WO2012058844A1 - 蒸发器和具有该蒸发器的制冷系统 - Google Patents

蒸发器和具有该蒸发器的制冷系统 Download PDF

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Publication number
WO2012058844A1
WO2012058844A1 PCT/CN2010/080259 CN2010080259W WO2012058844A1 WO 2012058844 A1 WO2012058844 A1 WO 2012058844A1 CN 2010080259 W CN2010080259 W CN 2010080259W WO 2012058844 A1 WO2012058844 A1 WO 2012058844A1
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WO
WIPO (PCT)
Prior art keywords
valve
header
refrigerant
evaporator
tube
Prior art date
Application number
PCT/CN2010/080259
Other languages
English (en)
French (fr)
Inventor
高强
李艳星
Original Assignee
三花丹佛斯（杭州）微通道换热器有限公司
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 三花丹佛斯（杭州）微通道换热器有限公司 filed Critical 三花丹佛斯（杭州）微通道换热器有限公司
Priority to EP10859192.6A priority Critical patent/EP2636973B1/en
Priority to JP2013536980A priority patent/JP5646767B2/ja
Priority to KR1020137014206A priority patent/KR101504720B1/ko
Priority to US13/883,570 priority patent/US9285145B2/en
Publication of WO2012058844A1 publication Critical patent/WO2012058844A1/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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/006—Preventing deposits of ice
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0232—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses
    • F25B2313/02322—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses during defrosting
    • 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0085—Evaporators

Definitions

  • the present invention relates to the field of refrigeration technology, and more particularly to an evaporator and a refrigeration system having the same. Background technique
  • Refrigeration systems such as air-conditioning refrigeration systems, operate in winter. When the ambient temperature is low, the evaporation temperature of the evaporator is below zero, so defrosting is required at regular intervals. Conventional refrigeration systems use full reverse cycle defrost, which turns the condenser into an evaporator and the evaporator as a condenser.
  • the refrigerant guiding tube is usually provided in the inlet and outlet headers of the evaporator, the flow resistance of the refrigerant is large during the defrosting process, and the refrigerant cannot quickly pass through the evaporator in a large amount, and therefore, the defrosting Slow.
  • a large temperature-sliding refrigerant for example, R407C
  • the location of the frosting is usually adjacent to the refrigerant inlet of the heat exchanger, so that the reverse cycle of the gas-phase refrigerant is introduced from the outlet of the outlet header.
  • the frost method does not allow the defrosting to proceed quickly, so the defrosting time is long and the unit operation efficiency is low. Summary of the invention
  • the present invention aims to solve at least one of the technical problems existing in the prior art.
  • an object of the present invention is to provide an evaporator which has a reduced defrosting time, a fast defrosting speed, and an improved running efficiency.
  • Another object of the present invention is to provide a refrigeration system having the above evaporator which can reduce temperature fluctuations in an indoor environment.
  • the evaporator according to the embodiment of the first aspect of the present invention includes a first header, one end of the first header is provided with a first refrigerant port; the second header is provided, the second current collector One end of the tube is provided with a second refrigerant port; a heat exchange tube, wherein the heat exchange tubes are respectively connected between the first and second headers to communicate the first and second headers; the fins, the fins The sheets are respectively disposed between adjacent heat exchange tubes; and the defrosting tube, the first end of the defrosting tube is connected to one of the first and second headers to be associated with the one
  • the header is internally connected, wherein a position at which the first end of the defroster tube is connected to the one header is offset from the one end of the one header by a predetermined distance.
  • the defroster tube is connected to the first header or the second header, when the evaporator needs to be defrosted, the refrigerant enters from the defroster tube.
  • the first header or the second header increases the defrosting speed, reduces the defrosting time, and improves the performance of the refrigeration system.
  • the evaporator according to the above embodiment of the present invention may further have the following additional technical features:
  • the first end of the defroster tube is connected to an intermediate portion of the one of the headers.
  • the angle between the axis of the defroster tube and the axis of the heat exchange tube is between 45 and 315 degrees.
  • the predetermined distance is greater than 100 mm.
  • a refrigerant guiding tube having an open end and a closed end, wherein the refrigerant guiding tube is formed with a plurality of openings, wherein the open end of the refrigerant guiding tube is from the one set
  • the refrigerant port of the flow tube protrudes.
  • a refrigeration system comprising: a compressor; a four-way valve having first to fourth valve ports, wherein the compressor and the four-way valve are first and third a valve port is connected; a condenser, an inlet of the condenser is connected to a second valve port of the four-way valve; a throttle mechanism, an inlet of the throttle mechanism is connected to an outlet of the condenser; an evaporator, the evaporator connection Between the fourth valve port of the four-way valve and the outlet of the throttle mechanism, wherein the evaporator is an evaporator according to the first aspect of the invention; and a refrigerant switching unit, the refrigeration switching unit The evaporator is connected and connected between the fourth valve port of the four-way valve and the outlet of the throttle mechanism for allowing the refrigerant to pass from the four-way valve through the throttle mechanism into the first header when the refrigeration system is in the normal operation mode And flowing back from the second header to the four-way valve, and
  • the refrigerant switching unit includes first to fourth valves, wherein the first valve is connected between a fourth valve port of the four-way valve and a second refrigerant port of the second header of the evaporator, and second One side of the valve is connected between the first valve and the refrigerant port of the second header, and the other side of the second valve is connected to the throttle mechanism, and one side of the third valve is connected to the other side of the second valve Between the other side of the third valve and the first refrigerant port of the first header of the evaporator, and the fourth valve is connected to the fourth valve port of the four-way valve and the defrosting tube Between the second ends.
