GB1596001A - Fluid-cooling heat-exchange apparatus - Google Patents

Fluid-cooling heat-exchange apparatus Download PDF

Info

Publication number
GB1596001A
GB1596001A GB414478A GB414478A GB1596001A GB 1596001 A GB1596001 A GB 1596001A GB 414478 A GB414478 A GB 414478A GB 414478 A GB414478 A GB 414478A GB 1596001 A GB1596001 A GB 1596001A
Authority
GB
United Kingdom
Prior art keywords
inner casing
inlet
outlet
casing
chambers
Prior art date
Legal status (The legal status 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 status listed.)
Expired
Application number
GB414478A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Serck Industries Ltd
Original Assignee
Serck Industries Ltd
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 Serck Industries Ltd filed Critical Serck Industries Ltd
Priority to GB414478A priority Critical patent/GB1596001A/en
Publication of GB1596001A publication Critical patent/GB1596001A/en
Expired legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/226—Transversal partitions

Description

(54) FLUID-COOLING HEAT-EXCHANGE APPARATUS (71) We. SERCK INDUSTRIES LIMITED, a British Company, of P.O. Box 598B, Warwick Road, Birmingham, B ii 2QY, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: This invention relates to apparatus for cooling a first fluid by heat-exchange with a second fluid, and principally to apparatus for cooling compressed air by heat-exchange with water.
Generally compressed air is supplied to such cooling apparatus by way of a pipe which is relatively small in diameter. Conse quently the velocity at which the compressed air flows into the apparatus tends to be high, and it is necessary to reduce this velocity in order to prevent damage being caused to the heat transfer surfaces of the cooling apparatus. Such a reduction in velocity can be effected by enlarging the cross-sectional area of the flow path of the compressed air, or by causing the compressed air to impinge upon a deflector plate. Often, a combination of both of these methods is used.
In addition. it is desirable to distribute the incoming compressed air evenly over the heat transfer surfaces to obtain maximum utilization of the latter and to ensure that the velocity of the air is low enough not to exceed an allowable pressure drop through the cooling apparatus. Furthermore, the temperature of the compressed air will often be reduced to below the dew point of any entrained vapours (such as water vapour), and it is then necessary to provide some means whereby the condensate can be extracted so that it is not carried out of the apparatus by the cooled air.
It is an object of the present invention to provide cooling appartus which can satisfy the ahove-descril)ed requirements.
According to the present invention, there is provided apparatus for cooling a first fluid by heat-exchange with a second fluid, corn- prising Inner and outer tubular casings defining therebetween two chambers which are mutually separated axially of the casings; heat exchange means disposed in the inner casing, through which the second fluid is passed in use, each of said chambers extending at least a part of the way around the heat exchange means externally of the inner casing; an inlet in the outer casing and an inlet in the inner casing communicating with one of said chambers at respective points which are generally on opposite sides of the heat exchange means; and an outlet in the outer casing and an outlet in the inner casing communicating with the other of said chambers at respective points which are also generally on opposite sides of the heat exchange means; the inlet and outlet in the casing being so disposed that first fluid entering the inner casing through said inlet thereto is constrained to flow across the heat exchange means before leaving the inner casing through said outlet therefrom.
By arranging for the inlets in the inner and outer casings to communicate with said one of the chambers at respective points on generally opposite sides of the heat exchange means, the first fluid entering the outer casing through the inlet therein is prevented from impinging directly on to the heat transfer surfaces of the heat exchange means.
Where the first fluid enters the apparatus at high velocity, this prevents damage being caused to these heat transfer surfaces.
By arranging for the outlets in the inner and outer casings to communicate with said other of the chambers at respective points on generally opposite sides of the heat exchange means, any entrained material in the first fluid is given an opportunity to separate out before the first fluid leaves the apparatus via the outlet in the outer casing.
A very compact arrangement can be provided by disposing the inner casing eccentrically with respect to the outer casing. In this case, the chambers are arranged to reach a minimum width in the vicinity of the inlet and outlet respectively in the inner casing, such that the cross-sectional area of said one of the chambers decreases from the inlet in the outer casing to the inlet in the inner casing, and that of said other of the chambers increases from the outlet in the inner casing to the outlet in the outer casing. The flow area of the first fluid through said other of the chambers thus gradually increases in the direction of flow.
