Plate heat exchanger

 

(57) Abstract:

Usage: to simplify the constructions of heat exchangers, while their cost and improving the heat exchange efficiency and reduce energy losses. The inventive heat exchanger includes a housing with coaxial inlet and outlet nozzles, distribution and cameras team for one of the fluids. The latter have a flat end and a cylindrical side walls. In the case set matrix consisting of a plate with a punch bumps. The plates are interconnected in pairs by peripheral edges to form channels for both carriers, are confined to surfaces of the mutually overlapping corrugation. The side walls of the casing and the adjacent edges of the plates are cylindrical in shape. The plates are made punch-UPS. They are connected in pairs with the formation of the inlet and outlet cylindrical collectors, partially protruding into the distribution team and a camera. Edge punch Windows deflected navstrechu flow inlet and flow outlet manifolds. The angle of the limb is in the range 0 - 60. The angle of the limb in the inlet manifold is reduced in the stream, and diverting the call is analy. The ends of the punch in places turning flow is rounded and directed towards the flow. The angle at the apex of the corrugation 40 - 80. Between the edges of the plates of the matrix adjacent to the building, installed seals. The heat exchanger is equipped with reinforced at one or both end walls of the housing inlet and outlet nozzles for the second heat transfer medium and installed in the pipes the pipes connected to the respective collectors. The plates are made symmetrical with respect to an axis parallel to the axis of the input and output sockets. The matrix of the heat exchanger offset from the center of symmetry of the hull so that the ratio of the lengths of the front surface of the die-side inlet of the heat carrier of 1.4 to 1.7. 10 C.p. f-crystals, 5 Il.

The invention relates to heat exchangers in which the channels for the coolant is formed by a plate separating the two media, i.e., to plate heat exchangers.

Known plate heat exchangers, consisting of plates with punch Windows and bumps that form in the collection heat exchange channels, the input and output manifolds for both environments [1] However, such heat exchangers are difficult to manufacture, bulky and heavy.

Also known heat exchangers, provided the Chennai flat end and cylindrical side walls and mounted in the housing matrix, consisting of plates with a punch of corrugated plates are interconnected in pairs by peripheral edges to form channels for both environments, the limited surfaces of the overlapping corrugation [2] the heat Exchanger closest to the invention by the combination of essential features and is taken as a prototype. The hull design of such heat exchangers, however, complex and expensive to manufacture, and the efficiency of heat transfer is not high enough due to the uneven distribution of the flow rate of coolant through the channels of the matrix. In addition, such heat exchangers is difficult to guarantee the tightness of the flowing parts of the matrix.

The invention is aimed at simplifying the design of heat exchangers for cost reduction while improving the heat exchange efficiency and reduce energy losses.

This is achieved in that the side walls of the housing and adjacent cover plates are cylindrical in shape, the plates are made punch-UPS, which are paired with the formation of the inlet and outlet cylindrical collectors, partially protruding into the distribution team and camera. Due to this, firstly, is extremely simplified constructia welded or fastened in any other way coaxial inlet and outlet for one of the fluids. The end wall of the casing, one of which (or each one) are attached to the nozzles of the other of the coolant, have a simple disk shape. Compared with plate heat exchangers with inlet and outlet manifolds for both environments formed by punch-UPS, this plate heat exchanger is much easier and cheaper.

In addition, the location of part of the inlet and outlet manifolds in the distribution and cameras team provides uniform distribution of the flow rate of one of the fluids in the heat exchange channels. Serve this goal and other private differences of heat exchanger-decrease the angle of the limb edges of the Windows on the flow in the inlet manifold and the increase in the flow of this angle in the output manifold. In addition, the specified contour edge reduces energy losses in the flowing part of the heat exchanger and improves manufacturability sloping edges conveniently welding electron beam welding through a manifold in the assembled condition of the matrix.

The implementation of the corrugation with the proposed angle at the vertex ( = 40-80about) allows to increase the number of points of contact plates. This reduces the surface tension, the possibility ), forming a zigzag channels for one of the fluids, increases the efficiency of heat transfer by increasing the number of turns, cross-flow pattern of the fluids.

The presence of the recesses at the ends of the punch in places turning flow reduces energy loss and improves the efficiency of heat transfer. The presence of seals between the edges of the plates of the matrix adjacent to the body, reduces the leakage of the coolant to bypass the heat exchange channels. In addition, placement in the lateral inlet and outlet nozzles of the tubes connected to the respective collectors, allows to minimize partecke between the flowing parts of the coolant, as the gap between the tube and nozzle can be effectively sealed even in a collapsible design.

In Fig. 1 shows a heat exchanger, a cross-section of Fig. 2 is a longitudinal section; Fig. 3 cut ABCD in Fig. 2; Fig. 4 cross section of the corrugations of Fig. 5 diagram illustrating the necessity of choosing the optimal angle of inclination of the edges (opt) relative to the flow axis.

