WO1998008042A1

WO1998008042A1 - Tube heat exchanger

Info

Publication number: WO1998008042A1
Application number: PCT/CZ1997/000022
Authority: WO
Inventors: Václav CHMELÍK; Pavel DIVIS^¿
Original assignee: Individual
Current assignee: Individual
Priority date: 1996-08-19
Filing date: 1997-06-20
Publication date: 1998-02-26
Anticipated expiration: 1999-02-19
Also published as: AU3087297A; CZ283016B6; CZ245096A3

Abstract

A tube type heat exchanger comprising coaxially arranged tubes of increasing diameter, characterised in that the first fluid tube (13, 15, 17, 19, 21) is interconnected with the first fluid distributor (3, 5, 7, 9, 11). The connection is ensured along the whole tube perimeter intersection (13, 15, 17, 19, 21) of the first medium tube and the first medium distributor (3, 5, 7, 9, 11). The upper part of the distributor (3, 5, 7, 9, 11) is fastened along the whole perimeter of intersection with the second fluid tube (14, 16, 18, 20, 22). By analogy, the second fluid leading tube (14, 16, 18, 20, 22) is interconnected with the first fluid leading tube (13, 15, 17, 19, 21). The first medium distributor (3, 5, 7, 9, 11) is interconnected with the first fluid inlet conduit (1). The second fluid distributor (4, 6, 8, 10, 12) is interconnected with the second fluid distributor (2).

Description

Tube heat exchanger

Technical area definition

This invention concerns of the tube heat exchanger for heat exchanging of liquids, gases and vapors.

Actual state of art

Most of the known heat exchangers are operating with relatively large rate of flow on both sides of tubes, and the heat transfer efficiency from the one delivered fluid to second is not too high. From variety of new designs the highest percentage of advantages may propose tube heat exchange according the patent BRD DE 31 25 933, where the heat exchanging is facilitate by means of co-axial embedded tubes of different diameter, which are on both ends equipped by two fluid feeding hollow plugs, so that every tube of increased diameter is connected to the inlet of one delivered fluid.

The high technological requirements and cost-consuming production of the feeding hollow plugs is the main disadvantage of this design. The inlet feeding hollow plug are furnished with gradually changed co-axial tube lugs, which must be dilatation resistant and tighten in circumferencial connection lines. From this reasons is difficult to get the most advantageous and minimum gaps between co-axial tubes of different diameters. In case of leakage of some co-axial circumferencial tube shoulder, one fluid can be contaminated with another one, without discovering this fact and the consecutive damages may be enormous.

Due to securing of the feeding hollow plugs strength, the space for alternating fluid inlet and outlet is minimized and cause the next disadvantage of this system. From above mentioned facts are the feeding hollow plugs placed on both ends of the heat exchanger from the pressure losses point of view is the limiting components. Described design can not be used for more type of fluid than two, for example for three and more. For multiple type of construction all co-axial tube bundles must be furnished with above described feeding hollow plugs. The design of tube exchangers with greater number of the co-axial tube bundles is limited and therefore the capacity of heat exchanger is limited too.

Merit of the invention

Aforementioned disadvantages are eliminated by the tube heat exchanger according this invention, which principles consist in following. Leading tube of firs fluid is connected to the distributor of the firs fluid so it make possible flow of first fluid through both parts . Connection is arranged in intersection of the leading tube end of the first fluid through lower part of the firs fluid distributor. The upper part of the first fluid distributor is connected in intersection of outer part leading tube second fluid with this second fluid leading tube. The first fluid distributor is next to this connected with second fluid leading tube.

In the similar way is second fluid leading tube connected with second fluid distributor, so that flow is possible through both parts. The connection is once again arranged in place of intersection second fluid leading tube end with second fluid distributor lover part. The upper part of the second fluid distributor body is connected with the outer part of the first fluid leading tube in place of its intersection through second fluid distributor.

The lower or opposite end of the first fluid leading tube and the second end of the second fluid leading tube are connected in similar way as upper tubes end with first and second fluid distributors, as described above. The first fluid distributor is connected to the first fluid discharger and second fluid distributor is in this case connected to the second fluid feeder.

Futures of this inventions area. The first and second fluid feeder and discharger and also the first and second fluid distributors has the tube diameter proportional to the diameters of individual tubes of the first and second fluid leading tubes, which are interconnected.

The gap between first fluid tube and second fluid tube is defined by lugs in the gap distributed.

The dilatation lugs are distributed in a circumferencial gap between first and second fluid leading tubes, in a few planes perpendicular to the axis of the mentioned tubes. On perimeter of this circumferencial gap are the distance lugs distributed roundwice on 120°.

Lover or opposite end of the first fluid leading tube and second end of the second fluid leading tube are connected with first and second fluid distributors, in mirrored way, but turned round an angle of 180° .

The advantages of this solution. Simple and synoptic exchanger design and at the same time low production costs and high lifetime. This design can operate under higher pressures, because individual arts of the heat exchanger are made of tubes, mounted by means of soldering and ending of the distributors is convex bottom type.

