Air source and geothermal source dual-stage heat pump system

Abstract

The application relates to the technical field of air source heat pump, in particular to an air source and geothermal source two-stage heat pump system, which comprises an air source heat pump mechanism, the air source heat pump mechanism comprises a fin evaporator, a condenser, a compressor, a four-way valve and an expansion valve, further comprises a geothermal source heat pump mechanism, the geothermal source heat pump mechanism comprises an underground heat exchanger and a fin radiator, the underground heat exchanger is provided with low-boiling-point refrigerant, the output end of the underground heat exchanger is connected with the air inlet of the fin radiator through an air pipe, and the input end of the underground heat exchanger is connected with the liquid outlet of the fin radiator through a liquid return pipe; the air source heat pump and the ground source heat pump are coupled, the fin radiator in the ground source heat pump is used for preheating the fin evaporator in the air source heat pump, so that the air source heat pump can more easily obtain heat from air, and the heating efficiency of the air source heat pump in severe winter can be improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of air source heat pump, in particular to an air source and geothermal source two-stage heat pump system. BACKGROUND

[0002] As a key means of efficient utilization of renewable energy, heat pump technology is widely used in building heating, industrial heating and other fields. However, its operating performance is heavily dependent on the ambient temperature, and it has significant limitations in low-temperature winter conditions.

[0003] Specifically, when the ambient temperature drops below-10℃, the fin evaporator surface of the air source heat pump is prone to frost, resulting in increased air flow resistance and reduced heat exchange efficiency. Research data shows that in a-20℃ environment, the heating capacity of a traditional air source heat pump can be reduced by more than 50% compared to the standard condition (7℃), and the COP (performance coefficient) can be reduced to below 2.0. More severely, when the temperature drops to-30℃, the evaporator has difficulty in effectively absorbing heat from the air, and the compressor faces problems such as insufficient suction pressure and excessive exhaust temperature, and even shutdown protection, which cannot meet the basic heating demand. This performance defect greatly limits the popularization and application of air source heat pumps in severe cold regions.

[0004] In contrast, the underground soil temperature is maintained at 10-15℃ (in mid-latitude regions) all year round, and is hardly affected by surface climate change. Even in extreme low-temperature weather in winter, it can still provide continuous and stable low-grade heat energy. Therefore, if the stability of the geothermal source can be combined with the flexibility of the air source to build a composite heat pump system that meets the heating demand in severe cold regions in winter, it will be able to make up for the deficiency of air source heat pumps in severe winter heating efficiency. For this reason, we propose an air source and geothermal source two-stage heat pump system to solve the above-mentioned drawbacks. SUMMARY

[0005] The purpose of the present application is to provide an air source and geothermal source two-stage heat pump system to solve the problems raised in the background art.

[0006] The present application is realized by the following technical scheme: an air source and geothermal source two-stage heat pump system, comprising an air source heat pump mechanism, the air source heat pump mechanism comprising a fin evaporator, a condenser, a compressor, a four-way valve and an expansion valve, further comprising:

[0007] a geothermal source heat pump mechanism, the geothermal source heat pump mechanism comprising an underground heat exchanger and a fin radiator, the underground heat exchanger having a low-boiling-point refrigerant therein, the output end of the underground heat exchanger being connected to the fin radiator air inlet through an air pipe, and the input end of the underground heat exchanger being connected to the fin radiator liquid outlet through a liquid return pipe;

[0008] A main box, the finned evaporator is located in the rear position inside the main box, the front and rear walls of the main box are open, and a fan is arranged on the front side of the finned evaporator in the main box.

[0009] A sub-box, the sub-box is located at the rear side of the main box, the rear wall of the sub-box is open, and the finned radiator is movably arranged in the sub-box.

[0010] The sub-box further comprises a gear adjusting mechanism, the gear adjusting mechanism is used for driving the finned radiator to overturn, so that the finned radiator is opposite to the finned evaporator or is distributed in a staggered manner.

