RU2726136C1 - Multi-pass cross-flow heat exchanger plate - Google Patents

Abstract

FIELD: heat exchange.SUBSTANCE: invention relates to heat engineering and can be used in heat exchangers for heat recovery. Plate multi-pass cross-exact heat exchanger contains a housing, in which corrugated plates are installed, forming a cavity for the first heat carrier with devices of supply and withdrawal, and also tubular heat exchange channels with V-shaped projections for the second heat carrier. Corrugated plates are welded to each other in pairs on peripheral edges of two through windows and seating surfaces of opposite end into a single heat exchange stack with collectors formed by adjacent corrugated plates through corners and communicated with supply devices and removal of the first heat carrier, for which multi-pass flow is provided with at least one overlapping of the throughput opening. In order to realize multi-pass flow of the second heat carrier, at least one partition wall is installed, which connects, without rigid connections of the supply and discharge device with a single heat exchange packet, separating the second heat carrier along the passages so that at the initial stroke the V-shaped projections of the tubular heat exchange channels are directed with their apices towards the flow of the second heat carrier, and their positions in the subsequent strokes are arbitrary.EFFECT: technical result is higher efficiency of heat utilization, self-cleaning heat-transferring surface.8 cl, 1 dwg

Description

The invention relates to heat engineering, mainly to small heat power engineering, and can be used, for example, as a heat exchanger for heat recovery of exhaust gases of internal combustion engines and microturbines.

The operating experience of internal combustion engines, in particular diesel engines, showed a decrease in the efficiency of the heat exchangers used in the recovery of exhaust heat. This is due to a large amount of soot, which is formed during the working process of the diesel engine and partially settles on the heat transfer surface of the heat exchangers, forming a heat-insulating layer. As a result, the efficiency of the heat exchangers decreases as the thickness of the soot layer increases. In addition, they increase the hydraulic resistance along the exhaust gas path, which, upon reaching a critical value, can negatively affect the diesel engine's working process. Therefore, this problem is relevant, and the present invention is aimed at solving it.

Known heat transfer tube of non-circular cross section (SU 1210050 A; IPC F28F 1/40; publ. 04.01.1984) containing V-shaped protrusions, the peaks of which are directed towards the flow of the coolant.

This heat exchanger tube does not constitute a heat exchanger design, therefore, it is not considered as a full-fledged analogue of the plate-type multi-way cross-flow heat exchanger proposed by the invention.

Known water-tube boiler heat exhaust gas (RU 136532 U1; IPC F22B 1/18; publ. 10.01.2014), containing a cylindrical body with water collectors associated with a pipe system of straight pipes, which is fixed in the annular tube sheets. The cylindrical housing is also equipped with devices for supplying and removing a second coolant washing the pipe system in the inner space.

The proposed utility model has several disadvantages: large mass-overall dimensions, contamination of the heat transfer surface of the pipe system, the ability to clean this surface only if the water-tube waste heat boiler is dismantled.

Known plate heat exchanger (SU 513234 A1; IPC F28F 3/08; publ. 05/05/1976) containing a stack of corrugated plates pairwise connected along the side windows, forming tubular heat exchange channels, which are tubes with cylindrical sections alternating with spiral segments along length.

The disadvantage of the presented plate heat exchanger is deposits on cylindrical sections in the heat exchange channels during the flow of contaminated coolant, as well as the absence of a multi-pass flow pattern for both coolants.

Known plate heat exchanger (RU 2435123 C2; IPC F28F 3/08; publ. 11/27/2011) containing a stack of corrugated plates connected through holes that form passages and communicate with the cavity for the first coolant. The cavity for the second coolant is formed by corrugations of the contacting plates in the form of rectilinear protrusions directed at an angle relative to the flowing coolant.

However, in this invention there is no multi-way motion scheme of the second coolant. In addition, the invention has low efficiency with contaminated coolants.

