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WO2013132679A1 - Échangeur de chaleur et dispositif de cycle de réfrigération - Google Patents

Échangeur de chaleur et dispositif de cycle de réfrigération Download PDF

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Publication number
WO2013132679A1
WO2013132679A1 PCT/JP2012/072132 JP2012072132W WO2013132679A1 WO 2013132679 A1 WO2013132679 A1 WO 2013132679A1 JP 2012072132 W JP2012072132 W JP 2012072132W WO 2013132679 A1 WO2013132679 A1 WO 2013132679A1
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WO
WIPO (PCT)
Prior art keywords
fluid
heat exchanger
fluid flow
flow path
heat
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.)
Ceased
Application number
PCT/JP2012/072132
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English (en)
Japanese (ja)
Inventor
宗史 池田
寿守務 吉村
瑞朗 酒井
裕之 森本
傑 鳩村
進一 内野
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2014503412A priority Critical patent/JP5784215B2/ja
Priority to EP12870627.2A priority patent/EP2840342B1/fr
Publication of WO2013132679A1 publication Critical patent/WO2013132679A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
    • F28F7/02—Blocks traversed by passages for heat-exchange media
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators

Definitions

  • the present invention relates to a heat exchanger and a refrigeration cycle apparatus, and in particular, a heat exchanger having a first fluid channel through which a high-temperature fluid flows and a second fluid channel through which a low-temperature fluid flows in a heat transfer block, and the heat exchanger. Relates to the refrigeration cycle apparatus.
  • a heat pump refrigeration / air-conditioning system including a vapor compression refrigeration circuit has been used.
  • a heat exchanger for exchanging heat between the first fluid and the second fluid is provided in the refrigeration circuit.
  • the first fluid channel through which the first fluid flows and the second fluid channel through which the second fluid flows are arranged substantially in parallel in the same block (solid), and the respective fluids are in the same direction with each other. (Hereinafter referred to as “parallel” or “parallel flow”) or in opposite directions (hereinafter referred to as “opposite” or “opposite flow”), and heat exchange is performed between the two.
  • the first fluid is “water” and the second fluid is “R410a”, and heat is exchanged between the low-temperature and low-pressure water and the high-temperature and high-pressure R410a to heat the water (at this time, R410a is Cooled).
  • the first fluid channel or the second fluid channel has a small diameter. By reducing the diameter, the heat transfer area per unit volume of the heat exchanger can be increased, and high heat transfer can be realized.
  • the first fluid channel and the second fluid are not included in the same block (solid), only one channel is formed in the block, and the block is disposed in the other channel.
  • a tube for heat exchange in which a flow path formed in a block is reduced in diameter is formed by integrally extruding a row of a plurality of flow paths through which a fluid flows in a flat cross section (for example, , See Patent Document 1).
  • the block since the block is arranged in the other channel, the block is located on the upstream side of the other channel and the downstream side of the other channel. Since there is a temperature difference (difference in heat exchange amount) with the flow path in the block, a horizontal hole is provided to communicate the flow path in the block located on the downstream side from the flow path in the block located on the upstream side, The difference in fluid temperature between the flow paths in the block is reduced. For this reason, in order to distribute and mix a fluid into each flow path, it is necessary to open a horizontal hole.
  • the combination of the first fluid channel and the second fluid channel is one stage, but when the heat exchanger is configured in multiple stages, the one stage is changed to the other. Since the fluid flows into the stage, the number of times of passing through the header portion increases. For this reason, as a result, the flow path cross-sectional area repeatedly expands and contracts, and the pressure loss of the heat exchanger increases.
  • the ratio of the flow rate of gas and liquid for each flow path in the condition of the fluid flowing into the heat exchanger, particularly in the gas-liquid two-phase state where gas and liquid are mixed is Different or non-uniform distribution occurs and the performance of the heat exchanger deteriorates.
  • the present invention solves the above problem, and even if a plurality of fluid flow paths are communicated with each other, pressure loss can be reduced, and even distribution to each flow path can be realized. It is possible to obtain a heat exchanger capable of suppressing performance degradation and a refrigeration cycle apparatus equipped with the heat exchanger.
  • a heat exchanger according to the present invention is formed in parallel to each other on a first surface, which is a plane in a heat transfer block, and a plurality of rows of first fluid flow paths penetrating the heat transfer block, and in the heat transfer block
  • a second surface parallel to the first surface is formed in parallel to the first fluid flow path, a plurality of rows of second fluid flow paths penetrating the heat transfer block, and formed in the heat transfer block,
  • the lateral hole communicates with the second fluid flow path, and the second fluid flow path is adjacent to the first fluid flow path. Characterized in that it does not protrude to the heat block portion.