The interior of the inner casing may be divided into two mutually separated parts which communicate with each other at a point opposed to the inlet and outlet in the inner casing, so that the first fluid is constrained to flow across the heat exchange means twice during its passage from the inlet to the outlet in the inner casing. In this case, a baffle plate can be used to divide the interior of the inner casing into said two separated parts, and said parts can communicate with each other by means of a manifold which projects externally of the inner casing and which preferably reaches a maximum cross-sectional area substantially in the plane of the baffle plate. Where such a manifold is provided, the two casings are preferably eccentrically disposed and the manifold is positioned where the two casings reach their maximum separation.
The chambers defined between the inner and outer casings can each be generally annular so as to surround the heat exchange means and cause the first fluid in the chamber to flow around opposite sides ofthe heat exchange means.
An embodiment of the present invention will now be described, by way of example, with reference to the accompanying drawing, in which:- Figure 1 is an axial sectional view of apparatus for cooling compressed air by heat exchange with water. according to the present invention: Figure 2 is a view of one end of the cooling apparatus shown in Figure 1; Figure 3 is a section taken along the line Ill-Ill in Figure 1; and Figure 4 is a section taken along the line IV IV in Figure 1.
The cooling apparatus shown in the drawing comprises an outer tubular casing 10 and an inner tubular casing II which are each of generally circular cross-section and which define a generally annular chamber 12 there between Axial ends of the chamber 12 are sealingly closed off by respective end plates 13 which Serve to mount the inner casing II eccentrically within the outer casing 10. A support plate 14. which is disposed approxi mately mid-way between the end plates 13 and which serves to support the inner casing II within the outer casing 10. is sealingly attached to both the inner and outer casings and divides the annular chamber 12 into two smaller annular chambers 15 and 16 which are mutually axially separated.An inlet pipe or branch connection 17 is located on an upper part of the outer casing 10 and opens into the annular chamber 15, and an outlet pipe I is disposed on an upper part of the outer casing 10 at a point spaced from the inlet pipe 17 and communicates with the annular chamber 16. Drainage openings 19 (the purpose of which will be described later) are formed in lower portions of the outer casing 10 and open into the annular chambers 15 and 16 respectively.
Disposed within the inner casing 11 is heat exchange means in the form of a tube stack or bundle 20 (shown in Figure 1 only), which may be of any convenient form. In the illustrated embodiment, the tube stack comprises a plurality of parallel tubes 21 having a series of longitudinally spaced plate-like fins 22 thereon. The fins 22 may be of any suitable shape, but are preferably either circular with a segment thereof removed (i.e.
D-shaped) or circular with two diametrically opposed segments removed. Alternatively, each tube 21 may be individually finned, the fins being integrally formed or wound thereon. In a further alternative, the fins may be omitted altogether. Ends.of the tube stack 20 are sealingly received by respective circular apertures 23 in the end plates 13, so as to close off the ends of the inner casing 11. The tube stack 20 is also provided with a header or headers (not shown) to enable water to be passed through the tubes 21 in use.
The interior of the casing 11 is divided into two axially separated parts 24 and 25 by a baffle plate 26 which is positioned generally in the same plane as the support plate 14, the tubes 21 of the tube stack 20 passing through respective holes (not shown) in the baffle plate 26. An elongate inlet opening 27 is formed in a lower portion of the inner casing I I so as to communicate with the part 24 of the interior thereof, and opens onto the annular chamber 15 at a point diametrically opposed to the inlet pipe 17 where the clearance between the inner and outer casings is a minimum. Similarly, an elongate outlet opening 28 is provided in a lower portion of the inner casing 11 so as to communicate with the part 25 of the interior thereof, and opens onto the annular chamber 16 at a point diametrically opposed to the outlet pipe 18. If desired, a series of smaller openings can be used in place of each of the elongate openings 27 and 28.
The parts 24 and 25 of the interior of the inner casing 11 communicate with each other by means of a manifold 29 which projects from the inner casing 11 in the region of maximum separation between the inner and outer casings. The manifold 29 is composed of two part-frusto conical shell portions 30 and 31 fitted over an elongate opening 29a in the inner casing 11, and reaches a maximum cross-sectional area in the plane of the baffle plate 26, the support plate 14 being suitably shaped to accommodate the manifold 29.
The opening 29a, which extends as close as practicable to the end plates 13, can be replaced by a series of smaller openings if desired.