[0011] Optionally, the air inlet of the finned radiator is connected with an air pipe through a hose, the liquid outlet of the finned radiator is connected with a liquid return pipe through a hose, and the air pipe and the liquid return pipe penetrate through the side wall of the sub-box and extend into the inside of the sub-box.

[0012] Optionally, the finned radiator comprises two groups of finned radiators, the two groups of finned radiators are distributed in a left-right symmetrical manner, the gear adjusting mechanism comprises an upper holding assembly and a lower holding assembly corresponding to the two groups of finned radiators, the upper holding assembly and the lower holding assembly are respectively installed on the top and the bottom of one group of finned radiators, the top surface of the upper holding assembly is provided with a first main shaft, the bottom surface of the lower holding assembly is provided with a second main shaft, and the first main shaft and the second main shaft are respectively rotationally connected with the upper and lower walls in the inside of the sub-box.

[0013] The gear adjusting mechanism further comprises two driving motors, the driving motors are fixedly installed on the top wall of the sub-box, and the output shafts of the two driving motors are respectively in transmission connection with the two first main shafts.

[0014] Optionally, the output shaft of the driving motor and the corresponding first main shaft are in transmission connection through a synchronous belt or a chain.

[0015] Optionally, each group of the finned radiators comprises two finned radiators, the upper holding assembly comprises two upper holding plates, the two upper holding plates are respectively fixedly connected with the top walls of the two finned radiators, and the two upper holding plates are hingedly arranged; the lower holding assembly comprises two lower holding plates, the two lower holding plates are respectively connected with the bottom walls of the two finned radiators, and the two lower holding plates are hingedly arranged.

[0016] The first main shaft and the second main shaft are respectively arranged on the upper holding plate and the lower holding plate close to the edge side.

[0017] Optionally, the two upper holding plates have a hinge shaft, the hinge shaft is rotatably connected to the upper holding plate near the edge side through a damping bearing, the hinge shaft is fixedly connected to the upper holding plate near the middle side, and when one of the upper holding plates rotates 180 degrees around the hinge shaft, the two upper holding plates can be distributed in a folded state.

[0018] Optionally, the top end of the hinge shaft is provided with a driven gear, and the inner top wall of the secondary machine box is provided with a first arc-shaped gear rack and a second arc-shaped gear rack; when each group of fin heat sinks rotates outward around the first main shaft, the driven gear can be engaged with the first arc-shaped gear rack and the second arc-shaped gear rack, respectively.

[0019] When the driven gear passes through the first arc-shaped gear rack, the hinge shaft rotates 45 degrees inward;

[0020] When the driven gear passes through the second arc-shaped gear rack, the hinge shaft rotates 135 degrees inward.

[0021] Optionally, the left and right side walls of the secondary machine box are both provided with air vents, and the left and right side walls inside the secondary machine box are both slidably provided with shielding plates, and the shielding plates are provided with through holes.

[0022] Optionally, the inner wall of the secondary machine box is rotatably provided with a vertical driving shaft, a driving gear is fixedly sleeved on the driving shaft, the surface of the shielding plate is provided with a driven gear rack, the driving gear and the driven gear rack are engaged, and the driving shaft and the first main shaft are connected through a synchronous belt transmission.

[0023] When the two groups of fin heat sinks are aligned, the through holes and the air vents are distributed in a staggered manner.

[0024] When the two groups of fin heat sinks are rotated to be parallel to the side wall of the secondary machine box, the through holes and the air vents are aligned.

[0025] Optionally, the air vent is located on the side wall of the secondary machine box and is close to one side of the main machine box, and a dust screen is further installed in the air vent.

