WO2023035511A1 - 一种空气源热泵系统及空气源热泵的控制方法 - Google Patents

一种空气源热泵系统及空气源热泵的控制方法 Download PDF

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Publication number
WO2023035511A1
WO2023035511A1 PCT/CN2021/143672 CN2021143672W WO2023035511A1 WO 2023035511 A1 WO2023035511 A1 WO 2023035511A1 CN 2021143672 W CN2021143672 W CN 2021143672W WO 2023035511 A1 WO2023035511 A1 WO 2023035511A1
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Prior art keywords
expansion valve
temperature
heat pump
steps
pipeline
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PCT/CN2021/143672
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English (en)
French (fr)
Inventor
马超
钟文朝
张登科
陶骙
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美的集团武汉暖通设备有限公司
广东美的制冷设备有限公司
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Publication of WO2023035511A1 publication Critical patent/WO2023035511A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating
    • H05K7/20218—Modifications to facilitate cooling, ventilating, or heating using a liquid coolant without phase change in electronic enclosures

Definitions

  • the present application relates to the technical field of heat pumps, in particular to an air source heat pump system and a control method for the air source heat pump.
  • the temperature of the water flow that exchanges heat with the refrigerant of the air source heat pump is too low, the temperature of the refrigerant flowing through the refrigerant cooling device will be too low, thereby causing the refrigerant cooling device to easily generate Condensation, and the existence of condensation may cause problems such as leakage or short circuit of the electronic control module, resulting in failure of the electronic control module.
  • the embodiment of the present application expects to provide an air source heat pump system and a control method of the air source heat pump that can prevent the condensation of the refrigerant cooling device.
  • an air source heat pump system including:
  • a heat pump module the heat pump module includes a circulation pipeline and a compressor, a four-way valve, a first heat exchanger, a refrigerant cooling device, a first expansion valve, and a second heat exchanger sequentially arranged on the circulation pipeline, so that The first heat exchanger is used for heat exchange with water, and the refrigerant cooling device is thermally connected to the electronic control module;
  • a bypass module includes a bypass pipeline and a control valve, the first end of the bypass pipeline is connected to the circulation pipe between the first heat exchanger and the refrigerant cooling device On the road, the second end of the bypass pipeline is connected to the circulation pipeline between the refrigerant cooling device and the first expansion valve, and the control valve is arranged on the bypass pipeline to When the air source heat pump system is in a heating mode, the bypass pipeline is selectively turned on or off.
  • the heat pump module further includes a second expansion valve, the second expansion valve is arranged on the circulation pipeline and is located between the refrigerant cooling device and the first end of the bypass pipeline , when the air source heat pump system is in the heating mode, when the control valve is in the conduction state of the bypass pipeline, the second expansion valve is in the throttling state.
  • control valve is a one-way valve or a two-way valve.
  • Another embodiment of the present application provides a method for controlling an air source heat pump, which is used in the above-mentioned air source heat pump system, and the method includes:
  • control valve is controlled to conduct the bypass pipeline.
  • the heat pump module further includes a second expansion valve, the second expansion valve is arranged on the circulation pipeline and is located between the refrigerant cooling device and the first end of the bypass pipeline , before controlling the control valve to conduct the bypass line, the method further includes:
  • the method further includes:
  • the number of steps of the second expansion valve is adjusted according to a preset rule.
  • the adjusting the number of steps of the second expansion valve according to preset rules includes:
  • the number of steps of the second expansion valve is adjusted according to the calculated number of adjustment steps.
  • the step number of the second expansion valve is adjusted according to the calculated number of adjustment steps, specifically:
  • the adjusting the number of steps of the second expansion valve according to preset rules further includes:
  • the number of adjustment steps is calculated every G seconds.
  • control valve when the control valve is in the conduction state of the bypass pipeline, if the temperature at the outlet side satisfies a first preset condition, the control valve is controlled to cut off the bypass pipeline. pipeline and control the number of steps of the second expansion valve to open to the maximum value; if the outlet-side temperature does not meet the first preset condition, and the duration of the outlet-side temperature A preset duration; or, the duration of the outlet side temperature being lower than the outdoor ambient temperature is equal to a first preset duration, then controlling the compressor to stop;
  • the first preset condition is: the outlet side temperature is greater than or equal to the minimum value of the first set temperature and the second set temperature; or, the outlet side temperature is equal to the first set temperature and the second set temperature The minimum value of two set temperatures, the second set temperature being the sum of the outdoor ambient temperature and the first hysteresis temperature.
  • the method further includes:
  • the compressor is controlled to start up, the control valve is controlled to block the bypass line and the number of steps of the second expansion valve is controlled to open to a maximum value;
  • the second preset condition is: the outlet side temperature is greater than or equal to the sum of the outdoor ambient temperature and the second return difference temperature, and the duration is greater than or equal to the second preset duration.
  • Embodiments of the present application provide an air source heat pump system and a control method for the air source heat pump.
  • the air source heat pump system is provided with a bypass module having a bypass pipeline and a control valve.
  • the control valve can lead to the bypass pipeline, allowing part of the refrigerant to flow through the bypass pipeline, thereby reducing the flow of refrigerant flowing through the refrigerant cooling device so that the refrigerant flowing through The temperature of the refrigerant in the heat dissipation device rises, thereby preventing the condensation of the refrigerant heat dissipation device, thereby avoiding the failure of the electronic control module due to the existence of condensation.
  • Fig. 1 is a schematic structural diagram of an air source heat pump system provided by an embodiment of the present application.
  • the half arrow in the figure indicates the direction of refrigerant flow in the heating mode;
  • Fig. 2 is a schematic structural diagram of another air source heat pump system provided by an embodiment of the present application.
  • the half arrow in the figure indicates the direction of refrigerant flow in the heating mode;
  • Fig. 3 is a front view of the cooperation relationship between the electronic control module and the refrigerant cooling device shown in Fig. 1 and Fig. 2;
  • Fig. 4 is the left view of Fig. 3;
  • Fig. 5 is a method schematic diagram of an air source heat pump control method provided by an embodiment of the present application.
  • Fig. 6 is a flow chart of an air source heat pump control method provided by an embodiment of the present application.