  • the cross-sectional area of the horizontal hole can be optimally designed, so that pressure loss can be suppressed, and performance degradation of the heat exchanger can be suppressed by even distribution. be able to.
  • Sectional drawing explaining the A type heat exchanger which concerns on Embodiment 1 of this invention Sectional drawing explaining the B type and C type heat exchanger which concern on Embodiment 1 of this invention, respectively. Sectional drawing explaining the D type heat exchanger which concerns on Embodiment 2 of this invention. Sectional drawing explaining the E type heat exchanger which concerns on Embodiment 2 of this invention. Sectional drawing explaining each F type heat exchanger which concerns on Embodiment 2 of invention. Sectional drawing explaining the H type and I type heat exchanger which concern on Embodiment 3 of this invention. Sectional drawing explaining the J type heat exchanger which concerns on Embodiment 4 of this invention. Sectional drawing explaining the K type, L type, and M type heat exchanger which concern on Embodiment 5 of this invention.
  • the block diagram of the apparatus which shows the heat pump type heating system explaining the refrigerating-cycle apparatus which concerns on Embodiment 7 of this invention.
  • the block diagram of the apparatus which shows the heat pump type hot-water supply system explaining the refrigerating-cycle apparatus which concerns on Embodiment 8 of this invention.
  • Baker diagram referred to for explaining a refrigeration cycle apparatus according to Embodiment 6 of the present invention.
  • FIG. 1A is a cross-sectional view of a cross section perpendicular to the longitudinal direction of the A type
  • FIG. 1 (b) is a cross-sectional view of a cross section parallel to the longitudinal direction of the A type
  • FIG. 2 (a) is a cross sectional view of the B type
  • FIG. 2 (b) is a cross section of the cross section of the B type parallel to the longitudinal direction
  • 2C is a cross-sectional view of the C type
  • FIG. 2D is a cross-sectional view of a cross section parallel to the longitudinal direction of the C type.
  • an A type heat exchanger 10a includes a plurality of (for example, four) first fluid channels 1 and a first fluid channel arranged in a heat transfer block 4. 1 and a plurality of (for example, 45) second fluid flow paths 2a arranged in parallel with each other in a flowing direction, and perpendicular to the second fluid flow paths 2a, and all the second fluid flow paths 2a communicate with each other. And one row of horizontal holes 3a formed to do so.
  • the first fluid channel 1 is disposed on a first surface 41 that is a flat surface, a plurality of rows are disposed in parallel to each other, and has a circular cross section.
  • the second fluid flow path 2a is parallel to the first fluid flow path 1 and has a plurality of rows (for example, 15 rows) arranged in the second surface 42a which is a plane substantially parallel to the first surface 41.
  • a plurality of rows (for example, 15 rows) of second fluid flow paths 21c arranged in 42c are collectively referred to.
  • the second fluid flow paths 2a are arranged in 15 rows each in three layers and have a rectangular cross section.
  • the axial direction of the first fluid channel 1 and the second fluid channel 2a is referred to as the “longitudinal direction”.
  • the above description shows that the first fluid channel 1 has a circular cross-sectional shape and the second fluid channel 2a has a rectangular cross-sectional shape, but the present invention is not limited to this.
  • the shape can be arbitrarily set.
  • the horizontal hole 3a is perpendicular to the second fluid channel and communicates a plurality of rows (for example, 45 rows) of the second fluid channels with each other, but the second fluid channel adjacent to the first fluid channel 1 It does not protrude into the heat transfer block 4 formed between 21a. Further, the pressure loss can be reduced by determining the diameter and number of the horizontal holes 3a according to the mass velocity of the fluid flowing in, the length of the horizontal holes, the size and the number of the second fluid flow paths. .
  • the second fluid flow path as shown in FIG. 1 is arranged in three layers, 15 rows with dimensions of 1 mm ⁇ 1 mm, the length of the heat transfer block is 300 mm, and the length of the lateral hole is 25 mm,
  • the horizontal hole 3a is drilled from one side surface 44 of the heat transfer block 4 by machining (drilling) or plastic working (punching).
  • the present invention does not limit the formation method. Absent.