  • the first end of the defroster tube is connected to the first header or the second header.
  • the first end of the defroster tube is connected to the second header, and the refrigerant switching unit includes a first valve and a fourth valve, wherein the first valve is connected to the fourth valve port of the four-way valve A fourth valve is connected between the fourth valve port of the four-way valve and the second end of the defroster tube between the second refrigerant ports of the second header of the evaporator.
  • the first end of the defroster tube is connected to the second header, the second end of the defroster tube is connected to the fourth valve port of the four-way valve, wherein the refrigerant switching unit comprises a first valve, The first valve is connected between the fourth valve port of the four-way valve and the second refrigerant port of the second header of the evaporator.
  • FIG. 1 is a schematic plan view of an evaporator according to an embodiment of the present invention.
  • Figure 2 is a side elevational view of the evaporator of Figure 1;
  • Figure 3 is a plan view showing an evaporator according to another embodiment of the present invention.
  • Figure 4 is a side elevational view of the evaporator shown in Figure 3;
  • Figure 5 is a plan view showing an evaporator according to still another embodiment of the present invention.
  • Figure 6 is a side elevational view of the evaporator shown in Figure 5;
  • Figure 7 is a schematic illustration of a refrigeration system in accordance with one embodiment of the present invention
  • Figure 8 is a schematic illustration of a refrigeration system in accordance with another embodiment of the present invention
  • FIG. 9 is a schematic view of a refrigeration system in accordance with still another embodiment of the present invention.
  • FIG. 10 is a schematic illustration of a refrigeration system in accordance with yet another embodiment of the present invention. detailed description
  • the evaporator 500 includes a first header 501, a second header 502, a heat exchange tube 503, fins 504, and a defroster tube 505.
  • first header 501 is provided with a first refrigerant port 5010
  • second header 502 is provided with a second refrigerant port 5020.
  • the first header 501 serves as an inlet header of the evaporator 500
  • the second header 502 serves as an outlet header of the evaporator 500
  • the first refrigerant port 5010 is an evaporator.
  • the refrigerant inlet of 500, the second refrigerant port 5020 is a refrigerant outlet of the evaporator 500, and the first refrigerant port 5010 and the second refrigerant port 5020 are in the form of a refrigerant inlet pipe and a refrigerant outlet pipe.
  • Heat exchange tubes 503, such as flat tubes, are connected between the inlet header 501 and the outlet header 502, respectively, to communicate the inlet header 501 and the outlet header 502.
  • the fins 504 are disposed between adjacent heat exchange tubes 503, respectively.
  • One end of the defroster tube 505 is connected to one of the inlet header 501 and the outlet header 502 to communicate with the inside of the header, wherein the first end of the defroster 505 and the one The position at which the header is connected is offset from the one end of the one of the headers where the refrigerant port is formed.
  • the defroster tube 505 is connected to the inlet header 501, and more specifically, one end of the defroster tube 505 is connected to a substantially intermediate portion of the inlet header 501.
  • the axis of the defroster tube 505 is at an angle of substantially 90 degrees to the axis of the heat transfer tube 503 (i.e., the length direction of the heat transfer tube).
  • FIG 3 and 4 show an evaporator 500 in accordance with another embodiment of the present invention, wherein one end of the defroster tube 505 is connected to a substantially intermediate portion of the inlet header 501.
  • the angle ⁇ between the axis of the defroster tube 505 and the axis of the heat exchange tube 503 is 45-315. In the range.
  • FIG. 5 and 6 illustrate an evaporator 500 according to still another embodiment of the present invention, wherein two defroster tubes 505 are connected to the inlet header 501, and two defroster tubes 505 are along the length of the inlet header 501.
  • the direction is spaced apart, wherein the distance of the left side defrosting tube 505 from the left end of the inlet header 501 and the distance of the right defrosting tube 505 from the right end of the inlet header 501 are both greater than 100 mm, thereby further improving the defrosting effect.
  • the number of the defroster tubes 505 is not limited thereto, and any suitable number of the defroster tubes 505 may be provided depending on the specific application.
  • an inlet refrigerant conduit 506 is inserted into the inlet header 501, and the inlet refrigerant conduit 506 has an open end and a closed end and is formed with a plurality of openings along the length direction, for example, The non-circular slots, the open end of the refrigerant guiding tube 506 protrudes from the refrigerant inlet of the inlet header 501, and more specifically, the open end of the refrigerant guiding tube 506 is connected to the inlet tube 5010.
  • an outlet refrigerant conduit 507 may also be inserted into the outlet header 502.
  • the outlet refrigerant conduit 507 has an open end and a closed end and is formed with a plurality of openings along the length direction, for example, a plurality of The non-circular slot, the open end of the refrigerant guiding tube 507 protrudes from the refrigerant outlet of the outlet header 502, and more specifically, the open end of the refrigerant guiding tube 507 is connected to the outlet tube 5020.
  • the defroster tube 505 can be coupled to the outlet header 502. Similarly, the connection position of the defroster tube 505 to the outlet header 502 is offset from one end of the outlet header 502, such as the generally intermediate portion of the outlet header 502.
  • the defroster tube 505 is connected to the inlet header 501 or the outlet header 502, the refrigerant is defrosted when the evaporator 500 needs to be defrosted.
  • the tube 505 enters the inlet header 501 or the outlet header 502, thereby increasing the defrosting speed, reducing the defrosting time, and improving the efficiency of the refrigeration system.
