EP3306234B1 - Évaporateur et circuit réfrigérant - Google Patents

Évaporateur et circuit réfrigérant Download PDF

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Publication number
EP3306234B1
EP3306234B1 EP17194601.5A EP17194601A EP3306234B1 EP 3306234 B1 EP3306234 B1 EP 3306234B1 EP 17194601 A EP17194601 A EP 17194601A EP 3306234 B1 EP3306234 B1 EP 3306234B1
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EP
European Patent Office
Prior art keywords
pipe
refrigerant
header
heat transfer
evaporator
Prior art date
Legal status (The legal status 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 status listed.)
Not-in-force
Application number
EP17194601.5A
Other languages
German (de)
English (en)
Other versions
EP3306234A1 (fr
Inventor
Takachika MORI
Masashi Maeno
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
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 Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3306234A1 publication Critical patent/EP3306234A1/fr
Application granted granted Critical
Publication of EP3306234B1 publication Critical patent/EP3306234B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • 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
    • F25B41/37—Capillary tubes
    • 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
    • F28F9/0243—Header boxes having a circular cross-section
    • 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
    • F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
    • 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
    • F25B2339/02—Details of 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/06—Derivation channels, e.g. bypass

Definitions

  • the present invention relates to an evaporator and a refrigerant circuit.
  • evaporators that constitute refrigeration systems or air-conditioning systems
  • heat exchange is performed between a refrigerant flowing through a heat transfer pipe and air around the heat transfer pipe.
  • evaporators for example, there is a structure including a plurality of heat transfer pipes disposed at intervals in a vertical direction.
  • the refrigerant which has flowed from an upstream side, branches and flows into a plurality of heat transfer pipes via a header on an evaporator inlet side.
  • a termination end of each heat transfer pipe is connected to a header on an evaporator outlet side that extends in the vertical direction.
  • the refrigerant that has exchanged heat in the heat transfer pipes flows into and joins the header on the evaporator outlet side from the respective heat transfer pipes.
  • the header on the evaporator outlet side is connected to a pipe provided downstream in the flow direction of the refrigerant.
  • the refrigerant is sent to an accumulator or a compressor through this pipe.
  • the lubricating oil flows with the refrigerant.
  • the lubricating oil circulates through the refrigerant circuit with the refrigerant and lubricates, for example, bearings within the compressor.
  • This lubricating oil may be accumulated with the liquid refrigerant at a bottom part of the header.
  • a low-pressure space is locally formed around first end (ejector part) of the oil return pipe that opens into the refrigerant return pipe when a gas refrigerant flows. Accordingly, the lubricating oil accumulated at the bottom part of the header tube is pumped up and sent to the compressor with the gas refrigerant.
  • PTL 2 relates to an air conditioner and evaporator inlet header distributor therefor.
  • Document US 2014/123696 A1 discloses an evaporator according to the preamble of claim 1.
  • the invention provides an evaporator and a refrigerant circuit capable of suppressing the accumulation of lubricating oil within a header while suppressing the outflow of a refrigerant in a configuration including a plurality of heat transfer pipes.
  • An evaporator related to a first aspect of the invention includes:
  • an installation space for the bypass pipe can be suppressed to be small while securing the length of the bypass pipe.
  • the refrigerant can be sent from the lower end through the bypass pipe to the refrigerant pipe without making the lubricating oil at the lower end of the header flow to the upper end. This can suppress the accumulation of the lubricating oil at the lower end of the header.
  • the bypass pipe is longer than the length of the flow passage passing through the upper end of the header, the flow rate of the refrigerant that flows through the bypass pipe is suppressed more than the flow rate of the refrigerant that flows through the upper end of the header. Hence, a situation in which the liquid refrigerant within the header flows out excessively via the bypass pipe can be suppressed.
  • the bypass pipe may have a flow passage cross-sectional area smaller than a flow passage cross-sectional area at the lower end of the header.
  • the flow rate of the refrigerant that passes through the bypass pipe can be suppressed more than the flow rate of the refrigerant that flows from the lower end of the header to the upper end. Hence, a situation in which the liquid refrigerant within the header flows out excessively via the bypass pipe can be effectively suppressed.
  • the bypass pipe may further include a valve member that controls a flow of the refrigerant within the bypass pipe.
  • the amounts and timings of the lubricating oil and the liquid phase (liquid refrigerant) of the refrigerant, which are sent to the refrigerant pipe via the bypass pipe, can be adjusted.
