WO2010081421A1 - Hybrid-driven cold/heat storage type heat pump unit utilizing solar photovoltaic power and commercial power - Google Patents

Hybrid-driven cold/heat storage type heat pump unit utilizing solar photovoltaic power and commercial power Download PDF

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Publication number
WO2010081421A1
WO2010081421A1 PCT/CN2010/070200 CN2010070200W WO2010081421A1 WO 2010081421 A1 WO2010081421 A1 WO 2010081421A1 CN 2010070200 W CN2010070200 W CN 2010070200W WO 2010081421 A1 WO2010081421 A1 WO 2010081421A1
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WO
WIPO (PCT)
Prior art keywords
heat
cold storage
subsystem
refrigerant
compressor
Prior art date
Application number
PCT/CN2010/070200
Other languages
French (fr)
Chinese (zh)
Inventor
袁卫星
杨宇飞
袁修干
Original Assignee
北京航空航天大学
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to CN 200910076400 priority Critical patent/CN101458005B/en
Priority to CN200910076400.X priority
Application filed by 北京航空航天大学 filed Critical 北京航空航天大学
Publication of WO2010081421A1 publication Critical patent/WO2010081421A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B27/00Machines, plant, or systems, using particular sources of energy
    • F25B27/002Machines, plant, or systems, using particular sources of energy using solar energy
    • F25B27/005Machines, plant, or systems, using particular sources of energy using solar energy in compression type systems
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B29/00Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07Details of compressors or related parts
    • F25B2400/075Details of compressors or related parts with parallel compressors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24Storage receiver heat
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19Pressures
    • F25B2700/193Pressures of the compressor
    • F25B2700/1931Discharge pressures
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19Pressures
    • F25B2700/193Pressures of the compressor
    • F25B2700/1933Suction pressures
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21Temperatures
    • F25B2700/2111Temperatures of a heat storage receiver

Abstract

A hybrid-driven cold/heat storage type heat pump unit utilizing a solar photovoltaic power and a commercial power, which has a DC compressor (2) and an AC compressor (8), is a dual supply heat pump system driven by a solar photovoltaic DC power and a common commercial AC power in combination. When there is sunshine, the DC generated by a solar cell panel (60) is used for driving the DC compressor (2) directly to produce cold and heat capacity, and the produced cold and heat capacity could be stored respectively in a phase-change cold storage medium (39) and a phase-change heat storage medium (20). When the DC power is insufficient, the AC power from power network is used for power supply.

Description

 Solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit

 The invention relates to a heat pump system, in particular to a dual power heat pump system which is driven by a hybrid of a solar photovoltaic direct current power source and a common mains alternating current power source. Background technique

The energy saving effect of the heat pump water heater is remarkable. Compared with ordinary electric water heaters, since the efficiency of the heat pump water heater is greater than 1, the amount of hot water of 3-4 kW can be obtained for each lkW of electricity consumed, so its energy-saving effect can produce ' 7 hot water'. Warm and hot water, cold water, season; air conditioning, cold water, multi-purpose, and energy saving, so it is the core equipment of the family's central energy system in the future, which is very important to improve the quality of life of residents. significance.

 An ordinary solar water heater is a device that collects the energy of sunlight by using a flat type collector, a vacuum tube collector, and the like, thereby warming the cold water. Ordinary solar water heaters cannot produce cold water while making hot water. Moreover, although solar energy itself is an inexhaustible source of clean energy, due to its intermittent and climate-dependent characteristics, solar water heaters can only function when the sun is sunny during the day, and most on cloudy and late days. When hot water is needed, it can't come in handy.

 At present, the existing solar photovoltaic vapor compression refrigeration system uses an inverter, that is, the direct current output from the solar panel is first boosted, inverted, and then converted into alternating current, and then the alternating current is used to drive the alternating current compressor, and the inverter The price is expensive, which adds extra cost to the system. Summary of the invention

 It is an object of the present invention to provide a solar photovoltaic-mains hybrid drive cold storage and heat storage type heat pump unit that can be driven by a hybrid of a solar photovoltaic direct current power source and a common commercial alternating current power source.

