EP0884549A2 - Statischer Mixer /Wärmetauscher - Google Patents

Statischer Mixer /Wärmetauscher Download PDF

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Publication number
EP0884549A2
EP0884549A2 EP98304556A EP98304556A EP0884549A2 EP 0884549 A2 EP0884549 A2 EP 0884549A2 EP 98304556 A EP98304556 A EP 98304556A EP 98304556 A EP98304556 A EP 98304556A EP 0884549 A2 EP0884549 A2 EP 0884549A2
Authority
EP
European Patent Office
Prior art keywords
fluid
tubes
conduit
core pipe
tube
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.)
Withdrawn
Application number
EP98304556A
Other languages
English (en)
French (fr)
Other versions
EP0884549A3 (de
Inventor
Leonard Tony King
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.)
Komax Systems Inc
Original Assignee
Komax Systems Inc
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 Komax Systems Inc filed Critical Komax Systems Inc
Publication of EP0884549A2 publication Critical patent/EP0884549A2/de
Publication of EP0884549A3 publication Critical patent/EP0884549A3/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F28D7/02—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 helically coiled
    • F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0052—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for mixers

Definitions

  • the present invention is directed to a device for effecting heat transfer from a first fluid medium to a second fluid medium and for enhancing mixing and uniform distribution of the second fluid medium within the confines of a conduit.
  • Mixers can contain active elements such as paddles and rotors although it is quite common to provide static elements whereby the turbulent flow of the fluids in and around these elements enhance fluid mixing without the need for moving parts which inherently add to the cost of the mixing operation both in terms of power requirements and labor intensive maintenance procedures.
  • Many static mixers rely on a mixing element configurations which presents a set of interstices to the product flow. Elements of this type divide a fluid stream along the mixing path and recombine locally created substreams into a more homogeneous mixture.
  • FIG. 1 showing a conventional tube and shell heat exchanger 10.
  • product enters orifice 13 at the upstream end of the heat exchanger and exits at orifice 14.
  • Heat transfer medium enters the heat exchanger at orifice 16 and travels in a counterflow direction within the heat exchanger to exit at orifice 15.
  • Devices such as metal strip 17 are frequently installed in the tubes or pipes of such conventional tube and shell heat exchangers in order to enhance the internal film coefficient at its inside tube wall. Such devices can be twisted strips of metal or static or motionless mixers.
  • the major resistance to heat transfer is due to what is called the film coefficient at the inside wall of the tubes where the product velocity is low.
  • the cooling or heating medium flows over the outside of the tubes in area 12. It has been determined that the improvement in heat transfer obtained by tube inserts for laminer flow applications is usually in the range of 2 to 5 times. However, the use of such devices significantly increases the pressure drop experienced and thus one using such expedients must pay a price.
  • FIG. 2 shows yet another conventional device employed as both a heat exchanger and static mixer.
  • Device 20 relies upon a different design concept than the conventional tube and shell heat exchanger of FIG. 1 in that the product of interest is introduced within conduit 23 at upstream end 21 while the cooling/heating medium is contained within tubes 24.
  • the linear tube structure shown as element 11 of FIG. 1 is replaced by tube structure 24 in the form of a static mixer built of tubing instead of sheet metal.
  • the device shown in FIG. 2 does not provide a good utilization of the exchanger shell available volume, less, in fact, than the conventional tube and shell heat exchanger.
  • FIG. 1 is a prior art depiction, in cutaway plan view, of a conventional tube and shell heat exchanger.
  • FIG. 2 is a perspective cutaway view of a modified tube and shell heat exchanger which represents the current state of the art.
  • FIGs. 3A to 3C depict, in plan view, the step-by-step construction of the presently configured invention.
  • FIG. 4 is a cutaway plan view depicting employment of the structure shown in FIG. 3 within a conduit for accomplishing the goals of the present invention.
  • FIG. 5 is a cutaway plan view depicting in more detail than as shown in FIG. 4 the structure of the present invention as its preferred embodiment.
  • FIG. 6 is a further cutaway plan view of yet another embodiment of the present invention.
  • the present invention is directed to a device for effecting heat transfer from a first fluid medium to a second fluid medium and for enhancing mixing and uniform distribution of the second fluid medium within the confines of a conduit.
  • the device comprises a conduit having a cross section and longitudinal axis. An inlet for introduction of the first fluid is provided within the conduit and an outlet for passing the first fluid from the conduit is further provided.
  • a core pipe is located at the approximate longitudinal axis of the conduit, the conduit having an upstream opening for receiving the second fluid and a downstream opening for passing the second fluid from it.
  • a series of tubes are provided. Each of the tubes is in fluid communication with the first fluid inlet and outlet, the series of tubes comprising at least two tubes, each of which are helically wound around the core pipe and each of which are configured to carry the first fluid medium.
