JP2568648B2 - Heat exchange device and method of manufacturing the same - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchange device that heats a refrigerant or the like using a high-temperature combustion gas that uses gas or oil as a heat source.

2. Description of the Related Art As a conventional example 1, refrigerant heating is performed by using a refrigerant as a fluid to be heated and heating by a combustion gas to evaporate and vaporize the liquid refrigerant to carry heat by latent heat and heat. There is a heater. In this method, the heat exchanger 1 in which the refrigerant heated by the combustion gas of the burner 1a is sealed and the radiator 2 are connected by the closed conduit 3, and the refrigerant is forcibly circulated by the refrigerant transporter 4 provided in the closed conduit 3. It is to let.

FIG. 4 shows a conventional example of the heat exchange apparatus 1 (Japanese Patent Laid-Open Publication No. Sho 59-107167). A plurality of fins 5 are provided on a cylindrical inner peripheral surface extending in the horizontal direction, Is a pipe provided with a pipe holding portion 6 and a pipe 7 through which a refrigerant flows through a circular portion. A horizontal pipe which is supplied by a refrigerant carrier 4 by flowing combustion gas from a burner portion 8 horizontally and horizontally to a cylindrical inner surface 9. 7 is for heating the refrigerant flowing in the inside 7.

Problems to be Solved by the Invention In the above-described heating system, external power is required for transporting the refrigerant, and in order to reduce the running cost during the heating operation, it is effective to eliminate the external power for transporting the refrigerant and carry out heat transport without power. When performing refrigerant heating and heating by unpowered conveyance, natural circulation force due to the buoyancy of a gas refrigerant generated by heating a liquid refrigerant is important. However, in the configuration of the conventional heat exchange device 1 shown in FIG. 4, since the refrigerant flows through the pipe 7 extending in the horizontal direction, the gas component of the heated gas-liquid two-phase mixed refrigerant smoothly exits. Since the refrigerant does not flow toward the outlet, the refrigerant stagnates, causing local abnormal heating, and there is a problem in reliability of the equipment such as thermal decomposition of the refrigerant or an abnormal rise in temperature of the equipment. On the other hand, since the flue gas radiates heat near its outlet and has a low temperature, the moisture in the flue gas may condense and condense on the cylindrical inner surface of the heat exchange device 1 and cause corrosion or the like to progress. FIG. 2 of the conventional example 2 has a combustion gas exhaust chamber 19 formed in the upper part, and has a parallel approaching surface in the lower part and is divergent from the lower end of the parallel approaching surface in order to eliminate the drawbacks of FIG. A refrigerant passage member 16 having a vertical passage is disposed on the outer surface of the heat transfer partition tube 15 having a combustion chamber in a shape of a circle, and a large number of heat transfer fins 18 are provided between the parallel approach surfaces, and the heat transfer partition tube 15 An exhaust connection port for a combustion exhaust gas outlet is provided from one end of the exhaust chamber 19. On the other hand, the end-shaped combustion chamber of the heat transfer partition tube 15 eliminates stagnation of exhaust gas to prevent partial overheating, and moisture condensation in the combustion exhaust gas forms the flared combustion chamber. It was possible to prevent corrosion and deterioration due to dew condensation of the heat exchange device by flowing out from a part of the hole 23 of the burner case 11 by connecting the inclined wall of the burner case 11.

However, the following problem occurs in FIG.

(1) Refrigerant passage members 16 on both sides are inlet header pipes
14 and an outlet header pipe 20, the refrigerant passage member
Since the heat transfer partition tube 15 and the heat transfer fins 18 are sandwiched by the inner parallel approaching surface of the heat transfer partition tube 15, the heat transfer fins are markedly shrunk or shrunk during continuous operation or intermittent operation. Deforms and significantly reduces durability quality such as combustion characteristics and heat exchange characteristics.

(2) Inconsistencies (inclination, insertion allowance, etc.) between the inlet header pipe 14, the outlet header pipe 20 and the refrigerant passage member 16, the connection irregularities between the outlet pipe 21 and the outlet header pipe 20, and the refrigerant passage 17 during brazing. There are many cases where the refrigerant is not equally distributed on both sides due to clogging of flux etc., causing local overheating of the refrigerant, causing thermal decomposition of the refrigerant or abnormal temperature rise of the equipment, etc., resulting in equipment reliability issues I do.

