EP0328044A1 - Dispositif de positionnement d'une pièce à usiner - Google Patents

Dispositif de positionnement d'une pièce à usiner Download PDF

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Publication number
EP0328044A1
EP0328044A1 EP89102075A EP89102075A EP0328044A1 EP 0328044 A1 EP0328044 A1 EP 0328044A1 EP 89102075 A EP89102075 A EP 89102075A EP 89102075 A EP89102075 A EP 89102075A EP 0328044 A1 EP0328044 A1 EP 0328044A1
Authority
EP
European Patent Office
Prior art keywords
tubes
heat exchanger
header
tube
collecting
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.)
Granted
Application number
EP89102075A
Other languages
German (de)
English (en)
Other versions
EP0328044B1 (fr
Inventor
Hubert Dr. Ing. Grieb
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.)
MTU Aero Engines AG
Original Assignee
MTU Motoren und Turbinen Union Muenchen GmbH
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 MTU Motoren und Turbinen Union Muenchen GmbH filed Critical MTU Motoren und Turbinen Union Muenchen GmbH
Publication of EP0328044A1 publication Critical patent/EP0328044A1/fr
Application granted granted Critical
Publication of EP0328044B1 publication Critical patent/EP0328044B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28D7/06—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 having a single U-bend
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/0243—Header boxes having a circular cross-section
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49389—Header or manifold making

