WO2010089957A1 - 熱交換器 - Google Patents
熱交換器 Download PDFInfo
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- WO2010089957A1 WO2010089957A1 PCT/JP2010/000267 JP2010000267W WO2010089957A1 WO 2010089957 A1 WO2010089957 A1 WO 2010089957A1 JP 2010000267 W JP2010000267 W JP 2010000267W WO 2010089957 A1 WO2010089957 A1 WO 2010089957A1
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- heat transfer
- transfer tube
- heat
- heat exchanger
- exchanger according
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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
- F28D7/0008—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 for one medium being in heat conductive contact with the conduits for the other medium
- F28D7/0016—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 for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
- F24H4/04—Storage heaters
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- 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
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
- F28F1/424—Means comprising outside portions integral with inside portions
- F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/12—Heat pump
- F24D2200/123—Compression type heat pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2270/00—Thermal insulation; Thermal decoupling
Definitions
- the present invention relates to a heat exchanger for exchanging heat between a first fluid and a second fluid, and more particularly to a heat exchanger suitable for a heat pump type water heater.
- a heat exchanger for exchanging heat between two types of fluids (for example, water and refrigerant, air and refrigerant) is used.
- Patent Document 1 discloses a heat exchanger 10 as shown in FIGS. 10A and 10B.
- the heat exchanger 10 one water circular tube 11 for flowing water and two refrigerant circular tubes 12 for flowing refrigerant are in close contact over the entire length, and these circular tubes 11 , 12 are formed in a track winding shape.
- the outer diameter of the refrigerant circular tube 12 is set to about half of the outer diameter of the water circular tube 11, and the two refrigerant circular tubes 12 are 45 degrees from the center of the water circular tube 11 across the horizontal line. It is arranged at the position.
- FIG. 4 of Patent Document 1 describes a heat exchanger unit in which a heat exchanger 10 formed in a track winding shape is stacked with a heat insulating sheet interposed therebetween.
- an object of the present invention is to provide a heat exchanger that can be further miniaturized.
- a plurality of first heat transfer tubes for flowing a first fluid and a plurality of second heat transfer tubes for flowing a second fluid that exchanges heat with the first fluid are in contact with each other.
- a plurality of recesses forming protrusions on the inner peripheral surface of the first heat transfer tube on both sides in the orthogonal direction on the outer peripheral surface of the first heat transfer tube.
- a heat exchanger is provided along the line.
- the first heat transfer tubes and the second heat transfer tubes constituting the spiral heat transfer tube group are provided, so that small-sized tubes can be used as these heat transfer tubes. For this reason, the minimum bending radius of the heat transfer tube group can be reduced.
- the first heat transfer tubes and the second heat transfer tubes are arranged in a direction orthogonal to the direction in which the heat transfer tube group is wound, the width of the row can be kept small.
- the first heat transfer tubes and the second heat transfer tubes are alternately arranged in contact with each other, one heat transfer tube is sandwiched between the other heat transfer tubes except for the heat transfer tubes located at both ends.
- the heat exchanger of the present invention can be further reduced in size as compared with the conventional heat exchanger having the same level of performance.
- each first heat transfer tube is provided with concave portions that form convex portions on the inner peripheral surface of the first heat transfer tube on both sides in the direction orthogonal to the arrangement direction. It is provided along the current direction. For this reason, the first fluid flows in the first heat transfer tube while colliding with the convex portion, and the flow of the first fluid is disturbed. Thereby, the temperature uniformity in the surface of the first fluid can be improved, and the heat exchange efficiency between the first fluid and the second fluid can be improved. Thereby, further downsizing becomes possible.
- FIG. Fig. 1 The top view which shows the heat exchanger which concerns on one Embodiment of this invention 1 is an enlarged view of the main part of FIG. Fig. 1 is an enlarged sectional view of the main part corresponding to the line III-III in Fig. 1.
- 1 is an enlarged side view of the main part of the heat exchanger of FIG. 5A is a cross-sectional view taken along line VA-VA in FIG. 4, and
- FIG. 5B is a cross-sectional view taken along line VB-VB in FIG. 6A is a graph showing the relationship between the maximum depth of the concave portion of the second heat transfer tube and the flow velocity of the refrigerant in the vicinity of the inner peripheral surface, and
- FIG. 5A is a cross-sectional view taken along line VA-VA in FIG. 4
- FIG. 5B is a cross-sectional view taken along line VB-VB in FIG. 6A is a graph showing the relationship between the maximum depth of the concave portion of the second heat transfer tube and the flow
- FIG. 6B is a graph showing the relationship between the maximum depth of the concave portion of the second heat transfer tube and the pressure loss.