  • the heat transfer area of the second fluid channel 2a is increased by configuring the second fluid channel 2a so as to extend over a plurality of layers in order to increase the diameter Da of the lateral hole 3a. Accordingly, it is possible to improve the heat exchange performance.
  • the heat exchanger is configured in multiple stages, there is a flow of the second fluid from one stage to the other, and the number of times of passing through the side hole 3a (corresponding to the header portion) increases.
  • the flow path cross-sectional area repeatedly expands and contracts, in the heat exchanger 10a, the flow path cross-sectional area of the horizontal hole 3a is large, so the effect of reducing the pressure loss becomes remarkable.
  • the horizontal hole 3a having the diameter Da of the channel cross-sectional area within the above range has the same diameter in one layer as in the conventional heat exchanger. Since the distance with the 1 fluid flow path 1 can be shortened, it becomes possible to improve heat exchange performance.
  • the horizontal hole 3a having the channel cross-sectional area diameter Da within the above range does not protrude from the heat transfer block 4 formed between the first fluid channel 1 and the second fluid channel 21a. Therefore, since the distance between the first fluid channel 1 and the second fluid channel 21a can be shortened, the heat exchange performance can be improved.
  • the lateral hole 3 a is configured not to protrude from the second fluid flow path 21 c located farthest from the first fluid flow path 1 to the portion of the heat transfer block 4 outside. That is, the height of the horizontal hole 3a is set to fall within the range from the lowest layer to the uppermost layer of the second fluid channel 2a with respect to the second fluid channel 2a arranged to form a plurality of layers. By doing in this way, the thickness of the heat-transfer block 4 can be made thin.
  • the layer of the second fluid channel 2a sandwiched between them is The heat exchange performance can be improved because it can be disposed close to the upper and lower layers of the first fluid flow path 1.
  • the formation method of the heat-transfer block 4 is not limited, For example, if it forms by integral extrusion processing, increase / decrease in the number of the lines of the 1st fluid flow path 1, the number of the 1st surfaces 41, or 2nd fluid. Since it is easy to increase or decrease the number of rows of the flow paths and the number of the second surfaces 42, the flow path cross-sectional area of the horizontal hole 3a can be optimally designed.
  • a pipe joint for example, a tube, not shown
  • the heat exchanger 10a can be used by connecting a pipe of a system (for example, a hot water supply system) to the pipe joint.
  • a pipe of a system for example, a hot water supply system
  • both ends in the longitudinal direction of the second fluid flow path 2a are closed.
  • a lid may be installed in the horizontal hole 3a on the one side surface 44 of the heat transfer block 4 to close the opening.
  • both ends of the second fluid flow path 2a in the longitudinal direction are connected to piping of a system (for example, a hot water supply system) (directly via a pipe joint or indirectly via an external header section). Connected).
  • the fluid flowing through the first fluid channel 1 (first fluid) and the fluid flowing through the second fluid channel 2a (second fluid) are not limited, and tap water, distilled water, and brine are used as the first fluid.
  • natural refrigerants such as chlorofluorocarbon refrigerants and hydrocarbons, and mixtures thereof may be used as the second fluid.
  • the flow direction of the fluid flowing through the first fluid flow path 1 and the flow direction of the fluid flowing through the second fluid flow path 2a may be parallel or opposed.
  • the B type heat exchanger 10b includes four rows of the first fluid flow paths 1 arranged in the heat transfer block 4, and 15 rows of 5 layers (75 rows in total).
  • the heat exchanger 10b includes a plurality of rows (for example, 15 rows) of the second fluid flow paths 21d and 21e disposed on the second surfaces 42d and 42e substantially parallel to the first surface 41, respectively. This is the same as that added to the heat exchanger 10a.
  • the inner diameter Db of the horizontal hole 3b is large because it extends over the five layers of the second fluid flow path 2b.
  • the C-type heat exchanger 10c includes four rows of first fluid flow paths 1 arranged in the heat transfer block 4, and 15 layers in two layers (30 rows in total). Second fluid flow path 2c, and a row of horizontal holes 3c formed perpendicular to the second fluid flow path 2c and communicating with each other. At this time, the inner diameter Dc of the horizontal hole 3c only needs to straddle the two layers of the second fluid flow path 2c, and thus has a small value.
  • the velocity of the fluid increases in the order of liquid, gas-liquid two-phase, and gas at the same mass velocity.
  • it is necessary to design the diameter of the horizontal hole according to the state of the refrigerant, that is, the speed of the refrigerant.
