Heat pump controlled by multi-coil temperature sensor

Abstract

The invention discloses a heat pump controlled by a multi-coil temperature sensor, and relates to the technical field of heat pump equipment.The heat pump comprises a heat pump main machine, an axial flow fan and a liquid storage tank, the heat pump main machine comprises a compressor and a control assembly, and the output end of the liquid storage tank is sequentially connected with an efficient tank heat exchanger and a fin evaporator through a pipeline; the axial flow fan is installed on one side of the fin evaporator, a plurality of defrosting temperature sensors and a plurality of valve step control temperature sensors are arranged on the outer wall of the fin evaporator, and a vapor-liquid separator is arranged on one side of the fin evaporator. According to the heat pump controlled by the multi-coil temperature sensor, the control accuracy and response speed of a heat pump system are remarkably improved, the performance of the heat pump system is optimized, the efficiency is improved, and the effect of controlling the average value of the electronic expansion valve and the defrosting minimum value is achieved.

Description

Technical Field

[0001] The invention relates to the technical field of heat pump equipment, and in particular to a heat pump controlled by a multi-coil temperature sensor. Background Art

[0002] The working principle of a heat pump is to force heat from a low-temperature object to a high-temperature object in a reverse cycle to achieve energy transfer. A heat pump controlled by a coil temperature sensor monitors the temperature inside the coil in real time by installing a temperature sensor on the coil, and feeds this temperature information back to the heat pump controller. The controller adjusts the working state of the heat pump system based on this temperature information to achieve precise temperature control and regulation. For example, in cooling mode, when the temperature of a coil is lower than the set value, the controller can adjust the opening of the electronic expansion valve corresponding to the coil to increase the refrigerant flow, thereby improving the cooling effect of the coil.

[0003] But in the original single coil temperature sensor control system, usually only one temperature sensor is used to monitor certain key parameters of the air source heat pump, such as suction temperature or condenser temperature. However, a single sensor may not fully reflect the actual state of the system, resulting in inaccurate control. Since there is only one monitoring point, especially under complex working conditions, the system may respond slowly to changes.

[0004] For example, taking the defrost process of an air source heat pump as an example, in a single coil sensor control system, there is usually only one sensor used to monitor the condenser temperature. When the condenser temperature drops to the set value, the system will start the defrost process. However, this method may not accurately reflect the actual temperature of the fin coil, resulting in the defrost starting too late or too early, affecting the system efficiency. Summary of the invention

[0005] The present invention discloses a heat pump controlled by a multi-coil temperature sensor, aiming to solve the technical problem that a single sensor may not be able to fully reflect the actual state of the system, resulting in inaccurate control, and since there is only one monitoring point, the system may have a slow response speed to changes, especially under complex working conditions.

[0006] In order to achieve the above object, the present invention adopts the following technical solutions:

[0007] A heat pump controlled by a multi-coil temperature sensor, comprising a heat pump main unit, an axial flow fan and a liquid storage tank, the heat pump main unit comprising a compressor and a control assembly, the output end of the liquid storage tank being connected to a high-efficiency tank heat exchanger and a fin evaporator in sequence through a pipeline, the axial flow fan being installed on one side of the fin evaporator, a plurality of defrosting temperature sensors and a plurality of valve step control temperature sensors being arranged on the outer wall of the fin evaporator, a vapor-liquid separator being arranged on one side of the fin evaporator, the output end of the fin evaporator and one end of the high-efficiency tank heat exchanger being both connected to the input end of the compressor through a pipeline, a return air probe being installed on the return air pipeline between the compressor and the vapor-liquid separator, an oil separator and a filter being installed on the output pipeline of the compressor, needle valves being welded at the interfaces of the vapor-liquid separator and the liquid storage tank, and a pressure controller being electrically connected between the compressor and the oil separator and between the compressor and the vapor-liquid separator;

[0008] Dividing mechanism: located at the inlet of the fin evaporator;

[0009] Adjustment mechanism: located at the bottom of the diversion mechanism.

[0010] The adoption of the above technical solution can significantly improve the accuracy and response speed of system control, optimize system performance and improve efficiency. Specifically, when in use, the original single coil temperature sensor is used to control the defrosting of the air source heat pump and the valve step adjustment of the electronic expansion valve, and is changed to a double coil temperature sensor (i.e., a defrost temperature sensor and a valve step control temperature sensor for adjusting the valve step of the electronic expansion valve) control. Since the traditional controller only uses one point control when controlling defrosting and the valve step adjustment of the electronic expansion valve, this is extended to the use of two or more coil temperature sensors (defrost temperature sensor and valve step control temperature sensor), the average value of the electronic expansion valve and the minimum value of defrosting are controlled, and a coil defrost temperature sensor is arranged for each shunt circuit of the fin evaporator. When the lowest temperature point is sensed, the unit starts defrosting to ensure that each shunt circuit of the heat pump is not frosted and the fin evaporator is not frozen. When controlling the valve step adjustment of the electronic expansion valve, a valve step adjustment coil probe can be added to convert the pressure data into a coil temperature value, thereby improving the accuracy and response speed of the valve step adjustment of the electronic expansion valve.