- Main part enlarged side view of a heat exchanger of a modification The principal part enlarged side view of the heat exchanger of another modification Configuration diagram of a heat pump type water heater including the heat exchanger shown in FIG. 10A is a plan view showing a conventional heat exchanger, and FIG. 10B is a cross-sectional view taken along line XB-XB in FIG. 10A.
- a heat exchanger for exchanging heat between water and a refrigerant such as carbon dioxide or CFC substitute which is used in equipment such as a heat pump water heater, will be described as an example.
- the invention is not limited to this, for example, a heat exchanger for exchanging heat between water and water (hot water), or for exchanging heat between a high-temperature refrigerant and a low-temperature refrigerant in a heat pump cycle. It can also be applied to internal heat exchangers.
- a heat exchanger 1 includes a heat transfer tube group 2 formed in a spiral shape having a flat rectangular plate shape.
- the heat transfer tube group 2 includes a plurality of (four in the illustrated example) first heat transfer tubes 3 and a plurality of (three in the illustrated example) second heat transfer tubes 4 in contact with each other over substantially the entire length. It is configured by being joined and integrated. Then, relatively low-temperature water (first fluid) flows in the first heat transfer tube 3 and relatively high-temperature refrigerant (second fluid) flows in the second heat transfer tube 4, so that the water and the refrigerant are separated from each other. Then, heat exchange is performed and water is heated by the refrigerant.
- first fluid relatively low-temperature water
- second fluid relatively high-temperature refrigerant
- the first heat transfer tube 3 and the second heat transfer tube 4 can be made of a metal having good thermal conductivity such as copper, copper alloy, SUS or the like.
- a metal having good thermal conductivity such as copper, copper alloy, SUS or the like.
- circular tubes are preferably used as the first heat transfer tube 3 and the second heat transfer tube 4.
- the first heat transfer tube 3 and the second heat transfer tube 4 are perpendicular to the extending direction (center axis direction) of the first heat transfer tube 3 and the second heat transfer tube 4 in a state of being in contact with each other ( In FIG. 3, they are arranged in a line alternately in the vertical direction).
- the first heat transfer tubes 3 and the second heat transfer tubes 4 are arranged so that their centers are aligned on the same straight line. And the adjacent 1st heat exchanger tube 3 and the 2nd heat exchanger tube 4 are joined mutually.
- the first heat transfer tube 3 and the second heat transfer tube 4 can be joined by brazing, soldering, a heat conductive adhesive, or the like. If the bonding using such a bonding agent is performed, the bonding area between the first heat transfer tube 3 and the second heat transfer tube 4 becomes large, and a large effective heat transfer area can be secured. It is also possible to join the first heat transfer tube 3 and the second heat transfer tube 4 by bundling the first heat transfer tube 3 and the second heat transfer tube 4 together with, for example, a heat shrink tube.
- the outer diameter D 1 of the first heat transfer tube 3 is preferably not less than the outer diameter D 2 of the second heat transfer tube 4 (D 2 ⁇ D 1 ).
- the first heat transfer tube 3 of the present embodiment has a larger outer diameter and wall thickness than the second heat transfer tube 4.
- CO 2 carbon dioxide
- the outer diameter D 2 of the second heat transfer tube 4 is 5.0 mm
- the outer diameter D 1 of the first heat transfer tube 3 is 6.0 mm.
- the heat transfer tube group 2 is wound in an orthogonal direction (hereinafter referred to as “X direction”) orthogonal to the arrangement direction (hereinafter referred to as “Y direction”) in which the first heat transfer tubes 3 and the second heat transfer tubes 4 are arranged. Yes.
- the heat transfer tube group 2 has a substantially rectangular spiral shape in which a straight portion 2a and a quarter-arc-shaped bent portion 2b that smoothly bends approximately 90 ° are alternately and repeatedly wound. Is formed.
- a gap S (see FIG. 2) is formed between the adjacent outer circumferential portion and the inner circumferential portion, that is, between the nth (n is a natural number) circumferential portion and the (n + 1) th circumferential portion counted from the outside. And (see FIG. 3) are preferably formed. If the gap S is formed, it is possible to prevent direct heat transfer between the adjacent circulating portions in the heat transfer tube group 2.
- a copper pipe or a resin sheet may be arrange
- the bending radii R of the bent portions 2b in the heat transfer tube group 2 are all constant. If it becomes like this, the kind of jig used at the time of a bending process can be decreased, and workability will improve.
- coolant will form a counterflow, heat exchange will be performed efficiently.
- first outlet member 6 and the second inlet member 7 are disposed on the spiral center side of the heat transfer tube group 2, and the spiral outer periphery side of the heat transfer tube group 2 is disposed on the spiral outer side.
- a first inlet member 5 and a second outlet member 8 are arranged.