The object of the present invention is achieved by the following technical solutions. The solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit of the present invention comprises: a compressor module including a direct current compressor subsystem; a photovoltaic direct current power supply subsystem coupled to the direct current compressor subsystem; finned condensation a throttle mechanism; a finned evaporator; a thermal storage subsystem coupled between the compression module and the fin condenser, including heat for absorbing heat from the refrigerant a heat storage medium; a cold storage subsystem coupled between the throttle mechanism and the finned evaporator, including a cold storage medium for being cooled by the refrigerant; the compressor module, a heat storage subsystem , finned condenser, throttle mechanism, cold storage subsystem, finned The evaporators are connected by a line into a circuit in which the refrigerant circulates.

 Preferably, the compressor module further includes an AC compressor subsystem in parallel with the DC compressor subsystem.

 According to an embodiment of the present invention, four fifth solenoid valves are disposed in the compressor module for controlling a DC compressor in the DC compressor subsystem and an AC compressor in the AC compressor subsystem Access to the state of the refrigerant circuit.

 According to an embodiment of the present invention, the thermal storage subsystem includes: a heat-insulating heat-storing container having the heat storage medium therein; the cold storage subsystem comprising: a heat-insulating cold storage container, the interior containing the Cool storage medium. The thermal storage subsystem may further include: a first coil heat exchanger disposed inside the thermal storage tank, coupled to the refrigerant circulation loop, for refrigerating the refrigerant therein The medium performs heat exchange; a second coil heat exchanger disposed inside the heat storage container for exchanging heat between the water flowing therethrough and the heat storage medium inside the heat storage container, the cold storage subsystem The method further includes: a third coil heat exchanger disposed inside the cold storage container, coupled to the refrigerant circulation loop for heat exchange between the refrigerant therein and the cold storage medium; A fourth coil heat exchanger inside the cold storage container is used for exchanging heat between the water flowing therethrough and the cold storage medium inside the cold storage container.

 According to an embodiment of the present invention, a first electromagnetic valve is provided in the refrigerant circulation circuit for bypassing the refrigerant without passing through the fin condenser; Circulating the refrigerant without passing through the fin evaporator; a third solenoid valve for bypassing the refrigerant without passing through the heat storage subsystem; a fourth solenoid valve, for The refrigerant is bypassed without passing through the cold storage subsystem.

 Preferably, a first temperature sensor is disposed in the thermal storage subsystem for sensing a temperature of the thermal storage medium to determine opening and closing of the first electromagnetic valve and the third electromagnetic valve; A second temperature sensor is disposed in the cold storage subsystem for sensing the temperature of the cold storage medium to determine opening and closing of the second electromagnetic valve and the fourth electromagnetic valve.

 In the solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit, the heat storage medium may be one of paraffin, water and salt, and sodium sulfate decahydrate, and the cold storage medium may be glycerin or water. One of water, salt and paraffin.

 According to an embodiment of the invention, the photovoltaic DC power subsystem comprises a solar cell module, a junction box, a battery, a power and a voltage regulator.

 According to an embodiment of the invention, a high pressure sensor is disposed on the high pressure line of the heat pump unit, a low pressure sensor is disposed on the low pressure line, and a safety valve is disposed in the heat storage subsystem and the cold storage subsystem, respectively.

The beneficial effects of the present invention are mainly embodied in: The solar photovoltaic DC-mains dual-purpose cold storage heat storage heat pump unit of the invention is a dual power heat pump system driven by a hybrid of a solar photovoltaic direct current power source and a common mains AC power source, which has a DC compressor supplemented by each other and An AC compressor. When there is sunlight, the direct current generated by the solar panel directly drives the DC refrigeration compressor to obtain the cooling capacity and heat. The produced cold and heat can be stored separately through the phase change cold storage and heat storage medium, which makes up for The shortcomings of solar energy and climate dependence. When the DC power supply is not enough, it is powered by AC power from the power grid, which greatly improves the system's adaptability. In addition, the present invention provides two refrigeration compressors: a DC compressor and an AC compressor. When the solar energy is sufficient, the AC compressor does not work. When the solar energy is insufficient and the energy storage is insufficient, the AC compressor is connected to the common AC. The power grid replaces the role of the DC compressor; it can be seen that: the air-conditioning load can be borne by the solar-powered and commercial-powered compressors at different times, and the appropriate sharing ratio can be determined according to the cost requirements, which greatly reduces the initial of the solar-powered air-conditioning system. Cost, which enhances the usability of the system.

