US20150241132A1 - Double pipe heat exchanger and refrigeration cycle device - Google Patents

Double pipe heat exchanger and refrigeration cycle device Download PDF

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Publication number
US20150241132A1
US20150241132A1 US14/432,630 US201314432630A US2015241132A1 US 20150241132 A1 US20150241132 A1 US 20150241132A1 US 201314432630 A US201314432630 A US 201314432630A US 2015241132 A1 US2015241132 A1 US 2015241132A1
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United States
Prior art keywords
pipe
transfer area
heat transfer
heat exchanger
area enlargement
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Abandoned
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US14/432,630
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English (en)
Inventor
Satoru Yanachi
Yohei Kato
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KATO, YOHEI, YANACHI, SATORU
Publication of US20150241132A1 publication Critical patent/US20150241132A1/en
Abandoned legal-status Critical Current

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    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F25B2400/13—Economisers
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/105—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being corrugated elements extending around the tubular elements

Definitions

  • the present invention relates to a double pipe heat exchanger in which circular pipes having different pipe diameters are combined to form two channels, and to a refrigeration cycle device including this double pipe heat exchanger.
  • Examples of conventional double pipe heat exchangers having enhanced heat-transfer performances include one in which a circular pipe having the smaller diameter (hereafter, referred to as an inner pipe) is inserted into a circular pipe having the larger diameter (hereafter, referred to as an outer pipe).
  • an inner pipe a circular pipe having the smaller diameter
  • an outer pipe a circular pipe having the larger diameter
  • a method is proposed in which the inside of the inner pipe is defined as a first channel, a channel between the two circular pipes is defined as a second channel, and a heat transfer area enlargement pipe that is formed into an undulating shape is inserted into the second channel and brought into intimate contact with the inner pipe and the outer pipe, so as to enhance a heat-transfer performance through an effect of increasing heat-transfer area (see, e.g., Patent Literature 1).
  • Patent Literature 1 Japanese Patent Laid-Open No. 2012-63067 ( FIG. 1 )
  • Patent Literature 1 proposes a double pipe heat exchanger in which a heat transfer area enlargement pipe is inserted to expand a heat-transfer area so as to enhance a heat-transfer performance.
  • Patent Literature 1 does not mention a specific measure and the like taken against the heat transfer area enlargement pipe that can enhance the heat-transfer performance efficiently.
  • the present invention has an object to obtain a double pipe heat exchanger and a refrigeration cycle device that can enhance a heat-transfer performance efficiently.
  • a double pipe heat exchanger includes an inner pipe inside which a first fluid passes, an outer pipe that has a diameter larger than the diameter of the inner pipe and that covers the inner pipe, the inner pipe and the outer pipe configured to allow a second fluid to pass through a space therebetween, and a heat transfer area enlargement pipe that is provided in the space and in which an angle between the heat transfer area enlargement pipe and the outer wall of the inner pipe at each of inner contact portions to be contact areas between an outer wall of the inner pipe and the heat transfer area enlargement pipe is smaller than an angle between the heat transfer area enlargement pipe and the inner wall of the outer-pipe at each of outer contact portions to be contact areas between an inner wall of the outer pipe and the heat transfer area enlargement pipe the heat transfer area enlargement pipe having a projection-depression shape in a pipe cross section in which fin portions between the inner contact portions and the outer contact portions that traverse the space in the pipe cross section come into contact with the outer wall of the inner-pipe and the inner wall of the outer-pipe in ob
  • a heat transfer area enlargement pipe that is in contact with an outer pipe and an inner pipe is provided in such a manner that the length in a pipe-circumferential direction of a contact area with the outer wall of the inner pipe is made larger than the length of the contact area with the inner wall of the outer pipe, and it is thus possible to scatter external force applied to the heat transfer area enlargement pipe in manufacturing, and to expand a heat-transfer area while suppressing poor contact in particular with the inner pipe, so as to enhance a heat-transfer performance.
  • FIG. 1 is a diagram for illustrating the configuration of a double pipe heat exchanger according to a first embodiment of the present invention.