- Each of the members 5 to 8 has a rectangular parallelepiped shape extending in the Y direction, and has internal spaces 51, 61, 71, and 81 that open to one of the end faces in the longitudinal direction (the end face drawn in FIG. 1). ing.
- One end of all the first heat transfer tubes 3 is connected to one side surface of the first outlet member 6, and the other end of all the first heat transfer tubes 3 is connected to one side surface of the first inlet member 5. .
- Every second heat transfer tube 4 is formed on one side surface of the second inlet member 7, and the other end of every second heat transfer tube 4 is connected to one side surface of the second outlet member 8. . That is, the first inlet member 5 forms a water inlet for guiding water into each first heat transfer tube 3, and the first outlet member 6 collectively discharges the water flowing through each first heat transfer tube 3. It forms an outlet for water. Further, the second inlet member 7 forms a refrigerant inlet for introducing the refrigerant into each second heat transfer tube 4, and the second outlet member 8 collectively discharges the refrigerant that has flowed through each second heat transfer tube 4. The refrigerant outlet is formed.
- the predetermined region E 1 in the long-side straight portion 2a and the predetermined region E 2 in the short-side straight portion 2a of the heat transfer tube group 2 shown in FIG. A plurality of recesses 3a and 4a as shown in FIGS. 5A and 5B are provided.
- the predetermined regions E 1 and E 2 may coincide with the length of the straight line portion 2a or may be shorter than that.
- the lengths of the predetermined regions E 1 and E 2 may be shortened toward the inside of the spiral shape.
- the recesses 3a and 4a do not need to be provided in both the long-side straight portion 2a and the short-side straight portion 2a, and may be provided in only one of them.
- a plurality of recesses 3 a are formed at a predetermined pitch along the extending direction of the first heat transfer tube 3 on both sides in the X direction on the outer peripheral surface 31 of each first heat transfer tube 3.
- a plurality of recesses 4 a are provided at predetermined pitches along the extending direction of the second heat transfer tubes 4 on both sides in the X direction on the outer peripheral surface 41 of each second heat transfer tube 4.
- the recess 3 a provided in the first heat transfer tube 3 forms a protrusion 3 b on the inner peripheral surface 32 of the first heat transfer tube 3, and the recess 4 a provided in the second heat transfer tube 3.
- FIG. 5A the recess 3 a provided in the first heat transfer tube 3 forms a protrusion 3 b on the inner peripheral surface 32 of the first heat transfer tube 3, and the recess 4 a provided in the second heat transfer tube 3.
- a convex portion 4 b is formed on the inner peripheral surface 42 of the second heat transfer tube 4.
- the recessed parts 3a and 4a should just be provided in the both sides of the X direction in the outer peripheral surfaces 31 and 41 of the heat exchanger tubes 3 and 4, and do not necessarily need to be located just beside the center of the heat exchanger tubes 3 and 4.
- FIG. the recesses 3a and 4a may be provided at positions shifted from the position directly beside the center of the heat transfer tubes 3 and 4 to the upper side or the lower side in FIG.
- the recess 3 a provided on one side in the X direction on the outer peripheral surface 31 of the first heat transfer tube 3 and the recess 3 a provided on the other side in the X direction are the extending direction of the first heat transfer tube 3.
- the recess 4 a provided on one side in the X direction on the outer peripheral surface 41 of the second heat transfer tube 4 and the recess 4 a provided on the other side in the X direction are along the extending direction of the second heat transfer tube 4.
- the recess 3 a provided in the first heat transfer tube 3 and the recess 4 a provided in the second heat transfer tube 4 are parallel to the extending direction of the first heat transfer tube 3 or the second heat transfer tube 4. It is a linear depression extending in the direction.
- the pitch of the recesses 4a of the second heat transfer tube 4 is 10 mm on both sides in the X direction and the length is 5.0 mm
- the pitch of the recesses 3a of the first heat transfer tube 3 is Both sides in the X direction are 10 mm and the length is 5.0 mm.
- the pitch refers to the distance between the centers of adjacent concave portions on one side in the X direction.
- the maximum depth (depth of the lowest point located in the deepest position) of the recessed parts 3a and 4a is 5% or more and 20% or less of the outer diameter of the heat transfer tubes 3 and 4, respectively.
- first heat transfer tubes 3 and second heat transfer tubes 4 are alternately stacked, and the stacked bodies are joined by the method described above.
- the recesses 3a and 4a are formed on the left and right surfaces of the heat transfer tube group 2 by pressing. Thereafter, the heat transfer tube group 2 may be bent on the same plane so as to exhibit a substantially rectangular spiral shape.
- the first heat transfer tube 3 and the second heat transfer tube in which the recesses 3a and 4a are formed in advance by press working or the like may be bent on the same plane so as to individually form a substantially rectangular spiral shape, and then stacked. Good.
