WO2011113295A1 - 多功能空调、热水系统 - Google Patents

多功能空调、热水系统 Download PDF

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Publication number
WO2011113295A1
WO2011113295A1 PCT/CN2011/000118 CN2011000118W WO2011113295A1 WO 2011113295 A1 WO2011113295 A1 WO 2011113295A1 CN 2011000118 W CN2011000118 W CN 2011000118W WO 2011113295 A1 WO2011113295 A1 WO 2011113295A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
hot water
way valve
outlet
heat exchange
Prior art date
Application number
PCT/CN2011/000118
Other languages
English (en)
French (fr)
Inventor
郭立华
Original Assignee
快意节能设备（深圳）有限公司
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
Application filed by 快意节能设备（深圳）有限公司 filed Critical 快意节能设备（深圳）有限公司
Priority to EP11755612A priority Critical patent/EP2549193A1/en
Priority to AU2011229069A priority patent/AU2011229069A1/en
Priority to SG2012068045A priority patent/SG184060A1/en
Publication of WO2011113295A1 publication Critical patent/WO2011113295A1/zh

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Classifications

    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/18—Hot-water central heating systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D5/00—Hot-air central heating systems; Exhaust gas central heating systems
    • F24D5/12—Hot-air central heating systems; Exhaust gas central heating systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0096—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater combined with domestic apparatus
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02731—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one three-way valve
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/12—Hot water central heating systems using heat pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/13—Hot air central heating systems using heat pumps

