SU1746185A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
SU1746185A1
SU1746185A1 SU904834135A SU4834135A SU1746185A1 SU 1746185 A1 SU1746185 A1 SU 1746185A1 SU 904834135 A SU904834135 A SU 904834135A SU 4834135 A SU4834135 A SU 4834135A SU 1746185 A1 SU1746185 A1 SU 1746185A1
Authority
SU
USSR - Soviet Union
Prior art keywords
pipes
spacers
heat exchanger
layers
transverse
Prior art date
Application number
SU904834135A
Other languages
Russian (ru)
Inventor
Оксана Кирилловна Красникова
Тамара Сергеевна Мищенко
Юрий Петрович Козьмин
Арнольд Эдмундович Брейво
Валерий Яковлевич Красносельский
Галина Алексеевна Седова
Original Assignee
Всесоюзный научно-исследовательский институт гелиевой техники
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Всесоюзный научно-исследовательский институт гелиевой техники filed Critical Всесоюзный научно-исследовательский институт гелиевой техники
Priority to SU904834135A priority Critical patent/SU1746185A1/en
Application granted granted Critical
Publication of SU1746185A1 publication Critical patent/SU1746185A1/en

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Abstract

The invention relates to heat exchangers and can be used in cryogenic, aviation, chemical, gas and other areas of technology, where heat exchangers with intensive heat exchange process and low flow resistance are required. The purpose of the invention is to increase the intensification of heat exchange by improving the uniformity of the transverse flow of pipes. In a heat exchanger containing a bundle of coil pipes. wound with coaxial layers and in staggered order in adjacent layers, and spacer spacers in the form of wavy ribbons placed between layers, tubes in a bundle are arranged with transverse and longitudinal steps, determined from the ratios - ti d; d + b ta 3.75 d, where ti is the transverse step of winding; t2 - longitudinal pitch; d - the thickness of the spacers. The heat exchanger consists of a housing 1 with inlet and outlet manifolds from the tube space and inlet and outlet fittings from the annular space, core 6, on which pipes 7 with spacers 8 and 9 are spirally wound to distribute gas flows through the core 6 and the last layer of the winding of the pipes 7 a cord 10 of elastic porous material, such as metal rubber, is laid. 3 hp f-ly, 3 ill. cl

Description

The invention relates to heat exchangers for cryogenic, aviation, chemical, gas and other branches of engineering that require heat exchangers with an intensive heat exchange process and low flow resistance.

A twisted tubular heat exchanger with spacers between the layers of pipes arranged parallel to the axis of the core is known.

In this heat exchanger design, a gas, the passage between the layers of pipes through the through-ring channels, washes only a part of the surface of the pipes. As a result, the intensity of heat transfer in the heat exchanger is low. In addition, the disadvantage of the heat exchanger is the technological complexity of maintaining the same geometry of the annular channels in the multilayer winding due to the fact that the width of the ring is fixed only at the locations of the discrete spacers.

A twisted heat exchanger is known, which has spacers arranged along helical lines between layers of smooth pipes, alternating right and left windings in adjacent layers.

Remote spacers located along a helical line improve the technological properties of the structure, however

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the disadvantage associated with incomplete flushing of the surface of the pipes and, consequently, intensive heat exchange is not eliminated.

Known heat exchanger, in the construction of which spacers are made sinuous. They are located between the pipe layers parallel to the core axis and contain protrusions defining the distance between the turns of the pipes in the layer. The centers of the pipes of one layer with respect to the centers of the pipes of the other layer are in a checkerboard pattern.

The disadvantage of this design is also a reduction in the intensity of heat exchange due to incomplete gas flow around the surface of the pipes.

In addition, the technological difficulties of obtaining the same and precisely maintained width of the codian channels between the layers of pipes should be attributed to the design drawbacks. The specified channel width is observed only at the locations of discrete spacers, and between the spacers the position of the pipes is not fixed. As a result, the shape and dimensions of the annular channels cannot be the same between all layers of pipes. This leads to an uneven distribution of gas flow between the layers of pipes, an uneven temperature field, and a decrease in the efficiency of the heat exchanger.

The purpose of the invention is to increase the intensity of heat exchange by improving the uniformity of cross flow around the pipes, reducing the metal intensity and the dimensions of the heat exchanger.

This goal is achieved by that in a heat exchanger containing a bundle of serpentine tubes wound with coaxial layers and in staggered order in adjacent layers, and spacer spacers in the form of wavy ribbons placed between the layers of tubes, the bundled tubes are arranged with transverse and longitudinal steps Emitted from the relations:

6 + d

ti d;

d + d ta S3,75d, where ti is the transverse winding pitch;

t2 longitudinal pitch;

d - thickness of the spacer; d is the outer diameter of the pipe.

To provide a small hydraulic resistance in the annular space, a part of the spacers is made of an elastic porous material, such as metal rubber, and the rest of the spacers can be made of a hard material.

In addition, the spacers, the next mow beam, made of rigid material.