  • the evaporator may further include a controller that controls opening and closing of the valve member, wherein controller may control the opening and closing of the valve member on the basis of an elapsed time from starting of a compressor provided downstream of the refrigerant pipe, or the degree of superheat of the refrigerant.
  • the valve body can be closed to cut off the flow of the bypass pipe such that the liquid refrigerant does not reach the compressor through the bypass pipe.
  • the controller may close the valve member to cut off the flow of the bypass pipe at the starting of the compressor, and may open the valve member to open the flow of the bypass pipe after elapse of a predetermined given time passing since the starting the compressor or in a case where the degree of superheat of the refrigerant becomes equal to or larger than a predetermined reference value.
  • valve body can be closed to cut off the bypass pipe such that the liquid refrigerant does not reach the compressor through the bypass pipe.
  • an evaporator related to a sixth aspect of the invention includes a plurality of heat transfer pipes that are provided at intervals in a vertical direction and allow a refrigerant to flow therethrough toward first ends; and a header that extends in the vertical direction, has the first ends of the plurality of heat transfer pipes connected thereto, and allows the refrigerant to flow from an upper end toward a lower end to which a refrigerant pipe is connected.
  • the header by configuring the header such that the refrigerant flows from the upper end toward the lower end to which the refrigerant pipe is connected, in the header, the refrigerant flows downward from above that is the same as the gravitational direction. Additionally, in the header, the refrigerants flowing in from the plurality of heat transfer pipes join together at the lower end of the header. Hence, the flow speed of the refrigerant increases at the lower end of the header. Accordingly, the lubricating oil accumulated at the lower end of the header due to gravity smoothly flows from the lower end of the header through the refrigerant pipe with the flow of the refrigerant. As a result, the accumulation of the lubricating oil at the lower end of the header can be suppressed.
  • a refrigerant circuit related to a seventh aspect of the invention includes the evaporator of any one of the first to sixth aspects.
  • the configuration including the plurality of heat transfer pipes it is possible to suppress the accumulation of the lubricating oil within the header while suppressing that the refrigerant flows in.
  • Fig. 1 is schematic view illustrating the configuration of an evaporator and a refrigerant circuit related to a first embodiment of the invention.
  • a refrigerant circuit 100A of the present embodiment is provided at an outdoor unit (not illustrated) of an air-conditioning system 1.
  • the air-conditioning system 1 includes the refrigerant circuit 100A.
  • the refrigerant circuit 100A has a heat exchanger (evaporator) 10A, an inlet-side pipe 2, an accumulator 3, an outlet-side pipe (refrigerant pipe) 4, and a compressor 5.
  • the heat exchanger 10A functions as an evaporator during a heating operation.
  • the inlet-side pipe 2 used as a flow passage for a refrigerant sent from an indoor unit (not illustrated) is connected to an inlet side that is an upstream side in a flow direction of the refrigerant.
  • the outlet-side pipe (refrigerant pipe) 4 for sending the refrigerant to the compressor 5 is connected to an outlet side that is a downstream side in the flow direction of the refrigerant via the accumulator 3.
  • the heat exchanger 10A includes a plurality of (three in the present embodiment) heat transfer pipes 11, a distributor 12, a plurality of capillary tubes 13, a header 20A, and an oil return pipe (bypass pipe) 30.
  • the plurality of heat transfer pipes 11 are connected to the inlet-side pipe 2 via the distributor 12 and the plurality of capillary tubes 13, respectively.
  • the flow passage for the refrigerant that flows through the inlet-side pipe 2 branches to the plurality of heat transfer pipes 11 via the distributor 12 and the plurality of capillary tubes 13. Accordingly, the refrigerant flows through the plurality of heat transfer pipes 11 to exchange heat.
  • the plurality of heat transfer pipes 11 are provided side by side at intervals in a vertical direction in the heat exchanger 10A.
  • Each heat transfer pipe 11 has a rising section 111, a lower pipe section 112, a bent section 113, and an upper pipe section 114.
  • the heat transfer pipe 11 is a pipe in which the rising section 111, the lower pipe section 112, the bent section 113, and the upper pipe section 114 are integrally formed.
  • the rising section 111 extends upward in the vertical direction from the distributor 12 side. An end (an end of the heat transfer pipe 11 on the other side) of the rising section 111 is connected to each capillary tube 13.
  • the lower pipe section 112 is continuous with the rising section 111.
  • the lower pipe section 112 horizontally extends in a lateral direction within the heat exchanger 10A.
  • the bent section 113 is continuous with the lower pipe section 112.
  • the bent section 113 is bent in a U-shape.
  • the upper pipe section 114 is continuous with the bent section 113.