Definitions

  • the present invention relates to a multifunctional air conditioning and hot water system capable of separately or simultaneously cooling, heating, and or making hot water.
  • the object of the present invention is to overcome the deficiencies of the prior art and provide a multi-functional air-conditioning and hot water system with reasonable structure, convenient use, high service life and energy saving and emission reduction requirements.
  • a multifunctional air conditioner and hot water system including a compressor, a dedicated three-way W, a four-way valve, a hydrothermal heat exchanger, an outdoor heat exchanger, an indoor heat exchanger, and a multi-function throttle channel conversion
  • the device and the pressure relief device wherein: the water inlet and the water outlet of the hydrothermal heat exchanger are respectively connected with the external supply cold water end and the receiving hot water end; the inlet of the special three-way valve is connected with the air outlet of the compressor, and one outlet and water
  • the heat exchanger has a heat exchange pipe inlet connection, the other outlet is connected to the inlet of the four-way valve, and another channel is connected to the inlet of the pressure relief device; and the hot water outlet end of the water heat exchanger is provided with a dedicated The three-way valve interlocking water outlet controller; the three outlets of the four-way valve are respectively connected with the heat exchange pipe of the outdoor heat exchanger, the heat exchange pipe of the indoor heat exchanger and the return port of the compressor; the exchange of the water heat
  • the multi-function throttle channel conversion device includes five unidirectional W and throttling devices, wherein four one-way valve bridges are connected a bridge channel, wherein the two diagonal points of the bridge channel are respectively connected to the other end of the heat exchanger pipe of the outdoor heat exchanger and the other end of the heat exchanger pipe of the indoor heat exchanger, and the connection point between the other two points The flow device; the remaining one-way valve is connected between the heat exchange pipe outlet of the hot water heat exchanger and the two-way check valve of the bridge channel.
  • the multi-functional throttle channel conversion device further includes a liquid reservoir and a filter, and the liquid storage device and the filter are disposed in the section.
  • the inlet of the flow device is between the two opposite check valves of the bridge channel.
  • the multi-function throttle channel conversion device further includes an ice water solenoid valve; the ice water solenoid valve is disposed in the bridge channel in the pointing chamber thereof The one-way wide of the heat exchanger On the channel.
  • the water inlet of the hydrothermal heat exchanger is provided with a condensing pressure adjustment for controlling the opening degree of the wide door by the high pressure gas at the outlet of the compressor. valve. - . -
  • the beneficial effects of the present invention are: 1), because it is a special special three-way valve, a four-way valve and a multi-function throttle conversion device for circulating the heat pump system, throughout the cycle
  • heat exchange is performed with one, two or three of the hydrothermal heat exchanger, the outdoor heat exchanger and the indoor heat exchanger, thereby achieving separate refrigeration, separate heating, separately preparing hot water, and while cooling
  • preparing hot water one of the six processes of preferentially preparing hot water, making ice water and hot water in the heating mode, it can be seen that the present invention is simple in the case where the system connection portion and the control portion are relatively simple.
  • the utility model can realize six functions, so the invention can realize multi-purpose use of one machine, meets many needs of people, and has a relatively reasonable structure and can meet the requirements of energy saving and emission reduction; 2) the system can be guaranteed due to the provision of a pressure relief device During the conversion, the pressure is balanced and the conversion is rapid. The residual high pressure generated by the system can be quickly vented to the low-pressure end through the pressure relief device, achieving the purpose of rapid and flexible conversion of the system, and the whole system works stably and balancedly.
  • the multi-function throttle channel conversion device is a mechanical structure, two pipes are connected at each port, but the two pipes are mechanical ( Or high voltage), one is mechanically conductive, so that high temperature and high pressure liquid coming in from one of the ports can only flow along one of the pipes to a port of the other two ports and be converted in the throttling device.
  • this mechanical function conversion device avoids the complicated circuit connection and program control when a circuit is used to control the conduction of one channel and the other channel is stopped, and the maintenance of circuit control is difficult, so
  • the structure of the invention is reasonable and convenient to use.
  • FIG. 2 is a flow diagram of a flow in a cold air (or ice water) mode according to an embodiment of the present invention
  • FIG. 3 is a workflow diagram of a heating mode in an embodiment of the present invention.
  • FIG. 4 is a flow diagram of a working flow in a hot water mode according to an embodiment of the present invention.
  • FIG. 5 is a flow diagram of the operation of the embodiment of the present invention in the simultaneous hot water production mode.
  • the present invention is a multifunctional air conditioning, hot water system, as shown in Figure 1, which includes a compressor 1, a dedicated three-way wide 2, a four-way valve 3, a hydrothermal heat exchanger 4, outdoor heat The exchanger 5, the indoor heat exchanger 6, the multi-function throttle passage conversion device 7 and the pressure relief device 8, wherein: the water inlet and the water outlet of the hydrothermal heat exchanger 4 are respectively connected with the external supply cold water end and the receiving hot water end
  • the inlet of the special three-way valve 2 is connected to the air outlet 11 of the compressor 1, one outlet is connected to the inlet of the heat exchange conduit 41 of the hydrothermal heat exchanger 4, the other outlet is connected to the inlet of the four-way valve 3, and another passage is provided.
  • the outlet of the pressure relief device 8 leads to the air return port of the compressor 1, so that the pressure balance and the rapid conversion during the system switching can be ensured, and the residual high pressure generated when the system is switched can be quickly discharged to the low pressure end through the pressure relief device. Rapid and flexible conversion of the system
  • the purpose is to make the whole system work stably and balanced, with adequate safety protection measures and improve the life of the system.
  • the function of the multi-function throttle passage conversion device 7 is to make the high-temperature high-pressure refrigerant liquid become a low-temperature low-pressure refrigerant liquid after flowing through the multi-function throttle passage conversion device, and then sent to the corresponding heat exchanger for evaporation.
  • the multi-function throttle channel conversion device is a mechanical structure, two pipes are connected at each port, but one of the two pipes is mechanical (or high-voltage) and one is mechanically turned on, so that The high-temperature pressurized liquid coming in from one of the ports can only flow along one of the pipes to a port of the other two ports, and is converted into a low-temperature and low-pressure liquid in the throttling device.
  • This mechanical function conversion device avoids It is common to use a circuit to control the complex circuit connection and program control when one channel is turned on and the other channel is turned off, and the maintenance of the circuit control is difficult, so the structure of the present invention is reasonable and convenient to use.
  • the present invention performs the circulation of the heat pump system through a special special three-way valve 2, a four-way wide 3 and a multi-function throttle conversion device 7.
  • the present invention is relatively simple in the system connection part and the control part thereof. In the case of the case, six functions can be realized, so the invention can realize multi-purpose use of one machine, meets many needs of people, and has a relatively reasonable structure and can meet the requirements of energy saving and emission reduction.
  • a condensing pressure regulating valve 60 for controlling the valve opening degree of the high pressure gas at the gas outlet of the compressor 1 is provided at the water inlet of the hydrothermal heat exchanger 4 to maintain the outlet water temperature. Constant, adjust the water inlet according to the change of high pressure (condensation pressure) during operation, and control the flow rate of cold water to reach the stable water temperature.
  • the special three-way valve 2 of the present invention is a specially designed three-way valve, and in addition to the three passages, there is a pressure relief passage composed of the pressure relief device 8, and is interlocked with the water discharge controller 110.
  • the channel can be automatically switched when using hot water in air-conditioning mode and heating mode.
  • the multi-function throttle channel conversion device after the high-pressure enthalpy refrigerant liquid condensed in each working condition is converted through the passage, both enter the same throttling device for throttling, and the low-pressure low-temperature refrigerant liquid after throttling passes through another One channel is converted to the corresponding heat exchanger for evaporation.