  • the configuration is such that the diameter of the horizontal hole 3 is increased according to the speed change accompanying the fluid state (the A type to the C type are properly used).
  • the pressure loss in the 2nd fluid flow path 2 can be reduced by using each type properly.
  • the diameter of the horizontal hole 3 is the diameter Da that can straddle the second fluid channel 21a and the second fluid channel 21c, but the second fluid channel 21a and the second fluid As long as it can straddle the flow path 21c, the diameter may be smaller than the diameter Da.
  • FIGS. 3 to 5 schematically illustrate a heat exchanger according to Embodiment 2 of the present invention.
  • FIG. 3A is a cross-sectional view in a cross section perpendicular to the longitudinal direction of the D type.
  • 3 (b) is a cross-sectional view of the D type in a cross section parallel to the longitudinal direction
  • FIG. 4 (a) is a cross section of the E type
  • FIG. 4 (b) is a cross section of the E type in a cross section parallel to the longitudinal direction
  • 5A is a cross-sectional view of the F type
  • FIG. 5B is a cross-sectional view of a cross section parallel to the longitudinal direction of the F type.
  • symbol is attached
  • the D-type heat exchanger 10d includes four rows of first fluid flow paths 1 arranged in the heat transfer block 4 and two layers of 15 rows of second fluid flow. It has a channel 2d and a rectangular lateral hole 3d that allows the second fluid channel 2d to communicate with each other. At this time, the horizontal hole 3d has the height of the second fluid channel 2d, has a long side in the longitudinal direction, and is provided perpendicular to the second fluid channel 2d. Other configurations and operations are the same as those in the first embodiment. In the heat exchanger 10d configured as described above, the following operational effects are obtained.
  • the flow path cross-sectional area in the horizontal hole 3d is increased as compared with a circular shape, so that the influence of the expansion / reduction of the flow path is reduced. Therefore, the pressure loss in the horizontal hole 3d, that is, the pressure loss in the heat exchanger 10d is reduced.
  • the length of the long side is designed such that the refrigerant distribution performance is good. Therefore, the performance deterioration of the heat exchanger accompanying the deterioration of distribution performance can be suppressed.
  • the thickness of the heat transfer block 4 is suppressed (not increased) by providing the lateral holes 3d in a rectangular shape, it is possible to reduce the material cost by reducing the thickness of the heat exchanger.
  • the cross-sectional area of the rectangular lateral hole 3d is larger than that in the case where the horizontal hole 3d is formed in a circular shape, the use member filled therein is compared with the case in which the horizontal hole 3d is formed in a circular shape.
  • the material cost can be reduced.
  • the long side of the horizontal hole 3d is the longitudinal direction, but a configuration having a short side in the longitudinal direction may be used.
  • an E-type heat exchanger 10e includes four rows of first fluid flow paths 1 arranged in the heat transfer block 4 and two layers of second fluid flow of 15 rows. It has a channel 2e and an elliptical lateral hole 3e that allows the second fluid channel 2e to communicate with each other. At this time, the horizontal hole 3e has the height of the second fluid channel 2e, has a long side in the longitudinal direction, and is provided perpendicular to the second fluid channel 2e. Other configurations and operations are the same as those in the first embodiment. In the heat exchanger 10e configured as described above, the following operational effects are obtained.
  • the flow passage cross-sectional area in the lateral hole 3e is increased as compared with a circular shape, so that the influence of expansion / reduction of the flow path is reduced. Therefore, the pressure loss in the horizontal hole 3e, that is, the pressure loss in the heat exchanger 10e is reduced.
  • the length of the long side is designed such that the refrigerant distribution performance is good. Therefore, the performance deterioration of the heat exchanger accompanying the deterioration of distribution performance can be suppressed.
  • the thickness of the heat transfer block 4 is suppressed (not increased) by providing the horizontal hole 3e in an elliptical shape, it is possible to reduce the material cost by reducing the thickness of the heat exchanger.
  • the cross-sectional area of the elliptical lateral hole 3e is larger than that in the case where the horizontal hole 3d is formed in a circular shape, the use member filled therein is compared with the case in which the horizontal hole 3d is formed in a circular shape. The material cost can be reduced.
  • the E type heat exchanger 10e is obtained by making one row of rectangular horizontal holes 3d in the D type heat exchanger 10d into an elliptical shape. It becomes easy to form the horizontal hole 3e by machining such as an end mill.
