WO2019020132A1 - 可以制取不低于100℃沸水的超高温热泵系统及方法 - Google Patents

可以制取不低于100℃沸水的超高温热泵系统及方法 Download PDF

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WO2019020132A1
WO2019020132A1 PCT/CN2018/106456 CN2018106456W WO2019020132A1 WO 2019020132 A1 WO2019020132 A1 WO 2019020132A1 CN 2018106456 W CN2018106456 W CN 2018106456W WO 2019020132 A1 WO2019020132 A1 WO 2019020132A1
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hot water
outlet
inlet
water
condensing
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English (en)
French (fr)
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夏文庆
黄倬然
娄宇航
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Nanjing University of Aeronautics and Astronautics
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Nanjing University of Aeronautics and Astronautics
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Priority to US16/475,003 priority Critical patent/US11293666B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series

Definitions

  • the invention relates to an ultra-high temperature heat pump system and method capable of preparing boiling water of not less than 100 ° C, belonging to the field of new energy utilization, based on the principle of minimum entropy increase of the compressor exhaust heat enthalpy, and utilizing the sensible heat of the exhaust heat enthalpy And latent heat, the method of turning low-grade thermal energy into high-grade thermal energy by heat pump technology.
  • the heat pump water heater is a new type of hot water and heating heat pump product, and is a heating device and a hot water device that can replace the boiler. Using the principle of the heat pump, it only needs to consume a small amount of electric energy, transfer the heat in a low temperature environment to the water heater in a high temperature environment, and heat to obtain high temperature hot water.
  • Heat pump water heaters have been put into production and have been widely used in the market. At present, heat pump water heaters can only produce hot water of about 85 °C. However, the water in the kitchen, the boiling water room and the like all need boiling water. The hot water generated by the ordinary heat pump water heater needs electric heating to further obtain boiling water. Therefore, how to use the heat pump technology to make boiling water, so that the heat pump can be expanded to provide living boiling water by providing sanitary hot water. It has become a breakthrough for further energy conservation and application expansion.
  • the object of the present invention is to solve the disadvantage that the ordinary heat pump water heater cannot directly prepare boiling water, and to provide an ultra-high temperature heat pump system and method capable of preparing boiling water of not less than 100 ° C.
  • An ultra-high temperature heat pump system capable of producing boiling water of not less than 100 ° C, characterized in that: the system comprises a compressor, a first-stage condensing/cooling device, a secondary condensing/cooling device, an expansion mechanism, a primary evaporator, and two Stage evaporator, first water pump, second water pump, hot water tank, boiling water tank, third water pump, valve; wherein the first-stage condensing/cooling device includes the working medium inlet and outlet and the hot water inlet and outlet; the secondary condensing/cooling device includes Quality inlet and outlet, hot water tank circulation inlet and outlet and evaporator heat exchange inlet and outlet; primary evaporator includes working fluid inlet and outlet; secondary evaporator includes working fluid inlet and outlet and hot water inlet and outlet; hot water tank has water inlet, hot water outlet, hot water Inlet and faucet; the boiling water tank has a venting hole, a hot water outlet, a boiling water inlet, and the hot water in the boiling water
  • the outlet of the working fluid is connected to the inlet of the compressor; the evaporator heat exchange outlet of the secondary condensing/cooling device is connected to the secondary evaporator hot water inlet through the valve, and the secondary evaporator hot water outlet passes through the third water pump and the secondary condensation/
  • the evaporator heat exchange inlet is connected;
  • the hot water tank hot water outlet is connected to the second condensing/heater hot water inlet through the first water pump, and the second condensing/heater hot water outlet is connected to the hot water tank hot water inlet;
  • the hot water tank and the boiling water tank are connected by a single-phase flow regulating valve; in addition, the hot water outlet of the boiling water tank is connected to the first-stage condensing/heater hot water inlet through the second water pump, the first-stage condensing/heating water outlet and the boiling water boiling water
  • the entrance is connected.