[0011] In a preferred embodiment, the diversion mechanism includes a bottom cover, a top cover, a limit ring, a liquid separation orifice plate and a clamping plate, a valve body is provided between the bottom cover and the top cover, the bottom outer wall of the bottom cover is connected to a main copper tube by threads near the central position, the top outer wall of the top cover is provided with eighteen thin copper tubes, and a heat exchange component is provided on the circumferential outer wall of every three thin copper tubes, the heat exchange component includes four fin bodies, eighteen first diversion holes and six groups of diversion components are opened on the top outer wall of the liquid separation orifice plate, a diversion plate and a second diversion tube are provided on the top outer wall of the liquid separation orifice plate near the central position, eight second diversion holes are opened on the circumferential outer wall of the diversion plate, and an elastic component is provided on the bottom inner wall of the diversion plate.

[0012] In this scheme, when liquid or gas-liquid mixed refrigerant (hereinafter also referred to as refrigerant fluid) enters the valve body through the thick copper tube, when the liquid refrigerant enters the valve body, due to the effect of inertia, most of the refrigerant will directly rush to the middle position of the liquid separation orifice plate (i.e., the diverter plate position), and at this time, due to the obstruction of the elastic component, the liquid or gas-liquid mixed refrigerant cannot flow out through the second diverter hole on the diverter plate, and can only flow out through the multiple first diverter holes on the liquid separation orifice plate and the corresponding diverter components; when the interior of the valve body is used as a partial heat recovery device, the gaseous refrigerant enters the interior of the valve body through multiple thin copper tubes, and part of the refrigerant flows out through the second diverter hole on the diverter plate. The divided refrigerant flows into the interior of the second diverter pipe along the guide pipe, and the elastic component will also open at the same time, so that part of the refrigerant flows out from the second diverter hole, greatly increasing the refrigerant flow cross-sectional area. This arrangement as a whole avoids the possibility of inaccurate defrost temperature sensor and valve step control temperature sensor due to insufficient diversion during defrosting and adjustment of the valve step position of the electronic expansion valve, which may cause defrost failure and inaccurate valve step adjustment of the electronic expansion valve. This arrangement avoids the situation where there is too much or too little refrigerant in certain areas, which helps to improve heat exchange efficiency and reduce energy consumption.

[0013] In a preferred embodiment, the diversion assembly includes six first diversion tubes and six guide tubes, and the six first diversion tubes and the six guide tubes are symmetrically distributed with the second diversion tube as the center, one end of the first diversion tube passes through the top outer wall of the card plate, and one end of the first diversion tube is connected to the thin copper tube.

[0014] In this solution, six first diversion tubes are evenly distributed around the second diversion tube, and are used to evenly distribute the refrigerant fluid into each thin copper tube through the first diversion tube. One end of the first diversion tube passes through the top outer wall of the card plate and communicates with the thin copper tube, ensuring that the refrigerant fluid can smoothly enter the thin copper tube for heat exchange.

[0015] In a preferred solution, the first shunt pipe is a trumpet-shaped structure, and the inlet end and the outlet end of the first shunt pipe are respectively configured as a reducing section and a diffusing section.

[0016] In this solution, the inlet section of the first diverter pipe adopts a tapered design to gradually reduce the cross-section to slow down the refrigerant flow rate, increase its residence time in the liquid distributor, and promote a more uniform distribution of the refrigerant to each output channel. The inner wall of the first diverter pipe adopts a smooth curve design to reduce fluid resistance and pressure loss. A diffusion section is set at the outlet end to enable the refrigerant to smoothly transition when flowing out of the microchannel to avoid local high-speed injection.

[0017] In a preferred embodiment, the adjustment mechanism includes a limit ring, which is connected to the top inner wall of the liquid separation orifice plate through a bearing, and the circumferential outer wall of the limit ring is fixedly connected with eight baffles. The circumferential inner wall of the liquid separation orifice plate is installed with a fixing ring, and the top outer wall of the fixing ring is provided with a plurality of equidistantly distributed mounting holes, and the baffle is located on the top outer wall of the fixing ring, and the baffle is fixed to the fixing ring by bolts.

[0018] In this solution, when the refrigerant fluid passes through the liquid separation orifice plate, the limit ring drives the baffle to move its position through the support and rotation of the bearing, further limiting the blocking range of the baffle on the first diversion hole, thereby limiting the flow range of the fluid, and further achieving precise control of the flow of the refrigerant fluid.