  • the present embodiment as shown in Fig.
  • the multi-function throttle passage switching device 7 includes five check valves 71 and a throttle device 72, of which four check valves 71 (71-1, 71- respectively) 2, 71-3 and 71-4) bridge-connected into a bridge channel (similar to a bridge rectifier circuit) at two diagonal points C, D of the bridge channel (equivalent to a bridge rectifier circuit
  • the AC input terminal is respectively connected to the other end of the heat exchange duct 51 of the outdoor heat exchanger 5 and the other end of the heat exchange duct 61 of the indoor heat exchanger 6, and the other two points A and B (corresponding to the output end of the bridge rectifier circuit)
  • the throttle device 72 is connected between the other; the remaining one-way cabinet 71-5 is connected between the outlet of the heat exchange conduit 41 of the hot water heat exchanger 4 and the two opposite check valves 71-4, 71-3 of the bridge passage.
  • the bridge channel connection of the four check valves is similar to the connection of the bridge rectifier circuit.
  • the two check valves are connected in series with each other in the same direction (as shown in Figure 1, one direction).
  • the valves 71-4 and 71-1 form one group, the check valves 71-2 and 71-3 form another group), and the two sets of check valves are further connected in parallel, and then at the parallel ends of the two groups.
  • the multi-function throttle passage conversion device 7 further includes a reservoir 73 and a filter 74 which are disposed at the inlet of the throttle device 72 and The two-way check valves 71-3, 71-4 of the bridge channel.
  • Multi-function throttle channel conversion The arrangement 7 may also include an ice water solenoid valve 75 disposed on the one-way valve 71 passage of the bridge passage at its point to the indoor heat exchanger. The ice water solenoid valve 75 is installed only when the ice making water belt is hot water.
  • the pressure relief device 8 may be a pressure relief valve, such as a 10KG pressure relief valve. When the system is switched, the air pressure of the original high pressure end of the dedicated three-way port 2 exceeds 10KG, and the high pressure gas flows back to the low pressure through the pressure relief valve. end.
  • the pressure relief device 8 can also be composed of a pressure switch and an electromagnetic wide. When the system is switched, the pressure switch operates and the solenoid valve opens to relieve pressure.
  • a fan speed control switch 10 In order to improve the safety protection of the system, a fan speed control switch 10, a high voltage bypass switch 20 and a high voltage protection switch 30 are provided at the high voltage end of the system to provide overvoltage protection; The low voltage bypass switch 40 and the low voltage protection switch 50 serve as a low voltage protection.
  • a high pressure bypass and a defrost bypass line and a high pressure bypass and defrost solenoid valve L00 are also provided, which are controlled by the high pressure bypass switch 20 and the low pressure bypass valve 40.
  • the high-temperature high-pressure refrigerant vapor from the compressor 1 passes through the dedicated tee W 2 and the four-way valve 3 to enter the outdoor heat exchanger 5 to condense.
  • the condensed high-temperature and high-pressure liquid enters the multi-function throttle passage conversion device 7, and enters the throttle device 72 along the check valve-4, the filter 74, and the accumulator 73 for throttling, at which time the one-way ⁇ 71-1 is at High back pressure cannot be turned on.
  • the low-pressure low-temperature liquid after throttling enters the indoor heat exchanger 6 through the check valve 71-2, absorbs heat from the air passing through the indoor heat exchanger 6, evaporates, and sends the low-temperature air into the room through the fan on the heat exchanger. Forming a cooling condition.
  • the evaporated low-temperature low-pressure refrigerant gas enters the compressor through the four-way valve 3 and is compressed into a high-temperature high-pressure refrigerant gas for the next cycle.
  • the present invention is shown in the flow direction of the fluid arrow of Figure 3 when heating alone.
  • the ⁇ warm high pressure refrigerant vapor from the compressor 1 enters the indoor heat exchanger 6 through the dedicated three-way read 2 and the four-way valve 3, and the temperature is raised after the air in the indoor heat exchanger absorbs the condensed heat, and the heated air is heated.
  • the fan is sent into the crucible to form a heating condition.
  • the condensed high-temperature and high-pressure liquid enters the multi-function throttle passage conversion device 7, and enters the throttle device 72 along the check valve 71-3, the filter 74, and the accumulator 73 for throttling, and at this time, the check valve 71-2 At high back pressure, it cannot be turned on.
  • the throttled low-pressure cryogenic liquid enters the outdoor heat exchanger 5 through the check valve 71-1 to evaporate, and the vaporized low-temperature low-pressure gas enters the compressor 1 through the four-way valve 3 to be compressed into high-temperature and high-pressure refrigerant gas for the next cycle. .
  • the present invention is shown in the flow direction of the fluid arrow of FIG.
  • the high-temperature squeezing refrigerant vapor from the compressor 1 enters the hydrothermal heat exchanger 4 through the dedicated three-way valve 2, and the condensed heat is taken away by the cold water entering the hydrothermal heat exchanger 4 to produce the required hot water. user.
  • the condensed high-temperature and high-pressure liquid enters the multi-function throttle passage conversion device 7, and enters the throttle device 72 along the one-way valve 71-5, the filter 74, and the accumulator 73 for throttling, and at this time, the indoor heat exchanger 6 tubes There is no flow in the road, the check valve 71-3 is in the back pressure and cannot be turned on, and the check valve 71-2 is also in the non-conducting state.
  • the throttled low-pressure cryogenic liquid enters the outdoor heat exchanger 5 through the check valve 71-1 to evaporate, and the vaporized low-temperature low-pressure gas enters the compressor 1 through the four-way valve 3 to be compressed into high-temperature and high-pressure refrigerant gas for the next cycle. .
  • the present invention is shown in the flow direction of the fluid arrow of FIG. 5 while simultaneously cooling and producing hot water.
  • the high-temperature and high-pressure refrigerant gas from the compressor 1 is condensed through the special tee I 2 into the hydrothermal heat exchanger 4, and the condensed heat is taken away by the cold water entering the hydrothermal heat exchanger 4 to produce the required hot water. user.
  • the condensed high-temperature and high-pressure liquid enters the multi-function throttle passage conversion device 7, and enters the throttle device 72 along the check valve 71-5, the filter 74, and the accumulator 73 for throttling, and at this time, the outdoor heat exchanger 5 tubes
  • the check valve 71-4 is in a high back pressure and cannot be turned on
  • the check valve 71-1 is also in a non-conducting state.
  • the throttled low-pressure cryogenic liquid enters the indoor heat exchanger 6 through the check valve 71-2, absorbs heat from the air passing through the indoor heat exchanger 6, evaporates, and sends the low-temperature air into the room through the fan on the heat exchanger. Forming a cooling condition.
  • the low-temperature low-pressure refrigerant gas after evaporation enters the compressor 1 through the four-way valve 3 and is compressed into a high-temperature high-pressure refrigerant gas for the next cycle.
  • the water outlet controller 110 interlocked with the dedicated three-way valve 2 is provided at the hot water outlet end of the hydrothermal heat exchanger 4. In this way, in the heating mode (as shown in Figure 3), if hot water is used, as long as the water outlet controller 110 is turned on, the dedicated three-way wide 2 is immediately converted into a separate hot water mode, as shown in FIG. run. When the hot water is used, the water outlet controller 110 is turned off, and the dedicated three-way reading 2 is automatically converted into a separate heating mode, and is operated in the heating mode shown in FIG.
  • the invention can heat recovery and obtain hot water when making ice water, that is, in the cooling mode, when operating as shown in FIG. 5, the indoor heat exchanger 6 prepares ice water below ao°c), and the water is hot.
  • the heat exchanger 4 produces hot water.
  • the ice water temperature reaches the set value, the cooling condition stops.
  • the four-way valve 3 is immediately converted into a separate hot water mode, as shown in FIG.
  • the four-way valve 3 is immediately converted into the mode operation of Fig. 5.
  • the ice making water mode is switched to the separate hot water mode, in order to prevent the low temperature and low pressure refrigerant liquid from leaking into the indoor heat exchanger 6 through the one-way crucible 71-2, at this time in the multi-function throttle passage conversion device 7
  • the addition of the ice water solenoid valve 75 can effectively prevent the refrigerant after the throttling from leaking into the indoor heat exchanger 6.
  • the ice water electromagnetic reading is turned on in the ice making mode, and is turned off when the hot water mode is separately prepared.
  • a magnetizer 70, a solenoid valve 80 and a ⁇ type filter 90 are also mounted on the water inlet of the hydrothermal heat exchanger 4.

