset of the heat collection tube; θ1 is the angle between the rod and the horizontal direction. Let O2C = b*r, where b is the coefficient of OC and radius r. It is recommended that the coefficient b be 0.92 to 0.99. OO′ = r - OC = r - O2C + OO2, that is, OO′ = b1*r + l2, ​​where OO2 is the vertical downward offset l2 between the center O2 of the heat collection tube and the focal point of the parabolic primary reflector. Given the horizontal offset, l2 can be deduced. Then, by the cosine theorem, we have: Substitution have:

[0196]

[0197] The position d of the secondary reflector is,

[0198]

[0199] For scenarios where vertical offset is easy to measure, the following method can be used: Right now Where y is the vertical offset of the heat collection tube; θ2 is the angle between the rod and the vertical direction; let O2C = b*r; where b is the coefficient of OC and radius r, the recommended coefficient b is 0.92~0.99, OO′ = r - OC = r - O2C + OO2, that is OO′ = b1*r + l2, ​​where OO2 is the vertical downward offset l2 between the center O2 of the heat collection tube and the focal point of the parabolic primary reflector. Given the vertical offset, l2 can be deduced, and then by the cosine theorem, we have:

[0200] Substitution have:

[0201]

[0202] The position d of the secondary reflector is,

[0203]

[0204] Regarding the size and location of the frequency divider: Considering the optical characteristics of the frequency divider itself (short-wave reflection, long-wave transmission), its obstruction of incident light should be minimized, allowing light to enter from the bottom as much as possible. This satisfies the condition that long-wave transmission is absorbed by the collector tubes, and short-wave reflection is received by the photovoltaic panel. Considering material savings and the optical characteristics of the frequency divider, to ensure that the trough collector can receive and reflect the entire solar spectrum before frequency division, the size of the frequency divider should be set so that it intersects the line connecting the edge point and the focal point of the trough collector. Figure 3 As shown, the farther away from the solar collector tube, the more material is needed, and the closer to the tube, the less material is needed. Considering that in reality, the frequency divider cannot achieve perfect short-wave reflection and long-wave transmission of sunlight, there will always be some absorption of light and heat generation. This heat generation will have a negative impact on the photovoltaic panel and reduce its power generation efficiency. However, the heat generation has certain advantages for the solar collector tube itself. In summary, the frequency divider should be arranged at a position perpendicular to and tangent to the edge point of the central axis of the solar collector tube. The specific shape should be a parabola that satisfies the equation of reflection through the same focal point after light concentration.

[0205] Regarding the size and location settings of the photovoltaic panels: Based on the simulation of TracePro software, a large amount of light is incident, and then the reflection band of the frequency divider is set. It can be observed that the light will be concentrated after the second reflection of the frequency divider. The main concentration position is the light band formed directly below the frequency divider, and the area is slightly wider than the frequency divider. This conforms to the optical condition that the size of the photovoltaic panel and the frequency divider are proportional.

[0206] While the present invention has been disclosed above, its scope of protection is not limited thereto. Those skilled in the art can make various changes and modifications without departing from the spirit and scope of the present invention, and all such changes and modifications will fall within the scope of protection of the present invention.