[0019] As can be seen from the above, a heat pump controlled by a multi-coil temperature sensor comprises a heat pump main unit, an axial flow fan and a liquid storage tank, the heat pump main unit comprises a compressor and a control component, the output end of the liquid storage tank is connected to a high-efficiency tank heat exchanger and a fin evaporator in sequence through a pipeline, the axial flow fan is installed on one side of the fin evaporator, a plurality of defrosting temperature sensors and a plurality of valve step control temperature sensors are arranged on the outer wall of the fin evaporator, a vapor-liquid separator is arranged on one side of the fin evaporator, the output end of the fin evaporator and one end of the high-efficiency tank heat exchanger are both connected to the input end of the compressor through a pipeline, a return air probe is installed on the return air pipeline between the compressor and the vapor-liquid separator, an oil separator and a filter are installed on the output pipeline of the compressor, needle valves are welded at the interfaces of the vapor-liquid separator and the liquid storage tank, and a pressure controller is electrically connected between the compressor and the oil separator and between the compressor and the vapor-liquid separator;

[0020] Dividing mechanism: located at the inlet of the fin evaporator;

[0021] The heat pump controlled by the multi-coil temperature sensor provided by the present invention has the technical effect of significantly improving the accuracy and response speed of the heat pump system control, optimizing the performance of the heat pump system and improving the efficiency, and realizing the control of the average value of the electronic expansion valve and the minimum value of defrosting. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 This is a circuit schematic diagram of a heat pump controlled by a multi-coil temperature sensor proposed by the present invention.

[0023] Figure 2 A schematic diagram of a control component of a heat pump controlled by a multi-coil temperature sensor proposed in the present invention.

[0024] Figure 3 This is a structural schematic diagram of a flow diversion mechanism of a heat pump controlled by a multi-coil temperature sensor proposed in the present invention.

[0025] Figure 4 This is a schematic structural diagram of a heat conduction component of a heat pump controlled by a multi-coil temperature sensor proposed in the present invention.

[0026] Figure 5 This is a schematic structural diagram of a flow diversion component of a heat pump controlled by a multi-coil temperature sensor proposed by the present invention.

[0027] Figure 6 This is a schematic diagram of the manifold structure of a heat pump controlled by a multi-coil temperature sensor proposed by the present invention.

[0028] Figure 7 This is a schematic diagram of the elastic component and adjustment mechanism structure of a heat pump controlled by a multi-coil temperature sensor proposed by the present invention.

[0029] Figure 8 This is a schematic diagram of the anti-collision plate structure of a heat pump controlled by a multi-coil temperature sensor proposed by the present invention.

[0030] In the figure: 1. Axial flow fan; 2. Compressor; 3. Gas-liquid separator; 4. Liquid storage tank; 5. High-efficiency tank heat exchanger; 6. Finned evaporator; 7. Oil separator; 14. Return air probe; 15. Defrost temperature sensor; 17. Four-way valve; 19. Economizer; 20. High-pressure gauge; 21. Pressure controller; 22. Filter; 23. Needle valve; 24. Enthalpy-increasing electronic expansion valve; 25. Main electronic expansion valve; 30. Valve step control temperature sensor; 31. Main copper pipe; 32. Bottom cover; 33. Valve body; 34. Top cover; 35. Thin copper tube; 36. Fin body; 37. Limiting ring; 38. Liquid separation orifice plate; 39. Card plate; 40. First diverter pipe; 41. Guide pipe; 42. Second diverter pipe; 43. Diverter plate; 44. First diverter hole; 45. Second diverter hole; 46. Fixing ring; 47. Baffle; 48. Limiting ring; 49. Fixing column; 50. Block; 51. Baffle; 52. Anti-collision plate; 53. Limiting port. DETAILED DESCRIPTION

[0031] The technical solutions in the embodiments of the present invention will be described clearly and completely below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments.

[0032] A heat pump controlled by a multi-coil temperature sensor disclosed in the present invention is mainly used in scenarios where a single sensor may not be able to fully reflect the actual state of the system, resulting in inaccurate control. Since there is only one monitoring point, the system's response speed to changes may be slow, especially under complex working conditions.