Description

多功能 调、 热水系统
【技术领域】
[0001 ] 本发明涉及一种既能单独或同时制冷、制暖和 I或制取热水的多功能空调、热水 系统。
【背景技术】
[0002] 现阶段,空调设备、热水供应设备已广泛应用于各行各业，伹当前的多数设备都只 具备一种或两种功能，即要么是只供应暖气或冷气，要么是只供应热水的。随着科技水平的 发展和人类环保意识的日益提高，人们对空调及热水系统的要求越来越高，一机多能，节能 减排、废能利用的系统已成为今后技术发展的大势所趋，这就要求有一个完善的多功能综 合控制系统。 为此，本申请人幵发出了一种较完善的空调、热水系统，在一套设备上就可实 现至少六种功能：单独制冷、单独制暖、单独制取热水、在制冷的同时制取热水、在制暖模式 时优先制取热水、制冰水带制热水等。
【发明内容】
C0003] 本发明的目的是在于克服现有技术的不足,提供了一种结构合理、使用方便、使用 寿命高、并能达到节能减排要求的一机多功能的空调、热水系统。
[0004] 为了解决上述存在的技术问题，本发明采用下述技术方案：
[0005] 一种多功能空调、热水系统，其包括有压缩机、专用三通 W、四通阀、水热换热器、 室外热交换器、室内热交换器、多功能节流通道转换装置和泄压装置，其中：水热换热器的 进水口、出水口分别与外界供应冷水端和接收热水端连接；专用三通阀的进口与压缩机的 出气口连接,一出口与水热换热器的换热管道进口连接，另一出口与四通阀的进口连接，另 有一通道与泄压装置的进口连接；在所述水热换热器的热水出口端设有与专用三通阀连锁 的出水控制器；四通阀的三个出口分别与室外热交换器的换热管道、室内热交换器的换热 管道和压缩机的回气口连接；水热换热器的换热管道出口、室外热交换器的换热管道另一 端和室内热交换器的换热管道另一端分别与多功能节流通道转换装置的三个端口连接；所 述泄压装置的出口通向压缩机的回气口。
[0006] 在对上述多功能空调、热水系统的改进方案中，所述多功能节流通道转换装置包 括有由五个单向 W和节流装置,其中四个单向阀桥式连接成桥式通道，在所述桥式通道的 两个对角线点分别与室外热交换器的换热管道另一端、室内热交换器的换热管道另一端连 接，另外两个点之间连接节流装置；其余一单向阀连接在热水换热器的换热管道出口与桥 式通道的两相向单向阀之间。
[0007] 在对上述多功能空调、热水系统的改进方案中，所述多功能节流通道转换装置还 包括有储液器和过滤器，所述的储液器和过滹器设置在节流装置的进口与桥式通道的两相 向单向阀之间。
[0008] 在对上述多功能空调、热水系统的改进方案中，所述多功能节流通道转换装置还 包括有冰水电磁阀；所述冰水电磁阀设置在桥式通道在其指向室内热交换器的那个单向阔 通道上。
[0009] 在对上述多功能空调、热水系统的改进方案中，在所述水热换热器的进水口设有 由压缩机出气口处的高压气体控制其阔门开度的冷凝压力调节阀。 - . -
[0010] 现有技术相比，本发明的有益效果是：1)、由于它是通过特殊的专门三通阀、四通 阀和多功能节流转换装置来进行热泵系统的循环，在整个循环过程中与水热换热器、室外 热交换器和室内热交换器中的一个、两个或三个进行热交换,从而实现单独制冷、单独制 暖、单独制取热水、在制冷的同时制取热水，在制暖的模式时优先制取热水、制冰水带制热 水等六种过程之一,可以看出，本发明在其系统连接部分和控制部分比较简单的情况下，即 可实现六种功能,所以本发明能实现一机多用，满足人们的多项需求,其结构比较合理、并 能达到节能减排要求；2)、由于设置有泄压装置,可保证系统转换时压力平衡、转换迅速， 系统转换时所产生的剩余高压可通过泄压装置迅速泄向低压端，达到系统迅速、灵活转换 的目的,并使整个系统工作稳定、平衡,并具有充分的安全保护措施，并可提高系统的寿命； 3)、由于多功能节流通道转换装置是机械式结构，在每一端口处连接有两条管道，但这两条 管道一条是机械式（或高压）止通的，一条是机械式导通的，这样从其中一个端口进来的高 温高压液体只能沿着其中的一条管道流向其余两个端口的某一端口，并在节流装置中转换 成低温低压液体，这种机械式的功能转换装置避免了人们常用的用电路控制某一通道导通 而另一通道止通时的复杂电路连接和程序控制，而且电路控制的维护比较困难,所以本发 明的结构比较合理、使用方便。
[001 1 ] 下面结合附图与具体实施方式对本发明作进一步的详细描述：
【附图说明】
[0012] 图 1是本发明实施例的连接关系图；
[0013] 图 2是本发明实施例在冷气（或冰水）模式下的工作流向图；
[0014] 图 3是本发明实施例在暖气模式下的工作流向图；
[0015] 图 4是本发明实施例在制取热水模式下的工作流向图；
[0016] 图 5是本发明实施例在冷气同时制取热水模式下的工作流向图。
【具体实施方式】