 The phase change energy storage device provided in the invention stores both the hot water and the cold water prepared by the heat pump, so that the time between collecting solar energy and the time period using solar energy is adjusted, and also in the cold The high production of hot water and the low usage of the user are used to make the solar energy fully and effectively utilized without any unnecessary waste.

 Compared with the existing ordinary solar water heater, the invention combines the solar energy with the heat pump hot and cold water unit to obtain the hot water while preparing the cold water. The utility model utilizes a solar photovoltaic panel to generate direct current, and then boosts and adjusts the direct current to drive the vapor compression refrigeration unit, and obtains hot water on the condenser side of the refrigerator, and obtains cold water on the evaporator side of the refrigerator. . This kind of equipment allows us to get free hot water and cold water in addition to equipment investment, that is, we can enjoy free domestic hot water and air conditioning effects. After the cold storage or heat storage reaches the limit, the airflow can be used to remove the heat from the finned condenser or to supplement the heat to the finned evaporator.

 Compared with the existing solar photovoltaic vapor compression refrigeration system, the system of the present invention does not require the use of an inverter, and the area of the solar panel can be greatly reduced. The system of the present invention overcomes the limitation of solar energy while making full use of solar energy, and has a very prominent cost advantage. DRAWINGS

 BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic view showing the structure of one embodiment of the present invention. detailed description

 The technical solutions of the present invention are specifically described below with reference to the accompanying drawings and specific embodiments.

The main body of the solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit of the present invention is a heat pump system, in which cold water can be produced on the evaporator side and hot water can be prepared on the condenser side. Cold water and hot water It can be stored separately through the phase change cold storage medium and the phase change heat storage medium to solve the contradiction between the working period of the refrigeration system and the use period of the hot and cold water. At the heart of the refrigeration system are two complementary compressors: a DC compressor and an AC compressor. The DC compressor uses the direct current generated by the solar photovoltaic system, while the AC compressor directly uses the AC mains from the power supply network.

 As shown in FIG. 1, a specific embodiment in accordance with the present invention includes: a DC compressor subsystem A, an optional AC compressor subsystem B, a thermal storage subsystem (, a finned condenser D, a reservoir E, and a drying Filter?, expansion valve or throttle mechanism G, cold storage subsystem H, finned evaporator I, photovoltaic DC power supply subsystem K. The connection relationship in this embodiment is: subsystem Α, Β parallel, parallel The system, the Β and the subsystems (, D, E, F, G, H, I are connected by a pipeline into a loop, in which the refrigerant circulates; the AC power subsystem J is connected to the AC compressor subsystem B by wires Junction box The photovoltaic DC power subsystem K is connected to the junction box of the DC compressor subsystem A by wires.

 The DC compressor subsystem A includes a DC refrigeration compressor 2. A solenoid valve 1 mounted on its exhaust line and a solenoid valve 3 mounted on its suction line.

 The AC compressor subsystem B includes an AC refrigeration compressor 8, a solenoid valve 7 and a tee 6 mounted on its exhaust line, a solenoid valve 9 and a tee 10 mounted on its suction line.

 The heat storage subsystem C includes a well-insulated container (heat storage tank), a safety valve 18, a temperature sensor 19, a phase change heat storage medium 20 in the heat storage tank 17, a hot water outlet valve 21, and a hot water return valve 22. The coil heat exchanger 23, the refrigerant outlet valve 24, the refrigerant inlet valve 25, the coil heat exchanger 26, the tee 27, the bypass solenoid valve 28, and the tee 29. The temperature sensor 19 is mounted on the upper portion of the heat storage tank 17.

 The bypass solenoid valve 28 is mounted on the inlet and outlet lines of the heat storage subsystem, and the bypass solenoid valve 28 is normally closed.

 The finned condenser D includes a fan 33, a finned tube heat exchanger 34, a tee 30, a solenoid valve 31, and a tee 32.