[0033] Reference Figure 1 and Figure 2 A heat pump controlled by a double multi-coil temperature sensor comprises a heat pump main unit, an axial flow fan 1 and a liquid storage tank 4, wherein the heat pump main unit comprises a compressor 2 and a control assembly, wherein the output end of the liquid storage tank 4 is sequentially connected to a high-efficiency tank heat exchanger 5 and a fin evaporator 6 through a pipeline, wherein the axial flow fan 1 is installed on one side of the fin evaporator 6, wherein a plurality of defrosting temperature sensors 15 and a plurality of valve step control temperature sensors 30 are arranged on the outer wall of the fin evaporator 6, wherein a vapor-liquid separator 3 is arranged on one side of the fin evaporator 6, wherein the output end of the fin evaporator 6 and one end of the high-efficiency tank heat exchanger 5 are both connected to the input end of the compressor 2 through a pipeline, wherein a return air probe 14 is installed on the return air pipeline between the compressor 2 and the vapor-liquid separator 3, wherein an oil separator 7 and a filter 22 are installed on the output pipeline of the compressor 2, wherein needle valves 23 are welded at the interfaces between the vapor-liquid separator 3 and the liquid storage tank 4, and a pressure controller 21 is electrically connected between the compressor 2 and the oil separator 7 as well as between the compressor 2 and the vapor-liquid separator 3;

[0034] Dividing mechanism: located at the inlet of the finned evaporator 6;

[0035] Adjustment mechanism: located at the bottom of the diversion mechanism.

[0036] Among them, the control component includes an electronic expansion valve and an economizer 19, the electronic expansion valve includes a main electronic expansion valve 25 and a reheat electronic expansion valve 24, the valve step control temperature sensor 30 is arranged on one side of the main electronic expansion valve 25, the reheat electronic expansion valve 24 is located between the liquid outlet and the gas inlet of the economizer 19, the reheat electronic expansion valve 24 is one of the key components in the jet reheat system, and is used to accurately control the flow rate of the refrigerant. In the system, the reheat electronic expansion valve 24 is located between the liquid outlet and the gas inlet of the economizer 19, and the refrigerant flow through the economizer 19 is controlled by adjusting the opening of the valve. The economizer 19 is connected through a specific pipeline, so that part of the refrigerant can bypass part of the compression process of the compressor 2, thereby improving the system energy efficiency ratio.

[0037] During the specific implementation process, a four-way valve 17 is arranged between the output end of the compressor 2 and the high-efficiency tank heat exchanger 5, a high-pressure gauge 20 is installed on the pipeline between the outlet of the oil separator 7 and the inlet of the compressor 2, and the pressure controller 21 is electrically connected to one of the high-pressure gauges 20. The oil separator 7 is used to separate the oil and refrigerant gas discharged from the compressor 2. The working state of the four-way valve 17 is automatically switched by the control system according to the set cooling / heating mode and external conditions such as temperature. The pressure controller 21 is based on the preset pressure threshold. When the system pressure exceeds this range, it can automatically cut off the power supply or adjust the system operation state to protect the equipment.

[0038] Specifically, when in use, the original single coil temperature sensor controlling the defrost of the air source heat pump and the valve step adjustment of the electronic expansion valve is changed to a double coil temperature sensor, namely the defrost temperature sensor 15 and the valve step control temperature sensor 30 for adjusting the valve step of the electronic expansion valve. Since the traditional controller only uses one point control when controlling the defrost and the valve step adjustment of the electronic expansion valve, this time it is extended to use two or more coil temperature sensors, the defrost temperature sensor 15 and the valve step control temperature sensor 30, and the electronic expansion valve average value and the minimum value for defrosting are controlled. One coil defrost temperature sensor 15 is arranged for each shunt circuit of the fin evaporator 6. When the lowest temperature point is sensed, the unit starts defrosting to ensure that each shunt circuit of the heat pump is not frosted and the fin evaporator 6 is not frozen. When controlling the valve step adjustment of the electronic expansion valve, a valve step adjustment coil probe can be added to convert the pressure data into a coil temperature value, thereby improving the accuracy and response speed of the valve step adjustment of the electronic expansion valve, thereby optimizing the system performance and improving the efficiency. Specifically: the defrost temperature sensor 15 is placed at the position where the copper tube of the fin evaporator 6 is prone to frost. After the fin evaporator 6 is frosted, the defrost time satisfied by the synchronous operation control of the unit, the synchronous operation time of the compressor 2 reaches the setting requirements, and the difference between the temperature of the defrost temperature sensor 15 and the ambient temperature meets the defrost conditions set by the controller, the air source heat pump enters the defrost state. When the defrost exit conditions are met, the unit exits the defrost state according to the program requirements. The valve step control temperature sensor 30 is placed at the outlet of the fin evaporator 6 and near the electronic expansion valve, so as to facilitate the precise control and adjustment of the valve step of the electronic expansion valve. The difference between the valve step control temperature sensor 30 and the return air temperature sensor indicates the superheat of the heat pump operation. The actual superheat must meet the target superheat requirements. When the actual superheat is smaller than the target superheat, the electronic expansion valve opens with a larger valve step number. When the actual superheat is larger than the target superheat, the electronic expansion valve closes with a smaller valve step number, and finally meets the target superheat.

