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WO1993004270A1 - Accouplement orientable creux perfectionne - Google Patents

Accouplement orientable creux perfectionne Download PDF

Info

Publication number
WO1993004270A1
WO1993004270A1 PCT/GB1992/001549 GB9201549W WO9304270A1 WO 1993004270 A1 WO1993004270 A1 WO 1993004270A1 GB 9201549 W GB9201549 W GB 9201549W WO 9304270 A1 WO9304270 A1 WO 9304270A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
pipe section
bulbous end
bulbous
pipe
Prior art date
Application number
PCT/GB1992/001549
Other languages
English (en)
Inventor
Fred Parker Birch
Original Assignee
Fred Parker Birch
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 Fred Parker Birch filed Critical Fred Parker Birch
Publication of WO1993004270A1 publication Critical patent/WO1993004270A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly
    • F01N13/1805—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body
    • F01N13/1811—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body with means permitting relative movement, e.g. compensation of thermal expansion or vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L27/00—Adjustable joints; Joints allowing movement
    • F16L27/02—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction
    • F16L27/04—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction with partly-spherical engaging surfaces

Definitions

  • This invention relates to an improved hollow pivotable coupling, and in particular to an improved hollow pivotable coupling for use in an engine exhaust system.
  • a hollow pivotable coupling which includes a first pip section, a first pipe section bulbous end having a firs part-spherical external surface, a second pipe section, a secon pipe section bulbous end having a second part-spherical interna surface, said first external surface being sized as a sliding fi within the secong internal surface, resilient spring means havin first and second ends, the resilient means being located to urge the pipe sections apart.
  • the spring means is however tightl located about the first pipe section, and so its second en cannot move together with the second pipe section bulbous end. Furthermore, the spring is heated throughout its length by conduction from the first pipe section i.e. at each spring coil.
  • the spring has at least its intermediate coils spaced from the pipe section.
  • my earlier proposal of PCT/GB90/00875 teaches an annular pressure ring slidably engagable with the second bulbous end external surface 24.
  • a first possible disadvantage is that the bulbous end of th second pipe section could wear "doubly" i.e. both at its inne surface from the sliding engagement with the external surface of the first pipe section, and at its outer surface from the sliding engagement with the annular pressure ring.
  • the bulbous end of the second pipe section could therefore wear more rapidly than the bulbous end of the first pipe section.
  • one spring-end usually the "downstream" end of the resilient means e.g. a coil spring, is located relative to the second pipe section bulbous end.
  • a second possible disadvantage is that the spring was not mounted to provide both a co-acting force in the tension direction and a constraining return force urging the ball and socket towards its optimal "at rest" or normal position. To provide such dual forces was thought to require an extra spring, with increased complexity and cost. I now propose a dual-acting spring, having a rate equivalent to that of those springs combined.
  • a hollow pivotable coupling which includes a first pipe section, a first pipe section bulbous end having a first part-spherical external surface, a second pipe section, a second pipe section bulbous end having a second part-spherical internal surface, the said first external surface being sized as a sliding fit withi the second internal surface, resilient spring means having firs and second ends, the resilient means being located to urge th pipe sections apart, characterised in that the said second end o the resilient spring means is movable together with the secon pipe section bulbous end, and in that the spring means i arranged both to urge the pipe sections apart and to return th pipe sections to their optimal relative position.
  • the spring means is an annular coil spring having a first spring-end located in or on an abutment, convenientl formed as a flange or cup rigidly fixed to the first (e.g. upstream) pipe section, but alternatively as an outwardl protruding pipe formation; in an alternative embodiment, the cu can be adjustably fixed to the first pipe section to permit a variable spring loading; the spring has a second spring-end engageable directly or indirectly with the second bulbous end.
  • the spring-ends can be ground, the better to fit the abutment and second bulbous end.
  • At least one such coupling would be mounted vertical or substantially vertical, with the exhaust gas flowing downwardly.
  • the coupling of the invention can be separate from but sealingly attached to adjacent pipe sections, or be made integral therewith.
  • the gas flow can be in either relative direction.
  • I also propose a method of forming a hollow pivotable coupling having a first pipe section terminating in a bulbous end with a sealing surface, and a second pipe section terminating in a bulbous end with a sealing surface, the said sealing surfaces being part-spherical and concentric, part of the first bulbous end being within and in sliding engagement with the second bulbous end at said sealing surfaces, and with resilient means to urge the sealing surfaces together,