The heat exchanger includes a housing 1, symmetric about a plane Oh, input 2 and output 3 sockets, distribution chamber 4, the collecting chamber 5, ply 11 collectors, punch 12 transverse partitions, mechanical seal 13, the tube 14 collectors, edge 15 punch-UPS, the transition section 16, the channels 17, 18 for heat transfer fluids, end walls 19, 20 of the housing, the inlet 21 and outlet 22 of the nozzle, the seal 23. The drawing shows the angle of the limb edges 15 and the angle at the apex of the corrugation.

A cylindrical housing 1 is manufactured, for example, from a scrap of pipe of the appropriate diameter, or in some other way. Attached input 2 and output 3 nozzles. In the case reinforced end walls 19, 20, and in the cavity of the body has a matrix consisting of plates 6, which are pairwise connected by peripheral edges 7, for example, by welding. The plates 6 are made of the punch 8 intersect each other in the collection of the corrugation, which form the channels 17 and 18 for heat transfer fluids. In addition, the plates 6 are punch 9 Windows, edges 15 which are pairwise connected by welding or other means. Between the peripheral edges 7 and the punch 8 is the transition section 16, playing the role of a damper. The open form of the inlet 11 and outlet 10 collectors. To the extreme edges of each collector is attached, for example, by welding the tubes 14, which are located in the inlet 21 and atmodas between the nozzles 21, 22 and the tube 14 is sealed by any known method. Between the peripheral edge 7 of the plate 6 adjacent to the inner surface of the housing 1, is placed seals 23. Between the end walls 19, 20 of the housing and the outer plates of the matrix are also equipped with a seal 13. The plates are made punch 12 transverse partitions, which are in the collection form a zigzag channels for the coolant. The ends of the punch 12 in places turning flow is rounded and directed towards the flow. The edge 15 of the window plate 6 is bent towards the flow in the inlet 11 and the flow outlet 10 reservoirs, optimally, when one of the plates, the edge 15 is located in the plane of the transition section 16, and coupled with it the other plate angle of the limb edges 15 ensures the parallelism of the edges of both plates. In addition, the angle of the inlet manifold 11 can be reduced along the flow, and the outlet 10 to increase in the range of 0opt60about.

As can be seen from Fig. 4, the angle at the apex of the corrugation 40-80 maboutthat is significantly less than in the known constructions (115-150about).

The heat exchanger works as follows.

One of the fluids flows through the input petruzalek is removed through the collecting chamber 5 and the outlet 3. The proposed location of the collectors 10, 11, partially protruding into the chamber 4, 5, ensures a uniform distribution of the flow rate of coolant through the channels 17, and this ensures efficient heat transfer throughout the volume of the matrix. Another coolant enters the inlet manifold 11 through the pipe 21. Here he gets into the channels 18 formed by the punch 8. Channel 18, the coolant enters the reservoir 10 and is removed through pipe 22. Due to the fact that the edges 15 of the punch Windows deflected towards the flow in the manifold 11 and the flow in the reservoir 10, reduced energy losses around the edges 15. If the angle is in the range 0-60aboutthen, as the calculations show, is achieved at least these losses. The change in the reservoir (increase the flow in the manifold 10 and a decrease in the collector 11) it is possible to achieve uniform distribution of coolant through the channels 18, which improves the efficiency of heat transfer. For the same purpose is executed punch 12 forming Assembly transverse partitions provide the zigzag movement of the heat carrier flowing in the channels 18.

Tube 14 attached to the reservoir 11, 10, serve to supply and discharge fluid, decodename partecke fluids. For this purpose is served seals 13, 23.

The use of relatively small angles at the tops of the corrugation (40-80about) allows to increase the number of contact points of adjacent plates. This makes it possible to reduce the contact stresses under load and thereby reduce the metal matrix. The implementation of the edges of the punch 12 facing towards the flow in the zone of its turn improves the flow of partitions, reduces the length of the vortex zones, improves heat transfer.

1. PLATE heat EXCHANGER, comprising a housing with coaxial input and output sockets, distribution and cameras team for one of the fluids, having a flat end and a cylindrical wall that is installed in the housing matrix consisting of plates with a punch bumps, that are interconnected in pairs by peripheral edges to form channels for both fluids, bounded by surfaces intersecting bumps, characterized in that the side walls of the casing and the adjacent edges of the plates are cylindrical in shape, the plates are made punch-UPS, United in pairs with the formation of the inlet and outlet cylindrical, collectora the same time, that edge punch Windows deflected towards the flow in the inlet and flow outlet headers.

3. Heat exchanger according to PP.1 and 2, characterized in that the angle of the limb edges of the Windows is in the range of 0 60o.