  • the method for preparing an ultra-high temperature heat pump system capable of producing boiling water of not less than 100 ° C characterized in that:
  • the working cycle of the working fluid is as follows: the working fluid control from the compressor is not lower than 110 ° C, and the working medium enters the first-stage condensing/cooling device, the second-stage condensing/heating device, and then the throttling and cooling through the expansion mechanism.
  • the hot water circulation system is as follows: after the normal temperature water enters the hot water tank, the first water pump is pumped into the secondary condensing/heating device to absorb heat to become about 65 ° C hot water and stored in the hot water tank; the hot water passes through the one-way flow.
  • the regulating pipeline enters the boiling water tank, and is pumped into the first-stage condensing/cooling device through the second water pump to further absorb heat to become 100°C boiling water and stored in the boiling water of the boiling water tank, wherein the water inlet serves as a water inlet passage, and the air outlet serves as a steam drain.
  • the water in the hot water tank flows into the boiling water tank in one direction, and the two can be discharged separately through the tap; in order to make the working fluid not lower than 110 ° C at the outlet of the compressor, it is necessary to increase the temperature of the heat source or increase the inlet of the compressor.
  • the superheat of the working fluid at this time, the pump will pump the water into the secondary condensing/cooling device to absorb the heat, and then pass through the valve to enter the secondary evaporator to release heat so that the working medium further absorbs heat and increases the temperature or evaporates.
  • the system and method of the present invention is based on the principle of minimum entropy increase of the compressor exhaust heat, and for the subcritical cycle, the sensible heat and latent heat of the exhaust heat enthalpy are used to divide the condenser into two.
  • the normal temperature water first passes through the secondary condenser/working medium condensation section, and the countercurrent heat exchange absorbs the latent heat of the working medium of about 70 °C, from normal temperature water to about 65 °C hot water, and then in the first stage condenser/work In the superheated isotherm cooling section, further countercurrent heat transfer absorbs sensible heat and becomes 100 °C boiling water.
  • the invention divides the evaporator into one or two stages.
  • the working medium can enter the secondary evaporator to further absorb heat after the primary evaporator absorbs heat, or in some cases, the ambient heat source. If the evaporation temperature is too low, the heat of the hot water can be directly absorbed.
  • Figure 1 is a schematic diagram of the system of the present invention.
  • FIG. 2 is a pressure diagram of a subcritical and transcritical cycle system of the present invention.
  • Figure 3 is a temperature entropy diagram of the subcritical and transcritical cycle systems of the present invention.
  • Fig. 1 the label name: 1-compressor 2-level condensing/cooling device 3-second condensing/cooling device 4-expansion mechanism 5 primary evaporator 6-secondary evaporator 7-first water pump 8-second Water pump 9-hot water tank 10-open water tank 11-inlet 12-exhaust hole 13-third water pump 14-valve 15-way flow valve
  • Figure 1 is a schematic diagram of an ultra-high temperature heat pump system.
  • the working fluid control from the compressor 1 is generally not lower than 110 ° C, and the working medium sequentially enters the first-stage condensing device 2, the second-stage condensing device 3 is exothermic, and then thaws through the expansion mechanism 4 to cool down and enters the first stage.
  • the evaporator 5 and the secondary evaporator 6 absorb heat, and finally enter the compressor to raise the temperature and increase the pressure, thus completing a thermal cycle project.
  • the hot water After the normal temperature water enters the hot water tank 9, it is pumped into the secondary condensing/cooling device 3 through the water pump 8 to become hot water of about 65 ° C and stored in the hot water tank 9; the hot water enters the boiling water tank 10 through the pipeline and passes through The first water pump 7 is pumped into the first-stage condensing device 2 to further absorb heat to become boiling water of about 100 ° C and stored in the boiling water tank 10, wherein the water inlet 11 serves as a water inlet passage, and the exhaust port 12 serves as a steam discharge port.
  • the pump 13 pumps the water into the secondary condensing device 3 to absorb the heat, and then passes through the valve 14 to enter the secondary evaporator 6 to release heat so that the working medium further absorbs heat and increases the temperature.
