EP3306232A1 - Evaporator and refrigerant circuit - Google Patents
Evaporator and refrigerant circuit Download PDFInfo
- Publication number
- EP3306232A1 EP3306232A1 EP17194600.7A EP17194600A EP3306232A1 EP 3306232 A1 EP3306232 A1 EP 3306232A1 EP 17194600 A EP17194600 A EP 17194600A EP 3306232 A1 EP3306232 A1 EP 3306232A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pipe
- heat transfer
- header
- refrigerant
- 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.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 title claims abstract description 113
- 239000010687 lubricating oil Substances 0.000 abstract description 41
- 238000009825 accumulation Methods 0.000 abstract description 11
- 239000003921 oil Substances 0.000 description 28
- 239000007788 liquid Substances 0.000 description 16
- 238000005304 joining Methods 0.000 description 11
- 238000004378 air conditioning Methods 0.000 description 8
- 239000007791 liquid phase Substances 0.000 description 7
- 230000000630 rising effect Effects 0.000 description 6
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 238000005219 brazing Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000005484 gravity Effects 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 238000003466 welding Methods 0.000 description 3
- 239000007792 gaseous phase Substances 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
- 239000010726 refrigerant oil Substances 0.000 description 1
Images
Classifications
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- 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
- F25B41/40—Fluid line arrangements
-
- 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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape
-
- 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 liquid refrigerant does not easily flow in diverging portions or joining portions from or to the plurality of heat transfer pipes. As a result, the liquid refrigerant may be accumulated in the header.
- separation of a liquid phase (liquid refrigerant) of the refrigerant from a gaseous phase in the header on the evaporator inlet side is suppressed by gradually reducing the flow passage cross-sectional area of the header.
- the flow of the liquid refrigerant is made smooth by further forming a guide or a groove for swirling a refrigerant in an inner wall of a diverging pipe (header) where the plurality of refrigerant pipes (heat transfer pipe) join together.
- 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.
- the lubricating oil may be accumulated at a lower end of the header on the evaporator outlet side where the lubricating oil that has flowed through the plurality of heat transfer pipes join together.
- the invention provides an evaporator and a refrigerant circuit capable of suppressing the accumulation of lubricating oil within a header in a configuration including a plurality of heat transfer pipes.
- An evaporator related to a first 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 a lower end toward an upper end to which a refrigerant pipe is connected.
- a flow passage cross-sectional area of a portion of the header to which the heat transfer pipe located at a lowermost stage among the plurality of heat transfer pipes is connected is smaller than a flow passage cross-sectional area at the upper end of the header.
- the header may have a flow passage cross-sectional area that becomes gradually larger from the lower end toward the upper end as the number of the heat transfer pipes to be connected increases.
- the header may have a plurality of piping members that are disposed side by side in the vertical direction and have mutually different internal diameters.
- the first ends of the plurality of heat transfer pipes may be joined to the piping member at positions spaced in the vertical direction from joint parts between the piping members adjacent to each other in the vertical direction.
- the joint parts between the piping members and joint parts between the piping member and the heat transfer pipes are separated from each other. For that reason, spaces for performing the joining work between the piping members and the joining work between the piping members and the heat transfer pipes can be secured, respectively. Accordingly, the joining work when manufacturing the header can be easily performed.
- the evaporator may further include a bypass pipe that allows the lower end of the header and the refrigerant pipe to communicate therethrough.
- 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 may further include the 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.
- a refrigerant circuit related to a seventh aspect of the invention includes the evaporator of any one of the first to sixth aspects.
- 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, and a header 20A.
- 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 (a 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 to the header 20A.
- a first heat transfer pipe 11A, a second heat transfer pipe 11B, and a third heat transfer pipe 11C are connected to the header 20A of the present embodiment in order from below in the vertical direction.
- the upper end 20t of the header 20A is connected to an outlet-side pipe 4.
- the lower end 20s of the header 20A of the present embodiment is blocked.
- the flow passage cross-sectional area of a portion of the header 20A 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 of the header 20A.
- the header 20A 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 20A 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 20A 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 20A.
- 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 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 the 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 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 20A 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 outlet-side pipe 4 has a first end joined to the upper end 20t of the header 20A.
- the outlet-side pipe 4 of the present embodiment is connected to the third piping member 31C.
- 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 that is a side where the outlet-side pipe 4 is not connected to the third piping member 31C.
- 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 third piping member 31C from the third heat transfer pipe 11C at the uppermost stage joins the refrigerant that has flowed in from the second piping member 31B.