4. Heat exchanger according to PP.1 to 3, characterized in that the angle of the limb in the inlet manifold is reduced in the flow, and the outlet manifold increases in flow.

5. The heat exchanger under item 1, characterized in that the plates are made of cross punch, forming a zig-zag channels.

6. Heat exchanger according to PP.1 and 5, characterized in that the ends of the punch in places turning flow is rounded and directed towards the flow.

7. The heat exchanger under item 1, characterized in that the angle at the apex of the corrugation is in the range of 40 to 80o.

8. The heat exchanger under item 1, characterized in that between the edges of the plates of the matrix adjacent to the building, installed the seals.

9. The heat exchanger under item 1, characterized in that it has strengthened in one or both end walls of the housing inlet and outlet nozzles for the second heat transfer medium and installed in the pipes the pipes connected to the respective collectors.

11. The heat exchanger under item 1, characterized in that the matrix of the heat exchanger offset from the center of symmetry of the hull, the ratio of the lengths of the front surface of the matrix by the supply of coolant and exhaust is 1.4 to 1.7.

 

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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

FIELD: heat-exchange apparatuses with fixed ducts for two heat-transfer agents, in which the ducts are formed by separating plates, having perforated fins located inside there ducts.

SUBSTANCE: the method for intensification of heat exchange of two heat-transfer agents consists in heat transfer by means of perforated fins separating the flow-through cavities of each heat-transfer agent into parallel-connected ducts, and plates separating the adjacent flow-through ducts of different heat-transfer agents; at a flow of heat-transfer agents through the parallel-connected ducts of the respective flow-through cavity, heat exchange of the heat-transfer agent with the perforated fins washed by it is intensified due to the flow of the heat-transfer agent through the perforated holes in the fins between the adjacent parallel-connected ducts as a result of fluctuation of static pressure differentials in them, or t a regular destruction of the boundary layer of the heat-transfer agent on them due to the location of the perforated fins in the direction of flow of the heat-transfer agent in approximately staggered order with formation of several successively positioned sections of parallel-connected ducts so that the perforated fin in the second and subsequent sections in the direction of flow of the heat-transfer agent is shifted across this direction relative to the perforated fins of the previous section. The heat-exchange apparatus has alternating flow-through cavities of cooling and cooled heat-transfer agents formed by the separating plates of heat-conducting material, besides, the flow-through cavities of both heat-transfer agents are separated into out-of-round in cross section parallel-connected ducts by the respective fins of heat-conducting material being in a heat contact with the separating plates, the perforated fins in each flow-through cavity even of one heat-transfer agent staggered with formation of several successively located sections of parallel-connected ducts so that the perforated fin in the second and the subsequent sections in the direction of flow of the heat-transfer agent is shifted across-this direction relative to both perforated fins of the previous section making up the duct just before the shifted perforated fin, the length of the fin in each of the successively located sections of the ducts of the cooling heat-transfer agent makes up 20 to 60 quotients obtained when the averaged duct section area in the section is divided by the averaged duct section area in the section to the averaged perimeter of one duct.

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

3 cl, 7 dwg

FIELD: applicable in devices for conduction of heat exchanging processes between two media through a wall, in particular, in chemical, food, petroleum refining branches of industry.

SUBSTANCE: the heat exchanger plate bunch has a heat exchanger bank assembled of plane-parallel plates with bundles welded in pairs in boxes fixed at the ends in tube plates with a clearance to one another and forming tubular and intertubular ducts for input and output of the hot and cold products, two plane-parallel plates with partitions for overlapping the free area of the cross-section between the plate and the body of the heat exchanger, seal belt and a detachable mounting-transport support, the heat exchanger bank is made of several successively connected modules, each provided with two side shields made in the form of plates located along the bank, except its terminal zone, and secured on the plane-parallel plates, tube and intertube headers are formed in the zones of connection of the modules. Besides, in the bunch of the plate heat exchanger the tube header is made in the form of closed plane in the central part of the bank of the adjacent modules, and the intertube header is made with two channels, one channel on each lateral side of the bank, each channel is formed by an additional shield that is mounted in the terminal zone between the shields of the adjacent modules and connected to these shields and to the plane-parallel plates. The section of each channel of the intertube header is made in the form of a segment restricted from one side by the arc of the additional shield, whose radius equals half the diagonal of the bunch section, and from the other side - by a chord, whose length equal the width of the shield plate. The seal belt is made in the form of a cylinder-shaped obturator and installed in the zone of product output from the intertube channels.

EFFECT: simplified procedure of manufacture, transportation and mounting of the bunch in the body of the heat exchanger, improved conditions of heat exchanger sealing at passage of the heat exchange products through it, reduced expenditures on manufacture.

8 dwg, 4 cl

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