 The cold storage subsystem H includes a well-insulated container (storage tank) 38, a phase change cold storage medium 39 in the cold storage tank 38, a refrigerant outlet valve 40, a refrigerant inlet valve 41, a temperature sensor 42, a coil heat exchanger 43, and cold water. The return valve 44, the cold water outlet valve 45, the coil heat exchanger 46, the relief valve 47, the tee 35, the bypass solenoid valve 36, and the tee 37. The temperature sensor 42 is installed at the lower portion of the cold storage tank 38.

 The bypass solenoid valve 36 is mounted on the inlet and outlet lines of the cold storage subsystem, and the bypass solenoid valve 36 is normally closed.

 The finned evaporator I includes a fan 52, a finned tube heat exchanger 51, a tee 48, a solenoid valve 49, and a tee 50.

The AC power subsystem J includes an AC junction box 55, and a wire 54 connected to the AC compressor 8. The photovoltaic DC power subsystem K includes a solar cell assembly 60, a junction box 59, a battery 58, a power and voltage regulator 57, and a wire 56 connected to the DC refrigeration compressor 2. Guide between various components The wires are connected as shown in Figure 1. The photovoltaic DC power supply subsystem K is used to receive sunlight and generate a DC power supply for the DC refrigeration compressor 2 to operate.

 In the initial state balanced with the room temperature, the phase change heat storage medium 20 in the heat storage tank 17 is in a solid state, and the phase change cold storage medium 39 in the cold storage tank 38 is in a liquid state.

 The thermal characteristic of the phase change heat storage medium 20 is: it is in a solid state at an initial temperature, and when it is heated and the temperature rises to its melting point, it begins to partially melt and maintain a solid-liquid mixed state, in which the temperature is substantially maintained. It does not change until it is completely converted into a liquid. If heating is continued at this time, its temperature will continue to rise. The phase change heat storage medium 20 may be a substance that satisfies this property, such as paraffin, water, and salt.

 The thermal characteristic of the phase change cold storage medium 39 is: it is in a liquid state at an initial temperature, and when it is cooled and exothermic, the temperature is lowered to its melting point, and it begins to partially condense and maintain a solid-liquid mixed state, in which the temperature is basically Leave it unchanged until it is completely converted to a solid. If you continue to cool it at this time, its temperature will continue to decrease. The phase change cold storage medium 39 may be glycerin, water and salt, paraffin or the like.

According to the above embodiment, the heat pump unit of the present invention is powered by the solar photovoltaic DC power supply subsystem K when exposed to sunlight. The solar panel is connected by a number of solar cell modules 60 in a certain manner in parallel and in series to achieve a certain voltage and current requirements. The photovoltaic power source is connected to the junction box 59, and is regulated and regulated by the power and voltage regulator 57 to supply the DC compressor 2 for work. When the DC compressor 2 is not performing work, excess electric energy can be stored in the battery 58.

The DC compressor 2 is operated by a DC power source, and the refrigerant in the compression line circulates in the system. The direction of the refrigerant cycle is: The refrigerant in the system passes through A→C D E F→G H → I→A. At this time, the solenoid valves 1, 3 are in an open state under the control of the system controller, and the solenoid valves 7, 9 are in a closed state under the control of the system controller, the wire 56 is in a connected state, and the wire 54 is in an open state. In this mode, the AC compressor 8 and the DC compressor 2 do not operate at the same time.

 The refrigerant gas is changed into a high-temperature and high-pressure gas by the DC compressor 2, and the heat storage medium 20 is first heated in the coil heat exchanger 23, and the temperature of the heat storage medium 20 rises, and a solid phase to a liquid phase phase transition occurs. The refrigerant gas is partially cooled. After the heat storage medium 20 is heated, it can be used as a heat source to transfer heat to the coil heat exchanger 26 to supply hot water to the outside.

 The partially cooled refrigerant gas then enters the finned tube heat exchanger 34 to continue cooling, and the condensation heat is carried away by the air sent from the condenser fan 33 and is released into the atmosphere. At the outlet of the fin condenser D, the refrigerant gas has all been converted into a liquid.

Then, the refrigerant liquid is first passed through the accumulator E, the drying filter F, and then reaches the throttle mechanism G. The change is to ensure that the pressure of the system does not fluctuate; ^大': The function of the drying filter F is to filter out the impurities in the circulating refrigerant to ensure the cleaning of the system and to absorb the moisture in the circulating refrigerant, so that it does not cause The throttling mechanism is blocked by water. The expansion valve or the throttle mechanism G may be any one of a capillary tube, a thermal expansion valve, an electronic expansion valve, or an orifice restrictor.