  • the air source heat pump system includes an electronic control module 10 , a heat pump module 20 and a bypass module 30 ;
  • the heat pump module 20 includes a circulation pipeline 21 And the compressor 22, the four-way valve 23, the first heat exchanger 24, the refrigerant cooling device 25, the first expansion valve 26 and the second heat exchanger 27 arranged in sequence on the circulation pipeline 21, the first heat exchanger 24
  • the refrigerant cooling device 25 is thermally connected to the electronic control module 10, that is to say, the refrigerant cooling device 25 can dissipate heat from the electronic control module 10 through heat exchange with the electronic control module 10;
  • bypass The module 30 includes a bypass pipeline 31 and a control valve 32.
  • the first end of the bypass pipeline 31 is connected to the circulation pipeline 21 between the first heat exchanger 24 and the refrigerant cooling device 25.
  • the bypass pipeline 31 The second end is connected to the circulation pipeline 21 between the refrigerant cooling device 25 and the first expansion valve 26, and the control valve 32 is arranged on the bypass pipeline 31 to selectively The ground conducts or cuts off the bypass line 31.
  • the air source heat pump system described in the embodiments of the present application can be used for floor heating, heat pump water heaters and other equipment that need to use the air source heat pump system.
  • the refrigerant circulates in the circulation pipeline 21 , can exchange heat with water when passing through the first heat exchanger 24 , and can exchange heat with the electronic control module 10 when passing through the refrigerant cooling device 25 .
  • the first heat exchanger 24 can be various heat exchangers with heat exchanging functions.
  • the first heat exchanger 24 can be a water-refrigerant heat exchanger. Flow into the water-refrigerant heat exchanger from the first water port 24a of the water-refrigerant heat exchanger, and flow out from the second water port 24b after exchanging heat with the refrigerant flowing through the water-refrigerant heat exchanger in the water-refrigerant heat exchanger .
  • the first heat exchanger 24 may also be a heat exchange coil, and an air source heat pump system is used for a heat pump water heater as an example, water flows into the water tank 40 from the water inlet 40a of the water tank 40, and flows from the water outlet 40b flows out, and in the heating mode, the water in the water tank 40 is heated to hot water after exchanging heat with the refrigerant flowing through the heat exchange coil.
  • an air source heat pump system is used for a heat pump water heater as an example, water flows into the water tank 40 from the water inlet 40a of the water tank 40, and flows from the water outlet 40b flows out, and in the heating mode, the water in the water tank 40 is heated to hot water after exchanging heat with the refrigerant flowing through the heat exchange coil.
  • the control valve 32 is used to control the conduction or cut-off of the bypass pipeline 31.
  • the control valve 32 conducts the bypass pipeline 31, a part of the refrigerant flowing out of the first heat exchanger 24 will dissipate heat through the refrigerant.
  • the device 25 flows to the first expansion valve 26 , and another part of the refrigerant flows to the first expansion valve 26 through the bypass pipe 31 , which is equivalent to reducing the flow rate of the refrigerant flowing through the refrigerant cooling device 25 .
  • control valve 32 shown in FIG. 1 and FIG. 2 is a two-way valve.
  • control valve 32 can also be a one-way valve, or other valves with a conduction or cut-off bypass line. 31 function valve or valve group.
  • the electronic control module 10 is mainly composed of a circuit board 11 and electronic components 12 , and pins of the electronic components 12 are welded on the circuit board 11 .
  • a bracket 13 for supporting the electronic component 12 may also be provided on the circuit board 11 .
  • the air source heat pump system of the embodiment of the present application is provided with a bypass module 30 having a bypass pipeline 31 and a control valve 32.
  • the control valve 32 can conduct the bypass pipeline 31, so that part of the refrigerant flows through the bypass pipeline 31, thereby reducing the flow rate of the refrigerant flowing through the refrigerant cooling device 25, so that the refrigerant flowing through the refrigerant cooling device 25
  • the temperature rises, thereby preventing condensation from occurring in the cooling medium cooling device, thereby avoiding the failure of the electronic control module 10 due to the existence of condensation.
  • the heat pump module 20 further includes a second expansion valve 28 , the second expansion valve 28 is arranged on the circulation pipeline 21 and is located at the first position between the refrigerant cooling device 25 and the bypass pipeline 31 .
  • the second expansion valve 28 is in the throttling state, that is, in the bypass
  • the second expansion valve 28 can be used to throttle the refrigerant flowing to the refrigerant cooling device 25, and the refrigerant throttled by the second expansion valve 28 flows to the first expansion valve 26 through the bypass pipeline 31, thereby Therefore, the flow rate of the refrigerant flowing through the refrigerant cooling device 25 can be adjusted.
  • the air source heat pump system of the embodiment of the present application can also have a cooling mode.
  • the cooling mode the first heat exchanger 24 can cool down or cool the water by exchanging heat with the water. That is to say, the air source heat pump system
  • the system can also be used in ground heating and ground cooling combined supply equipment or a heat pump water heater with cooling function, and the second expansion valve 28 can also be used to throttle the refrigerant flowing out of the refrigerant heat sink 25 in cooling mode.
  • the second expansion valve 28 can also be used to throttle the refrigerant flowing out of the refrigerant radiator 25 in the defrosting mode.
  • the refrigerant cooling device 25 includes a cooling plate 251, a fixing plate 252 and a refrigerant pipeline 253, the fixing plate 252 is arranged on the cooling plate 251 and between the fixing plate 252 and the cooling plate 251 A first installation passage is defined, and the heat dissipation plate 251 is thermally connected to the electronic control module 10, that is, the heat dissipation plate 251 can perform heat exchange with the electric control module 10, and part of the refrigerant pipeline 253 is arranged in the first installation passage. Two opposite ends of the refrigerant pipeline 253 protrude from the first installation passage along the extension direction and communicate with the circulation pipeline 21 respectively.
  • the fixing plate 252 and the heat dissipation plate 251 can be fastened and connected by fasteners such as bolts and screws, or can be fixedly connected by welding or the like, and the fixing plate 252 and the heat dissipation plate 251 can also be integrally formed.
  • the first installation channel can be formed on one of the fixing plate 252 and the heat dissipation plate 251, or grooves can be formed on the fixing plate 252 and the heat dissipation plate 251 respectively.
  • the fixing plate 252 is disposed on the heat dissipation plate 251 , and the fixing plate 252 and the groove on the heat dissipation plate 251 jointly form a first installation channel.
  • the refrigerant circulating in the circulation pipeline 21 flows through the refrigerant cooling device 25, it flows into the refrigerant pipeline 253 from one end of the refrigerant pipeline 253 along the extension direction, and then flows out from the other end of the refrigerant pipeline 253 along the extension direction.