Known plate heat exchanger (RU 2206851 C1; IPC F28D 9/00; publ. 06/20/2003) containing a stack of corrugated plates pairwise connected along the side windows with the formation of tubular heat exchange channels, connected along peripheral sides into a single heat exchange package with sectional overlapping of the side windows for a multi-pass flow of the first heat carrier, which is inserted into the housing with separated cavities for the inlet and outlet of the second heat carrier and is clamped by end plates with supply pipes to the side windows of the heat transfer package of the first heat carrier. The heat transfer bag is sandwiched between the end plates with seals by means of clamping elements.

The disadvantage of the presented plate heat exchanger is significant deposits in the heat exchange channels during the flow of contaminated coolant. The presence of compression elements in the design of the plate heat exchanger requires the use of high-quality seals. The scope of such a heat exchanger is limited by the resistance of the used seals to pressure and temperature.

The closest in technical essence, selected as a prototype, is a plate heat exchanger (Favstov BC Plate heat exchanger for utilization of heat of exhaust gases of a diesel engine / BC Favstov, V.A. Mukhachev, A.A. Pavlov, A.V. Zharov // 3rd All-Russian Scientific and Practical Conference "History and Prospects for the Development of Transport in the North of Russia": Sat. / Yaroslavl branch of MIIT - Yaroslavl, 2014. - P. 121-124), containing a housing in which corrugated plates are installed, forming cavity for the first coolant with inlet and outlet devices, as well as tubular heat exchange channels with V-shaped protrusions for the second coolant.

This prototype does not provide a multi-way flow diagram of the second coolant.

The objective of the invention is the creation of a plate multi-way cross-precision heat exchanger with improved performance properties when working with contaminated coolants in comparison with the presented analogues and prototype.

The solution to the problem is achieved by the fact that the plate multi-way cross-precision heat exchanger contains a housing in which corrugated plates are installed that form a cavity for the first heat carrier with inlet and outlet devices, as well as tubular heat exchange channels with V-shaped protrusions for the second heat carrier, while the corrugated plates in pairs are welded together along the peripheral edges of two passage windows and landing surfaces of the opposite end into a single heat transfer package with collectors formed by corrugated plates adjacent to each other through passage windows and in communication with the supply and removal devices of the first heat carrier, for which a multi-pass flow with at least one overlap of the passage window, and for the implementation of the multi-pass flow of the second heat carrier, at least one partition is installed that connects the supply and exhaust devices without a single connection to a single heat transfer package, dividing the second heat carrier along the way m so that at the initial turn the V-shaped protrusions of the tubular heat-exchange channels are directed by the vertices towards the flow of the second coolant, and in the subsequent moves their positions are arbitrary.

The use of tubular heat exchange channels with V-shaped protrusions for passing through a contaminated (second) coolant is based on the effect of self-cleaning of the heat transfer surface due to strictly oriented vortices arising near the walls in the contaminated coolant flow. They prevent particles from settling on the heat transfer surface and pull them from the periphery to the central core of the flow. From there, the particles are blown out due to the high flow rate from the tubular heat exchange channels with V-shaped protrusions. This phenomenon occurs due to the direction of the flow of contaminated coolant towards the tops of the V-shaped protrusions according to the patent of the Russian Federation No. 1210050. Since the bulk of the particles of the contaminated coolant is deposited at the initial stroke in the plate multi-pass cross-precision heat exchanger, then, in subsequent moves, the direction of flow relative to the vertices of the V-shaped protrusions is not significant. When moving from the first move to the second when turning through 180 ° in a plate multi-pass cross-precision heat exchanger, the particles will settle on a surface that is not involved in the heat transfer process, which will not lead to a deterioration in its operation.

Due to the developed heat transfer surface of the tubular heat exchange channels with V-shaped protrusions and the cross-precise system of movement of heat carriers, their flow is organized at high speeds. Firstly, it reduces the contamination of the heat transfer surface, as the appearance of stagnant zones with low coolant flow rates is unlikely, and secondly, it intensifies the heat transfer process.

A single heat transfer package of access ports in pairs welded along the peripheral edges and landing surfaces of the opposite end of the corrugated plates is dialed by turning each subsequent pair of corrugated plates 180 ° relative to the previous one parallel to the tubular heat exchange channels.

For a multi-pass flow of the first heat carrier, corrugated plates with one passage window are inserted in pairs welded along the peripheral edges of the passage windows and the seating surfaces of the opposite end into a single heat transfer package.