  • Figure 2 is a pressure diagram of an ultra high temperature heat pump system.
  • the working fluid reaches the state point 1 at the evaporator outlet, enters the compressor compression to reach the state point 2, enters the primary condenser heat release to reach the state point 2' (sensible heat part), and then goes to the secondary condenser Heat to state point 3 (latent heat part), after throttling to reach state point 4, and enter the primary evaporator to absorb the ambient heat source, according to different working conditions, the secondary condenser can absorb the heat of the secondary condenser, and then return State point 1, thus completing a thermodynamic cycle.
  • the process is the same, except that the condenser becomes a cooler.
  • Figure 3 is a temperature entropy diagram of an ultra high temperature heat pump system.
  • the working fluid reaches the state point 01 at the evaporator outlet, enters the compressor compression to reach the state point 02, enters the primary cooler heat release to reach the state point 02', and then releases the secondary cooler to the state point.
  • 03 after the throttling to reach the state point 04, and enter the first-stage evaporator to absorb the ambient heat source, according to different working conditions, the secondary evaporator can absorb the heat of the secondary cooler, and then return to the state point 01, thus completing a heat The cycle process.
  • the nonlinear temperature of the working fluid is similar to that of the condensing process, and it also needs grading cooling.
  • the hot water is separated from the boiling water, and the flow of hot water and boiling water is flown. Generally not equal, except that there is no phase change heat, it is basically the same as the subcritical cycle.

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  • Engineering & Computer Science (AREA)