  • the refrigerant flows through the region where the refrigerant pipeline 253 is located in the first installation channel, the refrigerant can exchange heat with the heat dissipation plate 251 , thereby dissipating heat from the electronic control module 10 .
  • the refrigerant cooling device 25 further includes a first thermally conductive material layer, and the first thermally conductive material layer is sandwiched between the electronic component 12 and the heat dissipation plate 251 .
  • the first heat conduction material layer is made of a material with heat conduction function, such as heat conduction silica gel, and the first heat conduction material layer is sandwiched between the electronic component 12 and the heat dissipation plate 251 to reduce the gap between the electronic component 12 and the heat dissipation plate 251.
  • the thermal resistance of the heat transfer is improved to improve the heat conduction effect between the electronic component 12 and the heat dissipation plate 251 .
  • the refrigerant cooling device 25 may also include a second heat-conducting material layer, and the second heat-conducting material layer is sandwiched between the heat dissipation plate 251 and the fixing plate 252 .
  • the second heat-conducting material layer is also made of a material with heat-conducting function, such as heat-conducting silica gel, and the second heat-conducting material layer is sandwiched between the heat dissipation plate 251 and the fixing plate 252 to reduce the size of the heat dissipation plate 251.
  • the heat transfer resistance between the heat dissipation plate 251 and the fixed plate 252 is used to improve the heat conduction effect between the heat dissipation plate 251 and the fixed plate 252 .
  • control method of an air source heat pump please refer to FIG. 5 , the control method mainly includes the following steps:
  • Step S601 In the heating mode, obtain the outlet side temperature of the refrigerant cooling device;
  • the temperature at the outlet side of the refrigerant cooling device 25 is mainly used to reflect the temperature of the refrigerant after heat exchange with the electronic control module 10.
  • the refrigerant cooling device 25 shown in FIG. 1 and FIG. 2 in In the heating mode, the end of the refrigerant pipeline 253 near the end of the first heat exchanger 24 is the inlet end 253a, and the end of the refrigerant pipeline 253 away from the end of the first heat exchanger 24 is the outlet end 253b.
  • a temperature-sensing package 50 is provided on the refrigerant pipeline 253 between the first installation channel, and the temperature of the refrigerant pipeline 253 detected by the temperature-sensing package 50 is the outlet side temperature.
  • the first expansion valve 26 is in a throttling state.
  • Step S602 If the temperature at the outlet side is lower than the outdoor ambient temperature, control the control valve to conduct the bypass line.
  • the bypass pipe can be connected to The passage 31 allows part of the refrigerant to flow through the bypass pipe 31 to increase the temperature of the refrigerant flowing through the refrigerant heat sink 25 by reducing the flow rate of the refrigerant flowing through the refrigerant heat sink 25 .
  • the method further includes: controlling the number of steps of the second expansion valve to open to a maximum value. That is to say, in the heating mode, before the bypass line 31 is turned on, the second expansion valve 28 can be in a conduction and non-throttling state, which means that before the bypass line 31 is turned on, the flow can not be reversed.
  • the refrigerant in the refrigerant radiator 25 is throttled.
  • the method further includes: adjusting the number of steps of the second expansion valve according to a preset rule, that is, after the bypass line 31 is turned on, it can pass The number of steps of the second expansion valve 28 is adjusted so that the second expansion valve 28 throttles the refrigerant flowing to the refrigerant radiator 25 .
  • adjusting the number of steps of the second expansion valve according to a preset rule includes: calculating the number of adjustment steps of the second expansion valve according to a preset formula; adjusting the number of steps of the second expansion valve according to the calculated number of adjustment steps, That is to say, the number of steps to be adjusted by the second expansion valve 28 can be determined according to the set formula, so as to be able to more accurately control the flow of refrigerant flowing to the refrigerant heat sink 25 .
  • the adjustment range of the number of adjustment steps can be 0 to 480 steps.
  • the adjustment coefficient can be a fixed value, for example, F can be fixed at 2, and the adjustment coefficient can also be changed according to certain rules, for example, it can be set when the outlet side temperature is equal to the outdoor temperature
  • the absolute value of the difference between the ambient temperature is less than 2, that is, when
  • the adjustment of the steps of the second expansion valve according to the calculated adjustment steps may be: if ⁇ P is less than 0, then Decrease the number of steps of the second expansion valve by ⁇ P steps; if ⁇ P is greater than 0, increase the number of steps of the second expansion valve by ⁇ P steps. That is to say, when the difference between the outlet side temperature and the outdoor ambient temperature is less than 0, it means that the current outlet side temperature is lower than the outdoor ambient temperature, and the possibility of condensation in the refrigerant cooling device 25 is relatively high.
  • the second The number of steps of the expansion valve 28 is reduced by ⁇ P steps to reduce the flow of refrigerant flowing through the refrigerant cooling device 25, and when the difference between the outlet side temperature and the outdoor ambient temperature is greater than 0, it means that the current outlet side temperature is higher than the outdoor ambient temperature , the possibility of condensation in the refrigerant cooling device 25 is small, therefore, the number of steps of the second expansion valve 28 can be increased by ⁇ P steps to increase the flow rate of the refrigerant flowing through the refrigerant cooling device 25 to improve the heat dissipation of the refrigerant The heat dissipation effect of the device 25 on the electronic control module 10 .
  • the step adjustment of the second expansion valve according to the preset rule further includes: calculating the adjustment step every G seconds, that is, calculating the adjustment step at intervals, and according to The calculated result adjusts the number of steps of the second expansion valve 28 accordingly, so that the flow rate of the refrigerant flowing through the refrigerant cooling device 25 can be dynamically adjusted.
  • the time interval for calculating the number of adjustment steps may be determined as required, for example, G may be greater than or equal to 10 and less than or equal to 200.
  • the control valve when the control valve is in the conduction state of the bypass pipeline, if the outlet side temperature meets the first preset condition, the control valve is controlled to cut off the bypass pipeline and control the number of steps of the second expansion valve open to maximum. That is to say, when the temperature at the outlet side satisfies the set first preset condition, it means that the temperature of the refrigerant flowing through the refrigerant heat dissipation device 25 has risen to a temperature that does not cause condensation to occur on the refrigerant heat dissipation device 25 . , the bypass line 31 can be blocked and the second expansion valve 28 can be switched to a conduction and non-throttling state.