- the refrigerant that has joined within the header 20A in this way is sent 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 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 20A. 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 20A.
- the flow speed of the refrigerant at the lower end 20s of the header 20A 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.
- the refrigerant and lubricating oil within the first piping member 31A are made to flow toward the upper end 20t side against gravity. This can suppress the accumulation of the lubricating oil contained in the refrigerant in the lower end 20s of the header 20A. As a result, the accumulation of the lubricating oil within the header 20A can be suppressed in the heat exchanger 10A including the plurality of heat transfer pipes 11.
- 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 becomes 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 inside of the header 20A.
- the header 20A 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 20A toward the upper end 20t thereof.
- the flow passage cross-sectional area of the header 20A 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 20A 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 20A 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 20A can be secured from the lower end 20s to the upper end 20t.
- the header 20A 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 20A 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.
- Fig. 2 is a schematic view illustrating of the evaporator of a modification example of the first embodiment of the invention. As illustrated in Fig. 2 , the termination end 115 of the first heat transfer pipe 11A at the lowermost stage may be directly joined so as to be continuous with the lower end of the first piping member 31A.
- Fig. 3 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to the second embodiment of the invention.
- a heat exchanger (evaporator) 10B further includes an oil return pipe (bypass pipe) 30 that 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 D11 of the first piping member 31A at the lowermost stage 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 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 outlet-side pipe 4. 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. Hence, a situation in which the liquid refrigerant within the header 20A flows out excessively via the oil return pipe 30 can be suppressed.
- the same components as those of the above first and second embodiments will be designated by the same reference signs in the drawings, and the description thereof will be omitted.
- the third embodiment is different from the second embodiment in that the bypass pipe has a valve member.
- Fig. 4 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to the third 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.
- Timings when the two-way valve 32 is opened and closed is not limited at all.
- the two-way valve 32 may be closed when the starting of the compressor 5 is started, and thereafter, the two-way valve 32 may be opened to bypass the lubricating oil through the oil return pipe 30 after a preset given time set in has elapsed.
- the two-way valve 32 Since the two-way valve 32 is closed in this way, the liquid refrigerant is made not to be bypassed via the oil return pipe 30 with the lubricating oil from the lower end 20s of the header 20A immediately after the starting of the compressor 5. If a given time has elapsed since the start of the compressor 5, the degree of superheat of the refrigerant within the header 20A increases, and the liquid refrigerant is gasified. For that reason, by closing the two-way valve 32 until a given time has elapsed and opening the two-way valve 32 after that, reaching of the liquid refrigerant to the compressor 5 is suppressed.
- the preset given time set may be counted by a timer.
- the heat exchanger 10C and the refrigerant circuit 100C as described above, in addition to the same effects as those of the above second embodiment, it is possible to switch the flow of the lubricating oil and the liquid phase (liquid refrigerant) of the refrigerant which bypassed to the outlet-side pipe 4 via the oil return pipe 30 by the two-way valve 32. 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.
- the flow within the oil return pipe 30 can be cut off by closing the two-way valve 32 immediately after the starting of the compressor 5. For that reason, a large amount of liquid refrigerant can be prevented from reaching the compressor 5 from the accumulator 3 through the oil return pipe 30 in a case where the refrigerant is in the easily liquefied state immediately after the starting of the compressor 5.
- the number of heat transfer pipes 11 provided with the heat exchangers 10A to 10C 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.
- the number of piping members 31 provided in the header 20A 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 unlike the above embodiments.
- 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 constitute the header 20A.
- the air-conditioning system 1 including the refrigerant circuit is exemplified as an instance, the invention is not limited to this, and the same configuration can also be applied to a refrigeration system including the refrigerant circuit.
- the evaporator and the refrigerant circuit it is possible to suppress the accumulation of the lubricating oil within the header in the configuration including the plurality of heat transfer pipes.
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Abstract
Description
- The present invention relates to an evaporator and a refrigerant circuit.
- In 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. As such evaporators, for example, there is a structure including a plurality of heat transfer pipes disposed at intervals in a vertical direction. In such an evaporator, 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.
- In the evaporator including such multi-stage heat transfer pipes, the liquid refrigerant does not easily flow in diverging portions or joining portions from or to the plurality of heat transfer pipes. As a result, the liquid refrigerant may be accumulated in the header. Thus, in an evaporator according to PTL 1, separation of a liquid phase (liquid refrigerant) of the refrigerant from a gaseous phase in the header on the evaporator inlet side is suppressed by gradually reducing the flow passage cross-sectional area of the header. Additionally, in this evaporator, the flow of the liquid refrigerant is made smooth by further forming a guide or a groove for swirling a refrigerant in an inner wall of a diverging pipe (header) where the plurality of refrigerant pipes (heat transfer pipe) join together.