(3) Because of the large amount of brazing, heating the refrigerant considerably
Since the cycle itself has a high temperature and a high pressure, the reliability of leakage of the refrigerant or the vaporized gas from the connection portion is reduced.

(4) The shape is complicated, a large investment is required for the production and management of equipment and jigs to guarantee the dimensions of the parts or the performance of the heat exchanger, and the provision of expensive parts is required.
The present invention solves the above-mentioned problems of the prior art, and aims to prevent the flow of the refrigerant smoothly, prevent corrosion due to dew condensation in the heat exchanger, prevent quality deterioration due to durability, and improve the reliability of parts.

Means for Solving the Problems In order to solve the above problems, a heat exchange device of the present invention has a heat transfer partition plate having an exhaust chamber formed at an upper portion thereof and a heat transfer partition plate formed at a lower portion of the exhaust chamber having a fixed interval. And a heat shield inner body plate having opposing parallel approaching surfaces, wherein the heat transfer bulkhead plate and the heat shield inner body plate gradually widen from the lower end of the parallel approaching surface. A heat transfer member having a vertical passage is joined to the outer surface of the heat transfer partition plate, and heat transfer fins are joined to the inner surface of the heat transfer partition plate at the parallel approach portion. A burner case with a burner inside is provided at the lower end of the heat transfer partition plate and the heat shield outer shell plate, and a gap is provided between the heat inner shell plate and the heat transfer fins. A configuration in which a bypass air passage with a bypass hole is formed in the body plate to reach the exhaust chamber It is what it was.

Function The present invention sufficiently heats the refrigerant in the vertical passage by the heat transfer fins provided on the parallel approach surface by the above-described structure, and gradually promotes the generation of air bubbles of the refrigerant from the lower position, thereby increasing the natural circulation force due to the rise in air level. The purpose of the present invention is to provide a highly reliable system that reliably performs non-powered heat transfer and does not cause thermal decomposition of a refrigerant.

On the other hand, the flared combustion chamber eliminates stagnation of exhaust gas to prevent partial overheating, and moisture condensation in the combustion exhaust gas is connected to the heat transfer partition plate and the inclined wall of the heat shield inner body plate, and from the partial hole of the burner case. It leaks to the outside, preventing corrosion of the heat exchanger device. On the other hand, the configuration of the present invention has an asymmetric structure as compared with the conventional example shown in FIG. 2, but this is an excellent feature in the following points.

(1) Since the shape of the refrigerant passage member is simple, manufacturing and assembling become easy.

(2) Since the refrigerant passage member does not have a structure in which the heat transfer partition tube is sandwiched, the refrigerant passage member accompanies expansion and contraction of the heat transfer partition tube (heat transfer partition plate 24 of this embodiment) due to heating and cooling of the burner portion. Cracks and the like hardly occur at the joint between the refrigerant passage member and the heat transfer partition plate without applying stress.

(3) Since a gap is provided between the heat transfer fin and the heat shield inner body plate, cracks and deformation due to expansion and contraction of the heat transfer partition tube and the heat transfer fin itself are unlikely to occur.