The design of the heat exchanger make possible to arrange it as a group of co-axial tube bundles, with minimum gap between tubes of the first and second fluid and in the system are no critical spots with increased inner flow resistance of both media. As the heat exchanger can be made of cooper, there exists minimum settlement of the minerals and the heat transfer coefficient will be almost ideal.

In case of leakage of any connection, the contamination of the one fluid with another can not occur, because the leaking fluid will occur only on outer surface of the heat exchanger. The repairs of such a leakage is simple. There are no problems with venting or draining, because there exist unambiguous technological highest and lowest points.

The design can include arbitrary number of co-axial fluid leading tubes in form of bundles, without any troubles from the design point of view of fluid distributors and other parts. Further advantages is that the fluid leading coaxial tubes can be arranged side by side in few sets, and exploitation of the space is very high. Such arrangement ensures high exchange surface and great capacity while preserving small dimensions. After some design modifications can be heat exchanger exploatated for more than tree media in one bundle of co-axial leading tubes,

List of drawings

The tube exchanger is fully described on the accompanying drawings, where Drwg. No. 1 is a longitudinal cross section of a said exchanger and Drwg. No. 2 is a partial view of the said exchanger in ground-plan and side view projection.

An example of the exchanger design

According to the present invention described on enclosed drawings No.

I and 2, the heat exchanger comprises of first fluid inlet section 1 being interconnected with distributors 3, 5, 7, 9, 11 of the first fluid. The distributor

I I of the first fluid 11 is interconnected to the first fluid leading pipe 21 , so that inner space of the first fluid distributor 11 and circumferential passages inner wall of the tube 21 and outer wall of the second fluid leading tube 22, ensures flow passages 31 of the first fluid.

Analogicaly, the first fluid distributor 3, 5, 7, 9 is interconnected with the first fluid leading tube 13, 15, 17, 19, ensures flow pass of the first fluid 23, 25, 27, 29.

The termination of the of the inlet section 1 is ensured by means of technologically operable vent 35 of the first fluid.

The second part of the tube type heat exchanger according this invention comprises of the second fluid discharger 2 interconnected with the second fluid distributor 4, 6, 8, 10, 12 . The second fluid distributor 12 is interconnected with the second fluid leading pipe 22 so that the second fluid distributor inner space 12 and the circumferencial passage between inner space of the second fluid pipe 22 and outer space of the first fluid leading pipe 19, to form flow passage of the second fluid 32. Analogicaly, the second fluid distributor 4, 6, 8, 10 is interconnected with the second fluid leading tube 14, 16, 18, 20 to form fluid passages 24, 26, 28, 30 of the second fluid.

The termination of the of the inlet section 2 is ensured by means of technologically operable vent 34 of the second fluid.

The pipe of the smallest diameter forming the axis of the leading pipes is not-functional skeleton of said exchanger.

The first fluid leading pipes 13, 15, 17, 19, 21 and second fluid pipes 14, 16, 18, 20, 22 are spaced apart by means of the dilatation lugs. The first and second fluid distributors are closed by the blinders 36.

To the coaxial pipes bundle 38 are in their lowest part attached the same not demonstrated inlet section of the second fluid discharger section of the first fluid. The invention also provides exchanging heat or could between two fluids, for example steam and process water. By means of special adaptation can be said exchanger exploatated for three or more fluids.

In such case is inlet part 1 in some stage blinded and over this stage is ensured inlet of third fluid. This requires also modification of the exchanger turned on 180° and the same modification of the not depicted second fluid outlet distributor.

According attached figures function of the exchanger may be described as follows. From the not depicted source of steam is steam fed into first fluid inlet section 1, by means of the first fluid distributors 3, 5, 7, 9, 11 is steam supplied into two coaxial arranged tube bundles 38 and than is passing the first fluid coaxial arranged tubes 13, 15, 17, 19, 21. The first fluid distributors 3, 5, 7, 9, 11 by this interconnection form flow passages 23, 25, 27, 29, 31 of the first fluid. This flow passage is formed so that first medium distributor 3, 5, 7, 9, 11 is in upper part, in intersection of the second fluid leading pipe 14, 16, 18, 20, 22 on this tube fastened on the total intersection perimeter, and in lower part is the first medium distributor 3,5,7,9,11 fastened on the total intersection perimeter on ends of the first medium leading tubes 13,15,17,19,21, so that steam can flow in this tubes downstream through circumferencial passages of the first medium tubes 23, 25, 27,29, 31. During vertical steam flow the heat is transferred between pipe walls, steam is cooled and condense and at the lowest point is said condensate drained into not depicted first medium distributor turned to the upper distributor on 180°.