  • FIG. 2 is a diagram showing a cross section of the double pipe heat exchanger according to the first embodiment of the present invention, in the other direction.
  • FIG. 3 is a diagram showing a cross section of a double pipe heat exchanger according to a third embodiment of the present invention.
  • FIG. 4 is a diagram for illustrating a lift of a heat transfer area enlargement pipe 3 .
  • FIG. 5 is a diagram showing parameters that are set to the double pipe heat exchanger.
  • FIG. 6 is a diagram showing brazed portions according to a fourth embodiment of the present invention.
  • FIG. 7 is a diagram showing refrigeration cycle devices each including the double pipe heat exchanger according to the present invention.
  • FIG. 1 is a diagram for illustrating the configuration of a double pipe heat exchanger according to a first embodiment of the present invention.
  • FIG. 1 shows a cross sectional view of the double pipe heat exchanger taken along the direction of flow of refrigerant (in an inner pipe 2 in particular).
  • the double pipe heat exchanger is formed by inserting the inner pipe 2 serving as a circular pipe having a smaller diameter into the inside of an outer pipe 1 serving as a circular pipe having a larger diameter.
  • end portions of the heat exchanger having a double cylinder structure is configured such that an inner-wall portion of the outer pipe 1 (outer-pipe inner wall) comes into contact with an outer-wall portion of the inner pipe 2 (inner-pipe outer wall) (such that side-wall portions closing the outer pipe 1 cover the inner pipe 2 ).
  • the inside of the inner pipe 2 is defined as an inner channel 4 serving as a first channel
  • a space formed between the inner pipe 2 and the outer pipe 1 is defined as an outer channel 5 serving as a second channel.
  • An inlet and outlet of the outer channel 5 for a refrigerant are through holes formed in the wall surface of the outer pipe 1 and connects contact pipes.
  • a first fluid and a second fluid are allowed to flow in the inner channel 4 and the outer channel 5 , respectively.
  • the first fluid and the second fluid having different temperatures flow through the respective channels, which enables heat exchange between the fluids in the double pipe heat exchanger.
  • FIG. 2 is a diagram showing a cross section of the double pipe heat exchanger according to the first embodiment of the present invention, taken along another direction.
  • FIG. 2 shows an A-A′ cross section in FIG. 1 (a pipe cross section. A cross section taken along a pipe-circumferential direction when viewed in a direction in which the fluids flow).
  • the double pipe heat exchanger of the present embodiment is configured by further inserting a heat transfer area enlargement pipe 3 having an undulating shape that includes projections and depressions, into a space portion of the outer channel 5 .
  • an inner wall comes into contact with the inner-pipe outer wall at the depressed portions
  • an outer wall comes into contact with the outer-pipe inner wall at the projecting portions.
  • a side wall obliquely traverses the outer channel 5 (the space between the inner pipe 2 and the outer pipe 1 ) in the pipe cross section, and comes into contact with the inner-pipe outer wall and the outer-pipe inner wall in oblique directions.
  • the amount of heat exchange Q, a heat-transfer area A, a heat transfer coefficient K, and a difference dT in temperature between the first fluid and the second fluid relating to the heat exchange generally have a relationship represented by Expression (1).
  • the heat transfer coefficient K is represented by Expression (2).
  • ⁇ 1 is the heat transfer coefficient of the first fluid
  • d 1 is the hydraulic diameter of the inner channel 4
  • ⁇ 2 is the heat transfer coefficient of the second fluid
  • d 2 is the hydraulic diameter of the outer channel 5 .
  • ⁇ is the thermal conductivity of the inner pipe 2
  • dio is the outer diameter of the inner pipe 2
  • dii is the inner diameter of the inner pipe 2
  • R is a thermal resistance.
  • the heat transfer area enlargement pipe 3 comes into contact with the inner pipe 2 to serve as a fin, enabling the enlargement of the heat-transfer area relating to the heat exchange, which enables the increase of the amount of heat exchanged between the first fluid and the second fluid.
  • contact areas between the inner-pipe outer wall and the inner wall of the heat transfer area enlargement pipe are defined as inner contact portions 6 (and the length of the contact portions in the pipe-circumferential direction is denoted as L 1 ).