- [PTL 1] Japanese Unexamined Patent Application, First Publication No. H11-325656
- In a refrigerant circuit of a refrigeration system or an air-conditioning system including such an evaporator, 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.
- However, in the evaporator including the multi-stage heat transfer pipe, the lubricating oil may be accumulated at a lower end of the header on the evaporator outlet side where the lubricating oil that has flowed through the plurality of heat transfer pipes join together.
- In contrast, in the configuration described in PTL 1 in which the flow passage cross-sectional area of the header is gradually reduced, the separation of the liquid phase (liquid refrigerant) of the refrigerant from the gaseous phase in the header on the evaporator inlet side is suppressed. The problem that the lubricating oil is accumulated within the header on the evaporator outlet side cannot be solved.
- The invention provides an evaporator and a refrigerant circuit capable of suppressing the accumulation of lubricating oil within a header in a configuration including a plurality of heat transfer pipes.
- An evaporator related to a first 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 a lower end toward an upper end to which a refrigerant pipe is connected. A flow passage cross-sectional area of a portion of the header to which the heat transfer pipe located at a lowermost stage among the plurality of heat transfer pipes is connected is smaller than a flow passage cross-sectional area at the upper end of the header.
- By adopting such a configuration, compared to a case where the flow passage cross-sectional area of the portion to which the heat transfer pipe at the lowermost stage is connected is not made smaller than the upper end of the header, a situation in which the flow speed of the refrigerant at the lower end of the header becomes excessively slow can be suppressed. Hence, the lubricating oil that has flowed into the lower end of the header flows toward the upper end side against gravity. This can suppress the accumulation of the lubricating oil contained in the refrigerant in the lower end of the header.
- Additionally, in the evaporator related to a second aspect of the invention based on the first aspect, the header may have a flow passage cross-sectional area that becomes gradually larger from the lower end toward the upper end as the number of the heat transfer pipes to be connected increases.
- By adopting such a configuration, a change in the flow speed caused with an increase in the flow rate of the refrigerant that flows through the header can be suppressed. For that reason, the flow speed at which the lubricating oil can be discharged from the inside of the header can be secured without changing the flow speed from the lower end toward the upper end.
- Additionally, in the evaporator related to a third aspect of the invention based on the first or second aspect, the header may have a plurality of piping members that are disposed side by side in the vertical direction and have mutually different internal diameters.
- By adopting such a configuration, just by connecting the plurality of piping members, the header of which the flow passage cross-sectional area becomes gradually larger from the lower end toward the upper end, can be easily manufactured at low costs.
- Additionally, in the evaporator related to a fourth aspect of the invention based on the third aspect, the first ends of the plurality of heat transfer pipes may be joined to the piping member at positions spaced in the vertical direction from joint parts between the piping members adjacent to each other in the vertical direction.
- By adopting such a configuration, the joint parts between the piping members and joint parts between the piping member and the heat transfer pipes are separated from each other. For that reason, spaces for performing the joining work between the piping members and the joining work between the piping members and the heat transfer pipes can be secured, respectively. Accordingly, the joining work when manufacturing the header can be easily performed.
- Additionally, in the evaporator related to a fifth aspect of the invention based on any one of the first to fourth aspects, the evaporator may further include a bypass pipe that allows the lower end of the header and the refrigerant pipe to communicate therethrough.
- By adopting such a configuration, 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.
- Additionally, in the evaporator related to a sixth aspect of the invention based on the fifth aspect, the bypass pipe may further include the valve member that controls a flow of the refrigerant within the bypass pipe.
- By adopting such a configuration, 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.
- A refrigerant circuit related to a seventh aspect of the invention includes the evaporator of any one of the first to sixth aspects.
- According to the invention, it is possible to suppress the accumulation of the lubricating oil within the header in the configuration including the plurality of heat transfer pipes.
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Fig. 1 is schematic view illustrating the configuration of an evaporator and a refrigerant circuit related to a first embodiment of the invention. -
Fig. 2 is a schematic view illustrating of the evaporator of a modification example of the first embodiment of the invention. -
Fig. 3 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to a second embodiment of the invention. -
Fig. 4 is a schematic view illustrating the configuration of the evaporator and a refrigerant circuit related to a third embodiment of the invention. - Hereinafter, embodiments for carrying out an evaporator and a refrigerant circuit according to the invention will be described with reference to the accompanying drawings. However, the invention is not limited only to these embodiments.