  • the upper pipe section 114 horizontally extends in the lateral direction.
  • the upper pipe section 114 is located to be spaced apart upward in the vertical direction with respect to the lower pipe section 112.
  • a termination end (first end of the heat transfer pipe 11) 115 of the upper pipe section 114 is connected to the header 20A.
  • the heat exchanger 10A of the present embodiment includes a first heat transfer pipe 11A, a second heat transfer pipe 11B, and a third heat transfer pipe 11C in order from below in the vertical direction, as the plurality of heat transfer pipes 11.
  • the first heat transfer pipe 11A, the second heat transfer pipe 11B, and the third heat transfer pipe 11C are disposed to be spaced apart from each other in the vertical direction.
  • the first heat transfer pipe 11A, the second heat transfer pipe 11B, and the third heat transfer pipe 11C are pipes having the same pipe diameter d1.
  • the capillary tube 13 is provided between the heat transfer pipe 11 and the distributor 12.
  • the capillary tube 13 has a flow passage cross-sectional area smaller than the heat transfer pipe 11 and is formed in a spiral shape.
  • a first capillary tube 13A that connects the first heat transfer pipe 11A and the distributor 12 together
  • a second capillary tube 13B that connects the second heat transfer pipe 11B and the distributor 12 together
  • a third capillary tube 13C that connects the third heat transfer pipe 11C and the distributor 12 together are provided as the plurality of capillary tubes 13.
  • the header 20A is disposed laterally of the plurality of heat transfer pipes 11.
  • the header 20A extends upward from below in the vertical direction.
  • the refrigerant flows through the header 20A from a lower end 20s toward an upper end 20t in the vertical direction.
  • the termination ends 115 of the plurality of heat transfer pipes 11 spaced apart from each other in the vertical direction are connected In the header 20A.
  • the upper end 20t of the header 20A is connected to an outlet-side pipe 4.
  • the header 20A of the present embodiment is a pipe having a constant pipe diameter in the vertical direction.
  • the header 20A has a pipe diameter D10 equal to or larger than a pipe diameter d1 of the first heat transfer pipe 11A (d1 ⁇ D10).
  • the outlet-side pipe 4 has first end joined to the upper end 20t of the header 20A.
  • the outlet-side pipe 4 has a return part 22 that is curved in a U-shape.
  • the outlet-side pipe 4 is connected to the accumulator 3, which recovers the liquid phase (liquid refrigerant) of the refrigerant, at the other end (second end) that is a side where the outlet-side pipe 4 is not connected to the header 20A.
  • the oil return pipe 30 allows the lower end 20s of the header 20A and the outlet-side pipe 4 to communicate with each other.
  • the oil return pipe 30 is connected to the lower end 20s of the header 20A, and a portion that is downstream of the return part 22 of the outlet-side pipe 4 and upstream of a location connected to the accumulator 3.
  • the oil return pipe 30 has a flow passage cross-sectional area smaller than a flow passage cross-sectional area at the lower end 20s of the header 20A.
  • the oil return pipe 30 of the present embodiment has a pipe diameter d31 smaller than the pipe diameter d1 of the first heat transfer pipe 11A at the lowermost stage and the pipe diameter D10 of the header 20A.
  • the length of the oil return pipe 30 is made longer than the length of a flow passage that leads from the lower end 20s of the header 20A through the upper end 20t thereof to a site to which the oil return pipe 30 of the outlet-side pipe 4 is joined. That is, it is more preferable that the oil return pipe 30 has a pipe length that is longer than a flow passage length that leads from the lower end 20s of the header 20A through the upper end 20t thereof to a portion to which a termination end 30e of the oil return pipe 30 of the outlet-side pipe 4 is connected. For this reason, it is preferable that the oil return pipe 30 is formed by a capillary tube having a spirally wound spiral part 30r to secure a length.
  • the refrigerant is sent through the inlet-side pipe 2 from the indoor unit side when performing a heating operation.
  • lubricating oil for lubricating a bearing and the like of the compressor 5 is mixedly present in the refrigerant.
  • the refrigerant in which the lubricating oil is mixedly present branches and flows from the inlet-side pipe 2 via the distributor 12 to the first capillary tube 13A, the second capillary tube 13B, and the third capillary tube 13C, respectively.
  • the refrigerant that has flowed into the first capillary tube 13A flows to the first heat transfer pipe 11A in a gas-liquid mixed two-phase state.
  • the refrigerant that has flowed into the second capillary tube 13B flows into the second heat transfer pipe 11B
  • the refrigerant that has flowed into the third capillary tube 13C flows into the third heat transfer pipe 11C.