In use, compressed air to be cooled is passed into the cooling apparatus through the inlet pipe 17 and is split into two streams which flow around opposite sides of the annular chamber 15 respectively before converging and entering the inner casing 11 via the inlet opening 27. The compressed air then flows across that part of the tube stack 20 which is disposed in the part 24 of the interior of the inner casing 11, so that it is cooled by the water flowing through the tubes 21, and into the manifold 29. From the manifold 29, the compressed air flows across the tube stack 20 for a second time as it passes through the part 25 of the interior of the inner casing 11 and is further cooled by the water flowing through the tubes 21. The cooled air then leaves the inner casing 11 via the outlet opening 28, is split into two streams which flow around opposite sides of the annular chamber 16.These streams converge at the top of the chamber 16 for removal from the cooling apparatus through the outlet pipe 18.
As the compressed air is cooled within the apparatus entrained water vapour condenses out and flows into the lower portion of the outer casing 10, whereupon it can drain out of the outer casing through the drainage openings 19. In particular, the cooled air leaving the inner casing via the opening 28 impinges upon the internal wall of the outer casing 10 and its velocity is reduced as it flows thrugh the annular chamber 16, thereby allowing the condensate to fall into the lower portion of the outer casing 10 for removal through the respective drainage opening 19. If desired. additional means for catching the condensate (e.g. deflector plates or a porous material) may be provided in the annular chamber 16.The design of the drainage openings 19 and the separation between the inner and outer casings in the region of these openings prevents the openings from becomming blocked by dirt and debris. The cooling apparatus described above has the advantage that the compressed air introduced through the inlet pipe 17 must flow through the annular chamber 15 before reaching the tube stack 30. and does not therefore impinge directly onto the heat transfer surfaces of the tube stack 20. This prevents damage being caused to these surfaces by the initial high velocity of the compressed air.
In addition, the shapes of the chambers 15 and 16 causes the air to be directed to the inlet opening 27, to enter and leave the inner casing 11, and to be directed away from the outlet opening 28 in a comparatively uniform manner. The shaping of the manifold 29 contributes to this effect since, when the inlet and outlet pipes 17 and IS are positioned close to the end plates 13, there is a minimum of restriction directly below the pipes .17 and 18 to air entering and leaving the apparatus.
The manifold shape also contributes to a reduction in air pressure losses.
Furthermore, in assembling the cooling apparatus, it is possible to arrange for the outer casing 10 to be fitted last so that the internal joints on the inner casing 11 and its associated parts can be performed easily.
Moreover, the openings 27 and 28 can be made sufficiently large to permit inspection of the space between the outer and inner casings from the interior of the inner casing when the tube stack 20 has been removed.
The cooling apparatus described above is arranged with its main axis horizontal, with the inlet and outlet pipes 17 and 18 extending from the top of the outer casing 10. These pipes may, however, penetrate the annular chambers 15 and 16 respectively at any desired entry angle (provided that the point of penetration is disposed above the horizontal axis of the apparatus) and may be positioned at any desired point between the end plates 13. In addition, the apparatus can be arranged with its main axis disposed vertically, with the drainage openings 19 being suitably repositioned (e.g. close to the support plate 14 or the end plates 13).
WHAT WE CLAIM IS: 1. Apparatus for cooling a first fluid by heat-exchange with a second fluid, comprising inner and outer tubular casings defining there between two chambers which are mutually separated axially of the casings; heat exchange means disposed in the inner casing, through which the second fluid is passed in use, each of said chambers extending at least a part of the way around the heat exchange means externally of the inner casing; an inlet in the outer casing and an inlet in the inner casing communicating with one of said chambers at respective points which are generally on opposite sides of the heat exchange means; and an outlet in the outer casing and an outlet in the inner casing communicating with the other of said chambers at respective points which are also generally on opposite sides of the heat exchange means; the inlet and outlet in the inner casing being so disposed that first fluid entering the inner casing through said inlet thereto is constrained to flow across the heat exchange means before leaving the inner casing through said outlet therefrom.
2. Cooling apparatus as claimed in Claim l. wherein the inner casing is disposed eccentrically with respect to the outer casing, said chambers reaching a minimum in width in the vicinity of the inlet and outlet respectively in the inner casing.
3. Cooling apparatus as claimed in Claim 1 or 2, wherein the interior of the inner
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (9)

