The heat exchanger

 

(57) Abstract:

Usage: as regenerators for gas turbine engines. The inventive heat exchanger includes a housing 1 with input and output pipes, distribution and cameras team for the first fluid. In case you have the package 8 of the corrugated plates, cross punch and Windows, and the plates are interconnected by a peripheral edge, the punch edges and window pairs with the formation of channels for both carriers, are confined to surfaces of the mutually overlapping corrugation, cross punch located in the channels, and inlet and outlet manifolds for the second fluid. In the cells and the package 8 is set accordingly deflectors 19 and the dividing wall 20, which together form a serially connected heat transfer section with a counter-current movement of the coolant. In the package 8 installed additional dividing wall 22 with an overflow channel connecting the reservoir and cross punch are V - shaped with the top facing up. On the side wall of the housing may be attached to the trap. Inlet and outlet of m is x the vessel wall. 5 C. p. F.-ly, 6 ill.

The invention relates to a surface gas-liquid or gas-air heat exchangers, such as a regenerator for gas turbine engines.

Known heat exchangers, containing the symmetric case with coaxial inlet and outlet nozzles, distribution and team cameras, limited flat end and cylindrical side walls and mounted in the housing package, consisting of plates with a punch of corrugated plates are interconnected in pairs by peripheral edges to form channels for both environments, limited by the surfaces of the mutually peresekajushihsya bumps.

The heat exchanger is closest to this invention, the essential features and adopted as a prototype.

The described heat exchanger is not effective enough and the degree of heat recovery for use in a gas turbine engine is insufficient.

The aim of the invention is to eliminate this drawback. This is solved in that the reservoir is formed is made in the plate Windows with flanging, bonded pairs, the plates are made of cross punch, forming a zigzag channels, is located in the cells, to consistently reported heat transfer section with privatecam movement of fluids. Within the sections there are additional separation wall, which made the bypass channels, informing inlet and outlet manifolds. The body is horizontal, cross punch are at the same angle relative to the vertical plane of symmetry of the hull with the formation of the inverted top up of V-shaped channels, with the side wall of the housing is equipped with a trap. One of the nozzles mounted on the side wall of the housing tangentially. The second nozzle is also mounted on the side wall of the housing tangentially, when the axes of the nozzles are mutually perpendicular, and the plate pack has two straight parallel peripheral edges, angled 45aboutto the axes of the nozzles. The axis of at least one of the socket is parallel to the axis of the housing.

In Fig. 1 shows a section of the heat exchanger of Fig. 2 the section of the heat exchanger along a 0 0 B; Fig. 3 the cross section of the package In Fig. 4, 5, 6 mounting options pipe.

The heat exchanger has a housing with side 1, end 2, and 3 walls, input 4 and output 5 patrol the package 8, consisting of plates 9 with a punch bumps, cross punch 11 and the window 12 with the formation of the channels 13 and 14 for both fluids, which are limited to the surfaces of vzaimoneperesekayuschihsya bumps and cross punch located in the channels 13 and 14 for the first and second heat transfer fluids. The window 12 in the collection form the inlet 15, the outlet 16 and coaxial with them intermediate 17 collectors for the second fluid. Plate 9 package 8 are interconnected by welding or soldering in pairs by edges 18 of the peripheral punch, and punch the window 12. At junction 6 and team 7 cameras installed deflectors 19 and the package 8 dividing wall 20, which together form a serially connected heat transfer section 21 counterflow movement of fluids. In addition, the package 9 can be installed additional dividing wall 22 made them overflow channels 23 connecting the collectors 15, 16 and 17. Cross punch 11 can be performed with symmetrical tilt relative to the vertical plane, as shown in Fig. 2. When the punch 1 is formed facing the top of the upward V-shaped channels 24. On the side wall 1 of the casing of the heat exchanger installed on the side wall 1 tangentially (see Fig. 4) when the radial position of the other of the socket 4. As shown in Fig. 5, both of the socket 4 and 5 can be installed tangentially to the wall 1 with mutually perpendicularly the position of the axes. The package 8 is tilted to the nozzles 4 and 5 at an angle of 45about. One of the nozzles (Fig. 6 is a pipe 5) can be strengthened and the end wall of the housing of the heat exchanger.

The heat exchanger works as follows.

The first fluid, for example in the turbine exhaust gas, if the heat exchanger is used as the regenerator of a gas turbine engine, is supplied to the inlet pipe 4, and then into the distribution chamber 6, passes through the channels 13 of the package 8 between the plates 9, consistently flowing in sections 21 formed by the deflectors 19 and wall 20. Giving its heat to the second fluid, for example air coming into the combustion chamber, the gas flows into the collecting chamber 7 and is removed through the outlet 5. The second fluid enters the inlet manifold 15, flows through the channels 14, the intermediate reservoir 17 and is discharged through the manifold 16, the heated first heat transfer fluid through the walls of the plates 9. This cross punch 11 form a zigzag course teplonositeley liquid medium. The use of partition walls 20 and baffles 19 provides a counter-current movement of fluids in the series connected sections 21, which significantly increases the efficiency of heat transfer in comparison with the prototype. To further increase the efficiency results of the application of the additional dividing walls 22 with a by-pass channels 23. The bypass of the second coolant through the channels 23 provides multiple countercurrent flow of fluids within the same partition 21, as shown in Fig. 1. If there is a risk of condensation in the flow part of the heat exchanger, cross punch, it is expedient to do so, as shown in Fig. 2. In this case, the condensate flows through the channels 24 on the inner surface of the wall 1 and is removed through the trap 25. Embodiments of the heat exchanger shown in Fig. 4, 5 and 6, can refuse suitable in different layout solutions of a system in which the heat exchanger.

1. A heat EXCHANGER comprising a housing and a package of pairs connected to each other at peripheral edges of the corrugated plates, and inlet and outlet nozzles, team and distribution chambers for the first theplanetary made in the plates Windows with flanging, bonded pairs, the plates are made of cross punch, forming a zigzag channels, and the body cavity separated by flat walls, installed within the package and flat baffles located in the cells, consistently reported heat transfer section with a counter-current movement of fluids.

2. The heat exchanger under item 1, characterized in that the inside of the sections, there are additional separation wall, which made the bypass channels, informing inlet and outlet headers.

3. Heat exchanger according to PP. 1 and 2, characterized in that the housing is horizontal, and transverse punch are at the same angle relative to the vertical plane of symmetry of the hull with the formation of the inverted top up of V-shaped channels, with the side wall of the housing is equipped with a trap.

4. Heat exchanger according to PP. 1 to 3, characterized in that one of the nozzles mounted on the side wall tangentially.

5. Heat exchanger according to PP. 1 to 4, characterized in that the second nozzle is also mounted on the side wall of the housing tangentially, when the axes of the nozzles are mutually perpendicu is UP>oto the axis of the pipe.

6. Heat exchanger according to PP. 1 to 3, characterized in that the axis of at least one of the socket is parallel to the axis of the housing.

 

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EFFECT: enhanced effectiveness and precision of assembly of the apparatus and elements thereof combined with reduction of labour and material consumption, reduction of hydraulic losses occurring in the apparatus as well as technological simplification of the hydraulic pressure testing of heat exchanger sections and manifolds of the apparatus for air cooling of gas, improved effectiveness and reduced labour intensity of their performance.

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EFFECT: reduced weight and cross-section dimensions of the heat-exchange apparatus characterized by a sufficiently high heat transfer within a wide range of temperates, pressures and flow rates of heat-transfer agents.

3 cl, 7 dwg

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