[0017] 本发明为一种多功能空调、热水系统，如图 1所示,其包括有压縮机 1、专用三通阔 2、四通阀 3、水热换热器 4、室外热交换器 5、室内热交换器 6、多功能节流通道转换装置 7和 泄压装置 8 ,其中：水热换热器 4的进水口、出水口分别与外界供应冷水端和接收热水端连 接；专用三通阀 2的进口与压缩机 1的出气口 11连接，一出口与水热换热器 4的换热管道 41进口连接，另一出口与四通阀 3的进口连接，另有一通道与泄压装置 8的进口连接；在所 述水热换热器 4的热水出口端设有与专用三通阀 2连锁的出水控制器 110 ;四通阀 3的三个 出口分别与室外热交换器 5的换热管道 51、室内热交换器 6的换热管道 61和压缩机 1的回 气口连接；水热换热器 4的换热管道 41出口、室外热交换器 5的换热管道 51另一端和室内 热交换器 6的换热管道 61另一端分别与多功能节流通道转换装置 7的三个端口连接：所述 泄压装置 8的出口通向压缩机 1的回气口，这样可保证系统转换时压力平衡、转换迅速，系 统转换时所产生的剩余高压可通过泄压装置迅速泄向低压端，达到系统迅速、灵活转换的 目的，并使整个系统工作稳定、平衡，具有充分的安全保护措施，并可提高系统的寿命。多功 能节流通道转换装置 7的作用是使高温高压的冷媒液体在流经多功能节流通道转换装置 后变为低温低压的冷媒液体，然后送到相应热交换器进行蒸发。 由于多功能节流通道转换 装置是机械式结构，在每一端口处连接有两条管道，但这两条管道一条是机械式（或高压） 止通的，一条是机械式导通的，这样从其中一个端口进来的高温髙压液体只能沿着其中的 一条管道流向其余两个端口的某一端口，并在节流装置中转换成低温低压液体,这种机械 式的功能转换装置避免了人们常用的用电路控制某一通道导通而另一通道止通时的复杂 电路连接和程序控制，而且电路控制的维护比较困难，所以本发明的结构比较合理、使用方 便。
[0018] 由于本发明是通过特殊的专门三通阀 2、四通阔 3和多功能节流转换装置 7来进行 热泵系统的循环。 在整个循环过程中与水热换热器、室外热交换器和室内热交换器中的一 个、两个或三个进行热交换,从而实现单独制冷、单独制暖、单独制取热水、在制冷的同时制 取热水，在制暖的模式时优先制取热水、制冰水带制热水等六种过程之一，可以看出，本发 明在其系统连接部分和控制部分比较简单的情况下，即可实现六种功能,所以本发明能实 现一机多用，满足人们的多项需求，其结构比较合理、并能达到节能减排要求。
[001 9] 在本实施例中，在所述水热换热器 4的进水口设有由压缩机 1出气口处的高压气 体控制其阀门开度的冷凝压力调节阀 60，以保持出水温度的恒定,在工作时根据高压（冷 凝压力） 的变化来调节进水的大小，控制冷水的流量大小来达到稳定出水温度。
[0020] 可以看出，本发明的专用三通阀 2为特殊设计的三通阀，除三条通道外还有由泄 压装置 8组成的髙压泄压通道，并且与出水控制器 110连锁,在冷气模式和暖气模式下使用 热水时可以自动转换通道。
[0021 ] 在多功能节流通道转换装置中，各工况冷凝后的高压髙温冷媒液体通过通道转换 后，均进入同一个节流装置进行节流,节流后的低压低温冷媒液体通过另一通道转换送到 相应换热器进行蒸发。在本实施例中，如图 1所示，多功能节流通道转换装置 7包括有五个 单向阀 71和节流装置 72，其中四个单向阀 71 (分别是 71-1 ,71-2, 71-3和 71-4)桥式连接 成桥式通道（类似于桥式整流电路），在所述桥式通道的两个对角线点 C、D (相当于桥式整 流电路的交流输入端）分别与室外热交换器 5的换热管道 51另一端、室内热交换器 6的换 热管道 61另一端连接，另外两个点 A、B (相当于桥式整流电路的输出端）之间连接节流装 置 72；其余一单向阁 71-5连接在热水换热器 4的换热管道 41出口与桥式通道的两相向单 向阀 71- 4、71-3之间 （即 D点）。 四个单向阀的桥式通道连接，类似于桥式整流电路的连 接，在连接时，先将四个单向阀的两两同向分别串联起两组（如图 1所示，单向阀 71-4和 71-1形成一组，单向阀 71-2和 71-3形成另一组），再将这两组单向阀再并联起来，接着在 这两组的并联端八、 B (相当于桥式整流电路的输出端）之间再并联上节流装置 72，每组的 两单向阀之间 C、D (相当于桥式整流电路的交流输入端）再分别与室外、室内热交换器 5、6 的换热管道 51、61另一端连接。通过四个单向闽 71的桥式通道，使到在每一端口处的两条 管道，一条是止通的，一条是导通的；而节流装置 72的作用是使离温髙压液体转换成低温 低压液体，它可以是电子膨胀阀、毛细管等。为了在功能转换过程中比较稳定和保护节流装 置，在本实施例中，多功能节流通道转换装置 7还包括有储液器 73和过滤器 74,它们设置在 节流装置 72的进口与桥式通道的两相向单向阀 71-3、71- 4之间。 多功能节流通道转换装 置 7还可以包括有冰水电磁阀 75，其设置在桥式通道在其指向室内热交换器的那个单向阀 71通道上。 冰水电磁阀 75仅在制冰水带制热水时安装。