  • contact areas between the outer-pipe inner wall and the outer wall of the heat transfer area enlargement pipe are defined as outer contact portions 7 (and the length of the contact portion in the pipe-circumferential direction is defined as L 2 ).
  • portions serving as fins between the inner contact portions 6 and the outer contact portions 7 (side wall surfaces in the projection-depression shape) are defined as fin portions 16 .
  • the double pipe heat exchanger is preferably formed such that the inner contact portions 6 and the outer contact portions 7 are each brought into contact at one point (point contact) in the pipe cross section.
  • the reduction of the contact areas increases, for example, the number of the fin portions 16 in a pipe circumference, a heat-transfer area per fin portion 16 , and the like, increasing the heat-transfer area of the whole double pipe heat exchanger.
  • points as referred below do not mean mathematical points, which have no area or the like, but mean points that have areas to an extent of securing reliable contacts between the pipes. Note that the contacts will be described as the point contacts, but the contact areas are linear in the double pipe heat exchanger as a whole.
  • the contact thermal resistance at each inner contact portions 6 is increased. This reduces the heat transfer coefficient K in the above-described Expression (2), resulting in the reduction of the amount of heat exchange Q.
  • forming the inner contact portions 6 to be the point contacts may cause spots of poor contact. If there are spots at which, for example, the inner-pipe outer wall is not in contact with the inner wall of the heat transfer area enlargement pipe when the inner contact portions 6 are formed to be the point contacts, poor heat transfer occurs, which prevents many heat-transfer areas from being used efficiently.
  • the outer contact portions 7 are formed to be point contacts (the length L 2 is reduced to zero) so as to expand the heat-transfer area.
  • the inner contact portions 6 are formed to have a contact length in the pipe cross section (contact areas are to form surfaces in the double pipe heat exchanger as a whole).
  • the outer contact portions 7 are formed to be the point contacts so as to enlarge the heat-transfer area, and the inner contact portions 6 are formed to have the contact length, which enables the prevention of the poor contact between the inner-pipe outer wall and the inner wall of the heat transfer area enlargement pipe. This does not impair but can enhance a heat-transfer performance.
  • the above-described double pipe heat exchanger of the first embodiment includes, as shown in FIG. 2 , the heat transfer area enlargement pipe 3 having the projection-and-depression (undulating) shape, in the outer channel 5 formed between the outer pipe 1 and the inner pipe 2 .
  • the inner wall of the heat transfer area enlargement pipe is in contact with the inner-pipe outer wall
  • the outer wall of the heat transfer area enlargement pipe is in contact with the outer-pipe inner wall.
  • the fin portions 16 to be the side walls traverse the outer channel 5 in the pipe cross section.
  • portions of the heat transfer area enlargement pipe 3 to be the fin portions 16 are formed to be perpendicular to the outer pipe 1 and the inner pipe 2 , forces applied to portions to be the inner contact portions 6 or the outer contact portions 7 are applied directly to the fin portions 16 , in expanding or shrinking the pipe. This incurs the risk of forming the fin portions 16 bent into an unexpected shape. For this reason, the portions to be the fin portions 16 are formed not to be perpendicular, reducing loads posed on the portions to be the fin portions 16 in expanding or shrinking the pipe. Then, the fin portions 16 are brought into contact with the inner-pipe outer wall and the outer-pipe inner wall in oblique directions.
  • an angle a at which the inner-pipe outer wall comes into contact with the inner wall of the heat transfer area enlargement pipe and an angle 13 at which the outer wall of the heat transfer area enlargement pipe comes into contact with the outer-pipe inner wall are made to be angles less than 90 degrees, although this is not in particular intended to limit the angles.
  • FIG. 3 is a diagram for illustrating a lift of the heat transfer area enlargement pipe 3 .
  • the inner contact portions 6 of the heat transfer area enlargement pipe 3 may be deformed, and middle portions thereof, which should be in contact, may be lifted.
  • the occurrence of the lift may increase, for example, the contact thermal resistance, which may impair a heat-transfer performance.