  • the first preset condition may be that the outlet side temperature is greater than the minimum value of the first set temperature and the second set temperature, wherein the first set temperature is a fixed value, and the second set temperature is an outdoor
  • the sum of the ambient temperature and the first differential temperature, the specific value of the first differential temperature can be determined according to needs, for example, the first differential temperature can be greater than 0 degrees and less than or equal to 20 degrees.
  • Tr>min ⁇ A, Ts+B ⁇ the control valve 32 is controlled to block the bypass line 31 and the number of steps of the second expansion valve 28 is controlled to open to the maximum value. That is to say, as long as Tr is greater than the minimum value of A and Ts+B, it means that the temperature of the refrigerant flowing into the refrigerant heat dissipation device 25 has risen to a temperature that does not cause condensation to occur on the refrigerant heat dissipation device 25.
  • the compressor when the control valve is in the conduction state, if the outlet side temperature does not meet the first preset condition, and the duration of the outlet side temperature being lower than the outdoor ambient temperature is longer than the first preset duration, the compressor is controlled to stop .
  • the specific value of the first preset duration can be determined according to needs, for example, the first preset duration can be greater than 0 minutes and less than or equal to 20 minutes.
  • the above-mentioned conditions for controlling the shutdown of the compressor 22 can be expressed as: when the control valve 32 is in a conduction state, if Tr does not satisfy In the first preset condition, and S1>C, the compressor 22 is controlled to stop.
  • S1>C reflects that within the first preset time period, the temperature at the outlet side is always lower than the outdoor ambient temperature, that is to say, the temperature of the refrigerant flowing through the refrigerant cooling device 25 is still Relatively low, therefore, it is necessary to stop the flow of refrigerant by controlling the shutdown of the compressor 22 .
  • the method further includes: if the temperature at the outlet side meets the second preset condition, then controlling the compressor to start, controlling the control valve to cut off the bypass pipeline and controlling the number of steps of the second expansion valve to open to the maximum value, that is to say, when the outlet side temperature satisfies the second preset condition, the compressor 22 can also be restarted, the bypass line 31 is blocked and the second expansion valve 28 is switched to a conduction and non-throttling state , so that the air source heat pump system can continue to work in heating mode.
  • the second preset condition may be that the temperature at the outlet side is greater than or equal to the sum of the outdoor ambient temperature and the second return difference temperature, and the duration is longer than the second preset time length, wherein the second return difference temperature and the second return difference temperature