  • the coupling in use being subject to tension forces acting in a direction to separate the pipe sections and compression forces acting in a direction to press the pipe sections together
  • the resilient means being arranged to co-act with the tension forces, characterised by locating the resilient means both to move together with the second pipe section bulbous end, and to urge the pipe sections towards their optimal relative position.
  • Fig.l is a schematic end view of an engine which is transversly and flexibly mounted on the chassis of a vehicle, including part of an exhaust system comprising a composite hollow and universally articulating pipe joint comprising three hollow pivotable couplings made according to the invention;
  • Fig.2 is an enlarged schematic sectional view of one hollow pivotable coupling according to the invention, with some components including the spring ends shown spaced apart for clarity, with the pipe sections in their optimal relative or at rest position;
  • Fig.3 is an enlarged schematic sectional view of a second hollow pivotable coupling according to the invention, with some components including the spring ends again shown spaced apart for clarity;
  • Fig.4 is a schematic sectional view of yet a further embodiment according to the invention.
  • Fig.5 is a schematic sectional view of another alternative embodiment, arranged for reverse exhaust gas flow, and with an internal pipe extension.
  • the vehicle engine 2 is transversly mounted, on chassis attachment points 13. Interposed flexible mountings 3 enable the engine 2, and consequently the exhaust manifold 4, to vibrate and lurch relative to exhaust pipe section 8, which is rigidly connected to the vehicle chassis 1.
  • a typical engine movement, about the centre of twist C, during vehicle motion is shown by arrow Cl.
  • a catalytic converter or exhaust silencer (muffler) box 15 is rigidly connected to chassis 1 by arms 17, and thus moves therewith; there may be sonant dampers between silencer box 15 and the chassis attachment points.
  • Exhaust manifold 4 has its egress directed generally downwards, and has bolted thereto a first pipe section 6 having a bulbous end 16 (Fig.2). It is partly surrounded by a second bulbous end
  • the bulbous ends 16,18 are elements of a pivotable coupling 11a; additional pivotable pipe couplings lib and lie are locate downstream of coupling 11a, and in a substantia horizontally-disposed exhaust run.
  • the first bulbous end of couplin lib is carried by the end of pipe 12 remote from bulbous end 18; similarly pipe section 14 carries at its inlet end the secon bulbous end for coupling lib, as well as the first bulbous en for coupling lie.
  • Each of the couplings 11a,lib,lie has a limited range universal pivoting.
  • a pipe length with three couplings i.e. between engine 2 and pipe 9 is an articulated joint 10, comprising couplings 11a,lib,lie, with, in this embodiment, the couplings being identical in structure and operation, but in an alternative embodiment, with at least the couplings being in accordance with this disclosure.
  • pipe section 8 is connected to inlet pipe 9 of silencer box 15.
  • silencer inlet pipe 9 is formed with the second bulbous end of coupling lie.
  • the firs bulbous end has a part-spherical mating surface 20 and is locate within the downstream second part-spherical bulbous end 18 whic has an internal concentric part-spherical surface 22.
  • Surface 20,22 are sized to mate, to permit relative rotation, includin pivotting and swivelling, of the bulbous ends 16,18, whils maintaining substantially complete exhaust gas sealin therebetween.
  • Such pivotting and swivelling as may temporaril be required in response to vehicle-induced movements is o restricted range, being shared between couplings 11a,lib,lie, fo instance until the terminal portion 23 of the second bulbous en 18 abuts pipe section 6.
  • the couplings are arranged t accept exhaust gas flow in the opposite relative direction i.e. from pipe section 12 (and thus from pipe 9) to pipe section 6 i.e. the couplings can be reversed axially.
  • Pipe sections 6,12 can be short in length to permit access fo welding internal pipe extensions (such as extension 6a of Fig. .)
  • the spring 30 acts both to urge the pipe sections 6,12 apart, and to urge them towards thei optimal relative position, which they naturally occupy “at rest”. It is a further feature of my invention that the "downstream" end 31 of spring 30 moves together with bulbous end 18.
  • coil spring 30 has sufficien flexibility to be deformed, temporarily, upon pivotting an swivelling of bulbous end 18 relative to bulbous end 16.
  • th wire diameter, the coil diameter, the coil pitch and the sprin length are selected to ensure that the frictional resistanc between end 31 and bulbous end 18 deforms spring 30, rather tha permitting slippage between spring-end 31 and bulbous end 18.
  • the second spring end engages the second bulbous end at a position such that the included angle "X" (Figs.2,3) between the central axis of spring 30 and the tangent at the contact point of spring end 31 to the second bulbous end 18 is less than 35 degrees, preferably between 5 degrees and 10 degrees when measured in the "at rest" in-line condition of the first and second pipe sections.
  • an abutment 32b is formed by outward deformation of pipe section 6, either as shown as an annular outward deformation, or in an alternative embodiment as a plurality of separate outward deformations, or a series of welded pips, which also act to separate the spring end 29 from pipe 6 t inhibit heat transfer.