[0022] 泄压装置 8可以是泄压阀，比如是 10KG的泄压阀，当系统转换时，专用三通阙 2内 原高压端的空气压力超过 10KG时，高压气体经泄压阀迅速流回低压端。泄压装置 8也可以 是由压力开关和电磁阔组成，当系统转换时，压力开关动作，电磁阀打开来泄压。
[0023] 为提高系统的安全保护，在系统的高压端设有风机调速控制开关 10、高压旁通开 关 20和高压保护开关 30，以起到过压保护作用；在系统的低压端设有低压旁通开关 40和 低压保护开关 50，以起到低压保护作用。 在系统中还设有高压旁通和除霜旁通合一的管路 和高压旁通、除霜电磁阀 L00，其由高压旁通开关 20和低压旁通阀 40控制工作与否。
[0024] 现将本发明的六种功能实现过程分述如下 -
[0025] 本发明在单独制冷气时，如图 2的流体箭头流向所示，由压缩机 1出来的高温高压 冷媒蒸气经过专用三通 W 2和四通阀 3进入室外换热器 5冷凝，冷凝后的高温高压液体进 入多功能节流通道转换装置 7，沿着单向阀 - 4、过滤器 74、储液器 73进入节流装置 72进 行节流,此时单向闽 71-1处于高背压不能导通。 节流后的低压低温液体经过单向阀 71-2 进入室内换热器 6 ,从通过室内换热器 6的空气中吸取热量进行蒸发，并通过换热器上的风 机将低温空气送入室内，形成制冷工况。 蒸发后的低温低压的冷媒气体通过四通阀 3进入 压缩机 1压缩为高温高压冷媒气体,进行下一次的循环。
[0026] 本发明在单独制暖时，如图 3的流体箭头流向所示。 由压缩机 1出来的髙温高压 冷媒蒸气经过专用三通阅 2和四通阀 3进入室内换热器 6冷凝，通过室内换热器的空气吸 收冷凝热后温度升高，加热后的空气由风机送入窒内，形成制暖工况。冷凝后的高温高压液 体进入多功能节流通道转换装置 7，沿着单向阀 71-3、过滤器 74、储液器 73进入节流装置 72进行节流,此时单向阀 71-2处于高背压不能导通。 节流后的低压低温液体经过单向阀 71-1进入室外换热器 5进行蒸发，蒸发为低温低压的气体通过四通阀 3进入压缩机 1压缩 为高温高压冷媒气体，进行下一次的循环。
[0027] 本发明在单独制取热水时，如图 4的流体箭头流向所示。 由压缩机 1出来的高温 髙压冷媒蒸气经过专用三通阀 2进入水热换热器 4冷凝，冷凝热被进入水热换热器 4的冷 水带走,制成所需要的热水,供应用户。冷凝后的高温高压液体进入多功能节流通道转换装 置 7 ,沿着单向阀 71- 5、过滤器 74、储液器 73进入节流装置 72进行节流，此时室内换热器 6 管路无流动，单向阀 71-3处于髙背压不能导通，单向阀 71- 2也处于不导通状态。节流后的 低压低温液体经过单向阀 71- 1进入室外换热器 5进行蒸发，蒸发为低温低压的气体经四通 阀 3进入压缩机 1压缩为高温高压冷媒气体，进行下一次的循环。
[0028] 本发明在同时制冷和制取热水时，如图 5的流体箭头流向所示。 由压缩机 1出来 的高温高压冷媒气体经过专用三通 I萄 2进入水热换热器 4冷凝，冷凝热被进入水热换热器 4的冷水带走，制成所需要的热水，供应用户。 冷凝后的高温高压液体进入多功能节流通道 转换装置 7，沿着单向阀 71-5、过滤器 74、储液器 73进入节流装置 72进行节流，此时室外换 热器 5管路无流动，单向阀 71-4处于高背压不能导通，单向阀 71-1也处于不导通状态。 节 流后的低压低温液体经过单向阀 71-2进入室内换热器 6，从通过室内换热器 6的空气中吸 取热量进行蒸发，并通过换热器上的风机将低温空气送入室内，形成制冷工况。蒸发后的低 温低压的冷媒气体经四通阀 3进入压縮机 1压缩为高温高压冷媒气体，进行下一次的循环。 [0029] 本发明在制暖模式下优先制取热水时,在水热换热器 4的热水出口端设有与专用 三通阀 2连锁的出水控制器 110。 这样在制暖气模式下（如图 3所示运行） 时，如果使用 热水，只要把出水控制器 110打开，专用三通阔 2立即进行转换为单独制取热水模式，如图 4所示运行。 当热水使用结柬时，关闭出水控制器 110，专用三通阅 2又立即自动转换为单 独制暖模式，按图 3所示制暖气模式运行。
[0030] 本发明在制冰水时可以热回收制取热水，即在制冷模式下，如图 5所示运行时，室 内换热器 6制取冰水 ao°c以下），同时水热换热器 4制取热水。当冰水温度到达设定值时， 制冷工况停止。此时如果还需继续制取热水，四通阀 3立即进行转换为单独制取热水模式， 如图 4所示运行。 冰水温度上升需再制冰水时，四通阀 3立即转换为图 5模式运行。 在制 冰水模式转换为单独制取热水模式时，为了防止低温低压的冷媒液体通过单向闺 71- 2渗 漏到室内换热器 6,此时在多功能节流通道转换装置 7中加装有冰水电磁阀 75，可以有效防 止节流后的冷媒渗漏到室内换热器 6。 在制冰水模式时冰水电磁阅 75打开，而在单独制取 热水模式时关闭。
[0031 ] 在水热换热器 4的进水口上还装有磁化器 70、电磁阀 80和 Υ型过滤器 90。