FIG. 1 shows a heat exchanger; general view; in fig. 2 - the same, winding cross-section (section along the axis of the heat exchanger); in fig. 3 is a section A-A in FIG. 2. The heat exchanger (Fig. 1) consists of a housing 1 with inlet 2 and outlet 3 collectors from the tubular space and fittings 4 and 5 of the inlet and outlet respectively from the annular space, core b, onto which the coaxial layers are helically

pipes 7 are wound with spacers 8 and 9 in the form of wavy ribbons.

To eliminate the gas overflows on the body and the core to the core 6 and the last layer of the winding pipes 7, the cord 10 is laid out of

elastic porous material, such as metal rubber.

Remote spacers 8, stacked on the core 6, are made tortuous and hard of low-heat

material, for example steel, and provide a step and a uniform winding. Both rigid spacers 8 and spacers 9 made of an elastic porous material, such as metal rubber (Figs. 2 and 3), are placed between the layers of the winding, it is possible to install gaskets only of elastic material.

The winding of the pipes 7 is made with transverse ti and longitudinal i steps in such a way that they correspond to the ratios

S “, Sd:

d + d g 3.75d, where d is the outer diameter of the tube, mm;

d - thickness of the spacer, mm.

The smaller value of the transverse pitch ti ti is limited by the minimum possible gap between the tubes for the passage of gas, equal to half the thickness of the spacers

8 or 9 (fig. 3).

And the smaller value of the longitudinal pitch t2 is limited by the shortest distance between the centers of the pipes in the adjacent layers S, which is equal to S d + d.

A larger value of the transverse winding pitch ti is determined as follows: when the value of ti is greater than d. Through-ring channels appear in the winding structure, which reduces the cross-flow effect and reduces the heat exchange intensity.

The larger value of the longitudinal pitch of the winding is selected based on the following considerations. It is known that the region of greatest turbulence of flow beyond the transversely flowed cylinder (tube) extends over a distance approximately equal to four cylinder diameters (t2 4d).

With a further increase in the longitudinal pitch ta, along with a decrease in the turbulence of the flow and, accordingly, a decrease in the intensity of heat exchange, the dimensions of the heat exchanger and its intensity of metal increase significantly.

The heat exchanger operates as follows.

The direct gas flow comes from the collector 2 to the pipes 7, where it is cooled (heated) by a reverse gas flow passing in the annular space. The cooled (heated) gas flow in the pipes 7 exits the heat exchanger through the collector 3. The return flow of gas flows through the nozzle 4 into the annular space, moves in countercurrent with the gas passing in the pipes 7, is heated (cooled) due to heat exchange with the gas passing through the pipes and through the nozzle 5 exits the heat exchanger.

The proposed heat exchanger will allow by intensification of heat exchange in the annular space to reduce the metal consumption by about 2 times, which is especially important for the transport option, as well as improve the manufacturability of the product.

Claims (4)

1. A heat exchanger containing a bundle of coil pipes wound with coaxial layers and in staggered order in adjacent layers, and spacer spacers in the form of wavy ribbons placed between the layers of pipes, characterized in that. that, in order to increase the intensification of heat exchange by improving the uniformity of the transverse flow of pipes, the latter are arranged in a beam with transverse and longitudinal steps determined from the ratios
s ,, sd:
d + (3.75 d. where ti is the transverse winding pitch; t2 is the longitudinal pitch of the coiling; d is the thickness of the spacer; d is the outer diameter of the pipe.
2. Heat exchanger according to claim 1, characterized in that part of the spacers is made of an elastic porous material.
3. Heat exchanger according to claim 2, characterized in that the remainder of the spacers is made of a rigid material.
4. Heat exchanger on PP. 1-3, wherein the spacers closest to the beam axis are made of rigid material.
FIG. Z
Aa
Fig.Z
SU904834135A 1990-04-03 1990-04-03 Heat exchanger SU1746185A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SU904834135A SU1746185A1 (en) 1990-04-03 1990-04-03 Heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SU904834135A SU1746185A1 (en) 1990-04-03 1990-04-03 Heat exchanger

Publications (1)

Publication Number Publication Date
SU1746185A1 true SU1746185A1 (en) 1992-07-07

Family

ID=21518092

Family Applications (1)

Application Number Title Priority Date Filing Date
SU904834135A SU1746185A1 (en) 1990-04-03 1990-04-03 Heat exchanger

Country Status (1)

Country Link
SU (1) SU1746185A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5845704A (en) * 1997-05-16 1998-12-08 Flowserve Management Company Heat exchanger baffle design
US6076597A (en) * 1997-12-31 2000-06-20 Flowserve Management Company Helical coil heat exchanger with removable end plates

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Патент US N 335484, кл. 165-76, опублик. 1967. *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5845704A (en) * 1997-05-16 1998-12-08 Flowserve Management Company Heat exchanger baffle design
US6076597A (en) * 1997-12-31 2000-06-20 Flowserve Management Company Helical coil heat exchanger with removable end plates
US6102106A (en) * 1997-12-31 2000-08-15 Flowserve Management Company Method of servicing a helical coil heat exchanger with removable end plates

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