Claims

1. A control method for an air-source heat pump heating system based on solar frequency-division heat-electricity combined utilization, characterized in that: The air source heat pump heating system includes a trough collector (1), a photovoltaic panel (2), a frequency divider (3), a collector tube (4), an oil tank (5), an oil circulation pump (6), a generator (7), an energy storage converter (8), a first ejector (9), a first compressor (10), a condenser (11), a liquid storage tank (12), a first throttle valve (13), an evaporator-condenser (14), a refrigerant circulation pump (15), a second throttle valve (16), an evaporator (17), a second compressor (18), a first regulating valve (30), a second regulating valve (31), a third regulating valve (32), and a fourth regulating valve (33). The oil outlet of the heat collection tube (4) is connected to the oil inlet of the oil tank (5), the oil outlet of the oil tank (5) is connected to the oil inlet of the oil circulation pump (6), the oil outlet of the oil circulation pump (6) is connected to the oil inlet of the generator (7), and the oil outlet of the generator (7) is connected to the oil inlet of the heat collection tube (4). The outlet of the generator (7) is connected to the high-pressure inlet of the first injector (9). The liquid outlet on the primary side of the evaporator-condenser (14) is connected to the liquid inlet of the second throttle valve (16), the liquid outlet of the second throttle valve (16) is connected to the liquid inlet of the evaporator (17), the liquid outlet of the evaporator (17) is connected to the liquid inlet of the second compressor (18), and the liquid outlet of the second compressor (18) is connected to the liquid inlet on the primary side of the evaporator-condenser (14). The condenser (11) has an inlet and an outlet on the other side. When the number of parabolic trough collectors (1) is at least 2, the parabolic trough collectors (1) are evenly distributed, each parabolic trough collector (1) is equipped with a heat collection tube (4), multiple heat collection tubes (4) are connected in series, at least one parabolic trough collector (1) is connected to a photovoltaic panel (2), the photovoltaic panel (2) is connected to an energy storage converter (8), the electrical energy generated by the photovoltaic panel (2) can be stored in the energy storage converter (8), and at the same time, DC-AC conversion is performed, the energy storage converter (8) is connected to the first compressor (10), the oil circulation pump (6), the refrigerant circulation pump (15) and the second compressor (18); It also includes a second injector (20), a gas-liquid separator (21), a fifth regulating valve (34), a sixth regulating valve (35), a seventh regulating valve (36), an eighth regulating valve (37), a ninth regulating valve (38), a tenth regulating valve (39), an eleventh regulating valve (40), a twelfth regulating valve (41), a fifth working refrigerant line (91), a third mixed refrigerant line (93), a fourth mixed refrigerant line (94), and an eighth gaseous refrigerant line (96). The liquid outlet of the condenser (11) merges with the liquid outlet on one side of the liquid storage tank (12) and is connected to the high-pressure liquid inlet of the second ejector (20). A ninth regulating valve (38) is provided on the high-pressure liquid inlet pipe of the second ejector (20). The liquid outlet of the second ejector (20) is connected to the liquid inlet of the gas-liquid separator (21). The gas outlet of the gas-liquid separator (21) merges with the gas outlet of the second ejector refrigerant pipeline (82) and is connected to the low-pressure gas inlet of the first ejector (9). A fifth regulating valve (34) is provided on the gas outlet pipe of the gas-liquid separator (21). The gas outlet of the first ejector (9) is connected to the liquid outlet of the gas-liquid separator (21). The inlet of the fourth mixed refrigerant line (94) is connected to the inlet of the third mixed refrigerant line (93). The third mixed refrigerant line (93) is equipped with a sixth regulating valve (35). The first regulating valve (30) is located on the fourth mixed refrigerant line (94). The liquid outlet on the primary side of the evaporator condenser (14) is connected to the low-pressure liquid inlet of the second ejector (20). The gas outlet on the primary side of the evaporator condenser (14) is connected to the inlet of the eighth gaseous refrigerant line (96). The eighth gaseous refrigerant line (96) is equipped with a fourth regulating valve (33). The second ejector (20) A seventh regulating valve (36) is provided on the low-pressure liquid inlet pipeline. The outlet of the eighth gaseous refrigerant pipeline (96) and the outlet of the third mixed refrigerant pipeline (93) merge and are connected to the inlet of the first compressor (10). The outlet of the first compressor (10) is connected to the inlet of the second ejector refrigerant pipeline (82) and the inlet of the sixth gaseous refrigerant pipeline (83). The outlet of the sixth gaseous refrigerant pipeline (83) and the outlet of the fourth mixed refrigerant pipeline (94) merge