  • a refrigerant system (e.g., a heat pump system) according to an embodiment of the present invention includes a compressor 100, a four-way valve 200, a condenser 300, a throttle mechanism 400, an evaporator 500, and a refrigerant switching unit.
  • the four-way valve 200 has first to fourth valve ports (in FIG. 7, the left side valve port, the right side valve port, the upper side port port, and the lower side port port, respectively), wherein the compressor 100 It is connected to the first valve A port and the third valve C port of the four-way valve 200.
  • the inlet of the condenser 300 is connected to the second valve B of the four-way valve 200.
  • the inlet of the throttle mechanism 400 e.g., expansion valve
  • the evaporator 500 is connected between the fourth port of the four-way valve 200 and the outlet of the throttle mechanism 400.
  • a refrigeration switching unit is coupled to the evaporator 500 and coupled between the fourth valve port of the four-way valve 200 and the outlet of the throttle mechanism 400 for passing refrigerant from the four-way valve 200 through the section when the refrigeration system is in the normal operating mode
  • the flow mechanism 400 enters the inlet header 501 and flows out of the outlet header 502 back to the four-way valve 200, and allows the refrigerant to pass from the four-way valve 200 through the defroster tube 505 when the refrigeration system is in the defrosting mode of operation. It is described in one of the headers and flows out of the other header of the evaporator 500 through the throttle mechanism 400 to return to the four-way valve 200.
  • the indoor unit is used as the condenser 300, and the fan F is driven by the motor M, so that the hot air heated by the condenser 300 is blown into the room for heating.
  • the refrigerant switching unit includes a first valve A, a second valve B, a third valve C, and a fourth valve D.
  • the first valve A is connected between the fourth valve port of the four-way valve 200 and the refrigerant outlet 5020 of the outlet header 502 of the evaporator 500
  • One side of the two valve B is connected between the first valve A and the refrigerant outlet 5020 of the outlet header 502
  • the other side of the second valve B is connected to the throttle mechanism 400
  • one side of the third valve C is connected
  • the other side of the second valve B is connected to the throttle mechanism 400 and the other side of the third valve C is connected to the refrigerant inlet 5010 of the inlet header 501 of the evaporator 500
  • the first end of the defrosting tube 505 is
  • the central portion of the inlet header 501 is connected
  • the fourth valve D is connected between the fourth valve port of the four-way valve 200 and the second end of the defroster tube 505.
  • the first end of the defroster tube 505 is connected to the inlet header 501, and when the refrigeration system is in the normal operation mode, the first valve A and the third valve C are opened and the second valve B and the fourth valve are opened. D is closed, so that the refrigerant enters the four-way valve 200 from the compressor 100 through the second valve B of the four-way valve 200, and then enters the condenser 300 along the solid arrow A through the third valve C of the four-way valve 200.
  • the third valve C is opened, so the refrigerant enters the refrigerant inlet 5010 of the inlet header 501 of the evaporator 500 from the throttle mechanism 400.
  • the tube 5010 enters the inlet header 501, for example, can be dispensed into the inlet header 501 through the inlet refrigerant conduit 506, thereby eliminating gas-liquid stratification.
  • the refrigerant enters the respective heat exchange tubes 503 from the inlet header 501, exchanges heat with the outside, and enters the outlet header 502 of the evaporator 500.
  • the refrigerant from the outlet header 502 passes through the first valve A and the four-way valve 200.
  • the fourth valve port returns to the four-way valve 200 and then enters the compressor 100 from the first valve A port of the four-way valve 200. Thereby, the circulation of the refrigerant is achieved.
  • the refrigeration system When defrosting is required, the refrigeration system performs a defrosting mode of operation. At this time, the first valve A and the third valve C are closed, the second and fourth valves D are opened, and the refrigerant enters the defroster tube 505 from the fourth valve port of the four-way valve 200 along the dotted arrow N through the fourth valve D.
  • the refrigerant enters the inlet header 501 of the evaporator 500 from the defroster tube 505, for example, from the substantially intermediate position of the inlet header 501 into the inlet header 501, thereby defrosting the evaporator 500, and the defrosting speed accelerate.
  • the refrigerant flows along the heat exchange tubes 503 to the outlet header 502 and is then discharged from the refrigerant outlet 5020. Since the first valve A and the third valve C are closed, the refrigerant from the outlet header 502 can only be returned to the four-way valve through the throttle mechanism 400, the condenser 300, and the third valve C of the four-way valve 200. Within 200.
  • the gaseous refrigerant enters the inlet header 501 from the defroster tube 505, avoiding the inlet refrigerant conduit 506, and the flow resistance is greatly reduced, and the flow resistance is greatly increased.
  • the refrigerant flow rate increases the defrosting speed.
  • the refrigeration system in which the frost accumulates in the vicinity of the refrigerant inlet 5010 of the inlet header 501 for example, R407C
  • the high-temperature gaseous refrigerant flows in from the inlet header 501, so that the frost can be directly accelerated, and It helps the defrosting melt water to evaporate.
  • the defroster tube 505 the defrosting process of the refrigeration system can be greatly accelerated, the defrosting time is shortened, and the defrosting effect can be enhanced, the indoor temperature fluctuation is reduced, and the comfort is improved. Moreover, the refrigerant does not need to be reversely circulated in the evaporator 500.
  • the first end of the defroster tube 505 is coupled to the outlet header 502.
  • the first valve A and the third valve C are open and the second valve B and the fourth valve D are closed.