[0026] Compared with the prior art, the air source and geothermal source two-stage heat pump system has the following beneficial effects:

[0027] 1. The air source heat pump and the geothermal heat pump are coupled, the fin heat sink in the geothermal heat pump is used to preheat the fin evaporator in the air source heat pump, so that the air source heat pump can more easily obtain heat from the air, and the heating efficiency of the air source heat pump in severe winter is improved;

[0028] 2. The gear adjusting mechanism in the application can control the alignment or misalignment of the finned radiator and the finned evaporator, thereby reducing air resistance and ensuring the contact efficiency of the finned evaporator and air in the working condition without preheating air;

[0029] 3. The finned radiator in the application can also maintain a semi-expanded posture, moderate air resistance, and preheat a part of air, so that the application can change its own form to adapt to various different environmental working conditions, and maintain the balance between energy consumption and heating efficiency of the application;

[0030] 4. When the finned radiator in the application is adjusted to a fully expanded posture, the air vents on both sides of the auxiliary machine box are automatically opened to further reduce the air inlet resistance of the main machine box, so that more air can contact the finned evaporator, which helps to improve the heating efficiency of the finned evaporator. BRIEF DESCRIPTION OF DRAWINGS

[0031] Figure 1 is a structural schematic diagram of the application;

[0032] Figure 2 is a structural schematic diagram of the main machine box and the auxiliary machine box of the application;

[0033] Figure 3 is a structural sectional view of the main machine box and the auxiliary machine box of the application;

[0034] Figure 4 is a structural schematic diagram of the finned radiator of the application;

[0035] Figure 5 is a structural front view of the finned radiator of the application;

[0036] Figure 6 is a top sectional view of the auxiliary machine box of the application;

[0037] Figure 7 is another top sectional view of the auxiliary machine box of the application in another state;

[0038] Figure 8 is a structural schematic diagram of the shielding plate of the application;

[0039] Figure 9 is Figure 8 is an enlarged view of position A in the above-mentioned corresponding diagram.

[0040] In the figure: 100, air source heat pump mechanism; 101, fin evaporator; 102, condenser; 103, compressor; 104, four-way valve; 105, expansion valve; 200, geothermal source heat pump mechanism; 201, underground heat exchanger; 202, fin radiator; 203, air pipe; 204, liquid return pipe; 300, main machine box; 301, fan; 400, auxiliary machine box; 401, first arc-shaped rack; 402, second arc-shaped rack; 403, air vent; 404, shielding plate; 405, through hole; 406, driving gear; 407, driven rack; 500, gear adjustment mechanism; 501, upper retaining assembly; 5011, upper retaining plate; 5012, hinge shaft; 502, lower retaining assembly; 5021, lower retaining plate; 503, first main shaft; 504, second main shaft; 505, driving motor; 506, driven gear. DETAILED DESCRIPTION

[0041] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0042] Embodiment one: please refer to Figure 1 Figure 4 An air source and geothermal source two-stage heat pump system, comprising an air source heat pump mechanism 100, the air source heat pump mechanism 100 comprising a fin evaporator 101, a condenser 102, a compressor 103, a four-way valve 104 and an expansion valve 105, the connection relationship between the above-mentioned components is the same as that of the air source heat pump in the prior art, and it is worth noting that the fin evaporator 101 in the present embodiment is in the form of a rectangular plate, and there are three rows of copper pipes inside.

[0043] The present embodiment also comprises a geothermal source heat pump mechanism 200, the geothermal source heat pump mechanism 200 comprising an underground heat exchanger 201 and a fin radiator 202, the underground heat exchanger 201 having a low-boiling-point refrigerant inside, the output end of the underground heat exchanger 201 being connected to the air inlet of the fin radiator 202 through an air pipe 203, and the input end of the underground heat exchanger 201 being connected to the liquid outlet of the fin radiator 202 through a liquid return pipe 204; wherein the low-boiling-point refrigerant can be R134a (tetrafluoroethane), which has a standard boiling point of -26.1℃, much lower than the underground soil temperature.