An embodiment of the present invention will be described below with reference to the accompanying drawings. In FIG. 1, a heat transfer partition plate 24 and a heat shield inner body plate 25 constitute a pair of parallel approaching portions 29 which face each other at a constant interval. A combustion chamber 30 diverging from the lower part of the parallel approach portion 29 is formed. Reference numeral 16 denotes a flat refrigerant passage member thermally joined to the outer surface of the heat transfer partition plate 24, and a plurality of vertical passages 17 are provided independently. 14 is an inlet header tube provided at the lower end of the refrigerant passage member 16, and 20 is a refrigerant passage member
Outlet header pipes provided at the upper part of 16, each communicating with a vertical passage 17. Reference numeral 18 denotes a heat transfer fin provided inside the parallel approach portion 29 and in thermal contact with the heat transfer partition plate 24. The heat transfer fins 18 and the heat shield inner body plate 25 have a minimum gap b. 27a is a bypass hole formed by the heat shield outer body plate 26 and the heat shield inner body plate 25, and 27 is a bypass air passage formed by the heat shield inner and outer body plate. The bypass air passage 27 is configured to reach the exhaust chamber 28. Reference numeral 11 denotes a burner case configured to cover the burner unit 10, and a hole 23 for discharging dew condensation water is provided on a part of the bottom surface. Also, seal packing 12 is provided on the heat transfer bulkhead plate 24 and the lower edge of the heat shield outer shell plate.
Has been through the device. 13 is installed in the heat shield plate burner part which is attached for the purpose of shielding the heat transfer partition plate from heat. 22 is a combustion air intake.

In the above-described configuration, the liquid refrigerant that has entered the inlet header pipe 14 through the refrigerant inlet is distributed to the plurality of vertical passages 17 from the lower portion of the refrigerant passage member 16. The heat transfer partition plate 24 absorbs the heat of the combustion exhaust gas passing through the heat transfer fins 18 from the combustion chamber 30 on the parallel approach surface 29 provided with the heat transfer fins, and the heat transfer partition plate 24 has a vertically joined refrigerant passage member. The refrigerant in the directional passage 17 is sufficiently heated from the lower portion near the inlet header tube 14.
Then, the heated liquid refrigerant starts vaporizing and evaporating, and enters a gas-liquid two-phase state in which bubbles are generated in the liquid. Then, the generated bubbles rise upward from below in the passage 17 provided in the vertical direction due to the buoyancy effect, and become a strong natural circulation force, and at the same time, transfer the refrigerant to the upper part of the passage 17 with the liquid refrigerant that has not been vaporized yet. Sending bubble pump action occurs. The refrigerant having reached the upper end of the passage 17 flows out of the outlet header tube 20 toward a radiator (not shown). In this way, by heating from the lower part to the upper part of the vertical passage 17, the natural circulation force is increased, the stir turbulence effect of the flow is generated by the ascending flow, and the local abnormal overheating of the refrigerant is prevented, so that the heat of the refrigerant is Reliability can be improved by disassembly or prevention of abnormal temperature rise of equipment.

In addition, dew condensation in the combustion exhaust gas reduces the size of the combustion chamber 30.
The heat transfer partition plate 24 and the inclined wall of the heat shield inner body plate 25 are formed, and the heat flows into the burner case 11 and flows out from the hole 23 provided in a part of the hole 23 through which dew condensation water flows out. Does not affect the corrosion and durability of the replacement device.

Further, since a minimum gap b is provided between the heat transfer fin 18 and the heat shield inner body plate 25 to absorb the contraction and expansion caused by continuous and intermittent combustion, the heat transfer fin 18 can be formed without deformation. The reliability of the equipment over the period can be secured. The bypass air passage 27 and the bypass hole 27a can suppress the temperature rise of the heat shield inner body plate 25, and the bypass hole 27a can easily adjust the excess combustion air rate.

Further, the refrigerant passage member 16 is a multi-hole flat extruded tube made of aluminum having a large number of holes therein, and the heat transfer fins 18 are formed by bending a band-shaped aluminum plate into a corrugated or rectangular or trapezoidal shape, and The heat bulkhead plate 24 is processed as a brazing sheet in which a brazing material is preliminarily clad with a brazing material on both the front and back surfaces of an aluminum core material, and the heat transfer bulkhead plate 24 using this material and aluminum heat transfer fins 18 on the inner and outer surfaces.
Passage member of multi-hole flat extruded pipe made of aluminum and aluminum
16 is assembled and simultaneously thermally bonded by integrally brazing. Therefore, a heat exchanger having excellent heat transfer performance without contact heat resistance can be practically used at a low cost and at a low cost.