 After the refrigerant liquid is throttled by the throttle mechanism G, the pressure is lowered, and some of the refrigerant becomes a flash gas, and the temperature is also lowered to become a gas-liquid mixture. The gas-liquid mixture of the refrigerant sequentially enters the coil radiator 46 in the cold storage tank 38 and the fin-and-tube heat exchanger 51 in the fin-type evaporator I and absorbs heat, at the outlet of the fin-type evaporator I, The refrigerant is all turned into a gas, and then enters the DC compressor 2 to start the next cycle.

 The cold storage medium 39 in the cold storage tank 38 is cooled, and a phase change from the liquid phase to the solid phase occurs. After the cold storage medium 39 is cooled, it can be used as a cold source to transfer cooling to the coil heat exchanger 43, and supply cold water to the outside.

Among the two compressors, the AC compressor 8 is normally used as a backup, and when the DC compressor 2 cannot operate due to insufficient DC power supplied from the solar system K, the AC compressor 8 operates in place of the DC compressor 2. At this time, the power of the AC compressor 8 is taken from the AC junction box 55, and the power of the AC junction box 55 is from ordinary utility power. When the AC compressor 8 is in operation, the flow direction of the refrigerant is: The refrigerant in the system sequentially passes B → C D E F G H I → B. At this time, the solenoid valves 7, 9 are in an open state under the control of the system controller, the solenoid valves 1, 3 are in a closed state under the control of the system controller, the wire 54 is in a connected state, and the wire 56 is in an open state.

 Both the regenerative subsystem C and the finned tube condenser D are used as condensers of the refrigeration system to output heat to the outside, which is responsible for the thermal load of the refrigeration system. Therefore, the two subsystems can work simultaneously or at different times. When the solenoid valve 31 is in the open state under the control of the controller, the refrigerant is bypassed, directly from the tee 30 to the tee 32, without passing through the coil of the fin-and-tube heat exchanger 34 (due to its piping) Longer, more resistant, if the resistance in the two passages is not much different, consider that a solenoid valve is also provided at the inlet of the fin-and-tube heat exchanger 34 to completely cut the passage. The condenser D does not work and the fan 33 does not need to be opened.

 The timing at which the fin condenser D starts to operate can be determined by the temperature condition of the heat storage medium 20. For example, according to a preferred mode of operation, the solid-liquid phase transition temperature of the phase change heat storage medium is Th, and the sensing temperature of the temperature sensor 19 is T1, then:

 • When T Th- Δ ΤΙ, the solenoid valve 31 is opened, the fan 33 is turned off, the fin condenser D is not operated, and the thermal load of the system is all used to heat the heat storage medium 20. Δ Τ1 is a certain degree of subcooling, which can be determined by the user based on experience and preference, but not less than or equal to zero.

 • When Tl > Th+ A T2, when the heat storage medium has completely melted, the solenoid valve 31 is closed and the fan 33 is turned on. At this time, the refrigerant can dissipate heat to the ambient air through the fin-and-tube heat exchanger 34. △ Τ2 is a certain degree of superheat, which can be determined by the user based on experience and preference, but cannot be less than 0.

• When Th Δ ΤΙ < TKTh + A T2, the operating states of the solenoid valve 31 and the fan 33 are kept unchanged. Thus, by controlling the operating state of the fin condenser D, it is possible to control the temperature of the heat storage medium 20 to always be within a certain temperature range, that is, the high pressure of the refrigeration system is not too high, and is always within a certain range. . When the temperature sensor 19 detects that the temperature of the heat storage medium 20 is above a certain upper limit value, or the user does not need to use hot water, the solenoid valve 28 can be opened, at which time the refrigerant gas is bypassed, and the refrigerant is condensed. The heat is completely borne by the finned tube heat exchanger D.