  • the refrigerant exchanges heat with surrounding air and thereby at least a portion thereof is gasified (evaporated).
  • the refrigerant that has exchanged heat by flowing into the first heat transfer pipe 11A, the second heat transfer pipe 11B, and the third heat transfer pipe 11C flows into the header 20A from the respective termination ends 115, and flows through the header 20A toward the upper end 20t.
  • the refrigerant that has flowed into the header 20A from the third heat transfer pipe 11C at an uppermost stage joins the refrigerant that has flowed in from the first heat transfer pipe 11A and the second heat transfer pipe 11B.
  • the refrigerant that has joined within the header 20A in this way is sent from the upper end 20t to the outlet-side pipe 4. Thereafter, the refrigerant is sequentially sent to the accumulator 3 and the compressor 5 through the return part 22.
  • the lubricating oil accumulated at the lower end 20s of the header 20A due to gravity is bypassed to the middle of the outlet-side pipe 4 downstream of the return part 22 through the oil return pipe 30 without passing through the upper end 20t of the header 20A.
  • the lubricating oil flows from the lower end 20s side toward the outlet-side pipe 4 side due to a pressure difference between the header 20A side and the accumulator 3.
  • the lubricating oil at the lower end 20s of the header 20A can be sent to the outlet-side pipe 4 through the oil return pipe 30.
  • the lubricating oil is directly discharged from the lower end 20s via the oil return pipe 30 to the outlet-side pipe 4 without passing through the upper end 20t of the header 20A. This can suppress the accumulation of the lubricating oil at the lower end 20s of the header 20A.
  • the oil return pipe 30 is formed to be longer than the flow passage length that leads from the lower end 20s of the header 20A through the upper end 20t thereof to the portion to which the termination end 30e of the oil return pipe 30 of the outlet-side pipe 4 is connected. For that reason, the flow rates of the refrigerant and the lubricating oil that flow through the oil return pipe 30 are suppressed more than the flow rates of the refrigerant and the lubricating oil that flow through the upper end 20t of the header. As a result, a situation in which a liquid phase (liquid refrigerant) of a lot of the refrigerant and the lubricating oil flows into the accumulator 3 through the oil return pipe 30 is suppressed.
  • the oil return pipe 30 is formed with the pipe diameter d31 smaller than the pipe diameter d1 of the first heat transfer pipe 11A at the lowermost stage and the pipe diameter D10 of the header 20A. That is, the oil return pipe 30 is formed with the flow passage cross-sectional area smaller than the flow passage cross-sectional area at the lower end 20s of the header 20A. For that reason, the flow rates of the liquid refrigerant and the lubricating oil that pass through the oil return pipe 30 can be suppressed to be lower than the flow rates of the liquid refrigerant and the lubricating oil that flow from the lower end 20s of the header 20A toward the upper end 20t. Hence, the situation in which the liquid refrigerant within the header 20A flows out excessively via the oil return pipe 30 can be effectively suppressed.
  • the oil return pipe 30 has the spirally wound spiral part 30r. For that reason, an installation space for the oil return pipe 30 can be suppressed to be small while securing the length of the oil return pipe 30.
  • Fig. 2 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to the second embodiment of the invention.
  • the oil return pipe 30 is provided with a two-way valve (valve member) 32 that controls the flow of the refrigerant and the lubricating oil within the oil return pipe 30.
  • a two-way valve valve member 32 that controls the flow of the refrigerant and the lubricating oil within the oil return pipe 30.
  • bypassing to the outlet-side pipe 4 for the lubricating oil and the liquid phase (liquid refrigerant) of the refrigerant can be switched by the two-way valve 32 via the oil return pipe 30. For that reason, the amounts and timings of the lubricating oil and the liquid phase (liquid refrigerant) of the refrigerant, which are sent to the outlet-side pipe 4 via the oil return pipe 30, can be adjusted.
  • Fig. 3 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to the third embodiment of the invention.
  • Fig. 4 is a view illustrating the flow of opening-and-closing control of the two-way valve by the controller related to the third embodiment of the invention.
  • a heat exchanger 10C of the third embodiment further includes a controller 33 that controls the opening and closing of the two-way valve 32.