- a plurality of the first heat transfer tubes 3 and the second heat transfer tubes 4 constituting the spiral heat transfer tube group 2 are provided.
- a small-sized tube can be used as the heat tube. For this reason, the minimum bending radius of the heat transfer tube group 2 can be reduced.
- the 1st heat exchanger tube 3 and the 2nd heat exchanger tube 4 are arranged in the direction orthogonal to the direction where the heat exchanger tube group 2 is wound, the width
- the first heat transfer tubes 3 and the second heat transfer tubes 4 are alternately arranged in contact with each other, one heat transfer tube is sandwiched between the other heat transfer tubes except for the heat transfer tubes located at both ends.
- the heat exchanger 1 of the present embodiment can be further reduced in size as compared with the conventional heat exchanger having the same level of performance.
- the recessed part 3a which forms the convex part 3b in the internal peripheral surface 32 of the 1st heat exchanger tube 3 in the outer peripheral surface 31 of each 1st heat exchanger tube 3 on both sides of a X direction. Is provided along the extending direction of the first heat transfer tube 3. For this reason, the water flows in the first heat transfer tube 3 while colliding with the convex portion 3b, and the flow of water is disturbed. Thereby, the temperature uniformity in the surface of water can be improved and the heat exchange efficiency of water and a refrigerant
- coolant can be improved. Thereby, further downsizing becomes possible. And since the recessed part 3a is provided in the X direction instead of the Y direction where the 1st heat exchanger tube 3 and the 2nd heat exchanger tube 4 contact, said effect is acquired, without increasing those contact thermal resistance.
- the recessed part 4a which forms the convex part 4b in the inner peripheral surface 42 of the 2nd heat exchanger tube 4 also on the outer peripheral surface 41 of the 2nd heat exchanger tube 4 for flowing a refrigerant
- coolants it is also possible to use the grooved pipe
- the cost can be reduced by using a circular tube having a recess 4a on the outer peripheral surface 41 as in the present embodiment.
- a track winding shape as shown in FIGS. 10A and 10B in other words, a pair of linear portions arranged in parallel so as to face each other, and ends of these linear portions 180 are connected to each other.
- a large dead space having a substantially right triangular shape is formed outside the semicircular arc-shaped portion, which causes an increase in the occupied area.
- the heat transfer tube group 2 is formed in a substantially rectangular spiral shape, and the bending radius R of the bent portion 2b located at the corner is constant.
- the bending radius of the bent portion 2b located on the outermost periphery is significantly reduced. For this reason, the dead space formed in the outer side of the heat exchanger 1 can be restrained small. If this is seen from another side, in the structure of this embodiment, unlike the track winding shape, the bending radius of the bent portion 2b does not decrease even from the spiral outer periphery side toward the center side. For this reason, the heat exchanger tube group 2 can be arrange
- the bending radius R of the bent portion 2b of the heat transfer tube group 2 formed in a spiral shape is reduced.
- the dead space having a substantially right triangular shape formed outside the heat exchanger 1 by the bent portion 2b can be further reduced.
- the 1st inflow port member 5 and the 2nd outflow port member 8 are arrange
- a member 6 and a second inlet member 7 are arranged.
- relatively low-temperature water flows in the first heat transfer tube 3 from the other end located on the spiral outer periphery side toward one end located on the spiral center side, and the second heat transfer tube 4 is compared.
- a high-temperature refrigerant flows from one end located on the spiral center side toward the other end located on the spiral outer periphery side.
- both the water and the refrigerant flow so as to increase in temperature from the peripheral edge of the heat exchanger 1 toward the center, so that the high temperature portion where the amount of heat radiation to the outside increases is small. It can arrange
- the convex part 4b which protrudes inside the 2nd heat exchanger tube 4 into which a refrigerant
- the refrigerant is usually mixed with oil for lubricating a compressor such as PAG (polyalkylene glycol).
- PAG polyalkylene glycol
- the flow in the second heat transfer tube 4 becomes a two-layer flow, and an oil film is formed on the inner peripheral surface 42 of the second heat transfer tube 4.
- the oil film is preferably as thin as possible.
- the convex portion 4b is also effective in reducing the thickness of the oil film.
- the flow rate of the refrigerant in the vicinity of the inner peripheral surface 42 increases, and thereby the speed difference between the oil film flowing on the inner peripheral surface 42 and the refrigerant increases. If it does so, much oil will be carried away from the surface of an oil film by a refrigerant
- the height of the convex part 4b becomes too high, the pressure loss increases and the performance of the heat exchanger 1 decreases. Therefore, it is preferable to appropriately set the maximum depth of the concave portion 4a and keep the height of the convex portion 4b within a preferable range.