The multi-pass flow of the second heat carrier is realized due to the partition connecting the supply and exhaust devices without rigid connections to a single heat-exchange package, which is movable by means of a fork connection with labyrinth grooves.

In the case of the flow of the second heat carrier through the number of strokes of more than two, one partition without rigid connections is connected only to the supply device and a single heat exchange package, and an additional partition from the opposite side relative to the supply device is also connected without a rigid connection to a single heat transfer package and removal device.

To provide additional tightness, the lateral technological channels along a single heat-exchange package are covered with corrugated tapes over the entire width of the passage windows.

The inlet and outlet devices of the first coolant are made in the form of thin-walled nozzles and are connected to the body fittings with a radial deformation gap to the welding zone.

A single heat transfer package on the sides rests on the corners that support it from sagging, mounted on the walls of the housing. Thus, a single heat transfer package is clamped in the housing without rigid connections, which avoids the negative effects of thermal shock.

Significant differences of the proposed plate multi-way cross-exchanger heat exchanger from the selected prototype are that the corrugated plates are pairwise welded together at the peripheral edges of two passage windows and landing surfaces of the opposite end in a single heat transfer package with collectors formed by adjacent passage windows corrugated plates and connected with the supply and removal devices of the first coolant, for which there is a multi-way flow with at least one overlap of the passage window. To implement the multi-path flow of the second heat carrier, at least one partition is installed that connects the supply and exhaust devices without a single connection with a single heat transfer package, separating the second heat carrier along the paths so that at the initial stroke the V-shaped protrusions of the tubular heat transfer channels are directed by their vertices towards the flow of the second heat carrier, and in subsequent moves their positions are arbitrary.

A single heat transfer package of access ports in pairs welded along the peripheral edges and landing surfaces of the opposite end of the corrugated plates is dialed by turning each subsequent pair of corrugated plates 180 ° relative to the previous one parallel to the tubular heat exchange channels.

For a multi-pass flow of the first heat carrier, corrugated plates with one passage window are inserted in pairs welded along the peripheral edges of the passage windows and the seating surfaces of the opposite end into a single heat transfer package.

For a multi-pass flow of the second heat carrier, the partition connecting the supply and exhaust devices without a single connection to a single heat-exchange package is movable by means of a forked connection with labyrinth grooves.

For a multi-pass flow of the second heat carrier with more than two strokes, one partition without rigid connections is connected only to the supply device and a single heat exchange package, and an additional partition from the opposite side relative to the supply device is also connected without a rigid connection to a single heat transfer package and removal device.

Lateral technological channels along a single heat-exchange package are blocked over the entire width of the passage windows with corrugated tapes.

The inlet and outlet devices of the first coolant are made in the form of thin-walled nozzles and are connected to the body fittings with a radial deformation gap to the welding zone.

A single heat transfer package on the sides rests on the corners fixed on the walls of the housing.

In FIG. 1 shows a plate multi-way cross-precision heat exchanger containing a housing (1), in which corrugated plates are installed that form a cavity for the first heat carrier with inlet (3) and outlet (4) devices, as well as tubular heat exchange channels with V-shaped protrusions for the second coolant, while the corrugated plates are welded in pairs along the peripheral edges of two passage windows and the seating surfaces of the opposite end into a single heat transfer package (2) with collectors formed by corridor plates adjacent to each other through passage windows and connected to the supply devices (3) and outlet (4) of the first coolant, for which a multi-pass flow with at least one passageway window overlap is provided, and for the multi-pass flow of the second coolant to be implemented, at least one partition (7) is installed that connects the supply (5) and exhaust (6) devices without rigid connections a single heat transfer package (2), separating the second the carrier of the courses so that at the initial course the V-shaped protrusions of the tubular heat-exchange channels are directed by the vertices towards the flow of the second coolant, and in the subsequent moves their positions are arbitrary.

A single heat transfer package (2) from access ports pairwise welded along the peripheral edges and landing surfaces of the opposite end of the corrugated plates is dialed by turning each subsequent pair of corrugated plates relative to the previous one 180 ° parallel to the tubular heat exchange channels.