  • the first valve A and the second valve B are closed and the third valve C and the fourth valve D are open.
  • the third valve C is normally open and the second valve B is normally closed.
  • the refrigerant enters the outlet header from the defroster 505 502, then enters the inlet header 501 through the heat exchange tube 503, and returns to the four-way valve 200 through the throttle mechanism 400 and the condenser 300.
  • Other operations of the refrigerant system in normal operating mode and defrost mode are not described in detail herein.
  • the defrosting tube 505 is connected to the outlet header 502, so that the defrosting tube 505 is used for the case where the frost is exported during the heating operation (such as the R410A, R22 system). It is disposed on the outlet header 502 to facilitate rapid melting of the upper frost.
  • the first end of the defroster tube 505 is connected to the outlet header 502, and the refrigerant switching unit includes a first valve A and a fourth valve D, wherein the first valve A is connected to four
  • the fourth valve port of the valve 200 is connected to the refrigerant outlet 5020 of the outlet header 502 of the evaporator 500, and the fourth valve D is connected to the fourth valve port of the four-way valve 200 and the second end of the defroster tube 505. between.
  • the first valve A When the refrigeration system is in the normal operating mode, the first valve A is open and the fourth valve D is closed, and the first valve A is closed and the fourth valve D is open while the refrigeration system is in the defrost mode.
  • the embodiment shown in Fig. 9 differs from the embodiment shown in Fig. 8 in that the normally closed second valve B and the normally open third valve C are omitted, and the second valve B is disconnected, the third valve The location of C is replaced by tubing, thus reducing cost and control complexity.
  • the operation of the refrigeration system shown in Figure 9 is similar to the refrigeration system shown in Figure 8, and will not be described in detail herein.
  • the first end of the defroster tube 505 is connected to the outlet header 502, and the second end of the defroster tube 505 is connected to the fourth port of the four-way valve 200, the refrigerant switching unit Including the first valve A, the first valve A is connected between the fourth valve port of the four-way valve 200 and the refrigerant outlet 5020 of the outlet header 502 of the evaporator 500.
  • the first valve A When the refrigeration system is in the normal operation mode, the first valve A is opened, and the refrigerant returns from the outlet header 502 through the first valve A to the four-way valve 200. Of course, a part of the small amount of refrigerant returns from the defroster 505 to four. Through the valve 200.