[0044] As Figure 1 ​As shown, underground heat exchanger 201 is buried underground at a depth of no less than 5 meters. The specific depth is determined by factors such as local soil moisture, altitude, and latitude. When the low-boiling-point coolant is located within underground heat exchanger 201, it boils and vaporizes due to the heat. The vaporized coolant then enters finned heat sink 202, releasing heat and liquefying. The liquefied coolant then returns to underground heat exchanger 201, forming a cycle.

[0045] This embodiment also includes a main case 300, the fin evaporator 101 is located at the rear side of the main case 300, and the condenser 102, compressor 103, four-way valve 104 and expansion valve 105 are also arranged inside the main case 300; the front and rear side walls of the main case 300 are both open, and a fan 301 is also provided inside the main case 300 and in front of the fin evaporator 101; when the fan is turned on, a negative pressure environment can be formed behind the fin evaporator 101, so that air passes through the fin evaporator 101 from back to front, and helps to increase the air convection speed.

[0046] like Figure 3 As shown, a sub-chassis 400 is provided on the rear side of the main chassis 300. The rear side wall of the sub-chassis 400 is open, and the finned heat sink 202 is movably arranged within the sub-chassis 400. A gear adjustment mechanism 500 is also provided inside the sub-chassis 400. The gear adjustment mechanism 500 is used to drive the finned heat sink 202 to flip so that the finned heat sink 202 and the finned evaporator 101 are aligned or offset. When the finned heat sink 202 and the finned evaporator 101 are aligned, external air will enter the sub-chassis 400 through the opening on the rear side of the sub-chassis 400. The air will then pass through the radiator to be preheated, and then pass through the finned evaporator 101, thereby helping to improve the heating efficiency of the finned evaporator 101.

[0047] In some embodiments of the present application, the air inlet of the finned heat sink 202 is connected to the air pipe 203 via a flexible hose, and the liquid outlet of the finned heat sink 202 is connected to the liquid return pipe 204 via a flexible hose. Both the air pipe 203 and the liquid return pipe 204 penetrate the side wall of the sub-chassis 400 and extend into the interior of the sub-chassis 400. Specifically, the flexible hose is a rubber hose, and the side wall of the sub-chassis 400 has two mounting holes for the air pipe 203 and the liquid return pipe 204 to pass through.

[0048] In addition, there are two groups of fin radiators 202, which are symmetrically distributed on the left and right. The gear adjustment mechanism 500 is used to drive the two groups of fin radiators 202 to open or close in a double-door shape, thereby determining whether air passes through the fin radiators 202.

[0049] In summary, in the actual application process, when the winter ambient temperature is lower than minus 20℃, it will be difficult for the air source heat pump to obtain heat from the air. In order to improve the heating efficiency of the heat pump at this time, the two sets of fin radiators 202 can be controlled to be closed by the gear adjusting mechanism 500. At this time, the external air is always preheated by the radiator first and then passes through the fin evaporator 101, thereby improving the thermal efficiency of the air source heat pump. In addition, when the temperature is relatively high, such as above 0℃, the fin evaporator 101 can easily obtain heat from the air at this time. Therefore, in this state, the geothermal heat pump mechanism 200 can be closed, and the two sets of fin radiators 202 can be expanded, so that the external air can directly pass through the fin evaporator 101.

[0050] It is worth mentioning that closing the geothermal heat pump mechanism 200 in a relatively high temperature environment not only reduces its energy consumption, but also reduces the wind resistance when the air enters the main machine box 300, improves the air convection speed, and also reduces the energy consumption of the fan 301.