**WARNING** start of CLMS field may overlap end of DESC **. replaced by a series of smaller openings if desired. In use, compressed air to be cooled is passed into the cooling apparatus through the inlet pipe 17 and is split into two streams which flow around opposite sides of the annular chamber 15 respectively before converging and entering the inner casing 11 via the inlet opening 27. The compressed air then flows across that part of the tube stack 20 which is disposed in the part 24 of the interior of the inner casing 11, so that it is cooled by the water flowing through the tubes 21, and into the manifold 29. From the manifold 29, the compressed air flows across the tube stack 20 for a second time as it passes through the part 25 of the interior of the inner casing 11 and is further cooled by the water flowing through the tubes 21. The cooled air then leaves the inner casing 11 via the outlet opening 28, is split into two streams which flow around opposite sides of the annular chamber 16.These streams converge at the top of the chamber 16 for removal from the cooling apparatus through the outlet pipe 18. As the compressed air is cooled within the apparatus entrained water vapour condenses out and flows into the lower portion of the outer casing 10, whereupon it can drain out of the outer casing through the drainage openings 19. In particular, the cooled air leaving the inner casing via the opening 28 impinges upon the internal wall of the outer casing 10 and its velocity is reduced as it flows thrugh the annular chamber 16, thereby allowing the condensate to fall into the lower portion of the outer casing 10 for removal through the respective drainage opening 19. If desired. additional means for catching the condensate (e.g. deflector plates or a porous material) may be provided in the annular chamber 16.The design of the drainage openings 19 and the separation between the inner and outer casings in the region of these openings prevents the openings from becomming blocked by dirt and debris. The cooling apparatus described above has the advantage that the compressed air introduced through the inlet pipe 17 must flow through the annular chamber 15 before reaching the tube stack 30. and does not therefore impinge directly onto the heat transfer surfaces of the tube stack 20. This prevents damage being caused to these surfaces by the initial high velocity of the compressed air. In addition, the shapes of the chambers 15 and 16 causes the air to be directed to the inlet opening 27, to enter and leave the inner casing 11, and to be directed away from the outlet opening 28 in a comparatively uniform manner. The shaping of the manifold 29 contributes to this effect since, when the inlet and outlet pipes 17 and IS are positioned close to the end plates 13, there is a minimum of restriction directly below the pipes .17 and 18 to air entering and leaving the apparatus. The manifold shape also contributes to a reduction in air pressure losses. Furthermore, in assembling the cooling apparatus, it is possible to arrange for the outer casing 10 to be fitted last so that the internal joints on the inner casing 11 and its associated parts can be performed easily. Moreover, the openings 27 and 28 can be made sufficiently large to permit inspection of the space between the outer and inner casings from the interior of the inner casing when the tube stack 20 has been removed. The cooling apparatus described above is arranged with its main axis horizontal, with the inlet and outlet pipes 17 and 18 extending from the top of the outer casing 10. These pipes may, however, penetrate the annular chambers 15 and 16 respectively at any desired entry angle (provided that the point of penetration is disposed above the horizontal axis of the apparatus) and may be positioned at any desired point between the end plates 13. In addition, the apparatus can be arranged with its main axis disposed vertically, with the drainage openings 19 being suitably repositioned (e.g. close to the support plate 14 or the end plates 13). WHAT WE CLAIM IS:
1. Apparatus for cooling a first fluid by heat-exchange with a second fluid, comprising inner and outer tubular casings defining there between two chambers which are mutually separated axially of the casings; heat exchange means disposed in the inner casing, through which the second fluid is passed in use, each of said chambers extending at least a part of the way around the heat exchange means externally of the inner casing; an inlet in the outer casing and an inlet in the inner casing communicating with one of said chambers at respective points which are generally on opposite sides of the heat exchange means; and an outlet in the outer casing and an outlet in the inner casing communicating with the other of said chambers at respective points which are also generally on opposite sides of the heat exchange means; the inlet and outlet in the inner casing being so disposed that first fluid entering the inner casing through said inlet thereto is constrained to flow across the heat exchange means before leaving the inner casing through said outlet therefrom.
2. Cooling apparatus as claimed in Claim l. wherein the inner casing is disposed eccentrically with respect to the outer casing, said chambers reaching a minimum in width in the vicinity of the inlet and outlet respectively in the inner casing.
3. Cooling apparatus as claimed in Claim 1 or 2, wherein the interior of the inner
casing is divided into two mutually separated parts which communicate with each other at a point opposed to the inlet and outlet in the inner casing, so that the first fluid is constrained to flow across the heat exchange means twice during its passage from the inlet to the outlet in the inner casing.
4. Cooling apparatus as claimed in Claim 3, wherein a baffle plate divides the interior of the inner casing into said two separated parts, and said parts communicate with each other by means of a manifold which projects externally of the inner casing.
5. Cooling apparatus as claimed in Claim 4, wherein the manifold reaches a maximum cross-sectional area substantially in the plane of the baffle plate.
6. Cooling apparatus as claimed in Claim 4 or 5, when appended to Claim 2, wherein the manifold projects from the inner casing in the region of maximum separation between the inner and outer casings.
7. Cooling apparatus as claimed in any preceding Claim, wherein the chambers defined between the inner and outer casings are each generally annular and completely surround the heat exchange means,
8. Cooling apparatus as claimed in any preceding Claim, wherein drainage openings are provided in lower portions of the chambers defined between the inner and outer casings.
9. Apparatus for cooling a first fluid by heat exchange with a second fluid, substantially as hereinbefore described with reference to the accompanying drawings.
GB414478A 1978-02-02 1978-02-02 Fluid-cooling heat-exchange apparatus Expired GB1596001A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB414478A GB1596001A (en) 1978-02-02 1978-02-02 Fluid-cooling heat-exchange apparatus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB414478A GB1596001A (en) 1978-02-02 1978-02-02 Fluid-cooling heat-exchange apparatus