  • the first valve A When the refrigeration system is in the defrosting mode, the first valve A is closed, the refrigerant enters the outlet header 502 from the defroster tube 505, and then passes through the heat exchange tube 503, the inlet header 501, the throttle mechanism 400, and the condenser. 300 returns to the four-way valve 200.
  • the refrigeration system shown in Figure 10 uses only one valve, so the structure is more compact, the cost is lower, and the control is easy.
  • the evaporator 500 of the refrigeration system has only one defroster tube 505.
  • any suitable number of defroster tubes 505 may be provided as needed, and the defroster tube 505 may be simultaneously connected to the inlet header 501 and the outlet header 502, and of course, to the inlet header 501.
  • the defroster tube 505 connected to the outlet header 502 may have a respective refrigerant switching unit.

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Description

蒸发器和具有该蒸发器的制冷系统 技术领域
本发明涉及制冷技术领域， 尤其是涉及一种蒸发器和具有该蒸发器的制冷系统。 背景技术
制冷系统， 例如空调的制冷系统， 在冬季运行时， 当环境温度很低时， 蒸发器的蒸发温 度会低于零度， 因此需要定时进行除霜。 传统的制冷系统釆用全逆循环除霜， 即将冷凝器变 为蒸发器， 蒸发器用作冷凝器。
传统制冷系统在除霜时， 室内环境温度会下降， 引起舒适度的降低。 另一方面， 除霜会 引起室内环境供热的中断， 机组的能效降低。
此外， 由于蒸发器的入口和出口集流管中通常设有制冷剂导引管， 在除霜过程中， 制冷 剂的流动阻力很大， 制冷剂不能快速大量地通过蒸发器， 因此， 除霜速度慢。 在釆用大温度 滑移的制冷剂 （例如 R407C ) 的制冷系统中， 结霜的位置通常邻近换热器的制冷剂入口， 因 此从出口集流管的出口位置引入气相制冷剂的逆循环除霜方式不能使除霜快速进行，因此除 霜时间长， 机组运行效率低。 发明内容
本发明旨在至少解决现有技术中存在的技术问题之一。
为此， 本发明的一个目的在于提出一种除霜时间减少、 除霜速度快、 且运行效率提高的 蒸发器。
本发明的另一目的在于提出一种可以减少室内环境的温度波动的具有上述蒸发器的制 冷系统。
才艮据本发明第一方面的实施例的蒸发器包括第一集流管，所述第一集流管的一端设有第 一制冷剂口； 第二集流管， 所述第二集流管的一端设有第二制冷剂口； 换热管， 所述换热管 分别连接在第一和第二集流管之间以连通第一和第二集流管； 翅片， 所述翅片分别设置相邻 的换热管之间； 和除霜管， 所述除霜管的第一端连接到所述第一和第二集流管中的一个集流 管上以与所述一个集流管内部连通，其中所述除霜管的第一端与所述一个集流管相连的位置 偏离所述一个集流管的所述一端预定距离。
才艮据本发明实施例的蒸发器， 由于在第一集流管或第二集流管上连接了除霜管， 因此在 需要对蒸发器进行除霜时， 制冷剂从除霜管进入到第一集流管或第二集流管，从而提高了除 霜速度， 降低了除霜时间， 制冷系统的效能提高。
另外， 根据本发明上述实施例的蒸发器还可以具有如下附加技术特征：
所述除霜管的第一端连接到所述一个集流管的中间部位。
所述除霜管的轴线与换热管的轴线之间的夹角在 45度 -315度之间。
所述预定距离大于 100毫米。 所述一个集流管内设有具有敞开端和封闭端的制冷剂导引管，所述制冷剂导引管上形成 有多个开口， 其中所述制冷剂导引管的开口端从所述一个集流管的制冷剂口伸出。
根据本发明第二方面实施例的制冷系统， 包括： 压缩机； 四通阀， 所述四通阀具有第一 至第四阀口， 其中所述压缩机与四通阀的第一和第三阀口相连； 冷凝器， 所述冷凝器的入口 与四通阀的第二阀口相连； 节流机构， 所述节流机构的入口与冷凝器的出口相连； 蒸发器， 所述蒸发器连接在四通阀的第四阀口与节流机构的出口之间，其中所述蒸发器为根据本发明 第一方面实施例所述的蒸发器； 和制冷剂切换单元， 所述制冷切换单元与蒸发器相连并且连 接在四通阀的第四阀口与节流机构的出口之间，用于在制冷系统处于正常运行模式时使制冷 剂从四通阀通过节流机构进入第一集流管内且从第二集流管流出返回到四通阀、且在制冷系 统处于除霜运行模式时使制冷剂从四通阀通过除霜管进入所述一个集流管内且从蒸发器的 另一个集流管流出通过节流机构返回到四通阀。
所述制冷剂切换单元包括第一至第四阀，其中所述第一阀连接在四通阀的第四阀口与蒸 发器的第二集流管的第二制冷剂口之间，第二阀的一侧连接在第一阀与第二集流管的制冷剂 口之间而第二阀的另一侧与节流机构相连，第三阀的一侧连接在第二阀的另一侧与节流机构 之间而第三阀的另一侧与蒸发器的第一集流管的第一制冷剂口相连，以及第四阀连接在四通 阀的第四阀口与除霜管的第二端之间。