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Fig. 1 is schematic view illustrating the configuration of an evaporator and a refrigerant circuit related to a first embodiment of the invention. As illustrated inFig. 1 , 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, anaccumulator 3, an outlet-side pipe (refrigerant pipe) 4, and acompressor 5. - The
heat exchanger 10A functions as an evaporator during a heating operation. In theheat exchanger 10A, 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. In theheat exchanger 10A, the outlet-side pipe (refrigerant pipe) 4 for sending the refrigerant to thecompressor 5 is connected to an outlet side that is a downstream side in the flow direction of the refrigerant via theaccumulator 3. Theheat exchanger 10A includes a plurality of (three in the present embodiment) heat transfer pipes 11, adistributor 12, a plurality of capillary tubes 13, and aheader 20A. - The plurality of heat transfer pipes 11 are connected to the inlet-
side pipe 2 via thedistributor 12 and the plurality of capillary tubes 13, respectively. In other words, the flow passage for the refrigerant that flows through the inlet-side pipe 2 branches to the plurality of heat transfer pipes 11 via thedistributor 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 theheat exchanger 10A. Each heat transfer pipe 11 has a risingsection 111, alower pipe section 112, abent section 113, and anupper pipe section 114. The heat transfer pipe 11 is a pipe in which the risingsection 111, thelower pipe section 112, thebent section 113, and theupper pipe section 114 are integrally formed. - The rising
section 111 extends upward in the vertical direction from thedistributor 12 side. An end (an end of the heat transfer pipe 11 on the other side) of the risingsection 111 is connected to each capillary tube 13. - The
lower pipe section 112 is continuous with the risingsection 111. Thelower pipe section 112 horizontally extends in a lateral direction within theheat exchanger 10A. - The
bent section 113 is continuous with thelower pipe section 112. Thebent section 113 is bent in a U-shape. - The
upper pipe section 114 is continuous with thebent section 113. Theupper pipe section 114 horizontally extends in the lateral direction. Theupper pipe section 114 is located to be spaced apart upward in the vertical direction with respect to thelower pipe section 112. A termination end (a first end of the heat transfer pipe 11) 115 of theupper pipe section 114 is connected to theheader 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. In the present embodiment, a first capillary tube 13A that connects the first heat transfer pipe 11A and thedistributor 12 together, a second capillary tube 13B that connects the second heat transfer pipe 11B and thedistributor 12 together, and a third capillary tube 13C that connects the third heat transfer pipe 11C and thedistributor 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. Theheader 20A extends upward from below in the vertical direction. The refrigerant flows through theheader 20A from alower end 20s toward anupper 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 to theheader 20A. A first heat transfer pipe 11A, a second heat transfer pipe 11B, and a third heat transfer pipe 11C are connected to theheader 20A of the present embodiment in order from below in the vertical direction. Theupper end 20t of theheader 20A is connected to an outlet-side pipe 4. Thelower end 20s of theheader 20A of the present embodiment is blocked. The flow passage cross-sectional area of a portion of theheader 20A 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 theupper end 20t of theheader 20A. - The
header 20A 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 thelower end 20s toward theupper end 20t in the vertical direction. In this embodiment, theheader 20A 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. In the present embodiment, a first piping member 31A, a second piping member 31B, and a third piping member 31C are provided sequentially from thelower end 20s side in the vertical direction. Theheader 20A 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 thelower end 20s of theheader 20A. 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 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 the 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. In the present embodiment, 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. In the present embodiment, 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 are fitted and joined together so as to slide on each other. An upper end of the third piping member 31C is joined to an end of the outlet-side pipe 4. 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 theheader 20A becomes gradually larger in the order of the first piping member 31A that forms thelower end 20s, the second piping member 31B, and the third piping member 31C that forms theupper end 20t. - Here, 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. However, in 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 outlet-
side pipe 4 has a first end joined to theupper end 20t of theheader 20A. The outlet-side pipe 4 of the present embodiment is connected to the third piping member 31C. The outlet-side pipe 4 has areturn part 22 that is curved in a U-shape. The outlet-side pipe 4 is connected to theaccumulator 3, which recovers the liquid phase (liquid refrigerant) of the refrigerant, at the other end that is a side where the outlet-side pipe 4 is not connected to the third piping member 31C. - In the air-conditioning system 1 including the
