JP2009074720A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve a problem that it is difficult to make compatible the improvement of heat exchanging performance and the reduction of weight in a conventional countercurrent heat exchanger. <P>SOLUTION: This heat exchanger 1 comprises an inner cylinder 2 having a flow channel 6 for a high-temperature fluid inside, and an outer cylinder 3 forming a flow channel 8 for a low-temperature fluid between an outer peripheral portion of the inner cylinder 2 and itself, and fins 7, 9 for a high temperature and a low temperature fluids are disposed on the flow channels 6, 8 for high-temperature fluid and low-temperature fluids, thus the improvement of heat exchanging performance and the reduction of the weight can be made compatible. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an improvement of a counter-flow heat exchanger.

  The counterflow type heat exchanger includes an inner cylinder having a flow path for high-temperature fluid inside and an outer cylinder that forms a flow path for low-temperature fluid between the outer periphery of the inner cylinder, and a wall portion of the inner cylinder There is an apparatus that performs heat exchange between a high-temperature fluid and a low-temperature fluid via a gas (Patent Document 1).

Such a heat exchanger is applied to, for example, a combustor of a liquid rocket, and circulates a combustion gas in an inner channel and circulates either an oxidant or fuel in an outer channel, In addition, the vaporization of the oxidant or fuel is promoted (Non-patent Document 1).
Japanese Unexamined Patent Publication No. 2000-74576 "Enhanced Edition, Aerospace Engineering Handbook" Maruzen Co., Ltd., April 25, 1983, p. 635-636

  However, in the conventional heat exchanger as described above, in order to obtain a desired heat exchange performance, various dimensions such as the diameter and length of the inner cylinder and the outer cylinder, and the effective length of the portion that performs heat exchange. However, there is a problem that it is difficult to improve the heat exchange performance and reduce the size and weight. The problem was to solve the problem.

  The present invention has been made paying attention to the above-described conventional problems, and an object thereof is to provide a heat exchanger capable of realizing both improvement in heat exchange performance and reduction in size and weight.

  A heat exchanger according to the present invention includes, as claim 1, an inner cylinder having a flow path for high-temperature fluid inside and an outer cylinder that forms a flow path for low-temperature fluid between the outer periphery of the inner cylinder, According to a second aspect of the present invention, a fin is provided in each flow path of the fluid and the low-temperature fluid, and the fin of the flow path of the high-temperature fluid forms a plate shape along the axial direction of the inner cylinder, and a predetermined interval around the axis of the inner cylinder According to a third aspect of the present invention, the fin of the flow path for the cryogenic fluid is provided at the outer peripheral portion of the inner cylinder, and the fin and the outer cylinder are joined together. The fin of the flow path is formed in a spiral shape around the axis of the inner cylinder, and the above configuration is a means for solving the conventional problems.

  According to the heat exchanger of the present invention, by selecting the number and shape of the fins in each flow path of the high temperature fluid and the low temperature fluid, the heat exchange performance can be adjusted without changing the size of the entire apparatus, Accordingly, it is possible to reduce the size and weight of the entire apparatus.

  1-4 is a figure explaining one Example of the heat exchanger of this invention.

  A heat exchanger 1 shown in FIG. 1 is used as a component of a liquid rocket combustor or nozzle, and includes an inner cylinder 2 having both ends opened, an outer cylinder 3 having both ends opened, An inlet side manifold 4 fixed to one end side (left side in FIG. 1) of the cylinder 2 and the outer cylinder 3 and an outlet side manifold 5 fixed to the other end side of the inner cylinder 2 and the outer cylinder 3 are provided.

  The inner cylinder 2 has a high-temperature fluid flow path 6 inside thereof, and a plurality of high-temperature fins 7 are provided in the high-temperature fluid flow path 6. The high-temperature fins 7 form a belt shape along the axial direction of the inner cylinder 2, protrude toward the center of the inner cylinder 2, and are provided at predetermined intervals around the axis of the inner cylinder 2 as shown in FIG. 4. The high-temperature fin 7 is formed by means such as cutting or pre-molded fin material fixed to the inner cylinder 2 by welding or the like. The inner cylinder 2 of this embodiment is made of copper or a copper alloy. In FIG. 4, the number of high-temperature fins 7 is omitted from FIG.

  A low-temperature fluid flow path 8 is formed between the outer peripheral portion of the inner cylinder 2 and the outer cylinder 3, and a plurality of low-temperature fins 9 are provided in the low-temperature fluid flow path 8. As shown in FIG. 2, the low-temperature fin 9 is formed on the outer peripheral portion of the inner cylinder 2 by cutting or the like. In this embodiment, the low-temperature fin 9 is formed in a spiral shape around the axis of the inner cylinder 2. It is.

  The outer cylinder 3 of this embodiment is made of nickel and is formed by electroforming. That is, the space between the low-temperature fins 9 is filled with a core made of a low-melting-point material so that the outer peripheral portion of the inner cylinder 2 has a smooth circumferential surface, and then the outer peripheral surface of the inner cylinder 2 is electroformed by electroforming. A nickel layer to be the outer cylinder 3 is formed, and then the core is melted and removed, so that the outer cylinder 3 is joined to the low-temperature fin 9. Therefore, the flow path 8 of the low-temperature fluid substantially becomes a groove portion between the low-temperature fins 9 as shown in an enlarged view in FIG.

  Further, as shown in FIG. 3, the outer cylinder 3 is formed with inlet-side and outlet-side flow holes 10 communicating from the outside to the low-temperature fluid flow path 8 in the vicinity of both ends. A number of flow holes 10 of this embodiment are formed at predetermined intervals in the circumferential direction in the vicinity of both end portions of the outer cylinder 3.