[0051] Embodiment two: please refer to Figure 1 Figure 7 The embodiment provides an air source and geothermal source two-stage heat pump system. The difference between the embodiment and the embodiment one is that:

[0052] The gear adjusting mechanism 500 includes an upper holding assembly 501 and a lower holding assembly 502 corresponding to the two sets of fin radiators 202. The upper holding assembly 501 and the lower holding assembly 502 are respectively installed at the top and the bottom of one set of fin radiators 202. The top surface of the upper holding assembly 501 is provided with a first main shaft 503, and the bottom surface of the lower holding assembly 502 is provided with a second main shaft 504. The first main shaft 503 and the second main shaft 504 are respectively rotationally connected to the upper and lower walls in the interior of the secondary machine box 400, and are located on the same vertical line. The gear adjusting mechanism 500 further includes two driving motors 505. The driving motors 505 are fixedly installed on the top wall of the secondary machine box 400. The output shafts of the two driving motors 505 are respectively in transmission connection with the two first main shafts 503. Specifically, the output shaft of the driving motor 505 and the corresponding first main shaft 503 are in transmission connection through a synchronous belt or a chain. Therefore, the two sets of fin radiators 202 can be directly driven to be expanded or closed in a double-door shape by the driving motor 505.

[0053] ​Specifically, each group of fin heat sinks 202 includes two fin heat sinks 202, the upper holding assembly 501 includes two upper holding plates 5011, the two upper holding plates 5011 are respectively fixedly connected with the top walls of the two fin heat sinks 202, and the two upper holding plates 5011 are hingedly arranged between the two upper holding plates 5011; the lower holding assembly 502 includes two lower holding plates 5021, the two lower holding plates 5021 are respectively connected with the bottom walls of the two fin heat sinks 202, and the two lower holding plates 5021 are hingedly arranged between the two lower holding plates 5021; that is, the two fin heat sinks 202 in each group of fin heat sinks 202 can be folded by the hinge part. It is worth mentioning that the first main shaft 503 and the second main shaft 504 are respectively arranged on the upper holding plate 5011 and the lower holding plate 5021 close to the edge side.

[0054] Further, the two upper holding plates 5011 have a hinge shaft 5012, the hinge shaft 5012 is rotatably connected with the upper holding plate 5011 close to the edge side through a damping bearing, the hinge shaft 5012 is fixedly connected with the upper holding plate 5011 close to the middle side, and when one of the upper holding plates 5011 rotates 180° around the hinge shaft 5012, the two upper holding plates 5011 can be distributed in a folded state. It is worth mentioning that the rotation torque of the damping bearing is not less than 8 N·m, and due to the arrangement of the damping bearing, the included angle of the two upper holding plates 5011 can be kept stable in a normal state.

[0055] In the embodiment, the top end of the hinge shaft 5012 is provided with a driven gear 506, and the inner top wall of the secondary machine box 400 is provided with a first arc-shaped gear rack 401 and a second arc-shaped gear rack 402; when each group of fin heat sinks 202 rotates outward around the first main shaft 503, the driven gear 506 can be engaged with the first arc-shaped gear rack 401 and the second arc-shaped gear rack 402 respectively; specifically, when the driven gear 506 passes through the first arc-shaped gear rack 401, the hinge shaft 5012 rotates 45° inward; when the driven gear 506 passes through the second arc-shaped gear rack 402, the hinge shaft 5012 rotates 135° inward. As shown in Figure 7 that is, after the driven gear 506 passes through the first arc-shaped gear rack 401 and the second arc-shaped gear rack 402, the two upper holding plates 5011 can be in a folded state. It should be noted that the outward rotation refers to the rotation towards the side wall of the secondary machine box 400, and the inward rotation refers to the approaching of one upper holding plate 5011 to the other upper holding plate 5011.

[0056] Specifically, when the driving motor 505 controls the two first main shafts 503 to rotate 45° outward, one fin heat sink 202 close to the edge side is in an inclined state, and one fin heat sink 202 close to the middle side is in a horizontal state, as shown in Figure 6As shown; at this time, the air inlet and liquid outlet of the two finned heat sinks 202 on the side close to the edge are closed, and only the two finned heat sinks 202 on the middle side are kept in working condition. At this time, the air resistance is moderate, and part of the air can be preheated by passing through the two finned heat sinks 202. Therefore, this working condition is suitable for the case where the air temperature is moderate, for example, 0℃ to -10℃.