  • the long side of the horizontal hole 3e is the longitudinal direction, but a configuration having a short side in the longitudinal direction may be used.
  • the F type heat exchanger 10f includes four rows of first fluid flow paths 1 arranged in the heat transfer block 4 and 15 layers of second fluid flow in two layers.
  • the passage 2f and a plurality of lateral holes 3f communicating with the second fluid passage 2f are provided.
  • the horizontal hole 3f has a diameter that is the height of the second fluid channel 2f, and is provided in a plurality of rows (for example, two rows) perpendicular to the second fluid channel 2f and in the direction of the channel.
  • Other configurations and operations are the same as those in the first embodiment.
  • the heat exchanger 10f configured as described above, the following operational effects are obtained.
  • the flow path cross-sectional area in the horizontal hole 3f is increased as compared with the case where there is one, so that the influence of the expansion / reduction of the flow path is reduced. Therefore, the pressure loss in the horizontal hole 3f, that is, the pressure loss in the heat exchanger 10f is reduced. Further, by providing a plurality of rows of the horizontal holes 3f, the thickness of the heat transfer block 4 is suppressed (not increased), so that it is possible to reduce the material cost by reducing the thickness of the heat exchanger.
  • the length of the long side is designed such that the refrigerant distribution performance is good.
  • the performance deterioration of the heat exchanger accompanying the deterioration of distribution performance can be suppressed.
  • the thickness of the heat transfer block 4 is suppressed (not increased), so that it is possible to reduce the material cost by reducing the thickness of the heat exchanger. Since the cross-sectional area of the horizontal holes 3f in the plurality of rows is larger than that in the case where the horizontal holes 3f are formed in a single circle, the cross holes are filled in compared to the case where the horizontal holes 3f are configured in a single circle. It becomes possible to reduce the material cost of the used members.
  • the F type heat exchanger 10f is configured such that one row of rectangular lateral holes 3d in the D type heat exchanger 10d is formed in a plurality of rows of circles. It becomes easy to form the horizontal hole 3f by machining such as an end mill. Furthermore, by configuring the horizontal holes 3f in a plurality of rows, it is possible to improve the pressure resistance performance as compared with the case of configuring the rectangular holes and the ellipse. In the above, the horizontal holes 3f are configured in two rows, but the number of rows is not limited.
  • FIG. 6 schematically illustrates a heat exchanger according to Embodiment 3 of the present invention.
  • FIG. 6A is a cross-sectional view in a cross section perpendicular to the longitudinal direction of the H type
  • FIG. b) is a cross-sectional view in a cross section parallel to the longitudinal direction of the H type
  • FIG. 6C is a cross sectional view in a cross section perpendicular to the longitudinal direction of the I type
  • FIG. 6D is parallel to the longitudinal direction of the I type.
  • It is sectional drawing in a simple cross section.
  • symbol is attached
  • an H type heat exchanger 10h includes four layers of first fluid flow paths 1 in one layer and two layers of second fluid flow in one layer in the heat transfer block 4. It has a passage 21a, a horizontal hole 3h, and a slit-like space 5h that is arranged on the opposite side of the first fluid passage 1 in parallel with the second fluid passage 21a. That is, the second fluid flow path 21a has a form sandwiched between the first fluid flow path 1 and the slit-shaped space 5h.
  • the slit-shaped space 5h is disposed on the third surface 43 parallel to the second surface 42a, and the lateral hole 3h is formed so as to straddle the second fluid flow path 21a and the slit-shaped space 5h.
  • Sealing is applied to the slit-shaped space 5h in the portion where the horizontal hole 3h is opened so that the second fluid does not flow from the flow path 21a into the slit-shaped space 5h via the horizontal hole 3h. That is, the sealing block 81 is liquid-tightly installed in a predetermined range of the slit-shaped space 5 h, and the horizontal hole 3 h penetrates a part of the sealing block 81. Note that the sealing process is not limited to the sealing block 81.
  • the side hole 3h is substantially half (semicircle) of a circle having a diameter Dh that covers the second fluid channel 21a and the slit-shaped space 5h in the side view, and the first fluid channel 1 and the second fluid channel. It functions as a flow path communicating with 21a.
  • Other configurations and operations are the same as those in the first embodiment.
  • the following effects can be obtained.
  • the flow path cross-sectional area the area of the semicircular communication portion
  • the pressure loss in the horizontal hole 3h that is, the heat exchanger 10h is reduced.