所述除霜管的第一端与第一集流管或第二集流管相连。
所述除霜管的第一端与第二集流管相连， 且所述制冷剂切换单元包括第一阀和第四阀， 其中所述第一阀连接在四通阀的第四阀口与蒸发器的第二集流管的第二制冷剂口之间，第四 阀连接在四通阀的第四阀口与除霜管的第二端之间。
所述除霜管的第一端与第二集流管相连， 所述除霜管的第二端与四通阀的第四阀口相 连， 其中所述制冷剂切换单元包括第一阀， 所述第一阀连接在四通阀的第四阀口与蒸发器的 第二集流管的第二制冷剂口之间。
本发明的附加方面和优点将在下面的描述中部分给出， 部分将从下面的描述中变得明 显， 或通过本发明的实践了解到。 附图说明
本发明的上述和 /或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和 容易理解， 其中：
图 1是根据本发明一个实施例的蒸发器的平面示意图；
图 2是图 1所示蒸发器的侧视示意图；
图 3是根据本发明另一实施例的蒸发器的平面示意图；
图 4是图 3所示蒸发器的侧视示意图；
图 5是根据本发明再一实施例的蒸发器的平面示意图；
图 6是图 5所示蒸发器的侧视示意图；
图 7是根据本发明一个实施例的制冷系统的示意图； 图 8是根据本发明另一实施例的制冷系统的示意图；
图 9是才 居本发明再一实施例的制冷系统的示意图； 和
图 10是根据本发明又一实施例的制冷系统的示意图。 具体实施方式
下面详细描述本发明的实施例， 所述实施例的示例在附图中示出， 其中自始至终相同或 类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的 实施例是示例性的， 仅用于解释本发明， 而不能理解为对本发明的限制。
在本发明的描述中， 术语 "纵向，，、 "横向"、 "上，，、 "下，，、 "前，，、 "后，，、 "左，，、 "右，，、 "竖直"、 "水平"、 "顶"、 "底" 等指示的方位或位置关系为基于附图所示的方位或位置关 系， 仅是为了便于描述本发明而不是要求本发明必须以特定的方位构造和操作， 因此不能理 解为对本发明的限制。
在本发明的描述中， 除非另有规定和限定， 需要说明的是， 术语 "安装"、 "相连"、 "连 接，， 应做广义理解， 例如， 可以是机械连接或电连接， 也可以是两个元件内部的连通， 可以 是直接相连， 也可以通过中间媒介间接相连， 对于本领域的普通技术人员而言， 可以根据具 体情况理解上述术语的具体含义。 此外， 术语 "第一，，、 "第二，， 仅用于描述目的， 而不能理 解为指示或暗示相对重要性。
下面参考附图描述根据本发明实施例的蒸发器 500。
才艮据本发明实施例的蒸发器 500包括第一集流管 501 , 第二集流管 502 , 换热管 503 , 翅 片 504 , 和除霜管 505。
第一集流管 501的一端设有第一制冷剂口 5010 ,第二集流管 502的一端设有第二制冷剂 口 5020。
为了方便， 在下面的描述中， 第一集流管 501作为蒸发器 500的入口集流管， 第二集流 管 502作为蒸发器 500的出口集流管， 第一制冷剂口 5010为蒸发器 500的制冷剂入口， 第 二制冷剂口 5020为蒸发器 500的制冷剂出口， 且第一制冷剂口 5010和第二制冷剂口 5020 为制冷剂入口管和制冷剂出口管的形式。
换热管 503 , 例如扁管， 分别连接在入口集流管 501和出口集流管 502之间以连通入口 集流管 501和出口集流管 502。
翅片 504分别设置相邻的换热管 503之间。除霜管 505的一端连接到入口集流管 501和 出口集流管 502中的一个集流管上以与所述一个集流管内部连通，其中除霜管 505的第一端 与所述一个集流管相连的位置偏离所述一个集流管的形成有制冷剂口的所述一端预定距离。
下面参考图 1和图 1描述才 居本发明一个实施例的蒸发器 500。 如图 1和 1所示， 除霜 管 505与入口集流管 501相连， 更具体而言， 除霜管 505的一端连接在入口集流管 501的大 体中间部位。除霜管 505的轴线与换热管 503的轴线（即换热管的长度方向）成大体 90度角。
图 3和图 4示出了才 居本发明另一实施例的蒸发器 500 , 其中除霜管 505的一端与入口 集流管 501 的大体中间部位相连。 除霜管 505 的轴线与换热管 503的轴线之间的夹角 α在 45-315。 的范围内。
图 5和图 6示出了根据本发明再一实施例的蒸发器 500 , 其中入口集流管 501上连接了 两个除霜管 505 ,两个除霜管 505沿入口集流管 501的长度方向间隔开，其中左侧除霜管 505 距离入口集流管 501左端的距离以及右侧除霜管 505距离入口集流管 501右端的距离均大于 100毫米， 由此能够进一步提高除霜的效果。 需要理解的是， 除霜管 505的数量并不限于此， 可以根据具体应用设置任何合适数量的除霜管 505。
在图 5和图 6所示的实施例中， 入口集流管 501内插入有入口制冷剂导管 506 , 入口制 冷剂导管 506具有敞开端和封闭端且沿长度方向形成有多个开口， 例如多个非圆形的狭槽， 制冷剂导引管 506的开口端从入口集流管 501的制冷剂入口伸出， 更具体而言， 制冷剂导引 管 506的开口端与入口管 5010相连。
可选地， 如图 6所示， 出口集流管 502内也可以插入有出口制冷剂导管 507 , 出口制冷 剂导管 507具有敞开端和封闭端且沿长度方向形成有多个开口， 例如多个非圆形的狭槽， 制 冷剂导引管 507的开口端从出口集流管 502的制冷剂出口伸出， 更具体而言， 制冷剂导引管 507的开口端与出口管 5020相连。
在本发明的一些实施例中， 除霜管 505可以与出口集流管 502相连。 同理， 除霜管 505 与出口集流管 502的连接位置偏离出口集流管 502的一端，例如出口集流管 502的大体中间 部位。