  • the controller 33 controls the opening and closing of the two-way valve 32 on the basis of the elapsed time since the starting of the compressor 5 provided on the downstream side of the outlet-side pipe 4, or the degree of superheat of the refrigerant. As illustrated in Fig. 4 , the controller 33 of the present embodiment is brought into a state where the two-way valve is closed at the starting of the compressor 5 (Step S101). Accordingly, the controller 33 cuts off the flow of the liquid refrigerant and the lubricating oil within the oil return pipe 30. The controller 33 causes the two-way valve to be opened after a predetermined given time has elapsed since the start of the compressor 5 (Step S102). Accordingly, the controller 33 opens the flow of the liquid refrigerant and the lubricating oil within the oil return pipe 30.
  • timing when the two-way valve 32 is opened may be after a given time has been elapsed since the starting of the compressor 5 as in the present embodiment by counting a preset given time by a timer, the invention is not limited to this. It is also possible to provide the header 20A or the like with a thermistor, a pressure sensor, or the like, thereby detecting the degree of superheat of the refrigerant, and determine the timing when the two-way valve 32 is opened in accordance with the detected degree of superheat.
  • the two-way valve 32 it is preferable to open the two-way valve 32 in a case where the degree of superheat of the refrigerant becomes equal to or higher than a predetermined reference value corresponding to the degree of superheat after the elapse of a given time since the starting.
  • the amounts and timings of the lubricating oil and the liquid phase (liquid refrigerant) of the refrigerant, which are sent to the outlet-side pipe 4 via the oil return pipe 30, can be adjusted in accordance with the starting of the compressor 5 by the controller 33.
  • the flow within the oil return pipe 30 can be cut off by closing the two-way valve 32.
  • Fig. 5 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to the fourth embodiment of the invention.
  • the flow passage cross-sectional area of a portion to which the first heat transfer pipe 11A located at the lowermost stage among the plurality of heat transfer pipes 11 is connected is smaller than the flow passage cross-sectional area at the upper end 20t.
  • the header 20D of the present embodiment is formed such that the flow passage cross-sectional area thereof becomes gradually larger as the number of heat transfer pipes 11 to be connected increases from the lower end 20s toward the upper end 20t in the vertical direction.
  • the header 20D is configured by joining a plurality of (three in the present embodiment) piping members 31 having different pipe diameters (external diameters) and internal diameters upward from below.
  • a first piping member 31A, a second piping member 31B, and a third piping member 31C are provided sequentially from the lower end 20s side in the vertical direction.
  • the header 20D of the present embodiment is formed by the first piping member 31A, the second piping member 31B, the third piping member 31C being joined together by joining means, such as brazing or welding.
  • the first piping member 31A is located at the lowermost position in the vertical direction.
  • the termination end 115 of the first heat transfer pipe 11A at the lowermost stage is connected to the first piping member 31A.
  • the first piping member 31A is a bottomed tubular pipe of which a lower end in the vertical direction is blocked so as to form the lower end 20s of the header 20D.
  • the first piping member 31A is a pipe having a constant pipe diameter in the vertical direction.
  • the first piping member 31A has a pipe diameter D11 equal to or larger than the pipe diameter d1 of the heat transfer pipe 11A (d1 ⁇ D11).
  • the pipe diameter D11 of the first piping member 31A is larger than the pipe diameter d31 of the oil return pipe 30 (d31 ⁇ D11).
  • the second piping member 31B is disposed above the first piping member 31A in the vertical direction.
  • the termination end 115 of the second heat transfer pipe 11B at a second stage from below is connected to the second piping member 31B.
  • the second piping member 31B is a tubular pipe that is open at both ends.
  • the second piping member 31B is a pipe having a constant pipe diameter in the vertical direction.
  • a lower end of the second piping member 31B in the vertical direction is joined to an upper end of the first piping member 31A in the vertical direction.
  • an inner peripheral surface of the lower end of the second piping member 31B in the vertical direction and an outer peripheral surface of the upper end of the first piping member 31A are fitted and joined together so as to slide on each other.
  • the second piping member 31B has a pipe diameter D12 larger than the pipe diameter D11 of the first piping member 31A immediately therebelow (D11 ⁇ D12).
  • the third piping member 31C is disposed above the second piping member 31B in the vertical direction.
  • the termination end 115 of the third heat transfer pipe 11C at a third stage from below is connected to the third piping member 31C.
  • the third piping member 31C is a tubular pipe that is open at both ends.
  • the third piping member 31C is a pipe having a constant pipe diameter in the vertical direction.
  • a lower end of the third piping member 31C is joined to an upper end of the second piping member 31B in the vertical direction.
  • an inner peripheral surface of the lower end of the third piping member 31C in the vertical direction and an outer peripheral surface of the upper end of the second piping member 31B in the vertical direction are fitted and joined together so as to slide on each other.