Definitions

  • the invention relates to a heat exchanger with two collecting tubes arranged in parallel, which are connected to one another via a plurality of U-shaped profile tubes.
  • Such a heat exchanger as it has become known for example from DE-PS 36 35 549 and is particularly suitable for high gas temperatures and high thermal, cyclical loads, has so far been produced in that the individual components, i. H. the profile tubes and header sections are firmly connected to one another by means of soldering or welding.
  • the collecting tubes can consist of two half shells joined together or of individual shorter tube sections which are arranged one behind the other and are soldered together.
  • a disadvantage of the designs described is that, in the event of leaks, which can occur either as a result of incorrect manufacture or as a result of material fatigue, an expensive repair or even an exchange of the entire heat exchanger is often required.
  • a shock load transversely to the header tube axis unsteady inertial forces can also result in high voltage peaks at the connection points between the header tube and the profile tubes, which entails the risk of cracks and leaks, since the header tubes accommodate a large number of profile tubes.
  • As a dangerous consequence of cracks there is a local weakening of the stiffness and strength of the header pipes, which triggers a progressive increase in the local stress peaks and thus a progressive damage until breakage.
  • the object of the invention is to improve a heat exchanger of the generic type in such a way that the formation of cracks is prevented by lower loads. Furthermore, a progressive higher load should be avoided in the event of cracks. In the event of mechanical shock loading, less deformation of the header pipes and thus a lower stress level at the endangered points should be achieved.
  • the object is achieved in that the manifolds consist of a number of manifold sections which are arranged axially one behind the other in a sealing and releasable manner and are held together by a draw tube which is supported on the manifold sections and is concentrically spaced within the manifolds.
  • the manifolds By designing the manifolds as a number of manifold sections arranged one behind the other and releasably braced together, it is possible in the event of a leak in the heat exchanger to disassemble it and to replace the defective element. This enables considerably more economical manufacture and maintenance of the heat exchanger. Furthermore, the manifolds are advantageously given increased flexural rigidity by the draw tubes, as a result of which the likelihood of cracking under impact loads is reduced. The inspection of individual heat exchanger elements is also much easier than the inspection of a complete heat exchanger.
  • the draw tubes arranged concentrically within the header tubes enable the heat exchanger to be stiffened, the impact and bending loads acting on the header tubes being absorbed by the stiffening means, and the header tube wall only having to absorb the compressive and inertial forces of the profile tubes. This significantly reduces the risk of cracking.
  • the draw tubes are provided with a multiplicity of openings distributed over the surface, so that the air flowing in the header tubes can enter the profile tubes unimpeded and from the profile tubes into the other header tube.
  • the wall thickness is dimensioned so that the required rigidity or strength is given in every direction.
  • the header pipes are under increased axial compressive stress when the heat exchanger is in operation, which further reduces the risk of cracks or leaks.
  • the draw tubes have a lower coefficient of thermal expansion than the header tubes. This effect is also achieved in that the header tubes heat up more than the inner draft tubes.
  • the tensioning by means of the draw tubes is to be set so that, during stationary operation, sufficiently high compressive forces act on the end faces of the header sections and, at the same time, the tensile loads on the draw tubes remain in the range of the elastic expansion.
  • FIG. 1 shows a heat exchanger 1, the manifolds 2 and 3 of which consist of a plurality of manifold sections 5, 6 arranged one behind the other.
  • the manifolds 2 and 3 are connected to one another via a plurality of U-shaped profile tubes 21.
  • the mode of action of the heat exchanger is as follows: A cool gas flow axially enters the manifold 2. The gas flow divides and flows through the large number of U-shaped profile tubes 21 embedded in the collecting tube 2 to the collecting tube 3. The gas heats up due to the hot gas flowing in the direction indicated by 36 in cross-countercurrent flow. The heated inner gas flow combines again in the collecting pipe 3 and flows axially through the collecting pipe 3.
  • Fig. 2 shows a section of the heat exchanger 1 in cross section.
  • the collecting pipe 2, which consists of individual collecting pipe sections 5, 6, is provided at one end with a collecting pipe end section 12, through which the internally directed gas stream is supplied.
  • a closed collecting pipe end section 11 is provided at the opposite end of the collecting pipe 2.
  • a large number of profile tubes 21 are attached in the wall of the collecting tube 2 by means of soldering or welding. Between the individual header sections 5, 6 with the connected profile tubes 21, intermediate plates 37 are provided.
  • a pull tube 15 Arranged in the interior of the collecting tube 2 is a pull tube 15, which is in fitting connection with the collecting tube 2 at the abutment points 4 of two collecting tube sections 5, 6 lying axially one behind the other.
  • the draw tube 15 is connected to the manifold end sections 11, 12 at points 7, 8, a defined bracing of the draw tube 15 being set by means of screw connections (not shown).
  • the draw tube 15 In the sections of the draw tube 15, which lie opposite the profile tubes 21, the draw tube 15 is provided with a number of openings 18, which can be distributed regularly over the circumference. This enables the gas flow from the inside of the draw tube 15 to the profile tubes 21 or in the header tube 3 in reverse.
  • At the header end sections 11 and 12 are also attached end plates 38 which are arranged parallel to the intermediate plates 27.
  • the arrangement of the collecting pipe 2 and the drawing pipe 15 shown in FIG. 2 and described above is implemented analogously in the collecting pipe 3 and the drawing pipe 16.
  • the intermediate plates 37 and end plates 38 are designed so that the header sections 5 and 6 receive narrow strips 39 without profile tubes 21 on their faces, which are necessary for reasons of strength.
  • the intermediate plates 37 arranged between the header pipe sections 5, 6 and the end plates 38 are connected to one another via the edge plates 40 on the arc sides 41 of the profile tubes, the edge plates 40 simultaneously serving to guide the gas. Furthermore, the intermediate plates 37 and end plates 38 together with the edge plates 40 prevent the deflection or deformation of the profiled tubes in the event of impacts in the collecting tube axial direction, in that the deflection of the arc sides 41 in the overall direction of the collecting tube is avoided.
  • a lug 42 is attached to one of the boundary plates 40, which is held in a certain position by a counterpart 44 fastened to the housing 43 surrounding the heat exchanger 1.
  • the part of the heat exchanger 1, d. H. the sum of all profile tubes 21, intermediate tube plates 38 and end plates 39 is recorded.
  • the intermediate plates 37 and end plates 38 are divided into two in the section tube axial direction in order to account for the different thermal expansion of the top and bottom of the heat exchanger 1 and thus of the intermediate and end plates 37, 38 due to the temperature gradient in Compensate flow direction 36.
  • the edge plates 40 are also made in two parts, since they are screwed to the intermediate and end plates 37, 38. The two parts of the edge plates 40 are connected by links 45 to ensure that the gap between the two parts remains the same under all thermal conditions in view of the required seal.
  • the concentrically arranged draw tubes 15, 16 are located inside the header tubes 2, 3. These have openings 18 distributed over the circumference.
  • a shielding plate 19 is attached to the hot gas inlet-side collecting tube 3, which ensures that the hot gas flow does not act directly on the collecting tube 3 and the connections between the collecting tube 3 and profile tubes 21 on the gas inlet side. As a result, the temperature gradients on the circumference of the collecting tube 3 are considerably reduced.
  • the manifold end sections 11, 12 also serve to center the manifolds 2, 3 and are designed so that the heat exchanger 1 can expand freely in the axial direction of the manifold.
  • the attachment of the draw tube 15 to the end sections 11 and 12 is shown enlarged.
  • the draw tube 15 is screwed to the end sections 11, 12 by means of screws 23, 24, a gap 23 being provided between the draw tube 15 and the end section 11 in order to apply the tensile load to the draw tube 15.
  • This gap 23 can advantageously be almost or completely eliminated by tightening the screw 22, as a result of which a defined prestressing of the draw tube 15 can be set.