才艮据本发明实施例的蒸发器 500 , 由于在入口集流管 501或出口集流管 502上连接了除 霜管 505 ,因此在需要对蒸发器 500进行除霜时，制冷剂从除霜管 505进入到入口集流管 501 或出口集流管 502 , 从而提高了除霜速度， 降低了除霜时间， 制冷系统的效能提高。
下面参考图 7描述根据本发明实施例的制冷系统。
根据本发明实施例的制冷剂系统（例如热泵系统） 包括压缩机 100 , 四通阀 200 , 冷凝 器 300 , 节流机构 400 , 蒸发器 500 , 和制冷剂切换单元。
更具体而言， 四通阀 200具有第一至第四阀口（在图 7中， 分别为左侧阀口、右侧阀口， 上侧阀口和下侧阀口）， 其中压缩机 100与四通阀 200的第一阀 A口和第三阀 C口相连。 冷 凝器 300的入口与四通阀 200的第二阀 B口相连。 节流机构 400 (例如膨胀阀） 的入口与冷 凝器 300的出口相连。蒸发器 500连接在四通阀 200的第四阀口与节流机构 400的出口之间。
制冷切换单元与蒸发器 500相连并且连接在四通阀 200的第四阀口与节流机构 400的出 口之间，用于在制冷系统处于正常运行模式时使制冷剂从四通阀 200通过节流机构 400进入 入口集流管 501内且从出口集流管 502流出返回到四通阀 200、 且在制冷系统处于除霜运行 模式时使制冷剂从四通阀 200通过除霜管 505进入所述一个集流管内且从蒸发器 500的另一 个集流管流出通过节流机构 400返回到四通阀 200。
例如， 当制冷系统处于制热模式时， 室内单元用作冷凝器 300 , 风扇 F由电机 M驱动， 从而将冷凝器 300加热的热风吹送到室内进行制热。
如图 7所示， 制冷剂切换单元包括第一阀 A , 第二阀 B, 第三阀 C和第四阀 D。 第一阀 A 连接在四通阀 200的第四阀口与蒸发器 500的出口集流管 502的制冷剂出口 5020之间， 第 二阀 B的一侧连接在第一阀 A与出口集流管 502的制冷剂出口 5020之间而第二阀 B的另一 侧与节流机构 400相连，第三阀 C的一侧连接在第二阀 B的另一侧与节流机构 400之间而第 三阀 C的另一侧与蒸发器 500的入口集流管 501的制冷剂入口 5010相连， 除霜管 505的第 一端与入口集流管 501 的大体中部相连， 第四阀 D连接在四通阀 200的第四阀口与除霜管 505的第二端之间。
下面参考图 7描述根据本发明实施例的制冷系统的正常运行模式状态和除霜运行模式状态。 如图 7所示， 除霜管 505的第一端与入口集流管 501相连， 在制冷系统处于正常运行模 式时， 第一阀 A和第三阀 C打开且第二阀 B和第四阀 D关闭， 从而制冷剂从压缩机 100通过 四通阀 200的第二阀 B口进入四通阀 200, 然后通过四通阀 200的第三阀 C口沿实线箭头 A 进入到冷凝器 300内， 接着， 沿实线箭头 A进入节流机构 400, 由于第二阀 B关闭， 第三阀 C打开， 因此制冷剂从节流机构 400进入蒸发器 500的入口集流管 501的制冷剂入口 5010 管 5010进入到入口集流管 501内，例如可以通过入口制冷剂导管 506分配到入口集流管 501 内， 由此可以消除气液分层。 制冷剂从入口集流管 501进入到各个换热管 503 , 与外界换热 后进入蒸发器 500的出口集流管 502内。 由于第二阀 B和第四阀 D关闭， 且第一阀 A打开， 因此从出口集流管 502 (例如从制冷剂出口管 5020 ) 出来的制冷剂通过第一阀 A和四通阀 200的第四阀口返回到四通阀 200, 然后从四通阀 200的第一阀 A口进入压缩机 100。 由此， 实现了制冷剂的循环。
当需要除霜时， 制冷系统进行除霜运行模式。 此时， 第一阀 A和第三阀 C关闭， 第二和 第四阀 D打开，制冷剂从四通阀 200的第四阀口沿虚线箭头 N通过第四阀 D进入除霜管 505 , 制冷剂从除霜管 505进入蒸发器 500的入口集流管 501 , 例如从入口集流管 501的大体中间 位置进入入口集流管 501内， 从而对蒸发器 500进行除霜， 并且除霜速度加快。
制冷剂沿着换热管 503流入到出口集流管 502 ,然后从制冷剂出口 5020管出来。 由于第 一阀 A和第三阀 C关闭， 因此从出口集流管 502出来的制冷剂只能通过节流机构 400、 冷凝 器 300和四通阀 200的第三阀 C口返回到四通阀 200内。
因此， 根据本发明实施例的制冷剂系统， 在需要除霜时， 气态制冷剂从除霜管 505进入 到入口集流管 501 , 避开了入口制冷剂导管 506 , 流动阻力大大降低， 加大了制冷剂流量， 提高了除霜速度。另一方面，对于霜在入口集流管 501的制冷剂入口 5010附近积累较多（如 R407C ) 的制冷系统， 高温气态制冷剂从入口集流管 501流入， 因此可直接加快霜的融化， 而且更有助于除霜的融水蒸发。 因此， 通过除霜管 505 , 制冷系统的除霜过程可大大加快， 缩短了除霜时间， 而且除霜效果也可加强， 减少了室内温度的波动， 提高了舒适度。 而且， 制冷剂无需在蒸发器 500内逆循环。
下面参考图 8描述根据本发明另一实施例的制冷系统。
在图 8所示的实施例中， 除霜管 505的第一端与出口集流管 502相连。 在制冷系统处于 正常运行模式时， 第一阀 A和第三阀 C打开且第二阀 B和第四阀 D关闭。在制冷系统处于除 霜运行模式时，第一阀 A和第二阀 B关闭且第三阀 C和第四阀 D打开。换言之，在此情况下， 第三阀 C为常开， 第二阀 B常闭。 在除霜运行模式下， 制冷剂从除霜管 505进入出口集流管 502 , 然后通过换热管 503进入入口集流管 501 , 并通过节流机构 400和冷凝器 300返回到 四通阀 200。 制冷剂系统在正常运行模式和除霜模式下的其他操作这里不再详细描述。
才艮据图 8所示的制冷剂系统， 除霜管 505与出口集流管 502相连， 因此对于结霜在制热 运行时出口较多的情况（如 R410A、 R22系统）， 除霜管 505设置在出口集流管 502上， 有助 于上部结霜的快速融化。
下面参考图 9描述 # ^据本发明再一实施例的制冷系统。