  • the third piping member 31C has a pipe diameter D13 larger than the pipe diameter D12 of the second piping member 31B immediately therebelow (D12 ⁇ D13). Hence, the pipe diameter of the header 20D becomes gradually larger in the order of the first piping member 31A that forms the lower end 20s, the second piping member 31B, and the third piping member 31C that forms the upper end 20t.
  • the joining positions in the vertical direction between the plurality of heat transfer pipes 11 and the plurality of piping members 31 are not limited at all by the present embodiment.
  • the termination ends 115 of the plurality of heat transfer pipes 11 are joined to the piping members 31 at positions spaced in the vertical direction from joint parts between the piping members 31 adjacent to each other in the vertical direction. That is, it is preferable that joint parts joined to the piping members 31 are formed at the positions apart from each other in the vertical direction with respect to the joint parts between the piping members 31.
  • the pipe diameter D11 of the first piping member 31A is smaller than the pipe diameter D12 of the second piping member 31B and the pipe diameter D13 of the third piping member 31C on the upper stage side, and the flow passage cross-sectional area thereof is the smallest in the header 20D. That is, the flow passage cross-sectional area of the first piping member 31A to which the first heat transfer pipe 11A at the lowermost stage is connected is made to be the smallest with respect to the upper end 20t of the header 20D.
  • the flow speed of the refrigerant at the lower end 20s of the header 20D can be enhanced compared to a case where the flow passage cross-sectional area is not made small. For that reason, since the refrigerant flows in only from the first heat transfer pipe 11A at the lowermost stage, it is suppressed that the flow speed thereof becomes excessively slow within the first piping member 31A having a low flow rate of the refrigerant flowing therethrough. As a result, the refrigerant and lubricating oil within the first piping member 31A are made to flow toward the upper end 20t side.
  • the header 20A by configuring the header 20A such that the flow passage cross-sectional area of the portion to which the first heat transfer pipe 11A is connected become larger than the flow passage cross-sectional area at the upper end 20t, the accumulation of the lubricating oil can be suppressed without forming a guide or a groove for guiding the lubricating oil to the header 20D.
  • the header 20D in which the accumulation of the lubricating oil is suppressed can be simply manufactured at low costs.
  • a tapered shape can also be formed such that the flow passage cross-sectional area thereof becomes gradually larger from the lower end 20s of the header 20D toward the upper end 20t thereof.
  • the flow passage cross-sectional area of the header 20D is increased in stage whenever the number of heat transfer pipes connected by providing the first piping member 31A, the second piping member 31B, and the third piping member 31C increases.
  • a change in the flow speed caused with increases in the flow rates of the refrigerant and the lubricating oil that flow through the header 20D can be suppressed.
  • the change in the flow speed while from the lower end 20s toward the upper end 20t is suppressed, and disturbance of the flow within the header 20D due to the change in the flow speed is suppressed. Accordingly, a flow speed at which the lubricating oil can be discharged from the inside of the header 20D can be secured from the lower end 20s to the upper end 20t.
  • the header 20D is configured by joining the first piping member 31A, the second piping member 31B, and the third piping member 31C having internal diameters different from each other side by side in the vertical direction. Accordingly, just by connecting the three piping members 31, the header 20D of which the flow passage cross-sectional area becomes gradually larger from the lower end 20s toward the upper end 20t can be simply manufactured at low costs.
  • the joint part between the first piping member 31A and the second piping members 31B, the joint part between the second piping members 31B and third piping members 31C, the joint part between the first piping member 31A and the first heat transfer pipe 11A, the joint part between the second piping member 31B and the third piping member 31C, and the joint part between the second heat transfer pipe 11B and the third heat transfer pipe 11C are spaced apart from each other in the vertical direction. For that reason, a space for performing the joining work (brazing, welding, or the like) between the plurality of piping members 31 and the joining work (brazing, welding, or the like) between the respective piping members 31 and the respective heat transfer pipe 11 can be secured. Accordingly, the joining work when manufacturing the header can be easily performed.
  • the pipe diameter D11 of the first piping member 31A is made to be equal to the pipe diameter d1 of the first heat transfer pipe 11A. Accordingly, a decrease in the flow speed when the refrigerant and the lubricating oil flow into the first piping member 31A from the first heat transfer pipe 11A is suppressed. Accordingly, the flow speed at which the lubricating oil can be discharged is more easily secured by the first piping member 31A.
  • the number of piping members 31 provided in the header 20D is not limited to three of the first piping member 31A, the second piping member 31B, and the third piping member 31C as in the present embodiment.