 Similarly, both the cold storage subsystem H and the finned evaporator I act as evaporators of the refrigeration system to absorb heat from the outside and take on the cooling load of the refrigeration system, so that the two subsystems can work simultaneously or at different times. When the solenoid valve 49 is in the open state under the control of the controller, the refrigerant is bypassed, directly from 50 to 48, without passing through the coil of the fin-and-tube heat exchanger 51 (also considered in the finned tube type) A solenoid valve is provided at the inlet of the heat exchanger 51 to completely cut off the passage. At this time, the fin evaporator I does not operate, and the fan 52 does not need to be opened.

 The timing at which the finned tube evaporator I starts to operate can be determined by the temperature condition of the cold storage medium 39. For example, according to a preferred mode of operation, the liquid-solid phase transition temperature of the phase change cold storage medium is Tc, and the temperature sensed by the temperature sensor 42 is T2, then:

 • When T2 > Tc + Δ Τ3, the solenoid valve 49 is opened, the fan 52 is turned off, the fin evaporator I is not operated, and the cooling load of the system is all used to cool the cold storage medium 39. Δ Τ3 is a certain degree of superheat, which can be determined by the user based on experience and preference, but cannot be less than or equal to zero.

 * When T2 Tc-A T4, when the cold storage medium has completely solidified, the solenoid valve 49 is closed, and the fan 52 is turned on. At this time, the refrigerant can absorb heat from the ambient air through the fin-and-tube heat exchanger 51. Δ Τ 4 is a certain degree of subcooling, which can be determined by the user based on experience and preference, but cannot be less than or equal to zero.

 • When Tc-△ T4 < T2 < Tc + △ T3, keep the operating state of solenoid valve 49 and fan 52 unchanged.

 Thus, by controlling the operating state of the fin evaporator I, it is possible to control the temperature of the cold storage medium 39 to always be within a certain temperature range, that is, to ensure that the low pressure of the refrigeration system is not too low, and is always within a certain range. When the temperature sensor 42 detects that the temperature of the cold storage medium 48 is below a certain lower limit value, or the user does not need to use cold water, the bypass solenoid valve 36 can be opened, at which time the refrigerant is bypassed, and the evaporation of the refrigerant is completely absorbed. It is carried by the fin-and-tube heat exchanger I.

 According to a preferred embodiment of the invention, a high pressure sensor 4 is provided on the high pressure line of the system, and a low pressure sensor 5 is provided on the low pressure line of the system. When it is detected that the high pressure is too high or the low pressure is too low, all compressors and fans are stopped to ensure the safety of the system.

According to a preferred embodiment of the invention, a safety valve 18 and a safety valve 47 are also provided on the heat storage tank 17 and the cold storage tank 38, respectively. When the heat storage or cold storage medium in the container is too high due to too high temperature and volume expansion, the safety valve will automatically open, and a part of the medium will be discharged, so that the pressure inside the container is lowered. This further increases the security of the system.

 In addition, those skilled in the art can understand that although the parallel DC compressor subsystem A and the AC compressor subsystem B are disposed in the above embodiment, the system still removes the AC compressor subsystem B and the AC power subsystem J. It can form a photovoltaic DC cold storage and regenerative cold water (heat pump) unit that does not depend on any auxiliary power supply. It can work independently and can be used in mobile applications.

 The above is only a specific application example of the present invention, and does not impose any limitation on the scope of protection of the present invention. Any technical solution formed by equivalent transformation or equivalent replacement is within the scope of the present invention.