- FIGS. 6A and 6B show the results of analyzing the flow state of the refrigerant when the maximum depth of the recess 4a of the second heat transfer tube 4 is changed when carbon dioxide is used as the refrigerant.
- software “FULL6.3” was used, and as conditions, the mass flow rate of the refrigerant was 650 kg / m 2 s, the temperature was 60 ° C., the pressure was 10 MPa, and the oil concentration in the refrigerant was 1.0 mass%. .
- the recesses 4a having a length of 5.0 mm are arranged at a pitch of 10 mm on both sides in the X direction in the manner shown in FIG. And it calculated about each case whose maximum depth of the recessed part 4a is 0, 0.4, 0.5, and 0.6 mm.
- the maximum depth of the recess 4a of 0 mm is a circular tube in which the recess 4a is not provided.
- the flow rate of the refrigerant in the vicinity of the inner peripheral surface 42 is saturated when the maximum depth of the recess 4a is in the range of 0.4 to 0.5 mm. This means that even if the maximum depth of the recess 4a is further increased, the oil film thickness is not reduced so much.
- the pressure loss increases rapidly when the maximum depth of the recess 4a is in the range of 0.4 to 0.5 mm. Therefore, it is preferable that the maximum depth of the recess 4a is 0.3 to 0.6 mm which is slightly wide on both sides from the above range.
- the heat exchanger 1 as described above is preferably used for the heat pump type water heater 200.
- FIG. 9 shows a heat pump water heater 200 including the heat exchanger 1 of the present embodiment.
- the heat pump hot water supply apparatus 200 includes a heat pump unit 201 and a tank unit 203.
- the tank unit 203 has a hot water storage tank 202 that stores the hot water produced by the heat pump unit 201, and the hot water stored in the hot water storage tank 202 is supplied to the hot water tap 204.
- the heat pump unit 201 includes a compressor 205 that compresses the refrigerant, a radiator 207 that radiates the refrigerant, an expansion valve 209 that expands the refrigerant, an evaporator 211 that evaporates the refrigerant, and a refrigerant pipe 213 that connects these devices in this order. It has. And the heat exchanger 1 of this embodiment is used as the heat radiator 207. In the heat pump unit 201, a positive displacement expander that can recover the expansion energy of the refrigerant may be used instead of the expansion valve 209.
- the present invention is not limited to the above-described embodiment, and various modifications are possible.
- the number and outer diameter of the first heat transfer tubes 3 and the second heat transfer tubes 4 may be appropriately selected according to the performance required for the heat exchanger 1 and the types of the first fluid and the second fluid.
- size which the heat exchanger tube group 2 circulates can also be determined suitably.
- the heat transfer tube group 2 does not need to be formed in a substantially rectangular spiral shape.
- the heat transfer tube group 2 may be formed in a circular spiral shape or a track winding shape as shown in FIG. 10A. It may be.
- the heat transfer tube group 2 is preferably formed in a substantially rectangular spiral shape.
- the 1st heat exchanger tube 3 and the 2nd heat exchanger tube 4 are arranged so that those centers may be located in a line
- the 1st heat exchanger tube 3 and the 2nd heat exchanger tube 4 are for example, if the outer diameter D 1 of the first heat transfer pipe 3 and the outer diameter D 2 of the second heat transfer pipe 4 are different, so that the outermost point on one side of the orthogonal direction orthogonal to the arrangement direction are arranged on the same straight line May be arranged.
- the centers of the first heat transfer tube 3 and the second heat transfer tube 4 are arranged in a staggered manner.
- the recessed part 3a provided in the one side of the X direction in the outer peripheral surface 31 of the 1st heat exchanger tube 3, and the recessed part 3a provided in the other side of the X direction are the extending direction of the 1st heat exchanger tube 3.
- they may be arranged at positions facing each other in the X direction.
- the recess 3a is parallel to the extending direction of the first heat transfer tube 3, such a disposition increases the portion that becomes narrower in the first heat transfer tube 3, and thus the above embodiment.
- Such an arrangement is preferable. This also applies to the recess 4a provided in the second heat transfer tube 4.
- each first heat transfer tube 3 extends linearly in a direction inclined with respect to the extending direction of the first heat transfer tube 3.
- the recesses 4 a provided on both sides in the X direction on the outer peripheral surface 41 of each second heat transfer tube 4 are linear recesses extending in a direction inclined with respect to the extending direction of the second heat transfer tube 4. May be. If it is such recessed part 3a, 4a, it can flow, stirring water or a refrigerant
- the heat exchanger 1 is used in a heat pump type water heater 200 as shown in FIG.