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  • Mechanical Engineering (AREA)
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Abstract

一种可以制取不低于100℃沸水的超高温热泵系统及方法，属于热泵技术领域。该系统包括压缩机（1），一、二级蒸发器（5、6），膨胀机构（4），一、二级冷凝/却器（2、3），水泵（7、8、13），水箱（9、10），阀门（14）。上述方案基于压缩机排气热焓利用最小熵增原理/技术，分级利用排气热焓的显热与潜热，出水温度突破100℃，拓展了目前热泵热水器只能制取低于100℃热水的功能，可以替代电热水器，节约能源，提高能源利用率。

Description

可以制取不低于100℃沸水的超高温热泵系统及方法 技术领域
本发明涉及可以制取不低于100℃沸水的超高温热泵系统及方法，属于新能源利用领域，基于压缩机排气热焓利用最小熵增原理/技术，分级利用排气热焓的显热与潜热，通过热泵技术把环境低品位热能变成高品位热能的方法。
背景技术
热泵热水器是一种新型热水和供暖热泵产品，是一种可替代锅炉的供暖设备和热水装置。运用热泵的原理，只需要消耗小部分的电能，将处于低温环境下的热量转移到高温环境下的热水器中，去加热制取高温的热水。热泵热水器已经在投入生产并在市场上获得了广泛应用，目前热泵热水器最高只可制取85℃左右的热水。但是厨房、开水房等用水都需要沸水，普通热泵热水器产生的热水还需要用电加热才能进一步得到沸水，所以如何利用热泵技术制取沸水，使得热泵由提供卫生热水，扩展为提供生活沸水，成为其进一步节约电能、扩大应用的突破口。
发明内容
本发明的目的在于解决普通热泵热水器不能直接制取沸水的缺点，提供一种可以制取不低于100℃沸水的超高温热泵系统及方法。
一种可以制取不低于100℃沸水的超高温热泵系统，其特征在于：该系统包括压缩机、一级冷凝/却器、二级冷凝/却器、膨胀机构、一级蒸发器、二级蒸发器、第一水泵、第二水泵、热水箱、开水箱、第三水泵、阀门；其中一级冷凝/却器包括工质出入口和热水的出入口；二级冷凝/却器包括工质出入口、热水箱循环出入口和蒸发器换热出入口；一级蒸发器包括工质出入口；二级蒸发器包括工质出入口和热水出入口；热水箱具有进水口、热水出口、热水入口和水龙头；开水箱具有排气孔、热水出口、开水进口，且开水箱中的热水和开水分开；压缩机出口与一级冷凝/却器工质入口相连，一级冷凝/却器工质出口与二级冷凝/却器工质入口相连，二级冷凝/却器工质出口经过膨胀机构与一级蒸发器入口相连，一级蒸发器出口与二级蒸发器工质入口相连，二级蒸发器工质出口与压缩机入口相连；二级冷凝/却器的蒸发器换热出口经过阀门与二级蒸发器热水入口相连，二级蒸发器热水出口经过第三水泵与二级冷凝/却器的蒸发器换热入口相连；热 水箱热水出口经过第一水泵与二级冷凝/却器热水入口相连，二级冷凝/却器热水出口与热水箱热水入口相连；热水箱和开水箱通过单相流量调节阀相连；另外，开水箱热水出口经过第二水泵与一级冷凝/却器热水入口相连，一级冷凝/却器热水出口与开水箱开水入口相连。
所述的可以制取不低于100℃沸水的超高温热泵系统的方法，其特征在于：
其中工质热力循环过程如下：从压缩机出来的工质控制不低于110℃，工质依次进入一级冷凝/却器、二级冷凝/却器放热，然后经过膨胀机构节流降温并进入一级蒸发器和二级蒸发器吸热，最后进入压缩机升温升压，如此完成一个热力循环工程；其中控制开水箱和一级冷凝/却器之间的循环热水流量小于热水箱和二级冷凝/却器之间的循环热水流量；使循环水与工质
Figure PCTCN2018106456-appb-000001
之间达到最优匹配，其匹配关系，根据公式：G wC pΔT w＝M rΔh r决定，循环热力利用率最大；其中左侧为水的流量G w、比热容C p、水温升ΔT w，右侧为制冷工质的流量M r及焓降Δh r；