  The inlet-side and outlet-side manifolds 4 and 5 are both made of stainless steel and have an annular shape, and are fixed to the ends of the inner cylinder 2 and the outer cylinder 3 by brazing or welding. The annular flow passages 11 and 12 on the inlet side and the outlet side are formed between the outer cylinder 3 and the outer peripheral portion including the flow hole 10.

  The inlet-side and outlet-side manifolds 4, 5 include flange portions 4 a, 5 a for connecting other pipes to the heat exchanger 1, and the inlet-side manifold 4 is provided with a low-temperature fluid supply pipe. The connecting portion 4b is provided on the outlet side manifold 5, and a connecting portion 5b for a low temperature fluid discharge pipe is provided.

  Since the heat exchanger 1 having the above-described configuration is used as a component of a liquid rocket combustor or a nozzle as described above, the heat exchanger 1 in the high-temperature fluid flow path 6 inside the inner cylinder 2 is formed in FIG. In addition, the combustion gas is circulated from the right side to the left side, and a low temperature fluid such as a gas (liquefied natural gas) or an oxidant (liquid oxygen) used as fuel in the low-temperature fluid flow path 8 formed between the inner cylinder 2 and the outer cylinder 3. Circulate fluid.

  At this time, the low-temperature fluid is supplied from the inlet-side manifold 4 through the inlet-side flow hole 10 to the flow path 8 and flows in the flow path 8 in the opposite direction to the combustion gas (from left to right in FIG. 1). From the flow hole 10 through the outlet side manifold 5.

  In this way, the heat exchanger 1 performs heat exchange between the high temperature fluid and the low temperature fluid to cool the heat exchanger 1 and promote vaporization of the low temperature fluid. At this time, since the heat exchanger 1 is provided with the high-temperature and low-temperature fins 7 and 9 in the high-temperature fluid and low-temperature fluid channels 6 and 8, the contact area of the flow channels 6 and 8 with respect to each fluid. The heat exchange efficiency is increased and the fins 7 and 9 for high temperature and low temperature are both formed in the common inner cylinder 2, so that the contact area between each fluid and the inner cylinder 2 is large. As a result, the heat exchange efficiency is very high.

  Further, the heat exchanger 1 includes high-temperature fins 7 in the high-temperature fluid flow path 6 provided at predetermined intervals around the axis of the inner cylinder 2, and the low-temperature fluid flow paths 8 in the low-temperature fluid flow path 8 Since it is provided in a spiral shape around the axis of the cylinder 2, the contact area with each fluid in the circumferential direction of the inner cylinder 2 becomes uniform, and further improvement in heat exchange efficiency can be realized.

  Furthermore, since the heat exchanger 1 has the inner cylinder 2 and the outer cylinder 3 integrated by joining the low temperature fin 9 and the outer cylinder 3 on the outer peripheral portion of the inner cylinder 2, the heat exchange efficiency is good. Improve product life and reliability. In addition, although the said Example demonstrated the case where the outer cylinder 3 was formed in the outer peripheral part of the inner cylinder 2 by electroforming, you may join the inner cylinder 2 and the outer cylinder 3 mutually by diffusion bonding or brazing.

  The heat exchanger 1 is excellent in heat exchange performance as described above, and if the number and shape of the high-temperature and low-temperature fins 7 and 9 in each of the flow paths 6 and 8 are selected, the size of the entire apparatus can be increased. The heat exchange performance can be adjusted without changing the thickness, and accordingly, the entire apparatus can be reduced in size and weight.

  In addition, the heat exchanger of the present invention is not limited to the above-described embodiment in details of the configuration, material, use, and the like. For example, as shown in FIG. The flow path 6 may be provided with a high-temperature fin 17 having a cross-shaped cross section, and as shown in FIG. 6, the high-temperature fin 17 having a cross-shaped cross section and the belt-shaped high-temperature fin 7 shown in the previous embodiment. In addition, even in the low-temperature fin in the flow path of the low-temperature fluid, an appropriate shape other than a spiral shape can be used.

It is sectional drawing explaining one Example of the heat exchanger of this invention. It is a side view explaining the inner cylinder shown in FIG. It is a side view explaining the outer cylinder shown in FIG. It is sectional drawing of the inner cylinder shown in FIG. It is sectional drawing explaining the other example of a shape of an inner cylinder. It is sectional drawing explaining the example of another shape of an inner cylinder.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Inner cylinder 3 Outer cylinder 6 High temperature fluid flow path 7 High temperature fin 8 Low temperature fluid flow path 9 Low temperature fin

Claims (4)

An inner cylinder having a flow path for high-temperature fluid on the inner side and an outer cylinder for forming a flow path for low-temperature fluid between the outer periphery of the inner cylinder and fins are provided in each flow path for high-temperature fluid and low-temperature fluid A heat exchanger characterized by that. 2. The heat exchanger according to claim 1, wherein fins of the flow path of the high-temperature fluid form a plate shape along the axial direction of the inner cylinder, and are provided at predetermined intervals around the axis of the inner cylinder. The heat exchanger according to claim 1 or 2, wherein fins of the flow path of the low-temperature fluid are provided on the outer peripheral portion of the inner cylinder, and the fins and the outer cylinder are joined. The heat exchanger according to claim 3, wherein fins of the flow path of the low-temperature fluid are formed in a spiral shape around the axis of the inner cylinder.

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