For a multi-pass flow of the first heat carrier, corrugated plates with one passage window are inserted in pairs welded along the peripheral edges of the passage windows and the seating surfaces of the opposite end into a single heat transfer package (2).

For a multi-pass flow of the second heat carrier, the partition (7) connecting the inlet (5) and outlet (6) devices with a single heat exchange package (2) is movable by means of a forked connection with labyrinth grooves.

Lateral technological channels along a single heat-exchange package (2) are blocked over the entire width of the passage windows with corrugated tapes (8).

The inlet (3) and outlet (4) devices of the first coolant are made in the form of thin-walled nozzles and are connected to the fittings (9) of the housing (1) with a radial deformation gap to the welding zone.

A single heat transfer package (2) on each side rests on the corners (10), mounted on the walls of the housing (1).

Plate multi-way cross-precision heat exchanger operates as follows.

The first heat carrier enters a single heat transfer package (2) through the supply device (3). Then, through the cavity formed by the corrugated plates, the first heat carrier flows in at least two strokes and exits through the exhaust device (4), simultaneously contacting the second heat carrier through the heat transfer surfaces. The second heat carrier enters through the supply device (5), passes through tubular heat-exchange channels with V-shaped protrusions directed by their vertices towards the flow at the first stroke. Then, the second heat carrier rotates through 180 ° and goes through tubular heat-exchange channels with V-shaped protrusions directed by vertices downstream in the second stroke and exits through the exhaust device (6). The inlet (5) and outlet (6) devices are connected to a single heat exchange package (2) without rigid connections by means of a partition (7), forming together with the body (2) a cavity of the second coolant with two strokes.

Claims (8)

1. Plate multi-way cross-precision heat exchanger containing a housing in which corrugated plates are installed that form a cavity for the first heat carrier with inlet and outlet devices, as well as tubular heat exchange channels with V-shaped protrusions for the second heat carrier, characterized in that the corrugated plates are pairwise welded together at the peripheral edges of two passage windows and landing surfaces of the opposite end into a single heat transfer package with collectors formed by corrugated plates adjacent to each other through passage windows and in communication with the supply and exhaust devices of the first coolant, for which a multi-pass flow with at least one by blocking the passage window, and to implement a multi-pass flow of the second heat carrier, at least one partition is installed that connects the supply and exhaust devices without a single connection to a single heat transfer package, separating the second heat carrier along the paths so that at the beginning Along the way, the V-shaped protrusions of the tubular heat-exchange channels are directed by the vertices towards the flow of the second heat carrier, and in the subsequent moves their positions are arbitrary. 2. The heat exchanger according to claim 1, characterized in that a single heat transfer package of the passage openings pairwise welded along the peripheral edges and the seating surfaces of the opposite end of the corrugated plates is dialed by turning each subsequent pair of corrugated plates 180 ° relative to the previous one parallel to the tubular heat exchange channels. 3. The heat exchanger according to claim 1, characterized in that corrugated plates with one passage window are inserted in pairs welded along the peripheral edges of the passage windows and landing surfaces of the opposite end for a multi-pass flow of the first heat carrier. 4. The heat exchanger according to claim 1, characterized in that for a multi-pass flow of the second heat carrier, a partition connecting without supplying rigid connections the supply and removal devices with a single heat transfer package is movable by means of a forked connection with labyrinth grooves. 5. The heat exchanger according to claim 1, characterized in that for a multi-pass flow of the second heat carrier with more than two strokes, one partition without rigid connections is connected only to the supply device and a single heat exchange package, and the additional partition from the opposite side relative to the supply device is also without rigid connections connected to a single heat transfer package and a removal device. 6. The heat exchanger according to claim 1, characterized in that the side technological channels along a single heat exchange package are blocked by the corrugated tapes over the entire width of the passage windows. 7. The heat exchanger according to claim 1, characterized in that the inlet and outlet of the first coolant are made in the form of thin-walled pipes and are connected to the body fittings with a radial deformation gap to the welding zone. 8. The heat exchanger according to claim 1, characterized in that a single heat transfer package on the sides rests on the corners mounted on the walls of the housing.

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