  • the present invention is directed to a device for effecting heat transfer from a first fluid medium to a second fluid medium and for enhancing mixing and uniform distribution of the second fluid medium within the confines of a conduit.
  • Device 40 is shown as consisting of conduit 41 having a cross section and longitudinal axis 42.
  • the conduit is provided with an inlet 43 for introduction of the first fluid within conduit 41 and an outlet 44 for passing the first fluid from the conduit.
  • the conduit further is provided with inlet 45 for the introduction of the fluid product as well as downstream exist 46 for passing the product fluid from conduit 41.
  • the device is provided with core pipe 47 which is depicted as element 31 in FIG. 3. As shown, the core pipe is located approximately at longitudinal axis 42.
  • the device is further provided with a series of tubes which, for the sake of simplicity, are not shown within FIG. 4 but which are contained in area 48. As will be discussed in more detail, these tubes are helically wound around core pipe 47 and each are configured to carry the first fluid medium.
  • the heating or cooling medium enters at 43 at the upper lefthand flange and flows via an outer jacket 49 to the output end of the conduit where it enters core tube 47.
  • the medium flows in core pipe 47 through the center of the conduit and to the end of the winding assembly where the product to be heated or cooled enters at 45 to flow over the outer surface of the tube assembly contained within area 48.
  • Appropriate tube connections take the first fluid from the core tube and distribute it to the winding assembly. This first fluid flows through an inlet to the pipe and on to the tube assembly where another set of tube connections at the downstream end of the winding assembly join the pipe providing for first fluid exit at 44.
  • the downstream end of core pipe 47 is plugged and rests against retainer cross 50 welded or otherwise connected to the conduit housing.
  • Retainer cross 50 prevents the tube assembly from extrusion out of the housing by forces produced by pressure drop across the tube assembly.
  • flanges are provided at the extremities of the conduit so that the tube assembly can be disconnected to allow the entire structure to be removed as required for inspection, cleaning and repair.
  • FIG. 3A shows a single tube 32 wound in a helical fashion about core pipe 31. Additional windings are shown in FIG. 3B wherein tubes 32, 33 and 34 are shown wound about core tube 31 each bearing the same sign.
  • FIG. 3C depicts core tube 31 having tube windings 32, 33 and 34 of one sign and tubes 35, 36, 37 and 38 also helically wound about core tube 31 of an opposite sign.
  • FIG. 3C shows the preferred manner in which the various series of tubes are wound about a core pipe.
  • each of the tubes being helically wound about the core tube are wound at equal and uniform angles to the longitudinal axis of the conduit/pipe.
  • each of the tubes is composed of a series of helical turns, each turn being approximately 45° to the longitudinal axis.
  • interstices are created between adjacent tubes of approximately 90°.
  • FIG 5A depicts the present invention in somewhat more detail than that shown in FIG. 4.
  • Structure 50 is comprised of conduit 53 having flanged end connectors 58.
  • a first fluid medium is introduced at port 51 and travels countercurrent to the flow of the second fluid entering conduit 53 at 56 and exiting the conduit at end 57.
  • the first fluid exits device 50 at 52, thus completing its countercurrent path.
  • the first fluid which acts as a heat transfer medium, is introduced to core pipe 55 whereupon the first fluid branches out into a series of helically wound tubes 54, each of which being ideally wound about core pipe 55 in a series of helical turns each of which being approximately 45° to longitudinal axis 59 so that adjacent tubes create consistent 90° interstices as an enhancement to the fluid mixing of the second fluid medium passing within conduit 53.
  • the helical turns of the windings are selected to be uniformly 45° to the longitudinal axis of core pipe the number of interstices per unit volume remains constant. This will provide maximum utilization of the volume in terms of mixing divisions for a given pressure drop.
  • first fluid acting as a heat transfer medium is introduced through inlet 64 and exits from the system at outlet 65.
  • the first fluid proceeds to fill annular space 62 contiguous to the inner wall of conduit 61.
  • baffles 63 are provided in annular space 62.
  • the present embodiment differs from those previously described in that first heat transfer fluid introduced via inlet 64 proceeds only through helically wound tube 68 and not core pipe 70.
  • core pipe 70 acts only as a mandrel upon which helically wound tubing 68 is applied.
  • all helical windings are configured to intersect each other at an angle of 90° (45° to the longitudinal axis of the core pipe). To accomplish this, the number of tubing starts must be increased as layers are added.
  • the present invention provides a static mixing system created by the helical windings of the tubes which will typically provide a heat transfer factor of two to five times for a net total heat transfer improvement of three to ten times that of a standard shell and tube exchanger.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP98304556A 1997-06-10 1998-06-09 Statischer Mixer /Wärmetauscher Withdrawn EP0884549A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US87231897A 1997-06-10 1997-06-10
US872318 1997-06-10