[0039] The operation process of a complete closed working design system is as follows: the high-temperature and high-pressure refrigerant gas discharged from the compressor 2 first flows through the high-efficiency tank heat exchanger 5 through the four-way valve 17 to transfer heat to the heat-carrying medium and then becomes liquid. The high-pressure refrigerant liquid coming out of the high-efficiency tank heat exchanger 5 flows through the liquid storage tank, which is equipped with a needle valve 23 for vacuuming. After passing through the filter 22, it directly enters the economizer 19 and is divided into two paths: the refrigerant liquid in the auxiliary path is throttled and reduced in pressure by the enthalpy-increasing electronic expansion valve 24 and becomes a gas-liquid mixture and also enters the economizer 19. The two are in the economizer 19. Heat exchange occurs in the process, the refrigerant liquid in the auxiliary circuit absorbs heat and becomes gas, and then is sucked into the auxiliary air inlet of compressor 2, and the refrigerant in the main circuit releases heat and becomes supercooled liquid, and then enters the fin evaporator 6 after throttling and reducing the pressure by the electronic expansion valve. In the fin evaporator 6, the refrigerant in the main circuit absorbs heat in the low-temperature environment and becomes low-pressure gas, which is sucked into the air intake port of compressor 2. The refrigerants in the main circuit and the auxiliary circuit are mixed in the working chamber of compressor 2, and then further compressed and discharged, forming a closed working cycle loop. The enthalpy increase and air supplement can increase the heating capacity of the unit and the low-temperature environment to avoid excessive exhaust temperature.

[0040] Reference Figure 3 , Figure 4 and Figure 5 In a preferred embodiment, the diversion mechanism includes a bottom cover 32, a top cover 34, a limit ring 37, a liquid separation orifice plate 38 and a clamping plate 39, a valve body 33 is provided between the bottom cover 32 and the top cover 34, the bottom outer wall of the bottom cover 32 is connected with the main copper tube 31 by threads near the central position, the top outer wall of the top cover 34 is provided with eighteen thin copper tubes 35, and a heat exchange component is provided on the circumferential outer wall of every three thin copper tubes 35, the heat exchange component includes four fin bodies 36, eighteen first diversion holes 44 and six groups of diversion components are opened on the top outer wall of the liquid separation orifice plate 38, a diversion plate 43 and a second diversion tube 42 are arranged on the top outer wall of the liquid separation orifice plate 38 near the central position, eight second diversion holes 45 are opened on the circumferential outer wall of the diversion plate 43, and an elastic component is provided on the bottom inner wall of the diversion plate 43.

[0041] It should be noted that one-way valves are installed at the connection points between the second flow diversion pipe 42 and the eight flow guide pipes 41, but they are not shown in the drawings.

[0042] Among them, the diversion component includes six first diversion tubes 40 and six guide tubes 41, and the six first diversion tubes 40 and the six guide tubes 41 are symmetrically distributed with the second diversion tube 42 as the center. One end of the first diversion tube 40 passes through the top outer wall of the card plate 39, and one end of the first diversion tube 40 is connected to the thin copper tube 35. The six first diversion tubes 40 are evenly distributed around the second diversion tube 42, and are used to evenly distribute the refrigerant fluid to each thin copper tube 35 through the first diversion tube 40. One end of the first diversion tube 40 passes through the top outer wall of the card plate 39 and is connected to the thin copper tube 35, ensuring that the refrigerant fluid can smoothly enter the thin copper tube 35 for heat exchange.

[0043] The first diverter tube 40 is a trumpet-shaped structure, and the inlet end and the outlet end of the first diverter tube 40 are respectively arranged as a reduction section and a diffusion section; the inlet section of the first diverter tube 40 adopts a tapered design, gradually reducing the cross-section to slow down the refrigerant flow rate, increase its residence time in the liquid distributor, and promote the refrigerant to be more evenly distributed to each output channel. The inner wall of the first diverter tube 40 adopts a smooth curve design to reduce fluid resistance and reduce pressure loss. A diffusion section is arranged at the outlet end so that the refrigerant can smoothly transition when flowing out of the microchannel to avoid local high-speed injection. In specific implementation, the length of the tapered section at the inlet end is 50 mm, and the cross-sectional change rate is 20%. The length of the diffusion section at the outlet end is 30 mm, and the cross-sectional change rate is 15%. In addition, the first diverter tube 40 can be made of corrosion-resistant, high thermal conductivity materials, such as stainless steel or titanium alloy. These materials have good mechanical properties and thermal stability, can withstand high temperature and high pressure refrigerant environments, and ensure efficient heat exchange.