  • the slit-shaped space 5h the slit-shaped space 5h portion becomes a heat insulating layer, and the heat exchange performance is improved by preventing heat radiation from the second fluid flow path 21a to the outside of the heat transfer block 4.
  • the horizontal hole 3h has a circular cross section, but the shape is not limited.
  • an I type heat exchanger 10i is obtained by dividing the slit-shaped space 5h in the H-type heat exchanger 10h into a plurality of slit-shaped spaces 5i.
  • the slit-shaped space 5i having a rectangular cross section is shown, the present invention is not limited to this, and may be a rectangle such as a circle, an ellipse, or a square.
  • the sealing block 82 is liquid-tightly installed in a predetermined range in the slit-shaped space 5i having a rectangular cross section.
  • the heat exchanger 10i can obtain the same effect as the heat exchanger 10h, and the rigidity of the side surface 45 close to the slit-like space 5i of the heat transfer block 4 is increased, so that heat transfer is performed as compared with the heat exchanger 10h.
  • the block 4 is more difficult to deform.
  • the formation method of the heat-transfer block 4 is not limited, For example, if it forms by integral extrusion processing, increase / decrease in the number of the lines of the 1st fluid flow path 1, the number of the 1st surfaces 41, or 2nd fluid. As the number of flow paths and the number of second surfaces 42 increase or decrease, the degree of freedom in selecting the form of the slit-shaped space 5 i increases.
  • Embodiment 4 7 schematically illustrates a heat exchanger according to Embodiment 4 of the present invention, in which (a) is a cross-sectional view in a cross section perpendicular to the longitudinal direction of the J type, and (b) is a J type. It is sectional drawing in a cross section parallel to a longitudinal direction.
  • symbol is attached
  • the heat exchanger 10j is a two-layered slit-like space 5i in the I-type heat exchanger 10i. That is, the slit-shaped space 5j includes a plurality of lower-layer slit-shaped spaces 51a disposed intermittently on the third surface 43a parallel to the second surface 42a, and a plurality disposed intermittently on the third surface 43b parallel to the third surface 43a. Upper-layer slit-like space 51b.
  • Each of the lower layer slit-like space 51a and the upper layer slit-like space 51b has a substantially square cross section, and the upper layer slit-like space 51b is disposed above the range sandwiched between the pair of lower-layer slit-like spaces 51a (a pair of upper-layer slit-like spaces 51a).
  • the lower slit-like space 51a is arranged below the area sandwiched by 51b), and has a checkered pattern.
  • a sealing block 83a and a sealing block 83b are liquid-tightly installed in predetermined ranges of the lower layer slit-like space 51a and the upper layer slit-like space 51b, respectively.
  • the slit-shaped space 5j is the same as the H-type heat exchanger 10h except that the slit-shaped space 5j is constituted by the lower-layer slit-shaped space 51a and the upper-layer slit-shaped space 51a that are fine flow paths. 10j has the same effect as the heat exchanger 10h.
  • the formation method of the heat-transfer block 4 is not limited, For example, if it forms by integral extrusion processing, increase / decrease in the number of the lines of the 1st fluid flow path 1, the number of the 1st surfaces 41, or 2nd fluid. As the number of flow paths and the number of second surfaces 42 increase or decrease, the degree of freedom in selecting the shape of the slit-shaped space 5j increases.
  • FIG. 8 schematically illustrates a heat exchanger according to Embodiment 5 of the present invention, in which (a) is a cross-sectional view in a cross section perpendicular to the longitudinal direction of the K type, and (b) is a K type. Sectional view in a cross section parallel to the longitudinal direction, (c) is a sectional view in a section perpendicular to the longitudinal direction of the L type, (d) is a sectional view in a section parallel to the longitudinal direction of the L type, (e) is an M type Sectional drawing in a cross section perpendicular
  • symbol is attached
  • the K-type heat exchanger 10k includes four rows of the first fluid flow paths 1 arranged in the heat transfer block 4, and six layers of 15 rows (total of 90 rows). Second fluid flow path 2k and a row of horizontal holes 3k that are perpendicular to the second fluid flow path 2k and are formed to communicate with each other. That is, in the heat exchanger 10k, a plurality of rows (for example, 15 rows) of second fluid flow paths 21f arranged on the second surface 42f substantially parallel to the first surface 41 are added to the B type heat exchanger 10b. Is the same. At this time, the inner diameter Dk of the horizontal hole 3k is a large value because it extends over the six layers of the second fluid flow path 2k.