Publications (2)

Publication Number Publication Date
EP0884549A2 true EP0884549A2 (de) 1998-12-16
EP0884549A3 EP0884549A3 (de) 1999-05-19

Family

ID=25359327

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98304556A Withdrawn EP0884549A3 (de) 1997-06-10 1998-06-09 Statischer Mixer /Wärmetauscher

Country Status (1)

Country Link
EP (1) EP0884549A3 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2629039A1 (de) 2012-02-17 2013-08-21 Armacell Enterprise GmbH Dehnströmungswärmetauscher für Polymerschmelzen
CN103542742A (zh) * 2013-11-02 2014-01-29 福州大学 可抽芯换热器
CN115218557A (zh) * 2022-07-07 2022-10-21 西安东方能源工程有限公司 一种均压螺旋管壳式降膜蒸发器

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB416096A (en) * 1933-03-13 1934-09-13 Air Liquide Improvements in coil-tube heat-exchange apparatus for fluids
US3335790A (en) * 1965-04-28 1967-08-15 Technoimpex Magyar Gepipari Ku Heat exchanger with crossing helicoidal tubes
FR1490717A (fr) * 1966-06-23 1967-08-04 Fives Penhoet échangeur de chaleur, en particulier pour centrales thermiques et centrales nucléaires
SE381509B (sv) * 1975-02-03 1975-12-08 Svenska Maskinverken Ab Vermevexlarbatteri
DE3136589A1 (de) * 1981-09-15 1983-03-31 Bayer Ag Temperierbarer statischer mischer und reaktor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2629039A1 (de) 2012-02-17 2013-08-21 Armacell Enterprise GmbH Dehnströmungswärmetauscher für Polymerschmelzen
CN103542742A (zh) * 2013-11-02 2014-01-29 福州大学 可抽芯换热器
CN103542742B (zh) * 2013-11-02 2015-09-09 福州大学 可抽芯换热器
CN115218557A (zh) * 2022-07-07 2022-10-21 西安东方能源工程有限公司 一种均压螺旋管壳式降膜蒸发器

Also Published As

Publication number Publication date
EP0884549A3 (de) 1999-05-19

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