  • the longitudinal axis of spring 30 makes only a small angl with the external surface of the second bulbous end at th engagement position of spring-end 31.
  • the radially inward force from spring 30 upon second bulbous end is small, so tha the changes in this inward force component with changing spatial positions of the bulbous ends results in no or minimal differential wear at the mating surfaces.
  • pipe section 6 can extend within the first and second bulbous ends, to inhibit direct impingement of the hot exhaust gases with surfaces 20,22.
  • bulbous end 16 is pre-formed and welded or otherwise secured at 19 to the pipe section 6, and is internally shaped to form a gaseous buffer zone 33 adjacent surfaces 20,22, containing exhaust gas likely to be cooler than the gas in pipe section 6, because of heat lost by convection and radiation from external surface 24 of the second bulbous end.
  • the interior of bulbous end 16 fills buffer zone 33.
  • Fig.3 embodiment has a tapered-bore spring with the abutment 32 formed by enlarging the pipe 6 diameter and by abutting the other spring end directly onto bulbbous end 18; in an alternative embodiment this other spring end abuts onto the pressure ring 26, " as shown in Fig.2.
  • the downstream end 31 of spring 30 is located in stools 35 spaced apart around bulbous end 18, and rigidly connected thereto as by welding.
  • the stools can be connected so to provide an annular location for spring-end 31, encircling surface 24.
  • stools 35 can be formed integrally with bulbous end 18, since the external surface 24 need not be part-spherical. Spring end 31 is thus constrained to move with bulbous end 18.
  • hollow pipe extension 6a is secured to the inner surface of pipe section 6 adjacent the widening thereof into bulbous end 16, as by welding, but alternatively by heat resisting adhesive 50.
  • the upstream end of pipe extension 6a is chamfered at 52.
  • Spring 30 can abut stools which though attached to bulbous end 18 as by welding are nevertheless inhibiting to heat conduction to spring 30.
  • the stools are formed as raised portions of the exterior surface of bulbous end 18.
  • annular stool 135 is not rigidly fixed to bulbous end 18. It is however of a size and shape to be located just upstream (for the flow direction indicated) of the diametral line "A" of bulbous end 18; thus spring 30 exerts a greater but nevertheless equilibrium radial component force via annular stool 135 in the ratio of the cotangent of the "approximate" angle of contact (9.51 at 6 degrees) from the common central axis of the pipe sections 6,12, to ensure that it grips bulbous end 18 - preferably at an angle of between 5 and 10 degrees.
  • the spring is selected to deform, in preference to inducing slippage between stool 135 and surface
  • stool 135 can be roughened or its coefficient of friction otherwise increased. There is thus co-movement of stool 135 and bulbous end 18.
  • stool 135 can be roughened or its coefficient of friction otherwise increased.
  • the 135 can either contain axial cuts, or be separated into at least two parts with each part encircling a portion of the second bulbous end.
  • Spring 30 exerts only a small component of force parallel to the median plane "A", so that small imbalances to diametrically opposite sides of the bulbous end 18 when the spring 30 flexes, result in minimal extra wear at the corresponding diametrically opposed positions on mating engagement surfaces 20,22.
  • pipe section 12 can have welded thereto a pipe extension, projecting towards but not reaching the pipe section 6.
  • annular gap is provided, which with the (upward) mass gas flow indicated, allows gas flow in the "reverse" direction into the buffer zone 33 which has been created, with “double-reverse” flow required if the gas is to penetrate between sealing surfaces 20,22. Since there is little, if any, escape of gas from between the sealing surfaces 20,22 there is little flow of hot exhaust gas into the buffer zone, the gas in this buffer zone thereby remaining substantially cooler in use (because of the heat lost through convection and radiation) than the exhaust gases in pipes 6,12.
  • one or both of the abutment 32a,32b, and stool 35,135 can be apertured, corrugated or castellated, both at the support surface for spring end 31 and at the engagement surface with pipe 6 or surface 24 respectively.
  • the coil spring 30 can be replaced by three or more springs (preferably four) equi-angularly spaced about the coupling, as on a spider or on dedicated arms.
  • the sections will not remain in their offset condition, as might occur with two diametrically-opposed springs in "tumbler-switch" array, but at least one spring will be active to return the pipe sections to their optimal relative position.
  • the second spring end is not circular, and is such that the last coil of at least one spring end provides a three-point engagement, preferably spaced apart by 120 degrees, with either the second pipe section bulbous end 18, or the pipe section 6.
  • the last coil acts as a gripping ring to the bulbous end; although this coil is normally "downstream", the gas flow can reversed so that it is upstream.
  • the invention permits improved sealing aainst exhaust ga escape, with consequent danger to the vehicle driver an passengers, and possible noisy operation.
  • the bulbous ends ar continuously urged towards their sealed condition, to permi continuous gas-tightness.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Exhaust Silencers (AREA)
  • Joints Allowing Movement (AREA)