  • the specific value of the set duration can be determined according to needs, for example, the second return temperature can be greater than 0 degrees and less than or equal to 20 degrees, and the second preset duration can be greater than or equal to 5 minutes and less than or equal to 60 minutes.
  • control method includes the following steps:
  • Step S701 Turn on the heating mode
  • Step S702 Control the control valve to cut off the bypass pipeline and control the number of steps of the second expansion valve to open to the maximum value;
  • Step S703 Obtain the outlet side temperature Tr of the refrigerant cooling device
  • Step S704 determine whether the outlet side temperature Tr is lower than the outdoor ambient temperature Ts, if so, then perform step S705, if not, then perform step S703;
  • Step S705 control the control valve to lead the bypass pipeline
  • Step S707 determine whether the outlet side temperature Tr satisfies: Tr>min ⁇ A, Ts+B ⁇ , if so, then execute step S702, if not, then execute step S708;
  • Step S708 determine whether the duration S1 of the outlet side temperature Tr lower than the outdoor ambient temperature Ts is greater than the first preset duration C, if so, execute step S710, if not, execute step S705;
  • Step S709 control the compressor to shut down
  • Step S710 judging whether it is satisfied: Tr ⁇ Ts+D, and S2>E, if so, then perform step S711, if not, then perform step S709;
  • Step S711 Control the start-up of the compressor, control the control valve to block the bypass pipeline and control the number of steps of the second expansion valve to open to the maximum value.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

本申请实施例提供一种空气源热泵系统及空气源热泵的控制方法，空气源热泵系统包括电控模块、热泵模块和旁通模块；热泵模块包括循环管路以及依次设置在循环管路上的压缩机、四通阀、第一换热器、冷媒散热装置、第一膨胀阀和第二换热器，第一换热器用于与水进行热交换，冷媒散热装置与电控模块热连接；旁通模块包括旁通管路和控制阀，旁通管路的第一端连接在第一换热器和冷媒散热装置之间的循环管路上，旁通管路的第二端连接在冷媒散热装置和第一膨胀阀之间的循环管路上，控制阀设置在旁通管路上，以在空气源热泵系统处于制热模式下，选择性地导通或截止旁通管路。

Description

一种空气源热泵系统及空气源热泵的控制方法
相关申请的交叉引用
本申请基于申请号为202111048754.0、申请日为2021年09月08日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本申请涉及热泵技术领域，尤其涉及一种空气源热泵系统及空气源热泵的控制方法。
背景技术
目前，空气源热泵的电控模块大多采用的是风冷的方式进行散热，而利用冷媒散热装置对电控模块进行散热已经成为趋势。
但是，在制热模式下，如果与空气源热泵的冷媒进行换热的水流的温度过低，则会导致流经冷媒散热装置的冷媒温度过低，由此，会使得冷媒散热装置上易产生凝露，而凝露的存在可能会导致电控模块发生漏电或短路等问题，造成电控模块失效。
发明内容
有鉴于此，本申请实施例期望提供一种能够防止冷媒散热装置产生凝露的空气源热泵系统及空气源热泵的控制方法。
为达到上述目的，本申请一实施例提供了一种空气源热泵系统，包括：
电控模块；
热泵模块，所述热泵模块包括循环管路以及依次设置在所述循环管路 上的压缩机、四通阀、第一换热器、冷媒散热装置、第一膨胀阀和第二换热器，所述第一换热器用于与水进行热交换，所述冷媒散热装置与所述电控模块热连接；
旁通模块，所述旁通模块包括旁通管路和控制阀，所述旁通管路的第一端连接在所述第一换热器和所述冷媒散热装置之间的所述循环管路上，所述旁通管路的第二端连接在所述冷媒散热装置和所述第一膨胀阀之间的所述循环管路上，所述控制阀设置在所述旁通管路上，以在所述空气源热泵系统处于制热模式下，选择性地导通或截止所述旁通管路。
一种实施方式中，所述热泵模块还包括第二膨胀阀，所述第二膨胀阀设置在所述循环管路上且位于所述冷媒散热装置与所述旁通管路的第一端之间，在所述空气源热泵系统处于所述制热模式下，当所述控制阀处于导通所述旁通管路的导通状态，所述第二膨胀阀处于节流状态。
一种实施方式中，所述控制阀为单向阀或二通阀。
本申请另一实施例提供了一种空气源热泵的控制方法，用于上述所述的空气源热泵系统，所述方法包括：
在制热模式下，获取所述冷媒散热装置的出口侧温度；
若所述出口侧温度低于室外环境温度，则控制所述控制阀导通所述旁通管路。
一种实施方式中，所述热泵模块还包括第二膨胀阀，所述第二膨胀阀设置在所述循环管路上且位于所述冷媒散热装置与所述旁通管路的第一端之间，在控制所述控制阀导通所述旁通管路之前，所述方法还包括：
控制所述第二膨胀阀的步数开到最大值。
一种实施方式中，在控制所述控制阀导通所述旁通管路之后，所述方法还包括：
根据预设规则调整所述第二膨胀阀的步数。
一种实施方式中，所述根据预设规则调整所述第二膨胀阀的步数，包 括：
根据预设公式计算所述第二膨胀阀的调整步数；
根据计算出的所述调整步数调整所述第二膨胀阀的步数。