Claims

权利要求
1. 一种多功能空调、热水系统，其特征在于：包括有压缩机（1〉、专用三通阀（2)、四通 阀（3)、水热换热器（4)、室外热交换器（5)、室内热交换器（6)、多功能节流通道转换装置 (7)和泄压装置 (8)，其中 :
水热换热器（4)的进水口、出水口分别与外界供应冷水端和接收热水端连接； 专用三通阀（2) 的进口与压缩机（1)的出气口连接，一出口与水热换热器（4) 的换热 管道（41)进口连接，另一出口与四通阀（3)的进口连接,另有一通道与泄压装置（8)的进 口连接；在所述水热换热器（4) 的热水出口端设有与专用三通 W (2)连锁的出水控制器 (110) ；
四通阀（3)的三个出口分别与室外热交换器（5)的换热管道（51)—端、室内热交换器 (6)一端的换热管道（61)和压縮机（1)的回气口连接；
水热换热器（4) 的换热管道（41) 出口、室外热交换器（5)的换热管道（51)另一端和 室内热交换器（6) 的换热管道（61)另一端分别与多功能节流通道转换装置（7) 的三个端 口连接；
所述泄压装置（8)的出口通向压缩机（1) 的回气口。
2.根据权利要求 1所述的多功能空调、热水系统，其特征在于：所述多功能节流通道 转换装置（7)包括有由五个单向阀（71)和节流装置（72)，其中四个单向阀（71-1、71-2、 71-3, 71-4)桥式连接成桥式通道，在所述桥式通道的两个对角线点（C、D)分别与室外热交 换器 5的换热管道 51另一端、室内热交换器（6)的换热管道（61)另一端连接，另外两个点 (A、 B)之间连接节流装置（72) ：其余一单向阀 (71-5)连接在热水换热器（4)的换热管道 (41)出口与桥式通道的两相向单向阀（71-4)、（71-3)之间。
3.根据权利要求 2所述的多功能空调、热水系统，其特征在于：所述多功能节流通道转 换装置（7)还包括有储液器 (73)和过滤器（74)，所述的储液器（73)和过滤器（74)设置在 节流装置（72) 的进口与桥式通道的两相向单向阀（7卜 3、71-4)之间。
4.根据权利要求 3所述的多功能空调、热水系统，其特征在于：所述多功能节流通道转 换装置（7)还包括有冰水电磁阀（75)；所述冰水电磁阀（75)设置在桥式通道在其指向室 内热交换器的那个单向阔 (71-2)通道上。
5.根据权利要求 1、2、3或 4所述的多功能空调、热水系统，其特征在于：在所述水热换 热器（4)的进水口设有由压缩机（1)出气口处的髙压气体控制其阀门开度的冷凝压力调节 阀（60)。
PCT/CN2011/000118 2010-03-13 2011-01-25 多功能空调、热水系统 WO2011113295A1 (zh)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112066497A (zh) * 2020-09-21 2020-12-11 珠海格力电器股份有限公司 一体式内机热泵空调系统及其控制方法
CN112629033A (zh) * 2019-09-24 2021-04-09 广东芬尼克兹节能设备有限公司 热水机低流量保护控制方法、装置、设备及存储介质
US11175074B1 (en) 2020-08-04 2021-11-16 Mitsubishi Electric Us, Inc. Refrigeration cycle device and method of operating refrigeration cycle device