  • an L-type heat exchanger 10l (10 ell) is obtained by dividing the lateral hole 3k in the K-type heat exchanger 10k into two strips. That is, the three layers of the second fluid flow paths 21a to 21c are a lower layer group, and the three layers of the small-diameter lateral hole 33a that communicates all the second fluid flow paths 21a to 21c of the lower layer group and the second fluid flow paths 21d to 21f. Is formed as an upper layer group, and a horizontal hole 3l (3 ell) is formed which includes a small-diameter horizontal hole 33b that communicates all the second fluid flow paths 21d to 21f of the upper layer group.
  • the inner diameter of the horizontal hole 3l (3 ell) is approximately 1 ⁇ 2 of the inner diameter of the horizontal hole 3k.
  • the fluid velocity increases in the order of liquid, gas-liquid two-phase, and gas at the same mass velocity.
  • an M type heat exchanger 10m is obtained by dividing the horizontal hole 3k in the K type heat exchanger 10k into three strips. That is, the two layers of the second fluid flow paths 21a and 21b are set as a lower layer group, and the two layers of the small-diameter lateral hole 32a that communicates all the second fluid flow paths 21a and 21b of the lower layer group and the second fluid flow paths 21c and 21d.
  • the middle layer group Is the middle layer group, and the two layers of the small-diameter lateral hole 32b and the second fluid flow channels 21e and 21f communicating with all the second fluid flow paths 21c and 21d of the middle layer group are the upper layer group, and the second fluid flow of the upper layer group
  • a horizontal hole 3m is formed, which includes a small-diameter horizontal hole 32c that allows the passages 21e and 21f to communicate with each other. Therefore, the inner diameter of the horizontal hole 3m is approximately 1/3 of the inner diameter of the horizontal hole 3k. Therefore, in the K-type heat exchanger 10k or the L-type heat exchanger 10l (10 ell), the M-type heat exchanger 10m can be selected when it is not possible to respond to the speed change associated with the fluid state. .
  • the 2nd fluid flow path which consists of 6 layers as an example
  • this invention is not limited to this,
  • the number of layers of a 2nd fluid flow path may be arbitrary.
  • any one of the slit-like spaces 5h to 5j described in the third and fourth embodiments may be provided.
  • the sealing block 81 or the like is installed in any of the provided slit-shaped spaces 5h to 5j, and a part of the installed sealing block 81 or the like is penetrated to provide the provided slit-shaped spaces 5h to 5j.
  • the second fluid flow paths 21d to 21f (or 21e, 21f) of the group closest to any of the above are formed.
  • the horizontal hole described in the first to fifth embodiments may be an ellipse or a rectangle.
  • the width of the horizontal hole can be expanded in the flow direction of the second fluid flow path for the ellipse or the rectangle. That is, the pressure loss can be reduced by determining the cross-sectional area of the horizontal hole in accordance with the mass velocity of the refrigerant flowing in, the ratio of the vapor and liquid mass velocity (hereinafter, dryness).
  • dryness the ratio of the vapor and liquid mass velocity
  • the flows that are easily distributed equally are an annular flow, an annular spray flow, a bubbling flow, a slag flow, and a spiral flow, and it is desirable to flow into the side holes in these flow modes.
  • the appearance of the fluid flow in the two-phase state can be confirmed by a flow pattern diagram (for example, the Baker diagram (see FIG. 11)).
  • the refrigeration cycle apparatus according to Embodiment 6 of the present invention described below takes into consideration the flow mode.
  • the mass velocity of the refrigerant flowing into the side hole is “G”
  • the mass velocities of the gas phase and liquid phase are “Gg and Gl”
  • the density of the gas phase and the liquid phase is “ ⁇ g and ⁇ l”
  • Viscosity coefficient of gas phase and liquid phase is “ ⁇ g and ⁇ l”
  • the surface tension is ⁇ ,
  • the density of air and water at an atmospheric temperature of 20 ° C. is “ ⁇ a and ⁇ w”,
  • FIG. 9 illustrates a refrigeration cycle apparatus according to Embodiment 7 of the present invention, and is a configuration diagram of equipment showing a heat pump heating system that uses warm heat.
  • symbol is attached
  • the heat pump heating system 60 is a heat exchange that performs heat exchange between the use side fluid pipe 61 through which the first fluid flows, the heat source side fluid pipe 62 through which the second fluid flows, and the first fluid and the second fluid.