[0057] It should be noted that the finned heat sink 202 on the middle side is kept in a horizontal position, which has the advantage of enabling it to be in full contact with the air. At the same time, compared with the condition that the finned heat sink 202 is completely closed, the air resistance is smaller, so that the fan 301 can operate at a lower power, which helps to reduce the energy consumption of the fan 301 and also helps to prolong the service life of the fan 301.

[0058] Embodiment three: please refer to Figure 1 Figure 9 The embodiment proposes a two-stage heat pump system of air source and geothermal source. The difference between this embodiment and embodiment one is that:

[0059] The left and right side walls of the auxiliary machine box 400 and located close to one end of the main machine box 300 are provided with air vents 403, and the air vents 403 are also provided with dust screens. The left and right side walls of the inside of the auxiliary machine box 400 are slidably provided with shielding plates 404, and the shielding plates 404 are provided with through holes 405. The shielding plates 404 can slide in the front and back directions to realize the alignment or misalignment of the through holes 405 and the air vents 403.

[0060] Specifically, the inner wall of the auxiliary machine box 400 is rotatably provided with a driving shaft arranged in the vertical direction, and a driving gear 406 is fixedly sleeved on the driving shaft. The surface of the shielding plate 404 is provided with a driven rack 407, and the driving gear 406 and the driven rack 407 are engaged. The driving shaft and the first main shaft 503 are connected through a synchronous belt transmission. When the two groups of finned heat sinks 202 are aligned, the through holes 405 and the air vents 403 are misaligned. When the two groups of finned heat sinks 202 are rotated to be parallel to the side wall of the auxiliary machine box 400, the through holes 405 and the air vents 403 are aligned. That is, in the state as Figure 7 shown, at this time, the finned heat sinks 202 are completely unfolded, and the air vents 403 are also aligned with the through holes 405; at this time, the geothermal source heat pump mechanism 200 is powered off and closed, and only the air source heat pump mechanism 100 works, so it is suitable for use in high temperature scenarios, such as above 0℃.

[0061] It should be noted that when the geothermal source heat pump mechanism 200 is not working, the smaller the air inlet resistance of the finned evaporator 101 is, the better; therefore, aligning the air vents 403 and the through holes 405 also helps to make the air inlet of the finned evaporator 101 more smooth.

[0062] ​It is to be understood that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting; it is not intended to exclude myriad other embodiments of the present application that other inventors can develop based on the same general inventive concepts embodied by the described embodiments. That is, although the present application is described in terms of particular embodiments and implementations, it is to be understood that the terminology used is for the purpose of descriptive clarity and that it is intended to be limited only by the words recited in the appended claims. The scope of the present application shall be limited only by the claims.

[0063] While the embodiments of the application have been shown and described herein, it is to be understood that the application is not limited to these embodiments. Rather, numerous modifications are possible without departing from the spirit and scope of the present application as delineated by the claims and their equivalents.