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101799227B (zh) * 2010-03-13 2011-11-09 快意节能设备（深圳）有限公司 多功能空调、热水系统
CN102777992A (zh) * 2012-07-27 2012-11-14 汤淑玲 多功能制冷、制热系统
CN104374115A (zh) * 2013-08-14 2015-02-25 开利公司 热泵系统、热泵机组及热泵系统的多功能模式控制方法
CN106766318A (zh) * 2017-02-06 2017-05-31 刘勇 用于极寒天气具有制热水制冰等多种功能的co2热泵
CN108870803A (zh) 2017-05-12 2018-11-23 开利公司 热泵系统及其控制方法
CN113237247A (zh) * 2021-05-17 2021-08-10 青岛海尔空调电子有限公司 热泵空调系统及空调机组

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2311717Y (zh) * 1997-09-25 1999-03-24 蓝勇前 节能型冷暖空调拖热水器
CN1385656A (zh) * 2001-05-12 2002-12-18 中国科学技术大学 一种四季节能冷暖空调热水三用机
JP2003240371A (ja) * 2002-02-21 2003-08-27 Denso Corp 空調装置
AU2010100284A4 (en) * 2010-03-30 2010-04-29 Vast Vision Limited Heat pump hot water air conditioner
CN101799227A (zh) * 2010-03-13 2010-08-11 郭立华 多功能空调、热水系统
CN201611192U (zh) * 2010-03-13 2010-10-20 郭立华 多功能空调、热水系统

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5937663A (en) * 1997-12-23 1999-08-17 Yang Fan Development Co., Ltd. Multipurpose heat pump system
CN2341089Y (zh) * 1998-05-08 1999-09-29 冯海芃 制冷系统压缩机的泄压启动装置
JP3932913B2 (ja) * 2002-01-29 2007-06-20 ダイキン工業株式会社 ヒートポンプ式給湯機
JP3972860B2 (ja) * 2003-05-15 2007-09-05 ダイキン工業株式会社 冷凍装置
CN1948863A (zh) * 2005-10-14 2007-04-18 颜军玲 高效热泵制冷制热装置
CN101592418A (zh) * 2009-06-26 2009-12-02 合肥天鹅制冷科技有限公司 水源采暖、空调、热水三用机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2311717Y (zh) * 1997-09-25 1999-03-24 蓝勇前 节能型冷暖空调拖热水器
CN1385656A (zh) * 2001-05-12 2002-12-18 中国科学技术大学 一种四季节能冷暖空调热水三用机
JP2003240371A (ja) * 2002-02-21 2003-08-27 Denso Corp 空調装置
CN101799227A (zh) * 2010-03-13 2010-08-11 郭立华 多功能空调、热水系统
CN201611192U (zh) * 2010-03-13 2010-10-20 郭立华 多功能空调、热水系统
AU2010100284A4 (en) * 2010-03-30 2010-04-29 Vast Vision Limited Heat pump hot water air conditioner

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112629033A (zh) * 2019-09-24 2021-04-09 广东芬尼克兹节能设备有限公司 热水机低流量保护控制方法、装置、设备及存储介质
CN112629033B (zh) * 2019-09-24 2022-05-27 广东芬尼克兹节能设备有限公司 热水机低流量保护控制方法、装置、设备及存储介质
US11175074B1 (en) 2020-08-04 2021-11-16 Mitsubishi Electric Us, Inc. Refrigeration cycle device and method of operating refrigeration cycle device
US11892203B2 (en) 2020-08-04 2024-02-06 Mitsubishi Electric Us, Inc. Method of operating refrigeration cycle device
CN112066497A (zh) * 2020-09-21 2020-12-11 珠海格力电器股份有限公司 一体式内机热泵空调系统及其控制方法

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