[0044] In specific practice, the cross-section of the liquid separation orifice plate 38 is an isosceles trapezoidal structure, and the fin body 36 is a wavy structure. The multiple first diversion holes 44 are evenly distributed on the circumferential outer wall of the liquid separation orifice plate 38, that is, the two non-parallel side waists in the cross-section, which helps to ensure that the refrigerant fluid maintains uniformity and stability during the distribution process, and can also reduce the pressure loss and fluctuation of the fluid during the distribution process. The wavy fin body 36 does help to improve the flow and heat transfer performance of the refrigerant in the fin evaporator. The wavy fin body 36 can increase the heat exchange area, while guiding the refrigerant to flow more evenly through the surface of the fin body 36, reducing the formation of flow dead zones and vortices.

[0045] Specifically, after a general refrigerant passes through a thermal expansion valve, it will become a two-phase fluid mixed with liquid and gas. When the liquid or gas-liquid mixed refrigerant, also referred to as the refrigerant fluid, enters the valve body 33 through a thick copper tube, due to the effect of inertia, most of the refrigerant will directly rush to the middle position of the liquid separation orifice 38, that is, the position of the diverter plate 43. At this time, due to the obstruction of the elastic component, the liquid or gas-liquid mixed refrigerant cannot flow out through the second diverter hole 45 on the diverter plate 43. The refrigerant will only be dispersed and then evenly flow out through the multiple first diverter holes 44 on the diverter orifice 38 and the corresponding diverter components. When the refrigerant passes through the interior of the multi-component diverter component, the inlet end of the diverter component is designed to be narrow, so the flow area is sharply reduced. In addition, due to a certain pressure difference between the upper surface of the liquid separation orifice 38 and the lower surface of the liquid separation orifice 38, the flow rate of the refrigerant will increase accordingly. When the refrigerant passes through the interior of the multi-component diverter component, the inlet end of the diverter component is designed to be narrow, so the flow area is sharply reduced. In addition, due to the pressure difference between the upper surface of the liquid separation orifice 38 and the lower surface of the liquid separation orifice 38, the flow rate of the refrigerant will increase accordingly. When the valve body 33 is inside When the part is used as a partial heat recovery device, the gaseous refrigerant enters the valve body 33 through multiple thin copper tubes 35. At this time, the pressure on the upper surface of the liquid separation orifice 38 is greater than the pressure on the lower surface of the liquid separation orifice 38. The one-way valve is now opened. In the process of the refrigerant flowing downward along the multiple first shunt pipes 40, part of the refrigerant flows into the second shunt pipe 42 along the guide pipe 41. At the same time, the elastic component will also open, so that part of the refrigerant flows out from the second shunt hole 45, greatly increasing the flow cross-sectional area of ​​the refrigerant. This arrangement as a whole avoids the possibility of inaccurate defrost temperature sensor 15 and valve step control temperature sensor 30 due to insufficient shunt during defrosting and adjusting the valve step position of the electronic expansion valve, which may cause defrosting to fail to start and inaccurate valve step adjustment of the electronic expansion valve. This arrangement avoids the situation where there is too much or too little refrigerant in some areas, which helps to improve heat exchange efficiency and reduce energy consumption.

[0046] Reference Figure 6 , Figure 7 and Figure 8 In a preferred embodiment, the elastic component includes a fixed column 49, and a stopper 50 and a stopper 51 are provided on the circumferential outer wall of the fixed column 49. The stopper 51 is located above the stopper 50, and the stopper 51 and the diverter plate 43 are both hemispherical structures.

[0047] Among them, eight anti-collision plates 52 are provided on the bottom outer wall of the card plate 39, and three limiting openings 53 are opened on the bottom outer wall of the card plate 39. One end of the first diversion pipe 40 passes through the inner wall of the limiting opening 53, and the inner wall of the limiting opening 53 is provided with a buffer pad. Adding a buffer pad in the area where the inner wall of the limiting opening 53 contacts the first diversion pipe 40 can reduce the damage caused by impact and vibration to the card plate 39 and the anti-collision plate 52, so as to adapt to the long-term use environment. The buffer material can be rubber pads, foam plastics, etc., which have good elasticity and wear resistance. At the same time, the setting of the limiting opening 53 effectively limits the first diversion pipe 40.

[0048] Specifically, when the baffle 51 is affected by the refrigerant fluid flowing upward from the main copper tube 31, the baffle 51 will be attached to the bottom inner wall of the liquid separation orifice plate 38 under the action of inertia. Since the baffle 51 and the liquid separation orifice plate 38 are both hemispherical structures, the contact area between them is large, and due to the setting of the baffle 51, the second diversion hole 45 on the liquid separation orifice plate 38 can be directly blocked, so that the baffle 51 can seal the second diversion hole 45 on the liquid separation orifice plate 38 more reliably to prevent the refrigerant fluid from passing directly. When the refrigerant enters the valve body 33 from multiple thin copper tubes 35, since the pressure on the upper surface of the liquid separation orifice plate 38 is greater than the pressure on the lower surface of the liquid separation orifice plate 38, there is a certain pressure difference, and part of the refrigerant fluid will pass through the second diversion hole 45 on the diversion plate 43, generating sufficient force to separate the baffle 51 from the diversion plate 43, and then flow out along the gap between the diversion plate 43 and the baffle 51 to continue its refrigeration cycle.