  • the number of piping members 31 may be two or more, for example, four.
  • the invention is not limited to one heat transfer pipe 11 being connected to one piping member 31.
  • two or more heat transfer pipes 11 may be joined to the first piping member 31A, the second piping member 31B, and the third piping member 31C that constitutes the header 20D.
  • Fig. 6 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to the reference example.
  • a header 20E circulates the refrigerant from the upper end 20t toward the lower end 20s in the vertical direction.
  • the termination ends 115 of the plurality of heat transfer pipes 11 spaced apart from each other in the vertical direction are connected to the header 20E.
  • An outlet-side pipe 4E is connected to the lower end 20s of the header 20E.
  • the upper end 20t of the header 20E of the reference example is blocked.
  • the header 20E is a pipe having a constant pipe diameter in the vertical direction.
  • the header 20E has the pipe diameter D10 equal to or larger than the pipe diameter d1 of the heat transfer pipe 11A (d1 ⁇ D10).
  • the outlet-side pipe 4E of the reference example has first end joined to the lower end 20s of the header 20E.
  • the outlet-side pipe 4E of the reference example has a return part 22E that is curved in a U-shape over two stages.
  • the outlet-side pipe 4E is connected to the accumulator 3, which recovers the liquid phase (liquid refrigerant) of the refrigerant, at an end on the side where the outlet-side pipe 4 is not connected to the header 20E.
  • the refrigerant when performing a heating operation, in each of the first heat transfer pipe 11A, the second heat transfer pipe 11B, and the third heat transfer pipe 11C, the refrigerant exchanges heat with surrounding air and thereby at least a portion thereof is gasified (evaporated).
  • the refrigerant that has exchanged heat by flowing into the first heat transfer pipe 11A, the second heat transfer pipe 11B, and the third heat transfer pipe 11C flows into the header 20E from the respective termination ends 115, and flows through the header 20E toward the lower end 20s.
  • the refrigerant flowing into the header 20E from the third heat transfer pipe 11C at the uppermost stage flows toward the lower end 20s.
  • the refrigerant flowing into the header 20E from the second heat transfer pipe 11B at the second stage from above joins the refrigerant flowing in from the third heat transfer pipe 11C.
  • the refrigerant flowing into the header 20E from the first heat transfer pipe 11A at the lowermost stage joins the refrigerant flowing in from the third heat transfer pipe 11C and the second heat transfer pipe 11B.
  • the refrigerant that has joined within the header 20E in this way is sent from the lower end 20s to the outlet-side pipe 4E. Thereafter, the refrigerant is sequentially sent to the accumulator 3 and the compressor 5 through the return part 22E.
  • the refrigerant flows downward from above within the header 20E, and the return part 22E that constitutes the outlet-side pipe 4E is connected to the lower end 20s of the header 20E.
  • the refrigerant flows downward from above that is the same as the gravitational direction.
  • the refrigerants that have flowed in from the first heat transfer pipe 11A, the second heat transfer pipe 11B, and the third heat transfer pipe 11C join together and the flow speed of the joined refrigerant is increasing.
  • the lubricating oil accumulated at the lower end 20s of the header 20E due to gravity smoothly flows from the header 20E through the return part 22E toward the accumulator 3 side with the flow of the refrigerant.
  • the accumulation of the lubricating oil in the lower end 20s of the header 20E can be suppressed.
  • header 20E may be provided in a reversed manner by turning the header 20A and the header 20D, which are illustrated in the first to fourth embodiments, upside down in the vertical direction, the header 20E can be simply manufactured at low costs.
  • the number of heat transfer pipes 11 provided with the heat exchangers 10A to 10E is not limited to three of the first heat transfer pipe 11A, the second heat transfer pipe 11B, and the third heat transfer pipe 11C as in the present embodiment.