- the recess 4 a provided in the second heat transfer tube 4 for flowing the refrigerant is in the extending direction of the second heat transfer tube 4. It is preferable that it inclines with respect to it. Oil that lubricates the compressor 205 is mixed in the refrigerant, and a relatively large amount of this oil may stay on the bottom of the second heat transfer tube 4 to reduce the heat exchange efficiency. Therefore, if the recess 4a is inclined, the refrigerant can be agitated to suppress oil retention.
- the recesses 3a and 4a on one side in the X direction and the recesses 3a and 4a on the other side face each other in the X direction as shown in FIG. It may be arrange
- first heat transfer tube 3 is provided with a recess 3a parallel to the extending direction
- second heat transfer tube 4 is provided with a recess 4a inclined with respect to the extending direction, or provided in the first heat transfer tube 3.
- the combination of shapes and positions can be selected as appropriate, for example, the recessed portions 3a on both sides are alternately disposed, and the recessed portions 4a on both sides provided in the second heat transfer tube 4 are disposed at opposing positions.
- the concave portion of the present invention does not need to be a linear depression, and may be any shape as long as a convex portion is formed on the inner peripheral surface of the first heat transfer tube or the second heat transfer tube.
- the first heat transfer tube 3 and the second heat transfer tube 4 may be wavy in a meandering manner in the X direction, and the valley portion may be a recess. That is, the convex portion of the present invention does not need to narrow the cross-sectional area of the space surrounded by the inner peripheral surface of the first heat transfer tube or the second heat transfer tube, and protrudes inward while maintaining the cross-sectional area. It may be a part.
- the concave portion of the present invention is a convexity that narrows the cross-sectional area of the space surrounded by the inner peripheral surfaces 32 and 42 of the first heat transfer tube 3 or the second heat transfer tube 4 as in the above embodiment. It is preferable that it is a hollow which forms the part 3b, especially the linear hollow extended in a predetermined direction.
- the heat exchanger of the present invention is useful as a heat exchanger for a heat pump, particularly as a heat exchanger for a heat pump type hot water heater.
- the present invention can also be applied to a heat exchanger for performing heat exchange between liquids or gases.
Abstract
Description
Claims (16)
- 第1流体を流すための複数本の第1伝熱管と、前記第1流体と熱交換する第2流体を流すための複数本の第2伝熱管と、が互いに接触する状態で交互に配列された伝熱管群であって、前記第1伝熱管と前記第2伝熱管とが並ぶ配列方向と直交する直交方向に巻き回されて渦巻き状に形成された伝熱管群を備え、
前記第1伝熱管のそれぞれの外周面には、前記直交方向の両側に、当該第1伝熱管の内周面に凸部を形成する複数の凹部が当該第1伝熱管の延在方向に沿って設けられている、熱交換器。 - 前記第1伝熱管の外周面における前記直交方向の一方側に設けられた凹部と前記直交方向の他方側に設けられた凹部とは、前記第1伝熱管の延在方向に沿って交互に配置されている、請求項1に記載の熱交換器。
- 前記第1伝熱管の外周面における前記直交方向の一方側に設けられた凹部と前記直交方向の他方側に設けられた凹部とは、前記直交方向で対向する位置に配置されている、請求項1に記載の熱交換器。
- 前記第2伝熱管のそれぞれの外周面にも、前記直交方向の両側に、当該第2伝熱管の内周面に凸部を形成する凹部が当該第2伝熱管の延在方向に沿って設けられている、請求項1~3のいずれか一項に記載の熱交換器。
- 前記第2伝熱管の外周面における前記直交方向の一方側に設けられた凹部と前記直交方向の他方側に設けられた凹部とは、前記第2伝熱管の延在方向に沿って交互に配置されている、請求項4に記載の熱交換器。
- 前記第2伝熱管の外周面における前記直交方向の一方側に設けられた凹部と前記直交方向の他方側に設けられた凹部とは、前記直交方向で対向する位置に配置されている、請求項4に記載の熱交換器。