[0049] Reference Figure 7 In a preferred embodiment, the adjustment mechanism includes a limit ring 48, which is connected to the top inner wall of the liquid separation orifice plate 38 through a bearing, and eight baffles 47 are fixedly connected to the circumferential outer wall of the limit ring 48. A fixing ring 46 is installed on the circumferential inner wall of the liquid separation orifice plate 38, and a plurality of mounting holes equidistantly distributed are opened on the top outer wall of the fixing ring 46. The baffle 47 is located on the top outer wall of the fixing ring 46, and the baffle 47 is fixed to the fixing ring 46 by bolts. When the refrigerant fluid passes through the liquid separation orifice plate 38, the limit ring 48 drives the baffle 47 to move its position through the support and rotation of the bearing, further limiting the blocking range of the baffle 47 on the first diversion hole 44, thereby limiting the flow range of the fluid, and further achieving precise control of the flow of the refrigerant fluid.

[0050] Working principle: When in use, the original single coil temperature sensor that controls the defrost of the air source heat pump and the valve step adjustment of the electronic expansion valve is changed to a double coil temperature sensor, namely the defrost temperature sensor 15 and the valve step control temperature sensor 30 for the valve step adjustment of the electronic expansion valve. Since the traditional controller only uses one point control when controlling defrost and valve step adjustment of the electronic expansion valve, this time it is extended to use two or more coil temperature sensors, the defrost temperature sensor 15 and the valve step control temperature sensor 30, the average value of the electronic expansion valve and the minimum value of defrost are controlled, and each shunt circuit of the fin evaporator 6 is arranged with a coil defrost temperature sensor 15. When the lowest temperature point is sensed, the unit starts defrosting to ensure that each heat pump The bypass circuit will not frost and the fin evaporator 6 will not be damaged. When controlling the valve step adjustment of the electronic expansion valve, a valve step adjustment coil probe can be added to convert the pressure data into a coil temperature value, thereby improving the accuracy and response speed of the valve step adjustment of the electronic expansion valve, thereby optimizing the system performance and improving efficiency. Specifically: the defrost temperature sensor 15 is placed at the position where the copper tube of the fin evaporator 6 is prone to frost. After sensing the fin evaporator 6 is frosted, the unit synchronous operation control meets the defrost time, the compressor 2 synchronous operation time reaches the set requirements, and the difference between the temperature of the defrost temperature sensor 15 and the ambient temperature meets the defrost conditions set by the controller, the air source heat pump enters defrost, and when the defrost exit conditions are met, the unit exits defrost as required by the program. The valve step control temperature sensor 30 is placed at the outlet of the fin evaporator 6 and near the electronic expansion valve, so as to facilitate the precise control and adjustment of the valve step of the electronic expansion valve. The difference between the valve step control temperature sensor 30 and the return air temperature sensor represents the superheat of the heat pump operation. The actual superheat must meet the target superheat requirement. When the actual superheat is smaller than the target superheat, the electronic expansion valve opens with a larger valve step number. When the actual superheat is larger than the target superheat, the electronic expansion valve closes with a smaller valve step number, and finally the target superheat is met.

[0051] The above description is only a preferred specific implementation manner of the present invention, but the protection scope of the present invention is not limited thereto. Any technician familiar with the technical field can make equivalent replacements or changes according to the technical scheme and inventive concept of the present invention within the technical scope disclosed by the present invention, which should be covered by the protection scope of the present invention.

Claims

1. A heat pump controlled by a multi-coil temperature sensor, comprising a heat pump main unit, an axial flow fan (1) and a liquid storage tank (4), characterized in that: The heat pump host comprises a compressor (2) and a control component. The output end of the liquid storage tank (4) is connected to a high-efficiency tank heat exchanger (5) and a fin evaporator (6) in sequence through a pipeline. The axial flow fan (1) is installed on one side of the fin evaporator (6). A plurality of defrosting temperature sensors (15) and a plurality of valve step control temperature sensors (30) are arranged on the outer wall of the fin evaporator (6). A vapor-liquid separator (3) is arranged on one side of the fin evaporator (6). The output end of the fin evaporator (6) and one side of the high-efficiency tank heat exchanger (5) are connected to each other. The ends are connected to the input end of the compressor (2) through pipelines, a return air probe (14) is installed on the return air pipeline between the compressor (2) and the vapor-liquid separator (3), an oil separator (7) and a filter (22) are installed on the output pipeline of the compressor (2), a needle valve (23) is welded at the interface between the vapor-liquid separator (3) and the liquid storage tank (4), and a pressure controller (21) is electrically connected between the compressor (2) and the oil separator (7) and between the compressor (2) and the vapor-liquid separator (3); A flow dividing mechanism: located at the inlet of the finned evaporator (6); Adjustment mechanism: located at the bottom of the diversion mechanism.