其中热水循环系统如下：常温水进入热水箱后,通过第一水泵泵入二级冷凝/却器处吸热变成65℃左右热水并储存于热水箱；热水通过单向流量调节管路进入开水箱，通过第二水泵泵入一级冷凝/却器处进一步吸热变成100℃沸水并储存于开水箱开水部分，其中进水口作为进水通道，排气口作为蒸汽泄放口；热水箱中的水单向流入开水箱，也二者可单独通过龙头放水；为了使得工质在压缩机出口处不低于110℃，需提高热源温度或增大压缩机入口处工质的过热度；此时泵将水泵入二级冷凝/却器吸收热量，再经过阀门，进入二级蒸发器释放热量使得工质进一步吸热增温，或提高蒸发温度。
对于二氧化碳等跨临界循环热泵系统，基于非线性温焓
Figure PCTCN2018106456-appb-000002
捕捉技术原理，其放热过程虽没有相变冷凝，但基于工质的非线性温焓与冷凝过程的工质相似，也需要分级冷却，热水与开水制取分开，热水与开水的流量一般不相等，除了没有相变换热外，与亚临界循环基本一样。
与现有技术相比，本发明的系统和方法基于压缩机排气热焓利用最小熵增原理/技术，对于亚临界循环，分级利用排气热焓的显热与潜热，将冷凝器分为一、二两级，常温水先通过二级冷凝器/工质冷凝段，逆流换热吸收70℃左右工质的潜热，由常温水变成65℃左右热水，再在一级冷凝器/工质过热等压降温 段，进一步逆流换热吸收显热变成100℃沸水。本发明将蒸发器分为一、二两级，为了使工质过热度增大，工质在一级蒸发器吸热后可以进入二级蒸发器进一步吸热，或者某些情况下，环境热源使蒸发温度过低，可以直接吸收热水的热量。
附图说明
图1是本发明的系统原理图。
图2是本发明亚临界和跨临界循环系统压焓图。
图3是本发明亚临界和跨临界循环系统温熵图。
图1中标号名称：1-压缩机 2-一级冷凝/却器 3-二级冷凝/却器 4-膨胀机构 5一级蒸发器 6-二级蒸发器 7-第一水泵 8-第二水泵 9-热水箱 10-开水箱 11-进水口 12-排气孔 13-第三水泵 14-阀门 15-单向流量阀
图2中标号名称：1-亚临界压缩机入口 2-亚临界压缩机出口 2’-高压干饱和状态点 3-亚临界冷凝器出口 4-亚临界蒸发器入口 1’-低压干饱和状态点 01-跨临界压缩机入口 02-跨临界压缩机出口 02’-分级冷却状态点 03-跨临界冷却器出口 04-跨临界蒸发器入口
图3中标号名称：1-亚临界压缩机入口 2-亚临界压缩机出口 2’-冷凝器分级状态点 3-冷凝器出口 4-亚临界蒸发器入口 01-跨临界压缩机入口 02-跨临界压缩机出口 02’-分级冷却状态点 03-跨临界冷却器出口 04-跨临界蒸发器入口。
具体实施方式
下面结合具体实施方式和附图对本发明的内容做进一步说明。
图1是超高温热泵系统的原理图。从压缩机1出来的工质控制一般不低于110℃，工质依次进入一级冷凝/却器2、二级冷凝/却器3放热，然后经过膨胀机构4节流降温并进入一级蒸发器5和二级蒸发器6吸热，最后进入压缩机升温升压，如此完成一个热力循环工程。
常温水进入热水箱9后,通过水泵8泵入二级冷凝/却器3处吸热变成65℃左右热水并储存于热水箱9；热水通过管路进入开水箱10，通过第一水泵7泵入一级冷凝/却器2处进一步吸热变成100℃左右沸水并储存于开水箱10，其中进水口11作为进水通道，排气口12作为蒸汽泄放口。进入一二级冷凝/却器中的热水流量不相等，开水箱循环热水流量小于热水箱循环热水流量，目的是让循环水与工质
Figure PCTCN2018106456-appb-000003
之间达到最优匹配，其匹配关系，根据公式：G wC pΔT w＝M rΔh r决 定，其中左侧为水的流量G w、比热容C p、水温升ΔT w，右侧为制冷工质的流量M r及焓降Δh r，由于过热显热的焓降Δh r小于潜热的冷凝焓降Δh r，制冷工质的流量M r是不变的，因此要达到大水温升ΔT w，必须降低水的流量G w，才能实现出水温度超过100℃，实现循环热力利用率最大。
为了使得工质在压缩机出口处不低于110℃，需提高热源温度或增大压缩机入口处工质的过热度。此时泵13将水泵入二级冷凝/却器3吸收热量，再经过阀门14，进入二级蒸发器6释放热量使得工质进一步吸热增温，或提高蒸发温度。
图2是超高温热泵系统的压焓图。对于亚临界循环，工质在蒸发器出口达到状态点1，进入压缩机压缩达到状态点2，进入一级冷凝器放热达到状态点2’(显热部分)，再到二级冷凝器放热至状态点3(潜热部分)，经过节流降压到达状态点4，并进入一级蒸发器吸收环境热源，依不同工况可在二级蒸发器吸收二级冷凝器热量，再回到状态点1，如此完成一个热力循环过程。对于跨临界循环，过程是一样的，只是冷凝器变为了冷却器。