Utility water, heated by steam is fed by means of first fluid not depicted inlet section and not depicted second fluid distributor into could water source. Both sections are turned on 180° against second medium distributors 4,6,8,10,12 and being connected to the second fluid leading tubes 14,16,18,20,22, which forms fluid flow path 13,15,17,19,21 of utility water flowing During utility water flow upwards is said water heated from both walls by steam flowing in opposite direction. In upper part demonstrated part of exchanger is heated utility water in distributor 4,6,8,10,12 drained into second fluid discharger 2 and can be used as a hot utility water. There is advantageous, to insure that the tubes diameter of the first and second fluid inlet section was reduced in dependence on decreasing diameter first and second distributors. The first and second distributors diameter is dependent on the first and second fluid leading tubes diameter. This diameter depends on first and second fluid leading tubes diameter and it is defined by ordering of said tubes in common tube bundle. Lowering of diameter response in fluid flow rate lowering.

Because the distributors of first and second medium according our example interconnect two coaxial tubes bundles 38, the cutout of the first and second medium tubes through inner part of the first and second medium distributors in such way, that intersection of the annular part of the first and second medium flow channel, which is formed by insert first medium tube in second medium tube, is smaller, than intersection formed by intersection first and second medium tubes and perpendicular tube intersection plane, forming the first and second medium distributor.

This is why gas or liquid equal pressure distribution is reached, without serious pressure losses in whole exchanger system. The annular space between tubes of the first medium coaxial leading tubes, which is important for the heat exchanging, ensure dilatation lugs, distributed on 120°, and which ensure also coaxiality of the heat exchanger functional tube bundles. The tube of smallest diameter 33 of the coaxial tube bundle has no functional importance.

Deaeration device of the tube heat exchanger is made at the highest point of the first medium inlet tube 1 and second medium discharge tube 2, where is ensured technological opening 35 for first medium and technological opening 34 for second medium.

At the lower part of the tube heat exchanger, which is not depicted but symmetrical and turned on 180^0, is deareation device arranged in the lowest part of the first medium inlet tube and second medium discharge tube. This technological openings of the first medium inlet tube and second medium discharge tube can be used as desliming and trapping device.

From the technological point of view is advised to use as a first medium and second medium distributors 36 covers the concave bottoms, which make possible to increase heat exchanger operation pressure. The heat exchanger design allows to get high exchange efficiency during heat or cold transfer and its dimensions are small. When one or more coaxial medium leading tubes 38 are used, the heat exchange concentration between mediums can be insured.

As an example of the coaxial leading tubes 38, forming main part of the exchanger is used bundle with ten (10) tubes. The heat exchanger output is define with number of the coaxial leading tubes 38 bundles, with number of the coaxial leading tubes 38 in one bundle and with its length.

Claims

1. A tube type heat exchanger comprising of coaxial arranged tubes of increased diameter, cha-racterized in that the first fluid tube (13, 15, 17, 19, 21) being interconnected with first fluid distributor (3, 5, 7, 9, 11) along whole perimeter of its end in intersection of the lower first fluid distributor (3, 5, 7, 9, 11), while its upper part being fastened along the whole perimeter of intersection of the second fluid tube (14, 16, 18, 20, 22), and the first fluid distributor (3,5,7,9,11) is interconnected with the first fluid inlet conduit (1), while the first fluid tube (14, 16, 18, 20, 22) is interconnected with the second fluid distributor (4, 6, 8, 10, 12) in whole perimeter of its end in intersection lover part of the second fluid distributor, while of its upper part being fastened along the whole perimeter of intersection of the first medium outer part tube (13, 15, 17, 19, 21) and the second fluid distributor (4, 6, 8, 10, 12) is interconnected with second fluid distributor (2) and the second end of the first fluid pipe (13, 15, 17, 19, 21) and also the second end of the second fluid pipe (14, 16, 18, 20, 22) is interconnected with the same first fluid distributors and discharges and to the second fluid distributors and inlet section.

2. A tube type exchanger as claimed in Claim 1 characterized in that the first and second fluid inlet and discharge conduits cross-section is reduced in dependence on reducing of the first and second fluid distributors, which cross- section is derived from cross-section of the first and second fluid pipes.

3. A tube type exchanger as claimed in Claim 1, characterized in that the gap between the first fluid tube (13, 15, 17, 19, 21) and the second fluid tube (14, 16, 18, 20, 22) are formed on tubes of the first and second fluid.

4. A tube type exchanger as claimed in Claims 1 and 3 character! zed in that the dilatation lugs (37) are formed in gaps between the first medium tube (13, 15, 17, 19, 21) and the second fluid tube (14, 16, 18, 20, 22) in planes perpendicular to the axis of said tubes and turned on 120°

5. A tube type exchanger as claimed in Claim l characterized in that the second end of the first fluid tube (13, 15, 17, 19, 21 ) is interconnected with the same distributor and inlet section turned on 180° in relation to the first fluid distributor (3, 5, 7, 9, 11) and inlet section (1) and second end of the second fluid tube (14, 16, 18, 20, 22) is interconnected with the same second fluid distributor and inlet section turned to the second fluid distributor (4, 6, 8, 10, 12) and discharger (2) on 180°.