一种实施方式中，所述预设公式为：△P＝(Tr﹣Ts)×F，其中，△P代表所述调整步数，Tr代表所述出口侧温度，Ts代表所述室外环境温度，F为调整系数。
一种实施方式中，所述根据计算出的所述调整步数调整所述第二膨胀阀的步数，具体为：
若△P小于0，则将所述第二膨胀阀的步数调小△P步；
若△P大于0，则将所述第二膨胀阀的步数调大△P步。
一种实施方式中，所述根据预设规则调整所述第二膨胀阀的步数，还包括：
每隔G秒计算一次所述调整步数。
一种实施方式中，在所述控制阀处于导通所述旁通管路的导通状态下，若所述出口侧温度满足第一预设条件，则控制所述控制阀截止所述旁通管路并控制所述第二膨胀阀的步数开到最大值；若所述出口侧温度不满足第一预设条件，且所述出口侧温度低于所述室外环境温度的持续时长大于第一预设时长；或，所述出口侧温度低于所述室外环境温度的持续时长等于第一预设时长，则控制所述压缩机停机；
其中，所述第一预设条件为:所述出口侧温度大于或等于第一设定温度和第二设定温度中的最小值；或，所述出口侧温度等于第一设定温度和第二设定温度中的最小值，所述第二设定温度为所述室外环境温度与第一回差温度之和。
一种实施方式中，所述控制所述压缩机停机之后，所述方法还包括：
若所述出口侧温度满足第二预设条件，则控制所述压缩机开机，控制控制阀截止旁通管路并控制第二膨胀阀的步数开到最大值；
其中，所述第二预设条件为:所述出口侧温度大于或等于所述室外环境温度与第二回差温度之和，且持续时长大于或等于第二预设时长。
本申请实施例提供一种空气源热泵系统及空气源热泵的控制方法，空气源热泵系统中设置了具有旁通管路和控制阀的旁通模块，在制热模式下，当流经冷媒散热装置的冷媒的温度相对较低时，控制阀可以导通旁通管路，使部分冷媒从旁通管路流过，由此，可以降低流经冷媒散热装置的冷媒流量，以使流经冷媒散热装置的冷媒的温度升高，从而可以防止冷媒散热装置产生凝露，进而可以避免凝露的存在而导致电控模块失效的情况发生。
附图说明
图1为本申请一实施例提供的一种空气源热泵系统的结构示意图，图中的半箭头表示制热模式下，冷媒流动的方向；
图2为本申请一实施例提供的另一种空气源热泵系统的结构示意图，图中的半箭头表示制热模式下，冷媒流动的方向；
图3为图1和图2中所示的电控模块和冷媒散热装置的配合关系主视图；
图4为图3的左视图；
图5为本申请一实施例提供的一种空气源热泵的控制方法的方法示意图；
图6为本申请一实施例提供的空气源热泵的控制方法的流程图。
具体实施方式
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的技术特征可以相互组合，具体实施方式中的详细描述应理解为本申请宗旨的解释说明，不应视为对本申请的不当限制。
本申请一实施例提供了一种空气源热泵系统，请参阅图1和图2，该空 气源热泵系统包括电控模块10、热泵模块20和旁通模块30；热泵模块20包括循环管路21以及依次设置在循环管路21上的压缩机22、四通阀23、第一换热器24、冷媒散热装置25、第一膨胀阀26和第二换热器27，第一换热器24用于与水进行热交换，冷媒散热装置25与电控模块10热连接，也就是说，冷媒散热装置25可以通过与电控模块10进行热交换而实现对电控模块10进行散热；旁通模块30包括旁通管路31和控制阀32，旁通管路31的第一端连接在第一换热器24和冷媒散热装置25之间的循环管路21上，旁通管路31的第二端连接在冷媒散热装置25和第一膨胀阀26之间的循环管路21上，控制阀32设置在旁通管路31上，以在空气源热泵系统处于制热模式下，选择性地导通或截止旁通管路31。
具体地，本申请实施例所述的空气源热泵系统可以用于地暖、热泵热水器等需要使用空气源热泵系统的设备。
冷媒在循环管路21内循环流动，冷媒流经第一换热器24时可以与水进行热交换，冷媒流经冷媒散热装置25时可以与电控模块10进行热交换。
第一换热器24可以是各种具有换热功能的换热器，示例性地，请参阅图1，第一换热器24可以是水-冷媒换热器，在制热模式下，水从水-冷媒换热器的第一水口24a流入水-冷媒换热器，并在水-冷媒换热器内与流经水-冷媒换热器的冷媒进行热交换后从第二水口24b流出。
示例性地，请参阅图2，第一换热器24也可以是换热盘管，以空气源热泵系统用于热泵热水器为例，水从水箱40的进水口40a流入水箱40，从出水口40b流出，在制热模式下，水箱40内的水与流经换热盘管的冷媒进行热交换后被加热成热水。
控制阀32用于控制旁通管路31的导通或截止，在制热模式下，当控制阀32导通旁通管路31时，从第一换热器24流出的一部分冷媒经冷媒散热装置25流向第一膨胀阀26，另一部分冷媒则经旁通管路31流向第一膨胀阀26，相当于降低了流经冷媒散热装置25的冷媒流量。
示例性地，图1和图2中所示的控制阀32为二通阀，在一些实施例中，控制阀32也可以是单向阀，还可以是其它具有导通或截止旁通管路31功能的阀或阀组。
请参阅图4，电控模块10主要由电路板11和电子元件12组成，电子元件12的管脚焊在电路板11上。为了便于支撑电子元件12，示例性地，请继续参阅图4，电路板11上还可以设置支撑电子元件12的支架13。
本申请实施例的空气源热泵系统中设置了具有旁通管路31和控制阀32的旁通模块30，在制热模式下，当流经冷媒散热装置25的冷媒的温度相对较低时，控制阀32可以导通旁通管路31，使部分冷媒从旁通管路31流过，由此，可以降低流经冷媒散热装置25的冷媒流量，以使流经冷媒散热装置25的冷媒的温度升高，从而可以防止冷媒散热装置产生凝露，进而可以避免凝露的存在而导致电控模块10失效的情况发生。
一实施例中，请参阅图1和图2，热泵模块20还包括第二膨胀阀28，第二膨胀阀28设置在循环管路21上且位于冷媒散热装置25与旁通管路31的第一端之间，在空气源热泵系统处于制热模式下，当控制阀32处于导通旁通管路31的导通状态，第二膨胀阀28处于节流状态，也就是说，在旁通管路31导通时，可以利用第二膨胀阀28对流向冷媒散热装置25的冷媒进行节流，被第二膨胀阀28节流的冷媒通过旁通管路31流向第一膨胀阀26，由此，可以对流经冷媒散热装置25的冷媒流量进行调节。
另外，本申请实施例的空气源热泵系统还可以具有制冷模式，在制冷模式下，第一换热器24能够通过与水进行热交换而对水进行降温或冷却，也就是说，空气源热泵系统还可以用于地暖地冷两联供设备或具有制冷功能的热泵热水器，而第二膨胀阀28则还可以用于在制冷模式下对从冷媒散热装置25中流出的冷媒进行节流。除此之外，第二膨胀阀28还可以用于在除霜模式下对从冷媒散热装置25中流出的冷媒进行节流。
一实施例中，请参阅图3和图4，冷媒散热装置25包括散热板251、 固定板252和冷媒管路253，固定板252设置在散热板251上且固定板252与散热板251之间限定出第一安装通道，散热板251与电控模块10热连接，也就是说，散热板251可以与电控模块10进行热交换，冷媒管路253的部分区域设置在第一安装通道中，冷媒管路253沿延伸方向的相对两端从第一安装通道中伸出且分别与循环管路21连通。
具体地，固定板252与散热板251之间可以利用螺栓、螺钉等紧固件进行紧固连接，也可以通过焊接等方式固定连接，固定板252与散热板251之间还可以一体成型。
第一安装通道的形成方式有多种，比如，可以在固定板252与散热板251的其中之一上形成第一安装通道，也可以在固定板252与散热板251上分别形成凹槽，当固定板252设置在散热板251上，固定板252与散热板251上的凹槽共同形成第一安装通道。