  • the fin portions 16 are brought into contact with the inner-pipe outer wall and the outer-pipe inner wall in the oblique directions, and in addition, the heat transfer area enlargement pipe 3 to be inserted into the outer channel 5 of the double pipe heat exchanger is made to have a shape in which the portions to be the fin portions 16 , between the portions to be the inner contact portions 6 (depressed portions) and the portions to be the outer contact portions 7 (projecting portions), are formed into arc shapes in the pipe cross section.
  • Forming such a shape allows the heat transfer area enlargement pipe 3 to be deformed to bend, spreading (absorbing) loads on the heat transfer area enlargement pipe 3 even when the heat transfer area enlargement pipe 3 is pressed excessively against the inner pipe 2 in expanding the inner pipe 2 or shrinking the outer pipe 1 . For this reason, also in the inner contact portions 6 , unreasonable forces are not applied to the heat transfer area enlargement pipe 3 , which can prevent a lift. This does not lose but can enhance a heat-transfer performance.
  • directions in which the portions to be the fin portions 16 are bent through expanding or shrinking are preferably directions in which the formed fin portions 16 project toward the inner pipe 2 side.
  • the fin portions 16 are deformed toward the inner pipe 2 side, increasing the contact areas between the fin portions 16 and the inner pipe 2 , which enlarges the inner contact portions 6 in length. Heat can be thereby efficiently transmitted from the inner pipe 2 .
  • the angle ⁇ the angle ⁇ is satisfied, which reduces gaps between the heat transfer area enlargement pipe 3 and the inner pipe 2 in size. Therefore, for example, in brazing the inner contact portion 6 , a brazing material is easy to penetrate. This allows heat to be further efficiently transmitted from the inner pipe 2 .
  • the increase of the angle ⁇ weakens pressing force in the contact areas between the fin portions 16 and the outer pipe 1 , which can suppress the enlargement of the outer contact portions 7 in size.
  • the shape of the heat transfer area enlargement pipe 3 is the arc shape, but is not limited to the arc shape, and a shape having a bent portion at least at one point can bring the advantages of scattering the loads on the portions to be the fin portions 16 and of preventing a lift in the inner contact portions 6 .
  • the above description similarly holds in a double pipe heat exchanger in which, for example, the outer contact portions 7 are not the point contact, and similar advantages can be brought.
  • FIG. 4 is a diagram showing a double pipe heat exchanger according to a third embodiment of the present invention.
  • FIG. 4 shows a pipe cross section similar to the A-A′ section in FIG. 1 described in the first embodiment.
  • the double pipe heat exchanger of the present embodiment is configured such that the length L 1 of the inner contact portions 6 between the inner-pipe outer wall and the inner wall of the heat transfer area enlargement pipe and the length L 2 of the outer contact portions 7 between the outer-pipe inner wall and the outer wall of the heat transfer area enlargement pipe satisfy L 1 >L 2 .
  • end points of the inner contact portion 6 may serve as fulcra to generate deformation when excessive external forces are applied to the outer pipe 1 , the inner pipe 2 , and the heat transfer area enlargement pipe 3 .
  • the middle portion of the inner contact portion 6 may be lifted from the inner pipe 2 , resulting in the loss of heat-transfer performance.
  • FIG. 5 is a diagram showing parameters that are set for shape analysis of the double pipe heat exchanger according to the third embodiment of the present invention.
  • the number of projecting portions (depressed portions) of the heat transfer area enlargement pipe 3 is denoted by n
  • the outer diameter of the inner-pipe is denoted by dio
  • the inner diameter of the outer pipe is denoted by doi.
  • AO denotes an angle between the top of a projecting portion of the heat transfer area enlargement pipe 3 and the top of the next projecting portion
  • ⁇ 1 denotes an angle that serves as a guide for forming the projecting portions
  • ⁇ 2 denotes an angle that serves as a guide for forming the depressed portions.
  • a length along which the inner pipe 2 is in contact with the heat transfer area enlargement pipe 3 is denoted by L 1
  • a length along which the outer pipe 1 is in contact with the heat transfer area enlargement pipe 3 is denoted by L 2 .
  • the shape of the projecting portions and the shape of the depressed portions are all an identical shape in the heat transfer area enlargement pipe 3 .