  • the number of heat transfer pipes 11 may be only two, or may be four or more.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (6)

  1. Evaporateur (10A, 10B, 10C, 10D, 10E) comprenant :
    une pluralité de tuyaux de transfert de chaleur (11, 11A, 11B, 11C) qui sont prévus à intervalles dans une direction verticale et permettent à un réfrigérant de s'écouler à travers ces derniers vers des premières extrémités (115) ;
    un collecteur (20A, 20D, 20E) qui est configuré pour s'étendre dans la direction verticale, a des premières extrémités (115) de la pluralité de tuyaux de transfert de chaleur (11, 11A, 11B, 11C) raccordées à ce dernier, et est configuré pour permettre au réfrigérant de s'écouler d'une extrémité inférieure (20s) vers une extrémité supérieure (20t) à laquelle un tuyau de réfrigérant (4, 4E) est raccordé ; et
    un tuyau de dérivation (30) configuré pour permettre à l'extrémité inférieure du collecteur (20A, 20D, 20E) et au tuyau de réfrigérant (4, 4E) de communiquer entre eux,
    caractérisé en ce que :
    une longueur du tuyau de dérivation (30) est plus longue que la longueur d'un passage d'écoulement configuré pour aller de l'extrémité inférieure (20s) du collecteur (20A, 20D, 20E) en passant par l'extrémité supérieure (20t) jusqu'à un site auquel le tuyau de dérivation (30) du tuyau de réfrigérant (4, 4E) est assemblé, et
    le tuyau de dérivation (30) a une partie de spirale (30R) enroulée en spirale.
  2. Evaporateur (10A, 10B, 10C, 10D, 10E) selon la revendication 1,
    dans lequel le tuyau de dérivation (30) a une zone transversale de passage d'écoulement inférieure à une zone transversale de passage d'écoulement au niveau de l'extrémité inférieure (20s) du collecteur (20A, 20D, 20E).
  3. Evaporateur (10A, 10B, 10C, 10D, 10E) selon les revendications 1 ou 2,
    dans lequel le tuyau de dérivation (30) comprend en outre un élément de valve (32) configuré pour réguler un écoulement de réfrigérant à l'intérieur du tuyau de dérivation (30).
  4. Evaporateur (10A, 10B, 10C, 10D, 10E) selon la revendication 3, comprenant en outre :
    un organe de commande (33) configuré pour commander l'ouverture et la fermeture de l'élément de valve (32),
    dans lequel l'organe de commande (33) est configuré pour commander l'ouverture et la fermeture de l'élément de valve (32) sur la base d'un temps écoulé depuis le démarrage d'un compresseur (5) prévu en aval du tuyau de réfrigérant (4, 4E) ou du degré de surchauffe du réfrigérant.
  5. Evaporateur (10A, 10B, 10C, 10D, 10E) selon la revendication 4,
    dans lequel l'organe de commande (33) est configuré pour fermer l'élément de valve (32) afin d'arrêter l'écoulement du tuyau de dérivation (30) au démarrage du compresseur (5), et est configuré pour ouvrir l'élément de valve (32) pour ouvrir l'écoulement du tuyau de dérivation (30) après l'écoulement d'un temps donné prédéterminé passant depuis le démarrage du compresseur (5) ou dans un cas dans lequel le degré de surchauffe du réfrigérant est égal ou supérieur à une valeur de référence prédéterminée.
  6. Circuit de réfrigérant (100A, 100B, 100C, 100D, 100E) comprenant l'évaporateur (10A, 10B, 10C, 10D, 10E) selon l'une quelconque des revendications 1 à 5.
EP17194601.5A 2016-10-05 2017-10-03 Évaporateur et circuit réfrigérant Not-in-force EP3306234B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016197401A JP2018059668A (ja) 2016-10-05 2016-10-05 蒸発器及び冷媒回路

Publications (2)

Publication Number Publication Date
EP3306234A1 EP3306234A1 (fr) 2018-04-11
EP3306234B1 true EP3306234B1 (fr) 2019-05-01

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ID=60019757

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Application Number Title Priority Date Filing Date
EP17194601.5A Not-in-force EP3306234B1 (fr) 2016-10-05 2017-10-03 Évaporateur et circuit réfrigérant

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EP (1) EP3306234B1 (fr)
JP (1) JP2018059668A (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11156412B2 (en) * 2016-09-12 2021-10-26 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
CN110230901A (zh) * 2019-05-27 2019-09-13 广州大学 一种气液两相共用型的冷媒分配管及热泵系统
DE202022105684U1 (de) * 2022-10-10 2022-11-04 Thermofin Gmbh Trockenexpansionsverdampfer für Ammoniakkälteanlagen

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0541318Y2 (fr) 1987-03-16 1993-10-19
US8166776B2 (en) * 2007-07-27 2012-05-01 Johnson Controls Technology Company Multichannel heat exchanger
US20140123696A1 (en) * 2012-11-02 2014-05-08 Hongseong KIM Air conditioner and evaporator inlet header distributor therefor
KR101550549B1 (ko) * 2014-08-01 2015-09-04 엘지전자 주식회사 공기 조화기

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EP3306234A1 (fr) 2018-04-11
JP2018059668A (ja) 2018-04-12

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