Claims

Claim
1. A solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit, comprising: a compressor module comprising a DC compressor subsystem (A);
 a photovoltaic DC power supply subsystem (K) for supplying power to the DC compressor subsystem (A); a finned condenser (D);
 Throttle mechanism (G);
 Finned evaporator ( I );
 a heat storage subsystem (C) coupled between the compressor module and the fin condenser (D), comprising a heat storage medium (20) for absorbing heat from the refrigerant;
 a cold storage subsystem (H) coupled between the throttle mechanism (G) and the finned evaporator (I), including a cold storage medium (39) for being cooled by the refrigerant,
 The compressor module, the heat storage subsystem (C), the finned condenser (D), the throttle mechanism (G), the cold storage subsystem (H), and the finned evaporator (I) are connected by a pipeline into a a circuit for circulating a refrigerant in the circuit.
 2. The solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit according to claim 1, wherein the compressor module further comprises an alternating current compressor subsystem connected in parallel with the direct current compressor subsystem (A). (B).
 3. The solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit according to claim 2, wherein four fifth electromagnetic valves (1, 3, 7, 9 are disposed in the compressor module). ) for controlling the state of the refrigerant circuit of the DC compressor (2) in the DC compressor subsystem (A) and the AC compressor (8) in the AC compressor subsystem (B).
 4. The solar photovoltaic-mains hybrid drive cold storage and heat storage heat pump unit according to claim 1, wherein
 The thermal storage subsystem (C) includes:
 a heat-insulating heat storage container (17) having the heat storage medium (20) therein;
 a first coil heat exchanger (23) disposed inside the heat storage container (17), connected to the refrigerant circulation loop, for refrigerating the refrigerant and the heat storage medium (20) Performing heat exchange; a second coil heat exchanger (26) disposed inside the heat storage container (17) for allowing water flowing therethrough and a heat storage medium inside the heat storage container (17) ( 20) Perform heat exchange,
 The cold storage subsystem (H) includes:
a well-insulated cold storage container (38) containing the cold storage medium (39) therein; a third coil heat exchanger (46) disposed inside the cold storage container (38) connected to the refrigerant a circulation circuit for causing heat exchange between the refrigerant therein and the cold storage medium (39); A fourth coil heat exchanger (43) disposed inside the cold storage container (38) is configured to exchange heat between the water flowing therethrough and the cold storage medium (39) inside the cold storage container (38).
 5. The solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit according to claim 1, further comprising: disposed in said refrigerant circulation circuit:
 a first solenoid valve (31) for bypassing the refrigerant without passing through the fin condenser (D); and a second solenoid valve (49) for bypassing the refrigerant without Pass the fin evaporator (1).
6. The solar photovoltaic-mains hybrid drive cold storage and heat storage heat pump unit according to claim 5, wherein
 A first temperature sensor (19) is disposed in the thermal storage subsystem (C) for sensing a temperature of the thermal storage medium (20) to determine opening and closing of the first electromagnetic valve (31) ;
 A second temperature sensor (42) is provided in the cold storage subsystem (H) for sensing the temperature of the cold storage medium (39) to determine opening and closing of the second electromagnetic valve (49).
 7. The solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit according to claim 1, wherein the heat storage medium (20) is one of paraffin, water and salt, and sodium sulfate decahydrate. The cold storage medium (39) is one of glycerin, water, water and salt, and paraffin.
 8. The solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit according to claim 1, further comprising: disposed in said refrigerant circulation circuit:
 a third solenoid valve (28) for bypassing the refrigerant without passing through the thermal storage subsystem (C);
 A fourth solenoid valve (36) is provided for bypassing the refrigerant without passing through the cold storage subsystem (H).
9. The solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit according to claim 1, wherein the photovoltaic direct current power supply subsystem (K) comprises a solar battery module (60) and a junction box (59) , battery ( 58 ), power and voltage regulator ( 57 ) 0
 10. The solar photovoltaic-mains hybrid drive cold storage heat storage heat pump unit according to claim 1, wherein a high pressure sensor (4) is disposed on the high pressure pipeline of the heat pump unit, and a low pressure is disposed on the low pressure pipeline. The sensor (5) is provided with a safety valve (18, 47) in the heat storage subsystem (C) and the cold storage subsystem (H), respectively.
PCT/CN2010/070200 2009-01-15 2010-01-15 Hybrid-driven cold/heat storage type heat pump unit utilizing solar photovoltaic power and commercial power WO2010081421A1 (en)

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AU2010205984A AU2010205984A1 (en) 2009-01-15 2010-01-15 Hybrid-driven cold/heat storage type heat pump unit utilizing solar photovoltaic power and commercial power
EP10731055.9A EP2388540A4 (en) 2009-01-15 2010-01-15 Hybrid-driven cold/heat storage type heat pump unit utilizing solar photovoltaic power and commercial power
US13/142,452 US20110296865A1 (en) 2009-01-15 2010-01-15 Solar photovoltaic -commercial electricity dually driven heat pump system with cold/heat storage

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CN101458005A (en) 2009-06-17
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EP2388540A1 (en) 2011-11-23
EP2388540A4 (en) 2013-07-31

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