and are connected to the inlet of the fifth working refrigerant pipeline (91) and the inlet of the condenser (11). The fifth working refrigerant pipeline (91) is equipped with an eighth regulating valve (37). The outlet of the fifth working refrigerant pipeline (91) and the outlet of the generator (7) are connected to the high-pressure inlet of the first injector (9). The outlet of the gas-liquid separator (21) is connected to the inlet of the liquid storage tank (12) and the inlet of the first throttle valve (13) respectively. The outlet pipeline of the gas-liquid separator (21) is equipped with a twelfth regulating valve (41). The inlet pipeline of the liquid storage tank (12) is equipped with an eleventh regulating valve (40). The outlet pipeline on one side of the liquid storage tank (12) is equipped with a tenth regulating valve (39). The control method executes in two modes: conventional heat pump operation mode and low-compression ratio compression heat pump operation mode. When in normal heat pump operation mode During the day, open the first regulating valve (30), the second regulating valve (31), the fourth regulating valve (33), the tenth regulating valve (39), and the eleventh regulating valve (40), and close the third regulating valve (32), the fifth regulating valve (34), the sixth regulating valve (35), the seventh regulating valve (36), the eighth regulating valve (37), the ninth regulating valve (38), and the twelfth regulating valve (41). The trough collector (1) concentrates sunlight and reflects it to the frequency divider (3). After the frequency divider (3) divides the frequency, the short wave reflection acts on the photovoltaic panel (2) to generate electricity, which is then stored in the energy storage converter (8). The electricity in the energy storage converter (8) directly drives the oil circulation pump (6), the refrigerant circulation pump (15), the first compressor (10) and the second compressor (18) to work, driving the first-stage compression heat pump cycle with low-temperature air as the low-grade heat source. The heat generated on the condensing side acts on the evaporating side of the second-stage heat pump cycle. The long wave transmission acts on the collector tube (4) to heat the heat transfer oil. The heat acts on the generator (7) as the driving heat source of the jet heat pump. At the same time, the heat on the first-stage condensing side is used as the low-grade heat source. The first compressor (10) acts as the jet auxiliary equipment to pressurize the ejector fluid and drive the jet heat pump cycle, realizing the compression-jet coupled solar air source heat pump cycle, ensuring the heating conditions during the day. At night, open the third regulating valve (32), the fourth regulating valve (33), the tenth regulating valve (39) and the eleventh regulating valve (40), and close the first regulating valve (30), the second regulating valve (31), the fifth regulating valve (34), the sixth regulating valve (35), the seventh regulating valve (36), the eighth regulating valve (37), the ninth regulating valve (38) and the twelfth regulating valve (41). At night, the stored electrical energy in the energy storage converter (8) is used as the power source for the first compressor (10) and the second compressor (18). The first-stage compression heat pump cycle uses low-temperature air as a low-temperature heat source. The heat generated on its condenser side is used as the low-temperature heat source of the second-stage compression heat pump cycle to directly drive the second-stage compression heat pump cycle, thereby realizing the cascade solar air source heat pump cycle and ensuring the heating conditions at night. When operating in low compression ratio compression heat pump mode Open the third regulating valve (32), the fourth regulating valve (33), the fifth regulating valve (34), the sixth regulating valve (35), the seventh regulating valve (36), the eighth regulating valve (37), the ninth regulating valve (38), and the twelfth regulating valve (41), and close the first regulating valve (30), the second regulating valve (31), the tenth regulating valve (39), and the eleventh regulating valve (40), and run the low compression ratio compression heat pump cycle with the first ejector (9) and the second ejector (20). The stored electrical energy in the energy storage converter (8) serves as the power source for the first compressor (10) and the second compressor (18). The first-stage compression heat pump cycle directly uses low-temperature air as a low-temperature heat source, and the heat generated on its condenser side serves as the low-temperature heat source for the second-stage low-compression ratio compression heat pump cycle, directly driving the second-stage low-compression ratio compression heat pump cycle. The second ejector (20) serves as an auxiliary device for the second-stage compression refrigeration.

2. The control method for an air source heat pump heating system based on solar frequency-division heat-electricity combined utilization as described in claim 1, characterized in that: The oil tank (5) can be a thermal storage tank (19).

Images