图3是超高温热泵系统的温熵图。对于跨临界循环，工质在蒸发器出口达到状态点01，,进入压缩机压缩达到状态点02，进入一级冷却器放热达到状态点02’，再到二级冷却器放热至状态点03，经过节流降压到达状态点04，并进入一级蒸发器吸收环境热源，依不同工况可在二级蒸发器吸收二级冷却器热量，再回到状态点01，如此完成一个热力循环过程。对于二氧化碳等跨临界循环热泵系统，基于非线性温焓
Figure PCTCN2018106456-appb-000004
捕捉技术原理，虽然其放热过程虽没有相变冷凝，但工质的非线性温焓与冷凝过程的工质相似，也需要分级冷却，热水与开水制取分开，热水与开水的流量一般不相等，除了没有相变换热外，与亚临界循环基本一样。

Claims (2)

  1. 一种可以制取不低于100℃沸水的超高温热泵系统，其特征在于：
    该系统包括压缩机(1)、一级冷凝/却器(2)、二级冷凝/却器(3)、膨胀机构(4)、一级蒸发器(5)、二级蒸发器(6)、第一水泵(7)、第二水泵(8)、热水箱(9)、开水箱(10)、第三水泵(13)、阀门(14)；
    其中一级冷凝/却器(2)包括工质出入口和热水的出入口；二级冷凝/却器(3)包括工质出入口、热水箱循环出入口和蒸发器换热出入口；一级蒸发器(5)包括工质出入口；二级蒸发器(6)包括工质出入口和热水出入口；热水箱(9)具有进水口(11)、热水出口、热水入口和水龙头；开水箱(10)具有排气孔(12)、热水出口、开水进口，且开水箱中的热水和开水分开；
    压缩机(1)出口与一级冷凝/却器(2)工质入口相连，一级冷凝/却器(2)工质出口与二级冷凝/却器(3)工质入口相连，二级冷凝/却器(3)工质出口经过膨胀机构(4)与一级蒸发器(5)入口相连，一级蒸发器(5)出口与二级蒸发器(6)工质入口相连，二级蒸发器(6)工质出口与压缩机(1)入口相连；
    二级冷凝/却器(3)的蒸发器换热出口经过阀门(14)与二级蒸发器(6)热水入口相连，二级蒸发器(6)热水出口经过第三水泵(13)与二级冷凝/却器(3)的蒸发器换热入口相连；
    热水箱(9)热水出口经过第一水泵(7)与二级冷凝/却器(3)热水入口相连，二级冷凝/却器(3)热水出口与热水箱(9)热水入口相连；
    热水箱(9)和开水箱(10)通过单相流量调节阀(15)相连；另外，开水箱热水出口经过第二水泵(8)与一级冷凝/却器(2)热水入口相连，一级冷凝/却器(2)热水出口与开水箱开水入口相连。
  2. 根据权利要求1所述的可以制取不低于100℃沸水的超高温热泵系统的方法，其特征在于：
    其中工质热力循环过程如下：
    从压缩机(1)出来的工质控制不低于110℃，工质依次进入一级冷凝/却器(2)、二级冷凝/却器(3)放热，然后经过膨胀机构(4)节流降温并进入一级蒸发器(5)和二级蒸发器(6)吸热，最后进入压缩机升温升压，如此完成一个热力循环工程；其中控制开水箱(10)和一级冷凝/却器(2)之间的循环热水流量小于热水箱(9)和二级冷凝/却器(3)之间的循环热水流量；使循环水与工质
    Figure PCTCN2018106456-appb-100001
    之 间达到最优匹配，其匹配关系，根据公式：G wC pΔT w＝M rΔh r决定，循环热力利用率最大；其中左侧为水的流量G w、比热容C p、水温升ΔT w，右侧为制冷工质的流量M r及焓降Δh r；
    其中热水循环系统如下：
    常温水进入热水箱(9)后,通过第一水泵(7)泵入二级冷凝/却器(3)处吸热变成65℃左右热水并储存于热水箱(9)；热水通过单向流量调节管路进入开水箱(10)，通过第二水泵(8)泵入一级冷凝/却器(2)处进一步吸热变成100℃沸水并储存于开水箱(10)开水部分，其中进水口(11)作为进水通道，排气口(12)作为蒸汽泄放口；热水箱中的水单向流入开水箱，也二者可单独通过龙头放水；为了使得工质在压缩机出口处不低于110℃，需提高热源温度或增大压缩机入口处工质的过热度；此时泵(13)将水泵入二级冷凝/却器(3)吸收热量，再经过阀门(14)，进入二级蒸发器(6)释放热量使得工质进一步吸热增温，或提高蒸发温度。
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