在循环管路21内循环流动的冷媒在流经冷媒散热装置25时，从冷媒管路253沿延伸方向的一端流入冷媒管路253，再从冷媒管路253沿延伸方向的另一端流出，当冷媒流经冷媒管路253位于第一安装通道内的区域时，冷媒可以与散热板251进行热交换，由此，可以对电控模块10起到散热作用。
一实施例中，冷媒散热装置25还包括第一导热材料层，第一导热材料层夹设在电子元件12与散热板251之间。
具体地，第一导热材料层由具有导热功能的材料，比如导热硅胶制成，第一导热材料层夹设在电子元件12与散热板251之间可以减小电子元件12与散热板251之间的传热热阻，以提高电子元件12与散热板251之间的导热效果。
一实施例中，冷媒散热装置25也可以包括第二导热材料层，第二导热材料层夹设在散热板251与固定板252之间。
与第一导热材料层类似，第二导热材料层也由具有导热功能的材料， 比如导热硅胶制成，第二导热材料层夹设在散热板251与固定板252之间可以减小散热板251与固定板252之间的传热热阻，以提高散热板251与固定板252之间的导热效果。
本申请另一实施例提供了一种空气源热泵的控制方法，请参阅图5，该控制方法主要包括以下步骤：
步骤S601:在制热模式下，获取冷媒散热装置的出口侧温度；
具体地，冷媒散热装置25的出口侧温度主要用于反映与电控模块10进行热交换之后的冷媒的温度，示例性地，以图1和图2所示的冷媒散热装置25为例，在制热模式下，冷媒管路253靠近第一换热器24一端的端部为入口端253a，冷媒管路253远离第一换热器24一端的端部为出口端253b，可以在出口端253b与第一安装通道之间的冷媒管路253上设置感温包50，感温包50检测到的此处的冷媒管路253的管温就是出口侧温度。
另外，在制热模式下，第一膨胀阀26处于节流状态。
步骤S602:若出口侧温度低于室外环境温度，则控制控制阀导通旁通管路。
具体地，若出口侧温度低于室外环境温度，则表示与电控模块10进行热交换的冷媒的温度相对较低，冷媒散热装置25上易产生凝露，因此，可以通过导通旁通管路31，使部分冷媒从旁通管路31流过，以通过降低流经冷媒散热装置25的冷媒流量来使流经冷媒散热装置25的冷媒的温度升高。
一实施例中，对于设置有第二膨胀阀的空气源热泵系统，在控制控制阀导通旁通管路之前，所述方法还包括：控制第二膨胀阀的步数开到最大值。也就是说，在制热模式下，在旁通管路31导通之前，第二膨胀阀28可以处于导通且非节流状态，相当于在旁通管路31导通之前，可以不对流向冷媒散热装置25的冷媒进行节流。
一实施例中，在控制控制阀导通旁通管路之后，方法还包括：根据预设规则调整第二膨胀阀的步数，也就是说，在旁通管路31导通之后，可以 通过调整第二膨胀阀28的步数，使第二膨胀阀28对流向冷媒散热装置25的冷媒进行节流。
一实施例中，根据预设规则调整第二膨胀阀的步数，包括：根据预设公式计算第二膨胀阀的调整步数；根据计算出的调整步数调整第二膨胀阀的步数，也就是说，可以根据设置的公式来确定第二膨胀阀28需要调整的步数，以便于能够较精准地控制流向冷媒散热装置25的冷媒流量。
示例性地，预设公式可以为：△P＝(Tr﹣Ts)×F，其中，△P代表调整步数，Tr代表出口侧温度，Ts代表室外环境温度，F为调整系数。也就是说，调整步数等于出口侧温度与室外环境温度之差再乘以调整系数，其中，调整系数为根据设计得出的参数，示例性地，调整系数可以大于或等于1且小于或等于10。
以最大步数为480步的第二膨胀阀28为例，调整步数的调整范围可以为0到480步。
在同一个空气源热泵系统中，调整系数可以是一个固定不变的值，比如，F可以固定为2，调整系数也可以根据一定的规则而改变，比如，可以设定当出口侧温度与室外环境温度的差值的绝对值小于2，即|Tr﹣Ts|＜2时，F为1，当出口侧温度与室外环境温度的差值的绝对值大于2且小于5，即2≤|Tr﹣Ts|＜5时，F为5。
另外，需要说明的是，由于第二膨胀阀28的步数为整数，所以，△P的计算结果也取整数。
进一步地，仍以预设公式为△P＝(Tr﹣Ts)×F为例，所述根据计算出的调整步数调整第二膨胀阀的步数，可以为：若△P小于0，则将所述第二膨胀阀的步数调小△P步；若△P大于0，则将所述第二膨胀阀的步数调大△P步。也就是说，当出口侧温度与室外环境温度的差值小于0，则表示当前出口侧温度低于室外环境温度，冷媒散热装置25产生凝露的可能性较大，因此，可以通过将第二膨胀阀28的步数调小△P步，来减少流经冷媒散热 装置25的冷媒流量，而当出口侧温度与室外环境温度的差值大于0，则表示当前出口侧温度高于室外环境温度，冷媒散热装置25产生凝露的可能性较小，因此，可以通过将第二膨胀阀28的步数调大△P步，来增大流经冷媒散热装置25的冷媒流量，以提高冷媒散热装置25的对电控模块10进行散热的效果。
可以理解的是，若△P等于0，则不调整第二膨胀阀的步数。
一实施例中，所述根据预设规则调整第二膨胀阀的步数，还包括：每隔G秒计算一次调整步数，也就是说，可以每隔一段时间计算一次调整步数，并根据计算出的结果对第二膨胀阀28的步数进行相应调整，由此，可以动态调整流经冷媒散热装置25的冷媒流量。
计算调整步数的间隔时间可以根据需要进行确定，示例性地，G可以大于或等于10且小于或等于200。
一实施例中，在控制阀处于导通旁通管路的导通状态下，若出口侧温度满足第一预设条件，则控制控制阀截止旁通管路并控制第二膨胀阀的步数开到最大值。也就是说，当出口侧温度满足设定的第一预设条件时，则表示流经冷媒散热装置25的冷媒的温度已经上升至不会使冷媒散热装置25上产生凝露的温度，此时，可以截止旁通管路31并使第二膨胀阀28切换至导通且不节流的状态。
示例性地，第一预设条件可以为出口侧温度大于第一设定温度和第二设定温度中的最小值，其中，第一设定温度为一个固定值，第二设定温度为室外环境温度与第一回差温度之和，第一回差温度的具体值可以根据需要进行确定，比如，第一回差温度可以大于0度且小于或等于20度。
以A表示第一设定温度，B表示第一回差温度，则上述控制控制阀32截止旁通管路31并控制第二膨胀阀28的步数开到最大值的条件可以表示为：若Tr>min{A，Ts+B}，则控制控制阀32截止旁通管路31并控制第二膨胀阀28的步数开到最大值。也就是说，只要Tr大于A和Ts+B中的最小 值，则表示流入冷媒散热装置25的冷媒的温度已经上升至不会使冷媒散热装置25上产生凝露的温度，此时，可以截止旁通管路31并使第二膨胀阀28切换至导通且不节流的状态。
在一些实施例中，第一预设条件也可以是出口侧温度等于第一设定温度和第二设定温度中的最小值，相当于若Tr＝min{A，Ts+B}，则控制控制阀32截止旁通管路31并控制第二膨胀阀28的步数开到最大值。
一实施例中，在控制阀处于导通状态下，若出口侧温度不满足第一预设条件，且出口侧温度低于室外环境温度的持续时长大于第一预设时长，则控制压缩机停机。
第一预设时长的具体值可以根据需要进行确定，比如第一预设时长可以大于0分钟且小于或等于20分钟。
以S1表示出口侧温度低于室外环境温度的持续时长，C表示第一预设时长，则上述控制压缩机22停机的条件可以表示为：在控制阀32处于导通状态下，若Tr不满足第一预设条件，且S1>C，则控制压缩机22停机。S1>C反映了在第一预设时长内，出口侧温度始终低于室外环境温度，也就是说，在旁通管路31导通的情况下，流经冷媒散热装置25的冷媒的温度仍然相对较低，因此，需要通过控制压缩机22停机来使冷媒停止流动。