Landscapes

  • 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)
EP89102075A 1988-02-10 1989-02-07 Dispositif de positionnement d'une pièce à usiner Expired - Lifetime EP0328044B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3803947 1988-02-10
DE3803947A DE3803947A1 (de) 1988-02-10 1988-02-10 Waermetauscher

Publications (2)

Publication Number Publication Date
EP0328044A1 true EP0328044A1 (fr) 1989-08-16
EP0328044B1 EP0328044B1 (fr) 1991-08-28

Family

ID=6347008

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89102075A Expired - Lifetime EP0328044B1 (fr) 1988-02-10 1989-02-07 Dispositif de positionnement d'une pièce à usiner

Country Status (7)

Country Link
US (1) US4940084A (fr)
EP (1) EP0328044B1 (fr)
JP (1) JP2678046B2 (fr)
BR (1) BR8900566A (fr)
CA (1) CA1305959C (fr)
DE (1) DE3803947A1 (fr)
ES (1) ES2025342B3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2677404A1 (fr) * 1991-06-07 1992-12-11 Mtu Muenchen Gmbh Dispositif pour l'assemblage d'un moteur a turbine a gaz avec un echangeur-recuperateur de chaleur.

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3911257C2 (de) * 1989-04-07 1994-05-26 Mtu Muenchen Gmbh Wärmetauscher
US5177865A (en) * 1989-05-05 1993-01-12 Mtu Motoren-Und Turbinen-Union Method for making heat exchanger having at least two collecting pipes
DE3914773C2 (de) * 1989-05-05 1994-03-03 Mtu Muenchen Gmbh Wärmetauscher mit mindestens zwei Sammelrohren
US5623987A (en) * 1992-08-04 1997-04-29 Ergenics, Inc. Modular manifold gas delivery system
DE10236380A1 (de) * 2002-08-08 2004-03-04 Mtu Aero Engines Gmbh Rekuperativ-Abgaswärmetauscher für ein Gasturbinentriebwerk
US6786202B2 (en) * 2002-09-24 2004-09-07 Caterpillar Inc Hydraulic pump circuit
DE102006021436A1 (de) * 2006-05-09 2007-11-15 Mtu Aero Engines Gmbh Gasturbinentriebwerk
JP5651991B2 (ja) 2010-05-10 2015-01-14 富士通株式会社 ラジエータ及びそれを備えた電子機器
US11092384B2 (en) * 2016-01-14 2021-08-17 Hamilton Sundstrand Corporation Thermal stress relief for heat sinks

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB277656A (en) * 1926-09-17 1928-05-10 Jules Basin Improvements in radiators for heating buildings
FR669324A (fr) * 1929-02-07 1929-11-14 Radiateur de chauffage en tôle
US3689972A (en) * 1970-11-19 1972-09-12 Modine Mfg Co Method of fabricating a heat exchanger
GB2078361A (en) * 1980-06-24 1982-01-06 Delanair Ltd Heat exchangers and heat exchanger headers

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE214188C (fr) *
US916640A (en) * 1908-03-23 1909-03-30 Robert Warg Steam-radiator.
GB134277A (en) * 1918-10-24 1919-10-24 John Melville James Improvements in or relating to Radiators for Cooling Fluids.
DE730039C (de) * 1935-12-11 1943-01-06 Getefo Ges Fuer Tech Fortschri Kuehler fuer Luft- und Kraftfahrzeuge
FR859510A (fr) * 1939-05-22 1940-12-20 Chausson Usines Sa Radiateur perfectionné
DE1928146A1 (de) * 1968-06-06 1969-12-11 Delaney Gallay Ltd Waermeaustauscher
US3605882A (en) * 1968-07-02 1971-09-20 Ass Eng Ltd Heat exchangers
DE3543893A1 (de) * 1985-12-12 1987-06-25 Mtu Muenchen Gmbh Waermetauscher
DE3635549C1 (de) * 1986-10-20 1988-03-03 Mtu Muenchen Gmbh Waermetauscher

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB277656A (en) * 1926-09-17 1928-05-10 Jules Basin Improvements in radiators for heating buildings
FR669324A (fr) * 1929-02-07 1929-11-14 Radiateur de chauffage en tôle
US3689972A (en) * 1970-11-19 1972-09-12 Modine Mfg Co Method of fabricating a heat exchanger
GB2078361A (en) * 1980-06-24 1982-01-06 Delanair Ltd Heat exchangers and heat exchanger headers

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 10, Nr. 189 (M-494)[2245], 3. Juli 1986; & JP-A-61 31 892 (SHOWA ALUM CORP.) 14-02-1986 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2677404A1 (fr) * 1991-06-07 1992-12-11 Mtu Muenchen Gmbh Dispositif pour l'assemblage d'un moteur a turbine a gaz avec un echangeur-recuperateur de chaleur.

Also Published As

Publication number Publication date
JP2678046B2 (ja) 1997-11-17
ES2025342B3 (es) 1992-03-16
DE3803947C2 (fr) 1990-03-01
US4940084A (en) 1990-07-10
CA1305959C (fr) 1992-08-04
DE3803947A1 (de) 1989-08-24
EP0328044B1 (fr) 1991-08-28
BR8900566A (pt) 1989-10-10
JPH01318891A (ja) 1989-12-25

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