- 前記凹部は、所定方向に延びる線状の窪みである、請求項1~6のいずれか一項に記載の熱交換器。
- 前記所定方向は、前記第1伝熱管または前記第2伝熱管の延在方向と平行な方向である、請求項7に記載の熱交換器。
- 前記所定方向は、前記第1伝熱管または前記第2伝熱管の延在方向に対して傾斜する方向である、請求項7に記載の熱交換器。
- 前記伝熱管群は、直線部と、一定の曲げ半径で略90°曲がる屈曲部とを交互に繰り返しながら巻き回された略矩形の渦巻き状に形成されている、請求項1~9のいずれか一項に記載の熱交換器。
- 前記伝熱管群における隣り合う外側周回部分と内側周回部分との間には、隙間が形成されている、請求項1~10のいずれか一項に記載の熱交換器。
- 前記伝熱管群における隣り合う外側周回部分と内側周回部分との間には、断熱材が挿入されている、請求項1~10のいずれか一項に記載の熱交換器。
- 前記第1流体は、前記第2流体によって加熱されるものである、請求項1~12のいずれか一項に記載の熱交換器。
- 前記第1流体は水であり、前記第2流体は冷媒である、請求項13に記載の熱交換器。
- 前記第1伝熱管および前記第2伝熱管は共に円形管であり、前記第1伝熱管の外径は前記第2伝熱管の外径以上である、請求項1~14のいずれか一項に記載の熱交換器。
- 前記第1流体は、前記第1伝熱管内を前記渦巻き状の外周側から中心側に向かって流れ、前記第2流体は、前記第2伝熱管内を前記渦巻き状の中心側から外周側に向かって流れる、請求項1~15のいずれか一項に記載の熱交換器。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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JP2010549372A JP5394405B2 (ja) | 2009-02-05 | 2010-01-19 | 熱交換器 |
CN201080005789.XA CN102301197B (zh) | 2009-02-05 | 2010-01-19 | 热交换器 |
US13/147,743 US20110284193A1 (en) | 2009-02-05 | 2010-01-19 | Heat exchanger |
EP10738301.0A EP2395308B1 (en) | 2009-02-05 | 2010-01-19 | Heat exchanger |
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JP2009024653 | 2009-02-05 | ||
JP2009-024653 | 2009-02-05 |
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WO2010089957A1 true WO2010089957A1 (ja) | 2010-08-12 |
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PCT/JP2010/000267 WO2010089957A1 (ja) | 2009-02-05 | 2010-01-19 | 熱交換器 |
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US (1) | US20110284193A1 (ja) |
EP (1) | EP2395308B1 (ja) |
JP (1) | JP5394405B2 (ja) |
CN (1) | CN102301197B (ja) |
WO (1) | WO2010089957A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012078022A (ja) * | 2010-10-01 | 2012-04-19 | Sharp Corp | 熱交換装置及びこれを用いた冷却庫 |
JP2021139543A (ja) * | 2020-03-04 | 2021-09-16 | 株式会社コベルコ マテリアル銅管 | 伝熱管 |
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CN103528394B (zh) * | 2013-09-27 | 2014-07-23 | 山东大学 | 一种圆弧型封闭式翅片管散热器 |
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US20150122459A1 (en) * | 2013-11-06 | 2015-05-07 | Carrier Corporation | Brazed heat exchanger design |
CN103968702B (zh) * | 2014-05-19 | 2015-02-25 | 山东大学 | 一种八棱柱形散热器 |
CN104048523B (zh) * | 2014-06-09 | 2015-05-06 | 赵炜 | 翅根到翅顶之间凸起高度降低的散热器 |
CN104019687B (zh) * | 2014-06-09 | 2015-05-06 | 赵炜 | 沿着主翅片凸起高度变小的散热器 |
CN108151372A (zh) * | 2017-12-28 | 2018-06-12 | 新昌县宏宇制冷有限公司 | 一种双重换热蒸发器 |
Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS54128041A (en) * | 1978-03-28 | 1979-10-04 | Hitoshi Tatsumi | Evaporation system cooling heat exchanger |
JPH03279788A (ja) * | 1990-03-27 | 1991-12-10 | Hitachi Cable Ltd | コイル状熱交換器 |
JPH0639463A (ja) * | 1992-11-06 | 1994-02-15 | Hitachi Ltd | 伝熱管の製造方法 |
JP2004226036A (ja) * | 2003-01-24 | 2004-08-12 | Toshiba Kyaria Kk | ヒートポンプ式給湯器 |
JP2005221094A (ja) * | 2004-02-03 | 2005-08-18 | Iwai Kikai Kogyo Co Ltd | 熱交換器用伝熱管 |
JP2005233479A (ja) * | 2004-02-18 | 2005-09-02 | Tokyo Radiator Mfg Co Ltd | 熱交換器用伝熱管 |
JP2006162204A (ja) | 2004-12-10 | 2006-06-22 | Mitsubishi Electric Corp | 給湯器用熱交換器 |
WO2006103788A1 (ja) * | 2005-03-25 | 2006-10-05 | Tsinghua University | 給湯用伝熱管 |
JP2007326141A (ja) * | 2006-06-09 | 2007-12-20 | Mitsubishi Electric Corp | 渦巻き多段形熱交換器の製造方法及び渦巻き多段形熱交換器 |
WO2008029639A1 (fr) * | 2006-09-08 | 2008-03-13 | Tsinghua University | tube ondulÉ pour Échangeur thermique destinÉ À une alimentation en eau chaude |