heat exchanger 10A of such a configuration, the refrigerant is sent through the inlet-side pipe 2 from the indoor unit side when performing a heating operation. In this case, lubricating oil for lubricating a bearing and the like of thecompressor 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 thedistributor 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. Similarly, the refrigerant that has flowed into the second capillary tube 13B flows into the second heat transfer pipe 11B, and the refrigerant that has flowed into the third capillary tube 13C flows into the third heat transfer pipe 11C. 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 theheader 20A from the respective termination ends 115, and flows through theheader 20A toward theupper end 20t. - The refrigerant that has flowed into the first piping member 31A from the first heat transfer pipe 11A at the lowermost stage flows toward the second piping member 31B. The refrigerant that has flowed into the second piping member 31B from the second heat transfer pipe 11B at a second stage from below joins the refrigerant that has flowed in from the first piping member 31A. Moreover, the refrigerant that has flowed into the third piping member 31C from the third heat transfer pipe 11C at the uppermost stage joins the refrigerant that has flowed in from the second piping member 31B. The refrigerant that has joined within the
header 20A in this way is sent to the outlet-side pipe 4. Thereafter, the refrigerant is sequentially sent to theaccumulator 3 and thecompressor 5 through thereturn part 22. - According to the
heat exchanger 10A, the refrigerant circuit 100A, and the air-conditioning system 1 as described above, 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 theheader 20A. 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 theupper end 20t of theheader 20A. For that reason, the flow speed of the refrigerant at thelower end 20s of theheader 20A 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 against gravity. This can suppress the accumulation of the lubricating oil contained in the refrigerant in thelower end 20s of theheader 20A. As a result, the accumulation of the lubricating oil within theheader 20A can be suppressed in theheat exchanger 10A including the plurality of heat transfer pipes 11. - Additionally, 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 becomes larger than the flow passage cross-sectional area at theupper 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 inside of theheader 20A. Hence, theheader 20A in which the accumulation of the lubricating oil is suppressed can be simply manufactured at low costs. - Additionally, in order to make the flow passage cross-sectional area of the portion to which the first heat transfer pipe 11A at the lowermost stage is connected small with respect to the
upper end 20t of theheader 20A, for example, a tapered shape can also be formed such that the flow passage cross-sectional area thereof becomes gradually larger from thelower end 20s of theheader 20A toward theupper end 20t thereof. In contrast, the flow passage cross-sectional area of theheader 20A 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. For that reason, a change in the flow speed caused with increases in the flow rates of the refrigerant and the lubricating oil that flow through theheader 20A can be suppressed. For that reason, the change in the flow speed while from thelower end 20s toward theupper end 20t is suppressed, and disturbance of the flow within theheader 20A 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 theheader 20A can be secured from thelower end 20s to theupper end 20t. - Moreover, the
header 20A 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, theheader 20A of which the flow passage cross-sectional area becomes gradually larger from thelower end 20s toward theupper end 20t can be simply manufactured at low costs. - Additionally, 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.
- Moreover, 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.
- In addition, in the above first embodiment, the first heat transfer pipe 11A at the lowermost stage is joined to the middle of the first piping member 31A in the vertical direction at the lowermost stage of the
header 20A. However, the invention is not limited to such a configuration. For example,Fig. 2 is a schematic view illustrating of the evaporator of a modification example of the first embodiment of the invention. As illustrated inFig. 2 , thetermination end 115 of the first heat transfer pipe 11A at the lowermost stage may be directly joined so as to be continuous with the lower end of the first piping member 31A. - Next, an evaporator and a refrigerant circuit related to a second embodiment of the invention will be described. In addition, in the second embodiment to be described below, the same components as those of the above first embodiment will be designated by the same reference signs in the drawings, and the description thereof will be omitted. The second embodiment is different from the first embodiment in that a bypass pipe is provided.