Abstract

Accouplement orientable creux, utilisé particulièrement pour un système d'échappement de véhicule, dans lequel les tuyaux ou parties de tuyaux adjacents possèdent des extrémités encastrables en forme de bulbes écartées l'une de l'autre par un ressort résilient. L'une des extrémités du ressort se déplace avec l'une des extrémités en forme de bulbe, tandis que l'autre s'appuie sur l'autre extrémité en forme de bulbe. Le ressort est installé de façon à écarter les parties de tuyaux les unes des autres et à les forcer à reprendre leur position optimale de repos relatif ou leur alignement.
PCT/GB1992/001549 1991-08-22 1992-08-21 Accouplement orientable creux perfectionne WO1993004270A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9118158.6 1991-08-22
GB919118158A GB9118158D0 (en) 1991-08-22 1991-08-22 Improved hollow pivotable coupling

Publications (1)

Publication Number Publication Date
WO1993004270A1 true WO1993004270A1 (fr) 1993-03-04

Family

ID=10700388

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1992/001549 WO1993004270A1 (fr) 1991-08-22 1992-08-21 Accouplement orientable creux perfectionne

Country Status (2)

Country Link
GB (1) GB9118158D0 (fr)
WO (1) WO1993004270A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1270890A3 (fr) * 2001-06-13 2004-05-26 Honda Giken Kogyo Kabushiki Kaisha Dispositif absorbeur de vibrations pour système d'échappement de moteur
GB2517028A (en) * 2013-05-23 2015-02-11 Snecma Interface device between two turbomachine elements
WO2016084646A1 (fr) * 2014-11-28 2016-06-02 オイレス工業株式会社 Procédé de détermination de position de disposition de joint sphérique pour coupler mutuellement des tuyaux d'échappement dans un système d'échappement, et système d'échappement

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2746996A1 (de) * 1977-10-19 1979-04-26 Weinhold Karl Rohrkupplung
FR2472713A2 (fr) * 1978-05-26 1981-07-03 Luchaire Sa Dispositif d'accouplement perfectionne
WO1990015229A1 (fr) * 1989-06-09 1990-12-13 Fred Parker Birch Couplage creux pivotant

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2746996A1 (de) * 1977-10-19 1979-04-26 Weinhold Karl Rohrkupplung
FR2472713A2 (fr) * 1978-05-26 1981-07-03 Luchaire Sa Dispositif d'accouplement perfectionne
WO1990015229A1 (fr) * 1989-06-09 1990-12-13 Fred Parker Birch Couplage creux pivotant

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1270890A3 (fr) * 2001-06-13 2004-05-26 Honda Giken Kogyo Kabushiki Kaisha Dispositif absorbeur de vibrations pour système d'échappement de moteur
US6863154B2 (en) 2001-06-13 2005-03-08 Honda Giken Kogyo Kabushiki Kaisha Vibration absorbing apparatus for exhaust system of engine
GB2517028A (en) * 2013-05-23 2015-02-11 Snecma Interface device between two turbomachine elements
GB2517028B (en) * 2013-05-23 2019-07-03 Snecma Interface device between two turbomachine elements
WO2016084646A1 (fr) * 2014-11-28 2016-06-02 オイレス工業株式会社 Procédé de détermination de position de disposition de joint sphérique pour coupler mutuellement des tuyaux d'échappement dans un système d'échappement, et système d'échappement
CN107002543A (zh) * 2014-11-28 2017-08-01 奥依列斯工业株式会社 确定排气系统中使排气管互连的球接头的布置位置的方法及排气系统
US10260401B2 (en) 2014-11-28 2019-04-16 Oiles Corporation Method of determining arrangement position of spherical joint for connecting exhaust pipes to each other in exhaust system, and exhaust system
CN107002543B (zh) * 2014-11-28 2019-06-14 奥依列斯工业株式会社 一种确定球接头的布置位置的方法

Also Published As

Publication number Publication date
GB9118158D0 (en) 1991-10-09

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