  • the usage-side fluid pipe 61 sequentially connects the heat exchanger 10a (first fluid flow path 1), the pump 61a, and the usage-side heat exchanger 61b to enable circulation of the first fluid.
  • the heat source side fluid pipe 62 sequentially connects the compressor 62a, the heat exchanger 10a (second fluid flow path 2), the expansion valve 62b, the heat source side heat exchanger 62c, and the fan 62d to enable circulation of the second fluid. ing.
  • the first fluid in the use side fluid pipe 61 is heated in the heat exchanger 10a (receives heat from the second fluid), is sent out by the pump 61a, and radiates heat in the use side heat exchanger 61b (to the use side fluid or the like). Hand over the heat).
  • the use-side heat exchanger 61b for example, a radiator or a floor heater is applied and used as a heating system.
  • the second fluid that has become high temperature and pressure in the compressor 62a exchanges heat with the first fluid in the heat exchanger 10a (delivering the heat).
  • the heat pump type heating system 60 using the heat exchanger 10 a of the present invention is used as a heat source to heat or hot water in the use side heat exchanger 61 b, thereby comparing with a heating system using a conventional boiler as a heat source. Energy saving effect.
  • the present invention is not limited to this, and any of the B type to M type may be used.
  • the number of rows of the first fluid channel 1, the number of layers of the second fluid channel 2, and the number of rows in each layer are not limited.
  • FIG. 10 illustrates a refrigeration cycle apparatus according to Embodiment 8 of the present invention, and is a configuration diagram of equipment showing a heat pump type hot water supply system using warm heat.
  • symbol is attached
  • a heat pump hot water supply system 70 is a hot water supply system in which the use-side heat exchanger 61 b in the heat pump hot water supply system 60 is installed in the tank 63 and the water supplied to the tank 63 is heated to take water. is there. As shown in FIG.
  • the heat pump hot water supply system 70 (same as the heat pump hot water supply / heating system) using the heat exchanger 10a of the present invention is used as a heat source for heating or hot water supply by the use side heat exchanger 61b. Compared to a hot water supply system using a boiler as a heat source, there is an energy saving effect.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2012/072132 2012-03-07 2012-08-31 Échangeur de chaleur et dispositif de cycle de réfrigération Ceased WO2013132679A1 (fr)

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JP2014503412A JP5784215B2 (ja) 2012-03-07 2012-08-31 熱交換器および冷凍サイクル装置
EP12870627.2A EP2840342B1 (fr) 2012-03-07 2012-08-31 Échangeur de chaleur et dispositif de cycle de réfrigération

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JP2012-050412 2012-03-07

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JP2015092122A (ja) * 2013-11-08 2015-05-14 三菱電機株式会社 熱交換器
WO2015162678A1 (fr) * 2014-04-21 2015-10-29 三菱電機株式会社 Collecteur stratifié, échangeur de chaleur et climatiseur
JP2017032244A (ja) * 2015-08-05 2017-02-09 東芝キヤリア株式会社 冷凍サイクル装置
WO2019078224A1 (fr) * 2017-10-17 2019-04-25 イビデン株式会社 Échangeur de chaleur
CN113922179A (zh) * 2020-07-08 2022-01-11 通用电气精准医疗有限责任公司 用于低温装置的高温超导电流引线组件

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CN111581844B (zh) * 2020-05-20 2023-04-25 山东大学 一种多模块换热器的设计方法
CN113883752B (zh) * 2020-07-01 2023-06-06 浙江盾安热工科技有限公司 换热器连接件及换热器

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JPWO2015162678A1 (ja) * 2014-04-21 2017-04-13 三菱電機株式会社 積層型ヘッダー、熱交換器、及び、空気調和装置
JP2017032244A (ja) * 2015-08-05 2017-02-09 東芝キヤリア株式会社 冷凍サイクル装置
WO2019078224A1 (fr) * 2017-10-17 2019-04-25 イビデン株式会社 Échangeur de chaleur
JP2019074264A (ja) * 2017-10-17 2019-05-16 イビデン株式会社 熱交換器
CN113922179A (zh) * 2020-07-08 2022-01-11 通用电气精准医疗有限责任公司 用于低温装置的高温超导电流引线组件

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JP5784215B2 (ja) 2015-09-24
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JPWO2013132679A1 (ja) 2015-07-30
EP2840342A4 (fr) 2016-02-17

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