Publications (1)

Publication Number Publication Date
GB1596001A true GB1596001A (en) 1981-08-19

Family

ID=9771587

Family Applications (1)

Application Number Title Priority Date Filing Date
GB414478A Expired GB1596001A (en) 1978-02-02 1978-02-02 Fluid-cooling heat-exchange apparatus

Country Status (1)

Country Link
GB (1) GB1596001A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2820987A1 (en) * 2001-02-16 2002-08-23 Jean Luc Maire Liquid/gas separator for cooling circuit, e.g. heat pump, comprises longitudinal tube passing through cylindrical separator body carrying coolant from exchanger to compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2820987A1 (en) * 2001-02-16 2002-08-23 Jean Luc Maire Liquid/gas separator for cooling circuit, e.g. heat pump, comprises longitudinal tube passing through cylindrical separator body carrying coolant from exchanger to compressor

Similar Documents

Publication Publication Date Title
US4016835A (en) Moisture separator-reheater
US3834133A (en) Direct contact condenser having an air removal system
US4302227A (en) Baffled moisture separator
US4253315A (en) Refrigerated air dryer
EP3586938B1 (en) Helical water collector
KR950006505B1 (en) Separator with winged fins for the separation of liquid particles
JP3735405B2 (en) Condenser
JPS6119347Y2 (en)
GB2148480A (en) Shell and tube heat exchanger
US4254561A (en) Drying cylinder for a paper-making machine
US4252186A (en) Condenser with improved heat transfer
FI91601C (en) Selective condensing unit
GB1596001A (en) Fluid-cooling heat-exchange apparatus
US6269867B1 (en) Condenser and power plant
EP0067044B1 (en) Heat exchanger
EP0068529A1 (en) Heat exchanger
JPH0619929Y2 (en) Steam generator
GB2155821A (en) Gas cleaning apparatus
RU2159903C1 (en) Gas dehumidifier
JPS631515B2 (en)
JPS6157997B2 (en)
SU892176A1 (en) Heat exchanger
SU934766A2 (en) Collecting manifold of heat exchanger
DD291825A5 (en) SEPARATE TRANSFER DEVICE WITH SEPARATING AND BUFFER DEVICE IN A COMMON APPARATUS HOUSE FOR GAS COMPRESSION FACILITIES
JPS58187788A (en) Condenser

Legal Events

Date Code Title Description
PS Patent sealed
PCNP Patent ceased through non-payment of renewal fee