  • ⁇ 0 , ⁇ 1 , ⁇ 2 , ⁇ 1 ′, and ⁇ 2 ′ are geometrically represented by Expressions (3) to (6).
  • the length L 1 of the inner contact portions 6 and the length L 2 of the outer contact portions 7 can be represented by Expressions (7) and (8) respectively.
  • the length L 1 of the inner contact portions 6 between the inner-pipe outer wall and the inner wall of the heat transfer area enlargement pipe, the length L 2 of the outer contact portions 7 between the outer-pipe inner wall and the outer wall of the heat transfer area enlargement pipe are made to have the relationship of L 1 >L 2 , and thus the external forces applied to the outer contact portions 7 can be scattered.
  • the external forces applied to inner contact portions 6 substantially identical to the external forces applied to outer contact portions 7 excessive external forces are not applied only to the inner contact portions 6 but scattered, which can prevent a lift in the inner contact portions 6 . The above enables the prevention of excessive deformation of each pipe.
  • each contact area is brazed with a brazing material 15 so as to further secure the contact between the inner-pipe outer wall and the inner wall of the heat transfer area enlargement pipe, and the contact between the outer-pipe inner wall and the outer wall of the heat transfer area enlargement pipe.
  • FIG. 6 is a diagram showing brazed portions according to a fourth embodiment of the present invention.
  • a brazing material 15 or the like is applied, furnace brazing or the like is performed to melt the brazing material 15 , brazing contact portions.
  • the pipes are made of an aluminum or the like, an Al—Si-based (aluminum-silicon-based) alloy in which an aluminum is alloyed with a silicon is used as the brazing material 15 .
  • a cladding material in which the heat transfer area enlargement pipe 3 is clad in (covered with) the brazing material 15 in advance may be used.
  • a fifth embodiment there will be described an example of a refrigeration cycle device to which the double pipe heat exchanger described in the first to fourth embodiments is applied.
  • four kinds of configurations of the refrigeration cycle device will be described.
  • FIG. 7 is a diagram showing examples of the configurations of the refrigeration cycle devices according to the fifth embodiment.
  • a compressor 8 a condensor 9 , an expansion valve 10 , an evaporator 11 , and a double pipe heat exchanger 12 are connected with pipes to configure a refrigerant circuit.
  • the compressor 8 sucks and compresses a refrigerant, and discharges the refrigerant at a high temperature and pressure.
  • the compressor 8 may be configured by, for example, a compressor that controls a rotation speed with an inverter circuit or the like to adjust the amount of discharged refrigerant.
  • the condensor 9 to be a heat exchanger is for performing heat exchange between, for example, air supplied from a blower (not shown) and the refrigerant to condense the refrigerant into a liquid refrigerant (to condense and liquefy the refrigerant).
  • the expansion valve (pressure-reducing valve or throttle) 10 is for decompressing and expanding the refrigerant.
  • the expansion valve is configured by, for example, flow control means such as an electronic expansion valve, and may be configured by, for example, refrigerant amount adjusting means or the like such as an expansion valve and a capillary including a temperature sensitive cylinder.
  • the evaporator 11 is for performing heat exchange between air or the like to evaporate the refrigerant into a gas refrigerant (to evaporate and gasify).
  • the double pipe heat exchanger 12 of the refrigeration cycle device in FIG. 7( a ) performs heat exchange between a refrigerant at a high temperature and pressure flowing from the condensor 9 and a refrigerant at a low temperature and pressure flowing from the evaporator 11 .
  • Using the double pipe heat exchanger 12 in such a manner enables increasing the temperature of the refrigerant in the condensor 9 . It is thereby possible to enhance a capability in heating, and to increase a COP (Coefficient Of Performance: a value obtained by dividing a capability by an input).
  • the refrigerant flowing from the evaporator 11 can be gasified, which can prevent the liquid refrigerant from returning to the compressor 8 .