在图 9所示的实施例中， 除霜管 505的第一端与出口集流管 502相连， 且制冷剂切换单 元包括第一阀 A和第四阀 D, 其中第一阀 A连接在四通阀 200的第四阀口与蒸发器 500的出 口集流管 502的制冷剂出口 5020之间，第四阀 D连接在四通阀 200的第四阀口与除霜管 505 的第二端之间。
制冷系统处于正常运行模式时第一阀 A打开且第四阀 D关闭，在制冷系统处于除霜运行 模式时第一阀 A关闭且第四阀 D打开。图 9所示的实施例与图 8所示的实施例的区别在于省 去了常闭的第二阀 B和常开的第三阀 C , 并且第二阀 B的位置断开， 第三阀 C的位置用管路 替代， 因此降低了成本和控制复杂程度。 图 9所示制冷系统的运行与图 8所示的制冷系统类 似， 这里不再详细描述。
下面参考图 10描述 据本发明又一实施例的制冷系统。
在图 10所示的实施例中， 除霜管 505的第一端与出口集流管 502相连， 除霜管 505的 第二端与四通阀 200的第四阀口相连， 制冷剂切换单元包括第一阀 A, 第一阀 A连接在四通 阀 200的第四阀口与蒸发器 500的出口集流管 502的制冷剂出口 5020之间。
当制冷系统处于正常运行模式时， 第一阀 A打开， 制冷剂从出口集流管 502通过第一阀 A返回到四通阀 200 , 当然， 一部分少量的制冷剂从除霜管 505返回到四通阀 200。
当制冷系统处于除霜运行模式时， 第一阀 A关闭， 制冷剂从除霜管 505进入出口集流管 502 , 然后经过换热管 503、入口集流管 501、 节流机构 400和冷凝器 300返回到四通阀 200。
图 10所示的制冷系统仅用了一个阀， 因此结构更加筒单， 成本更低， 控制根据容易。 在上面描述的实施例中， 制冷系统的蒸发器 500仅具有一个除霜管 505。 但是， 需要说 明的是， 根据需要， 可以设置任何合适数量的除霜管 505 , 并且除霜管 505可以同时与入口 集流管 501和出口集流管 502相连， 当然， 与入口集流管 501和出口集流管 502相连的除霜 管 505可以具有各自的制冷剂切换单元。
在本说明书的描述中，参考术语"一个实施例"、 "一些实施例"、 "示例"、 "具体示例"、 或 "一些示例" 等的描述意指结合该实施例或示例描述的具体特征、 结构、 材料或者特点包 含于本发明的至少一个实施例或示例中。在本说明书中， 对上述术语的示意性表述不一定指 的是相同的实施例或示例。 而且， 描述的具体特征、 结构、 材料或者特点可以在任何的一个 或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例， 本领域的普通技术人员可以理解： 在不脱离本 发明的原理和宗旨的情况下可以对这些实施例进行多种变化、 修改、 替换和变型， 本发明的 范围由权利要求及其等同物限定。

Claims

权利要求书
1、 一种蒸发器， 其特征在于， 包括：
第一集流管， 所述第一集流管的一端设有第一制冷剂口；
第二集流管， 所述第二集流管的一端设有第二制冷剂口；
换热管， 所述换热管分别连接在第一和第二集流管之间以连通第一和第二集流管； 翅片， 所述翅片分别设置相邻的换热管之间； 和
除霜管，所述除霜管的第一端连接到所述第一和第二集流管中的一个集流管上以与所述 一个集流管内部连通，其中所述除霜管的第一端与所述一个集流管相连的位置偏离所述一个 集流管的所述一端预定距离。
2、 根据权利要求 1所述的蒸发器， 其特征在于， 所述除霜管的第一端连接到所述一个 集流管的中间部位。
3、 根据权利要求 1所述的蒸发器， 其特征在于， 所述除霜管的轴线与换热管的轴线之 间的夹角在 45度 -315度之间。
4、 根据权利要求 1所述的蒸发器， 其特征在于， 所述预定距离大于 100毫米。
5、 根据权利要求 1所述的蒸发器， 其特征在于， 所述一个集流管内设有具有敞开端和 封闭端的制冷剂导引管， 所述制冷剂导引管上形成有多个开口， 其中所述制冷剂导引管的开 口端从所述一个集流管的制冷剂口伸出。
6、 一种制冷系统， 其特征在于， 包括：
压缩机；
四通阀， 所述四通阀具有第一至第四阀口， 其中所述压缩机与四通阀的第一和第三阀口 相连；
冷凝器， 所述冷凝器的入口与四通阀的第二阀口相连；
节流机构， 所述节流机构的入口与冷凝器的出口相连；
蒸发器， 所述蒸发器连接在四通阀的第四阀口与节流机构的出口之间， 其中所述蒸发器 为根据权利要求 1-5中任一项所述的蒸发器； 和
制冷剂切换单元，所述制冷切换单元与蒸发器相连并且连接在四通阀的第四阀口与节流 机构的出口之间，用于在制冷系统处于正常运行模式时使制冷剂从四通阀通过节流机构进入 第一集流管内且从第二集流管流出返回到四通阀，而在制冷系统处于除霜运行模式时使制冷 剂从四通阀通过除霜管进入所述一个集流管内且从蒸发器的另一个集流管流出通过节流机 构返回到四通阀。
7、 根据权利要求 6所述的制冷系统， 其特征在于， 所述制冷剂切换单元包括第一至第 四阀， 其中所述第一阀连接在四通阀的第四阀口与蒸发器的第二集流管的第二制冷剂口之 间，第二阀的一侧连接在第一阀与第二集流管的制冷剂口之间而第二阀的另一侧与节流机构 相连，第三阀的一侧连接在第二阀的另一侧与节流机构之间而第三阀的另一侧与蒸发器的第 一集流管的第一制冷剂口相连， 以及第四阀连接在四通阀的第四阀口与除霜管的第二端之 间。
8、 根据权利要求 7所述的制冷系统， 其特征在于， 所述除霜管的第一端与第一集流管 或第二集流管相连。
9、 根据权利要求 6所述的制冷系统， 其特征在于， 所述除霜管的第一端与第二集流管 相连， 且所述制冷剂切换单元包括第一阀和第四阀， 其中所述第一阀连接在四通阀的第四阀 口与蒸发器的第二集流管的第二制冷剂口之间，第四阀连接在四通阀的第四阀口与除霜管的 第二端之间。
10、 根据权利要求 6所述的制冷系统， 其特征在于， 所述除霜管的第一端与第二集流管 相连，所述除霜管的第二端与四通阀的第四阀口相连，其中所述制冷剂切换单元包括第一阀， 所述第一阀连接在四通阀的第四阀口与蒸发器的第二集流管的第二制冷剂口之间。
PCT/CN2010/080259 2010-11-04 2010-12-24 蒸发器和具有该蒸发器的制冷系统 WO2012058844A1 (zh)

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