Claims

1. An air source and ground source two-stage heat pump system, comprising an air source heat pump mechanism, wherein the air source heat pump mechanism comprises a finned evaporator, a condenser, a compressor, a four-way valve and an expansion valve, characterized in that: Also includes: A geothermal heat pump mechanism, comprising an underground heat exchanger and a finned radiator, wherein the underground heat exchanger contains a low-boiling-point refrigerant, the output end of the underground heat exchanger is connected to the air inlet of the finned radiator via an air pipe, and the input end of the underground heat exchanger is connected to the liquid outlet of the finned radiator via a liquid return pipe; The main chassis, the finned evaporator is located at the rear side of the main chassis, the front and rear side walls of the main chassis are both open, and a fan is also provided inside the main chassis and in front of the finned evaporator; A sub-chassis, the sub-chassis is located at the rear side of the main chassis, the rear side wall of the sub-chassis is open, and the fin heat sink is movably arranged in the sub-chassis; The auxiliary chassis is further provided with a gear adjustment mechanism, which is used to drive the finned heat sink to flip so that the finned heat sink and the finned evaporator are aligned or staggered. There are two groups of finned heat sinks, which are symmetrically distributed on the left and right. The gear adjustment mechanism includes an upper holding assembly and a lower holding assembly corresponding to the two groups of finned heat sinks. The upper holding assembly and the lower holding assembly are respectively installed on the top and bottom of one group of finned heat sinks. The top surface of the upper holding assembly is provided with a first main shaft, and the bottom surface of the lower holding assembly is provided with a second main shaft. The first main shaft and the second main shaft are respectively rotatably connected to the upper and lower walls inside the auxiliary chassis; The gear adjustment mechanism further includes two drive motors, which are fixedly mounted on the top wall of the auxiliary chassis, and the output shafts of the two drive motors are respectively connected to the two first main shafts in a transmission manner; Each group of fin heat sinks includes two fin heat sinks, the upper retaining assembly includes two upper retaining plates, the two upper retaining plates are respectively fixedly connected to the top walls of the two fin heat sinks, and the two upper retaining plates are hingedly arranged; the lower retaining assembly includes two lower retaining plates, the two lower retaining plates are respectively connected to the bottom walls of the two fin heat sinks, and the two lower retaining plates are hingedly arranged; The first main shaft and the second main shaft are respectively arranged on the upper holding plate and the lower holding plate close to the edge side; The left and right side walls of the auxiliary chassis are both provided with ventilation holes, and the left and right side walls inside the auxiliary chassis are both slidably provided with shielding plates, and the shielding plates have through-holes; A drive shaft arranged vertically is rotatably provided on the inner wall of the auxiliary chassis, a driving gear is fixedly sleeved on the drive shaft, a driven rack is provided on the surface of the shielding plate, the driving gear and the driven rack are meshed, and the drive shaft and the first main shaft are connected by a synchronous belt transmission; When the two groups of finned heat sinks are aligned, the through openings and the air vents are staggered. When the two groups of fin heat sinks are rotated to be parallel to the side wall of the auxiliary chassis, the through openings and the air vents are aligned and distributed.

2. The air source and ground source two-stage heat pump system according to claim 1, characterized in that: The air inlet of the finned radiator is connected to the air pipe through a hose, and the liquid outlet of the finned radiator is connected to the liquid return pipe through a hose. Both the air pipe and the liquid return pipe pass through the side wall of the auxiliary chassis and extend into the inner side of the auxiliary chassis.

3. The air source and ground source two-stage heat pump system according to claim 1, characterized in that: The output shaft of the driving motor is connected to the corresponding first main shaft through a synchronous belt or chain transmission.

4. The air source and ground source two-stage heat pump system according to claim 1, characterized in that: There is a hinge shaft between the two upper retaining plates, which is rotatably connected to an upper retaining plate near the edge side through a damping bearing, and the hinge shaft is fixedly connected to an upper retaining plate near the middle side. When one of the upper retaining plates rotates 180° around the hinge shaft, the two upper retaining plates can be distributed in a folded shape.

5. The air source and ground source two-stage heat pump system according to claim 4, characterized in that: A driven gear is provided at the top end of the hinge shaft, and a first arc-shaped rack and a second arc-shaped rack are provided on the inner top wall of the auxiliary chassis; when each group of fin heat sinks rotates outward around the first main axis, the driven gear can engage with the first arc-shaped rack and the second arc-shaped rack respectively; When the driven gear passes the first arc-shaped rack, the hinge shaft rotates 45 degrees inward; When the driven gear passes the second arc-shaped rack, the hinge shaft rotates 135 degrees inward.

6. The air source and ground source two-stage heat pump system according to claim 1, characterized in that: The air vent is located on the side wall of the auxiliary chassis and close to one side of the main chassis. A dustproof net is also installed in the air vent.

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