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Fig. 3 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to the second embodiment of the invention. As illustrated inFig. 3 , a heat exchanger (evaporator) 10B further includes an oil return pipe (bypass pipe) 30 that allows thelower end 20s of theheader 20A and the outlet-side pipe 4 to communicate with each other. - The
oil return pipe 30 is connected to thelower end 20s of theheader 20A, and a portion that is downstream of thereturn part 22 of the outlet-side pipe 4 and upstream of a location connected to theaccumulator 3. Theoil return pipe 30 has a flow passage cross-sectional area smaller than a flow passage cross-sectional area at thelower end 20s of theheader 20A. Specifically, theoil 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 D11 of the first piping member 31A at the lowermost stage of theheader 20A. The length of theoil return pipe 30 is made longer than the length of a flow passage that leads from thelower end 20s of theheader 20A through theupper end 20t thereof to a site to which theoil return pipe 30 of the outlet-side pipe 4 is joined. That is, it is more preferable that theoil return pipe 30 has a pipe length that is longer than a flow passage length that leads from thelower end 20s of theheader 20A through theupper end 20t thereof to a portion to which atermination end 30e of theoil return pipe 30 of the outlet-side pipe 4 is connected. For this reason, it is preferable that theoil return pipe 30 is formed by a capillary tube having a spirallywound spiral part 30r to secure a length. - The lubricating oil accumulated at the
lower end 20s of theheader 20A due to gravity is bypassed to the middle of the outlet-side pipe 4 downstream of thereturn part 22 through theoil return pipe 30 without passing through theupper end 20t of theheader 20A. Here, in theoil return pipe 30, the lubricating oil flows from thelower end 20s side toward the outlet-side pipe 4 side due to a pressure difference between theheader 20A side and theaccumulator 3. - According to the
heat exchanger 10B and the refrigerant circuit 100B as described above, in addition to the same effects as those of the above-described first embodiment, the lubricating oil at thelower end 20s of theheader 20A can be sent to the outlet-side pipe 4 through theoil return pipe 30. Hence, the lubricating oil is directly discharged from thelower end 20s via theoil return pipe 30 to the outlet-side pipe 4 without passing through theupper end 20t of theheader 20A. This can suppress the accumulation of the lubricating oil at thelower end 20s of theheader 20A. - Additionally, the
oil return pipe 30 is formed to be longer than the flow passage length that leads from thelower end 20s of theheader 20A through theupper end 20t thereof to the portion to which thetermination end 30e of theoil 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 theoil return pipe 30 are suppressed more than the flow rates of the refrigerant and the lubricating oil that flow through the outlet-side pipe 4. As a result, a situation in which a liquid phase (liquid refrigerant) of a lot of the refrigerant and the lubricating oil flows into theaccumulator 3 through theoil return pipe 30 is suppressed. Hence, a situation in which the liquid refrigerant within theheader 20A flows out excessively via theoil return pipe 30 can be suppressed. - Next, an evaporator and a refrigerant circuit related to a third embodiment of the invention will be described. In addition, in the third embodiment to be described below, the same components as those of the above first and second embodiments will be designated by the same reference signs in the drawings, and the description thereof will be omitted. The third embodiment is different from the second embodiment in that the bypass pipe has a valve member.
-
Fig. 4 is a schematic view illustrating the configuration of the evaporator and the refrigerant circuit related to the third embodiment of the invention. As illustrated inFig. 4 , theoil 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 theoil return pipe 30. By opening and closing the two-way valve 32, it is possible to turn on and off the flow of the lubricating oil bypassing aheader 20A through theoil return pipe 30. - Timings when the two-way valve 32 is opened and closed is not limited at all. For example, the two-way valve 32 may be closed when the starting of the
compressor 5 is started, and thereafter, the two-way valve 32 may be opened to bypass the lubricating oil through theoil return pipe 30 after a preset given time set in has elapsed. - Since the two-way valve 32 is closed in this way, the liquid refrigerant is made not to be bypassed via the
oil return pipe 30 with the lubricating oil from thelower end 20s of theheader 20A immediately after the starting of thecompressor 5. If a given time has elapsed since the start of thecompressor 5, the degree of superheat of the refrigerant within theheader 20A increases, and the liquid refrigerant is gasified. For that reason, by closing the two-way valve 32 until a given time has elapsed and opening the two-way valve 32 after that, reaching of the liquid refrigerant to thecompressor 5 is suppressed. - Here, as for the timing when the two-way valve 32 is opened, the preset given time set may be counted by a timer. However, 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. - According to the
heat exchanger 10C and the refrigerant circuit 100C as described above, in addition to the same effects as those of the above second embodiment, it is possible to switch the flow of the lubricating oil and the liquid phase (liquid refrigerant) of the refrigerant which bypassed to the outlet-side pipe 4 via theoil return pipe 30 by the two-way valve 32. 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 theoil return pipe 30, can be adjusted. Hence, for example, in a case where thecompressor 5 is provided, the flow within theoil return pipe 30 can be cut off by closing the two-way valve 32 immediately after the starting of thecompressor 5. For that reason, a large amount of liquid refrigerant can be prevented from reaching thecompressor 5 from theaccumulator 3 through theoil return pipe 30 in a case where the refrigerant is in the easily liquefied state immediately after the starting of thecompressor 5. - Hereinbefore, the embodiments of the present invention are described with reference to the drawings. However, the configuration of the embodiments, combinations thereof, or the like are examples, and addition, omission, replacement, or other modifications of the configurations can be applied within a scope which does not depart from the gist of the present invention. In addition, the present invention is not limited by the above-described embodiments and is limited by only claims.