  • the double pipe heat exchanger 12 of a refrigeration cycle device in FIG. 7( b ) performs heat exchange between a high-pressure liquid refrigerant at a refrigerant outlet of the condensor 9 and a middle-pressure two-phase refrigerant that has passed through the flow control valve 13 . Then, the refrigerant that has been subjected to the heat exchange and has changed into a middle-pressure gas refrigerant is caused to perform bypassing to a suction-side pipe to the compressor 8 .
  • the refrigeration cycle device in FIG. 7( b ) causes the refrigerant that has passed through the condensor 9 to diverge before passing through the expansion valve 10 and to perform bypassing using the double pipe heat exchanger 12 , which can reduce the amount of refrigerant flowing downstream side from the expansion valve 10 . It is thereby possible to reduce pressure drop, increasing the COP.
  • the double pipe heat exchanger 12 of the refrigeration cycle device in FIG. 7( c ) performs heat exchange between a high-pressure liquid refrigerant at the refrigerant outlet of the condensor 9 and a middle-pressure two-phase refrigerant that has passed through the flow control valve 13 . Then, the refrigerant that has been subjected to the heat exchange and has changed into a middle-pressure gas refrigerant is injected into a middle portion of a compression part of the compressor 8 .
  • the compressor 8 of the refrigeration cycle device in FIG. 7( c ) is a compressor having a multistage configuration that can perform the injection.
  • the refrigeration cycle device in FIG. 7( c ) causes the refrigerant that has passed through the condensor 9 to diverge before passing through the expansion valve 10 and to perform bypassing using the double pipe heat exchanger 12 , which can reduce the amount of refrigerant flowing downstream side from the expansion valve 10 .
  • the injection into the middle portion of the compressing part of the compressor 8 having the multistage configuration can be performed, and thus an input such as the discharge temperature of the compressor can be reduced, increasing the COP.
  • the refrigeration cycle device in FIG. 7( d ), the double pipe heat exchanger 12 is used as a condensor. Then, a fluid to be subjected to heat exchange with a refrigerant flowing through a refrigerant circuit is assumed to be water, brine, or the like (hereafter, the description will be made assuming that the fluid is water).
  • a pump 14 forms the flow of water and supplies the water into the double pipe heat exchanger 12 .
  • the water is heated through the heat exchange with the refrigerant.
  • the double pipe heat exchanger 12 is used as the condensor, and can be used as an evaporator.

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  • 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)
US14/432,630 2012-10-02 2013-09-03 Double pipe heat exchanger and refrigeration cycle device Abandoned US20150241132A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JPPCT/JP2012/075530 2012-10-02
PCT/JP2012/075530 WO2014054117A1 (ja) 2012-10-02 2012-10-02 二重管式熱交換器および冷凍サイクル装置
PCT/JP2013/073688 WO2014054370A1 (ja) 2012-10-02 2013-09-03 二重管式熱交換器および冷凍サイクル装置

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US (1) US20150241132A1 (de)
EP (1) EP2916091B1 (de)
JP (1) JP5944009B2 (de)
CN (2) CN104704311B (de)
WO (2) WO2014054117A1 (de)

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US11644252B2 (en) * 2019-03-28 2023-05-09 Ngk Insulators, Ltd. Flow path structure of heat exchanger, and heat exchanger
US11719489B2 (en) * 2019-03-27 2023-08-08 Ngk Insulators, Ltd. Heat exchanger

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JP6471867B2 (ja) * 2015-10-06 2019-02-20 スズキ株式会社 排熱回収装置
CN107166995A (zh) * 2017-06-17 2017-09-15 福建德兴节能科技有限公司 高效换热器及其用途
JP6844791B2 (ja) * 2018-11-21 2021-03-17 株式会社ニチリン 二重管式熱交換器の製造方法
CN109848499B (zh) * 2019-03-08 2021-05-14 西安远航真空钎焊技术有限公司 一种复杂换热器芯体的制备方法
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WO2014054370A1 (ja) 2014-04-10
EP2916091A4 (de) 2016-08-10
JP5944009B2 (ja) 2016-07-05
JPWO2014054370A1 (ja) 2016-08-25
CN203605763U (zh) 2014-05-21
CN104704311B (zh) 2017-03-01
CN104704311A (zh) 2015-06-10

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