2. A heat pump controlled by a multi-coil temperature sensor according to claim 1, characterized in that: The control component comprises an electronic expansion valve and an economizer (19), wherein the electronic expansion valve comprises a main electronic expansion valve (25) and an enthalpy-increasing electronic expansion valve (24), wherein the valve step control temperature sensor (30) is arranged on one side of the main electronic expansion valve (25), and the enthalpy-increasing electronic expansion valve (24) is located between the liquid path outlet and the gas path inlet of the economizer (19).

3. A heat pump controlled by a multi-coil temperature sensor according to claim 2, characterized in that: A four-way valve (17) is provided between the output end of the compressor (2) and the high-efficiency tank heat exchanger (5), a high-pressure gauge (20) is installed on the pipeline between the outlet of the oil separator (7) and the inlet of the compressor (2), and the pressure controller (21) is electrically connected to one of the high-pressure gauges (20).

4. A heat pump controlled by a multi-coil temperature sensor according to claim 1, characterized in that: The flow dividing mechanism comprises a bottom cover (32), a top cover (34), a limiting ring (37), a liquid dividing orifice plate (38) and a clamping plate (39); a valve body (33) is arranged between the bottom cover (32) and the top cover (34); a main copper tube (31) is connected to the bottom outer wall of the bottom cover (32) near the central position by means of a thread; eighteen thin copper tubes (35) are arranged on the top outer wall of the top cover (34); and a replacement valve (36) is arranged on the circumferential outer wall of every three of the thin copper tubes (35). A heat exchange component, the heat exchange component includes four fin bodies (36), the top outer wall of the liquid separation orifice plate (38) is provided with eighteen first diversion holes (44) and six groups of diversion components, the top outer wall of the liquid separation orifice plate (38) is provided with a diversion plate (43) and a second diversion pipe (42) near the central position, the circumferential outer wall of the diversion plate (43) is provided with eight second diversion holes (45), and the bottom inner wall of the diversion plate (43) is provided with an elastic component.

5. A heat pump controlled by a multi-coil temperature sensor according to claim 4, characterized in that: The flow diversion assembly comprises six first flow diversion tubes (40) and six flow guide tubes (41), the six first flow diversion tubes (40) and the six flow guide tubes (41) are symmetrically distributed with the second flow diversion tube (42) as the center, one end of the first flow diversion tube (40) passes through the top outer wall of the clamping plate (39), and one end of the first flow diversion tube (40) is in communication with the thin copper tube (35).

6. A heat pump controlled by a multi-coil temperature sensor according to claim 5, characterized in that: The first shunt pipe (40) is a trumpet-shaped structure, and the inlet end and the outlet end of the first shunt pipe (40) are respectively arranged as a reduction section and a diffusion section.

7. A heat pump controlled by a multi-coil temperature sensor according to claim 6, characterized in that: The cross section of the liquid separation orifice plate (38) is an isosceles trapezoidal structure, and the fin body (36) is a wavy structure.

8. A heat pump controlled by a multi-coil temperature sensor according to claim 4, characterized in that: The elastic component comprises a fixed column (49), a stopper (50) and a stopper (51) are provided on the circumferential outer wall of the fixed column (49), the stopper (51) is located above the stopper (50), and the stopper (51) and the diverter plate (43) are both hemispherical structures.

9. A heat pump controlled by a multi-coil temperature sensor according to claim 5, characterized in that: The bottom outer wall of the clamping plate (39) is provided with eight anti-collision plates (52), the bottom outer wall of the anti-collision plate (52) is provided with three limiting openings (53), one end of the first shunt pipe (40) passes through the inner wall of the limiting opening (53), and the inner wall of the limiting opening (53) is provided with a buffer pad.

10. A heat pump controlled by a multi-coil temperature sensor according to claim 4, characterized in that: The regulating mechanism comprises a limiting ring (48), wherein the limiting ring (48) is connected to the top inner wall of the liquid separation orifice plate (38) through a bearing, and eight baffles (47) are fixedly connected to the circumferential outer wall of the limiting ring (48), and a fixing ring (46) is installed on the circumferential inner wall of the liquid separation orifice plate (38), and a plurality of mounting holes equidistantly distributed are opened on the top outer wall of the fixing ring (46), and the baffle (47) is located on the top outer wall of the fixing ring (46), and the baffle (47) and the fixing ring (46) are fixed by bolts.

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