- For example, the number of heat transfer pipes 11 provided with the
heat exchangers 10A to 10C 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. For example, the number of heat transfer pipes 11 may be only two, or may be four or more. - Additionally, the number of piping members 31 provided in the
header 20A 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. - Additionally, the invention is not limited to one heat transfer pipe 11 being connected to one piping member 31 unlike the above embodiments. For example, 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 constitute the
header 20A. - Moreover, although the air-conditioning system 1 including the refrigerant circuit is exemplified as an instance, the invention is not limited to this, and the same configuration can also be applied to a refrigeration system including the refrigerant circuit.
- According to the evaporator and the refrigerant circuit, it is possible to suppress the accumulation of the lubricating oil within the header in the configuration including the plurality of heat transfer pipes.
-
- 1: AIR-CONDITIONING SYSTEM
- 2: INLET-SIDE PIPE
- 3: ACCUMULATOR
- 4: OUTLET-SIDE PIPE (REFRIGERANT PIPE)
- 5: COMPRESSOR
- 10A, 10B, 10C: HEAT EXCHANGER (EVAPORATOR)
- 100A, 100B, 100C: REFRIGERANT CIRCUIT
- 11: HEAT TRANSFER PIPE
- 11A: FIRST HEAT TRANSFER PIPE
- 11B: SECOND HEAT TRANSFER PIPE
- 11C: THIRD HEAT TRANSFER PIPE
- 111: RISING SECTION
- 112: LOWER PIPE SECTION
- 113: BENT SECTION
- 114: UPPER PIPE SECTION
- 115: TERMINATION END (FIRST END)
- 12: DISTRIBUTOR
- 13: CAPILLARY TUBE
- 13A: FIRST CAPILLARY TUBE
- 13B: SECOND CAPILLARY TUBE
- 13C: THIRD CAPILLARY TUBE
- 20A: HEADER
- 20s: LOWER END
- 20t: UPPER END
- 22: RETURN PART
- 30: OIL RETURN PIPE (BYPASS PIPE)
- 30e: TERMINATION END
- 30r: SPIRAL PART
- 31: PIPING MEMBER
- 31A: FIRST PIPING MEMBER
- 31B: SECOND PIPING MEMBER
- 31C: THIRD PIPING MEMBER
- 32: TWO-WAY VALVE
Claims (7)
- An evaporator (10A; 10B; 10C) comprising:a plurality of heat transfer pipes (11A, 11B, 11C) that are provided at intervals in a vertical direction and allow a refrigerant to flow therethrough toward first ends (115); anda header (20A) that is configured to extend in the vertical direction, has the first ends (115) of the plurality of heat transfer pipes (11A, 11B, 11C) connected thereto, and allows the refrigerant to flow from a lower end (20s) toward an upper end (20t) to which a refrigerant pipe (4) is connected,wherein a flow passage cross-sectional area of a portion of the header (20A) to which the heat transfer pipe (11A) located at a lowermost stage among the plurality of heat transfer pipes (11A, 11B, 11C) is connected is smaller than a flow passage cross-sectional area at the upper end (20t) of the header.
- The evaporator (10A; 10B; 10C) according to Claim 1,wherein the header (20A) has a flow passage cross-sectional area that becomes gradually larger from the lower end (20s) toward the upper end (20t) as the number of the heat transfer pipes (11A, 11B, 11C) to be connected increases.
- The evaporator (10A; 10B; 10C) according to Claim 1 or 2,wherein the header (20A) has a plurality of piping members (31A, 31B, 31C) that are disposed side by side in the vertical direction and have mutually different internal diameters (D11, D12, D13).
- The evaporator (10A; 10B; 10C) according to Claim 3,wherein the first ends (115) of the plurality of heat transfer pipes (11A, 11B, 11C) are joined to the piping members (31A, 31B, 31C) at positions spaced in the vertical direction from joint parts between the piping members (31A, 31B, 31C) adjacent to each other in the vertical direction.