在一些实施例中，也可以是在控制阀处于导通状态下，若出口侧温度不满足第一预设条件，且出口侧温度低于室外环境温度的持续时长等于第一预设时长，即，S1＝C，则控制压缩机停机。
一实施例中，控制压缩机停机之后，方法还包括：若出口侧温度满足第二预设条件，则控制压缩机开机，控制控制阀截止旁通管路并控制第二膨胀阀的步数开到最大值，也就是说，在出口侧温度满足第二预设条件时，还可以重新启动压缩机22，截止旁通管路31并使第二膨胀阀28切换至导通且非节流状态，以使空气源热泵系统能够继续在制热模式下工作。
示例性地，第二预设条件可以为出口侧温度大于或等于室外环境温度 与第二回差温度之和，且持续时长大于第二预设时长，其中，第二回差温度和第二预设时长的具体值均可以根据需要进行确定，比如，第二回差温度可以大于0度且小于或等于20度，第二预设时长可以大于或等于5分钟且小于或等于60分钟。
另外，需要说明的是，通常情况下，压缩机22停机之后，压缩机22的停机时长需要达到一定的时长(一般最少为3分钟)，待压缩机22的压差满足重启要求之后，才能重新启动压缩机22，因此，本申请所述的控制压缩机22开机至少需要保证压缩机22的停机时长能够满足重启要求。
以D表示第二回差温度，S2表示出口侧温度大于或等于室外环境温度与第二回差温度之和的持续时长，E表示第二预设时长，则上述控制压缩机22开机的条件可以表示为：若Tr≥Ts+D，且S2>E，则控制压缩机22开机。也就是说，若Tr大于或等于Ts+D，且S2大于E，则表示流入冷媒散热装置25的冷媒的温度已经上升至不会使冷媒散热装置25上产生凝露的温度，此时，可以重新启动压缩机22。
在一些实施例中，第二预设条件也可以是出口侧温度大于或等于所述室外环境温度与第二回差温度之和，且持续时长等于第二预设时长，即Tr≥Ts+D，且S2＝E。
一具体的实施例中，请参阅图6，所述控制方法包括以下步骤：
步骤S701:开启制热模式；
步骤S702:控制控制阀截止旁通管路并控制第二膨胀阀的步数开到最大值；
步骤S703:获取冷媒散热装置的出口侧温度Tr；
步骤S704:判断出口侧温度Tr是否低于室外环境温度Ts，若是，则执行步骤S705，若否，则执行步骤S703；
步骤S705:控制控制阀导通旁通管路；
步骤S706:根据预设公式：△P＝(Tr﹣Ts)×F每隔G秒计算一次△P，并 根据计算出的△P调整第二膨胀阀的步数；
步骤S707:判断出口侧温度Tr是否满足：Tr>min{A，Ts+B}，若是，则执行步骤S702，若否，则执行步骤S708；
也就是说，判断出口侧温度Tr是否大于第一设定温度A以及室外环境温度Ts与第一回差温度B之和中的最小值。
步骤S708:判断出口侧温度Tr低于室外环境温度Ts的持续时长S1是否大于第一预设时长C，若是，则执行步骤S710，若否，则执行步骤S705；
步骤S709:控制压缩机停机；
步骤S710:判断是否满足：Tr≥Ts+D，且S2>E，若是，则执行步骤S711，若否，则执行步骤S709；
也就是说，判断出口侧温度Tr大于或等于室外环境温度Ts与第二回差温度D之和的持续时长S2是否大于第二预设时长E。
步骤S711:控制压缩机开机，控制控制阀截止旁通管路并控制第二膨胀阀的步数开到最大值。
本申请提供的各个实施例/实施方式在不产生矛盾的情况下可以相互组合。
以上所述仅为本申请的较佳实施例而已，并不用于限制本申请，对于本领域的技术人员来说，本申请可以有各种更改和变化。凡在本申请的精神和原则之内，所作的任何修改、等同替换、改进等，均包含在本申请的保护范围之内。

Claims (12)

  1. 一种空气源热泵系统，包括：
    电控模块；
    热泵模块，所述热泵模块包括循环管路以及依次设置在所述循环管路上的压缩机、四通阀、第一换热器、冷媒散热装置、第一膨胀阀和第二换热器，所述第一换热器用于与水进行热交换，所述冷媒散热装置与所述电控模块热连接；
    旁通模块，所述旁通模块包括旁通管路和控制阀，所述旁通管路的第一端连接在所述第一换热器和所述冷媒散热装置之间的所述循环管路上，所述旁通管路的第二端连接在所述冷媒散热装置和所述第一膨胀阀之间的所述循环管路上，所述控制阀设置在所述旁通管路上，以在所述空气源热泵系统处于制热模式下，选择性地导通或截止所述旁通管路。
  2. 根据权利要求1所述的空气源热泵系统，所述热泵模块还包括第二膨胀阀，所述第二膨胀阀设置在所述循环管路上且位于所述冷媒散热装置与所述旁通管路的第一端之间，在所述空气源热泵系统处于所述制热模式下，当所述控制阀处于导通所述旁通管路的导通状态，所述第二膨胀阀处于节流状态。
  3. 根据权利要求1或2所述的空气源热泵系统，所述控制阀为单向阀或二通阀。
  4. 一种空气源热泵的控制方法，用于权利要求1所述的空气源热泵系统，所述方法包括：
    在制热模式下，获取所述冷媒散热装置的出口侧温度；
    若所述出口侧温度低于室外环境温度，则控制所述控制阀导通所述旁通管路。
  5. 根据权利要求4所述的控制方法，所述热泵模块还包括第二膨胀阀， 所述第二膨胀阀设置在所述循环管路上且位于所述冷媒散热装置与所述旁通管路的第一端之间，在控制所述控制阀导通所述旁通管路之前，所述方法还包括：
    控制所述第二膨胀阀的步数开到最大值。
  6. 根据权利要求5所述的控制方法，在控制所述控制阀导通所述旁通管路之后，所述方法还包括：
    根据预设规则调整所述第二膨胀阀的步数。
  7. 根据权利要求6所述的控制方法，所述根据预设规则调整所述第二膨胀阀的步数，包括：
    根据预设公式计算所述第二膨胀阀的调整步数；
    根据计算出的所述调整步数调整所述第二膨胀阀的步数。
  8. 根据权利要求7所述的控制方法，
    所述预设公式为：△P＝(Tr﹣Ts)×F，其中，△P代表所述调整步数，Tr代表所述出口侧温度，Ts代表所述室外环境温度，F为调整系数。
  9. 根据权利要求8所述的控制方法，所述根据计算出的所述调整步数调整所述第二膨胀阀的步数，具体为：
    若△P小于0，则将所述第二膨胀阀的步数调小△P步；
    若△P大于0，则将所述第二膨胀阀的步数调大△P步。
  10. 根据权利要求7所述的控制方法，所述根据预设规则调整所述第二膨胀阀的步数，还包括：
    每隔G秒计算一次所述调整步数。
  11. 根据权利要求5所述的控制方法，在所述控制阀处于导通所述旁通管路的导通状态下，若所述出口侧温度满足第一预设条件，则控制所述控制阀截止所述旁通管路并控制所述第二膨胀阀的步数开到最大值；若所述出口侧温度不满足第一预设条件，且所述出口侧温度低于所述室外环境温度的持续时长大于或等于第一预设时长，则控制所述压缩机停机；
    其中，所述第一预设条件为:所述出口侧温度大于或等于第一设定温度和第二设定温度中的最小值，所述第二设定温度为所述室外环境温度与第一回差温度之和。
  12. 根据权利要求11所述的控制方法，所述控制所述压缩机停机之后，所述方法还包括：
    若所述出口侧温度满足第二预设条件，则控制所述压缩机开机，控制控制阀截止旁通管路并控制第二膨胀阀的步数开到最大值；
    其中，所述第二预设条件为:所述出口侧温度大于或等于所述室外环境温度与第二回差温度之和，且持续时长大于或等于第二预设时长。
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