Effect of the Invention As described above, the heat exchange device of the present invention has a heat transfer partition plate having an exhaust chamber formed in the upper part, and a parallel approaching surface that is opposed to the heat transfer partition plate in the lower part of the exhaust chamber at a certain interval. Having a heat shield inner body plate, wherein the heat transfer bulkhead plate and the heat shield inner body plate form a combustion chamber in a shape that gradually widens from the lower end of the parallel approach surface to a divergent shape, A refrigerant passage member having a vertical passage is joined to an outer surface of the heat transfer partition plate, a heat transfer fin is joined to an inner surface of the heat transfer partition plate at the parallel approach surface portion, and the heat shield inner body plate and the heat transfer fin are joined to each other. Since the gap is provided between the heat fins, the following effects can be expected.

(1) Since the refrigerant is heated from the lower part of the passage, the bubble pump action can be strengthened, and the flow of the generated bubbles rises, and the flow is agitated. Can be improved.

(2) The non-powered heat transfer becomes possible by the bubble pump action by the rising bubble flow, so that low running cost and heating can be provided.

(3) In order to prevent deterioration of durability quality such as combustion characteristics and heat exchange characteristics due to remarkable deformation of the heat transfer fins, open the other of the heat transfer fins and increase the reliability of the equipment by providing a gap with the heat shield inner body plate. It can be dramatically improved.

(4) The number of constituent parts is small, and the improvement of the refrigerant branching performance, the improvement of reliability by reducing leakage points, and the provision of inexpensive parts can be achieved.

(5) Because of the flared combustion chamber, moisture condensate in the combustion exhaust gas is connected to the inclined wall and flows out to the outside through a hole provided in a part of the burner case, preventing deterioration of the heat exchange device due to corrosion. The durability of the equipment can be improved.

(6) Since the heat transfer fins and the coolant passage member are integrated by brazing on the heat transfer partition plate using the clad material, the contact heat resistance is small and the heat transfer performance is excellent.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of a heat exchanger showing one embodiment of the present invention, and FIG. 2 is a longitudinal sectional view of a heat exchanger of a conventional example (2).
FIG. 3 is a circuit configuration diagram of a refrigerant heating / heating machine of a conventional example (1),
FIG. 4 is an external perspective view of a heat exchanger of a conventional example (1). 24 heat transfer partition plate, 25 heat shield inner shell plate, 26 heat shield outer shell plate, 27 bypass air passage, 27a bypass hole, 28
…… Exhaust chamber, 29… Parallel approaching surface, b …… Gap, 16 ……
Refrigerant passage member, 17 refrigerant passage, 18 heat transfer fins, 30
… Combustion chamber, 11 Burner case, 10 Burner section.

Claims (3)

(57) [Claims] 1. A heat shield in which a heat transfer partition plate having an exhaust chamber formed in an upper part thereof and a parallel approach surface which is opposed to the heat transfer partition plate in a lower part of the exhaust chamber at a predetermined interval. Having a body plate, wherein the heat transfer partition plate and the heat shield inner body plate form a combustion chamber in a shape that gradually widens from a lower end portion of the parallel approaching surface to form a combustion chamber, and an outer surface of the heat transfer partition plate. In this case, a refrigerant passage member having a vertical passage is joined, a heat transfer fin is joined to the inner surface of the heat transfer partition plate in the parallel approaching surface portion, and a gap is provided between the heat shield inner body plate and the heat transfer fin. Heat exchange equipment. 2. A bypass which is attached to the lower end portions of the heat transfer partition plate and the heat shield outer shell plate, and has a burner case provided with a burner therein, and has a bypass hole in the heat shield outer shell plate and the heat shield inner shell plate. 2. The heat exchange device according to claim 1, wherein an air passage is formed, and the bypass air passage faces the exhaust chamber. 3. The heat exchanger according to claim 1, wherein the refrigerant passage member is an aluminum multi-hole flat extruded tube having a large number of holes therein, and the heat transfer fins are aluminum plates bent in a corrugated, rectangular or trapezoidal shape. The heat transfer partition plate is an aluminum plate clad with brazing material on the front and back surfaces, and the refrigerant passage member is heated by contacting the heat transfer fins to the outer surface of the heat transfer partition plate and the heat transfer fins to the inner surface of the heat transfer partition plate. A method for manufacturing a heat exchange device that is at least brazed.