- The evaporator (10B; 10C) according to any one of Claims 1 to 4, further comprising:a bypass pipe (30) that allows the lower end (20s) of the header (20A) and the refrigerant pipe (4) to communicate therethrough.
- The evaporator (10C) according to Claim 5,wherein the bypass pipe (30) further includes a valve member (32) that controls a flow of the refrigerant within the bypass pipe (30).
- A refrigerant circuit (100A; 100B; 100C) comprising the evaporator (10A; 10B; 10C) according to any one of Claims 1 to 6.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016197354A JP2018059664A (en) | 2016-10-05 | 2016-10-05 | Evaporator and refrigerant circuit |
Publications (2)
Publication Number | Publication Date |
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EP3306232A1 true EP3306232A1 (en) | 2018-04-11 |
EP3306232B1 EP3306232B1 (en) | 2019-05-22 |
Family
ID=60019756
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP17194600.7A Active EP3306232B1 (en) | 2016-10-05 | 2017-10-03 | Evaporator and refrigerant circuit |
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EP (1) | EP3306232B1 (en) |
JP (1) | JP2018059664A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN113171627A (en) * | 2021-04-14 | 2021-07-27 | 响水中山生物科技有限公司 | Distillation plant in adjustable bentazone production |
US11156412B2 (en) * | 2016-09-12 | 2021-10-26 | Mitsubishi Electric Corporation | Heat exchanger and air-conditioning apparatus |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3310236A1 (en) * | 1983-03-22 | 1984-09-27 | Autokühler-Gesellschaft mbH, 3520 Hofgeismar | Refrigerant distributor for the evaporator of a refrigerator or heat pump |
JPH0325656A (en) | 1989-06-23 | 1991-02-04 | Nec Corp | Slave processor |
JPH0331665A (en) * | 1989-06-28 | 1991-02-12 | Matsushita Electric Ind Co Ltd | Flow diverter |
JPH03260567A (en) * | 1990-03-08 | 1991-11-20 | Mitsubishi Electric Corp | Two-phase fluid distributor for gas and liquid |
JPH094995A (en) * | 1995-06-19 | 1997-01-10 | Matsushita Refrig Co Ltd | Header |
WO2010143704A1 (en) * | 2009-06-12 | 2010-12-16 | ダイキン工業株式会社 | Flow divider, expansion valve with the flow divider, and refrigeration device with the expansion valve |
WO2013095424A1 (en) * | 2011-12-21 | 2013-06-27 | Alstom Technology Ltd | Shape optimized headers and methods of manufacture thereof |
US20150226472A1 (en) * | 2014-02-07 | 2015-08-13 | Pdx Technologies Llc | Refrigeration system with separate feedstreams to multiple evaporator zones |
-
2016
- 2016-10-05 JP JP2016197354A patent/JP2018059664A/en active Pending
-
2017
- 2017-10-03 EP EP17194600.7A patent/EP3306232B1/en active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3310236A1 (en) * | 1983-03-22 | 1984-09-27 | Autokühler-Gesellschaft mbH, 3520 Hofgeismar | Refrigerant distributor for the evaporator of a refrigerator or heat pump |
JPH0325656A (en) | 1989-06-23 | 1991-02-04 | Nec Corp | Slave processor |
JPH0331665A (en) * | 1989-06-28 | 1991-02-12 | Matsushita Electric Ind Co Ltd | Flow diverter |
JPH03260567A (en) * | 1990-03-08 | 1991-11-20 | Mitsubishi Electric Corp | Two-phase fluid distributor for gas and liquid |
JPH094995A (en) * | 1995-06-19 | 1997-01-10 | Matsushita Refrig Co Ltd | Header |
WO2010143704A1 (en) * | 2009-06-12 | 2010-12-16 | ダイキン工業株式会社 | Flow divider, expansion valve with the flow divider, and refrigeration device with the expansion valve |
WO2013095424A1 (en) * | 2011-12-21 | 2013-06-27 | Alstom Technology Ltd | Shape optimized headers and methods of manufacture thereof |
US20150226472A1 (en) * | 2014-02-07 | 2015-08-13 | Pdx Technologies Llc | Refrigeration system with separate feedstreams to multiple evaporator zones |
Cited By (2)
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 |
CN113171627A (en) * | 2021-04-14 | 2021-07-27 | 响水中山生物科技有限公司 | Distillation plant in adjustable bentazone production |
Also Published As
Publication number | Publication date |
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EP3306232B1 (en) | 2019-05-22 |
JP2018059664A (en) | 2018-04-12 |
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