JP2008188599A (ja) * | 2007-02-01 | 2008-08-21 | Matsushita Electric Ind Co Ltd | 熱交換器の製造方法 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2080626A (en) * | 1936-06-18 | 1937-05-18 | Oliver W Mojonnier | Tube |
SE441302B (sv) * | 1980-05-27 | 1985-09-23 | Euroheat Ab | Trekretsvermevexlare med spirallindade ror i en stapel |
JP3279788B2 (ja) * | 1993-12-09 | 2002-04-30 | 積水ハウス株式会社 | コンクリート天端の設定用ビスの支持具 |
SE517450C2 (sv) * | 1999-06-18 | 2002-06-04 | Valeo Engine Cooling Ab | Fluidtransportrör samt sätt och anordning för framställning av detsamma |
JP3768147B2 (ja) * | 2001-11-09 | 2006-04-19 | 三洋電機株式会社 | 熱交換器及びヒートポンプ式給湯機 |
FR2835046B1 (fr) * | 2002-01-21 | 2004-05-28 | Rhodia Polyamide Intermediates | Serpentin de circulation d'un fluide caloporteur, procede de fabrication d'un tel serpentin et reacteur comprenant un tel serpentin |
JP2004340455A (ja) * | 2003-05-15 | 2004-12-02 | Taiheiyo Seiko Kk | 熱交換器 |
US6945320B2 (en) * | 2004-01-26 | 2005-09-20 | Lennox Manufacturing Inc. | Tubular heat exchanger with offset interior dimples |
JP4634357B2 (ja) * | 2006-09-29 | 2011-02-16 | 三菱電機株式会社 | ヒートポンプ式給湯機 |
-
2010
- 2010-01-19 WO PCT/JP2010/000267 patent/WO2010089957A1/ja active Application Filing
- 2010-01-19 CN CN201080005789.XA patent/CN102301197B/zh not_active Expired - Fee Related
- 2010-01-19 JP JP2010549372A patent/JP5394405B2/ja not_active Expired - Fee Related
- 2010-01-19 EP EP10738301.0A patent/EP2395308B1/en not_active Not-in-force
- 2010-01-19 US US13/147,743 patent/US20110284193A1/en not_active Abandoned
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS54128041A (en) * | 1978-03-28 | 1979-10-04 | Hitoshi Tatsumi | Evaporation system cooling heat exchanger |
JPH03279788A (ja) * | 1990-03-27 | 1991-12-10 | Hitachi Cable Ltd | コイル状熱交換器 |
JPH0639463A (ja) * | 1992-11-06 | 1994-02-15 | Hitachi Ltd | 伝熱管の製造方法 |
JP2004226036A (ja) * | 2003-01-24 | 2004-08-12 | Toshiba Kyaria Kk | ヒートポンプ式給湯器 |
JP2005221094A (ja) * | 2004-02-03 | 2005-08-18 | Iwai Kikai Kogyo Co Ltd | 熱交換器用伝熱管 |
JP2005233479A (ja) * | 2004-02-18 | 2005-09-02 | Tokyo Radiator Mfg Co Ltd | 熱交換器用伝熱管 |
JP2006162204A (ja) | 2004-12-10 | 2006-06-22 | Mitsubishi Electric Corp | 給湯器用熱交換器 |
WO2006103788A1 (ja) * | 2005-03-25 | 2006-10-05 | Tsinghua University | 給湯用伝熱管 |
JP2007326141A (ja) * | 2006-06-09 | 2007-12-20 | Mitsubishi Electric Corp | 渦巻き多段形熱交換器の製造方法及び渦巻き多段形熱交換器 |
WO2008029639A1 (fr) * | 2006-09-08 | 2008-03-13 | Tsinghua University | tube ondulÉ pour Échangeur thermique destinÉ À une alimentation en eau chaude |
JP2008188599A (ja) * | 2007-02-01 | 2008-08-21 | Matsushita Electric Ind Co Ltd | 熱交換器の製造方法 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012078022A (ja) * | 2010-10-01 | 2012-04-19 | Sharp Corp | 熱交換装置及びこれを用いた冷却庫 |
JP2021139543A (ja) * | 2020-03-04 | 2021-09-16 | 株式会社コベルコ マテリアル銅管 | 伝熱管 |
JP7254307B2 (ja) | 2020-03-04 | 2023-04-10 | 株式会社Kmct | 伝熱管 |
Also Published As
Publication number | Publication date |
---|---|
CN102301197A (zh) | 2011-12-28 |
US20110284193A1 (en) | 2011-11-24 |
EP2395308A4 (en) | 2013-09-11 |
CN102301197B (zh) | 2014-07-23 |
EP2395308A1 (en) | 2011-12-14 |
EP2395308B1 (en) | 2018-10-24 |
JP5394405B2 (ja) | 2014-01-22 |
JPWO2010089957A1 (ja) | 2012-08-09 |
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