EP0100334A1 - Appareil de pressage de parties tubulaires. - Google Patents

Appareil de pressage de parties tubulaires.

Info

Publication number
EP0100334A1
EP0100334A1 EP83900555A EP83900555A EP0100334A1 EP 0100334 A1 EP0100334 A1 EP 0100334A1 EP 83900555 A EP83900555 A EP 83900555A EP 83900555 A EP83900555 A EP 83900555A EP 0100334 A1 EP0100334 A1 EP 0100334A1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
clamping jaws
annular
cylinder sleeve
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
EP83900555A
Other languages
German (de)
English (en)
Other versions
EP0100334B1 (fr
Inventor
Karl Sauder
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.)
Compat AG
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0100334A1 publication Critical patent/EP0100334A1/fr
Application granted granted Critical
Publication of EP0100334B1 publication Critical patent/EP0100334B1/fr
Expired legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
    • B21D39/04—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods
    • B21D39/046—Connecting tubes to tube-like fittings
    • 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
    • Y10T29/53—Means to assemble or disassemble
    • Y10T29/5367—Coupling to conduit

Definitions

  • the invention relates to a device for pressing tubular parts, in particular for pressing or pressing pipe connectors onto pipes, sleeves or hoses, consisting of a plurality of spring-loaded clamping jaws which are adjustable in the radial direction and a piston which is annular in cross-section and which acts on the clamping jaws.
  • the inside of the end region facing the clamping jaws is expanded conically, the clamping jaws with their radially outer boundary surfaces bearing on the conical extension with a corresponding angle of inclination, and the piston being hydraulically displaceable in its rest position in the direction of the clamping jaws.
  • Such a device is used to press pipe fittings onto the ends of hydraulic hoses.
  • Such pipe connectors usually consist of two coaxial tubular sections which are connected at one end to each other and the pipe connecting parts, e.g. Thread sections, wear. An annular gap remains between the two tubular parts, the end of a hose being inserted into this gap. These attached pipe connectors are then inserted between the jaws of the device and pressed radially, so that the end of the hose used is firmly clamped between the two tubular sections.
  • a plurality of clamping jaws are arranged around an axis and located within a press-on element which has a conically tapering inner surface.
  • a cylindrical hydraulic piston is provided here in order to press the pressing element against the To move the jaws, whereby the jaws are moved against each other in the radial direction by this displacement and the conical surfaces abutting each other.
  • the hose connection inserted between the clamping jaws is thereby pressed.
  • measuring devices which indicate whether the desired final outside diameter has been reached. For this purpose, the operator must observe the grinder in order to stop the operation of the device at this point. In such a device, relatively large hydraulic cylinders must be used to achieve the necessary contact pressure. If only a low operating pressure is available, there are still far more serious design problems since the device then becomes too bulky.
  • a piston is displaceably mounted in a cylindrical housing with a stop collar, which is also provided with a stop collar, which is directed outwards.
  • a cylinder space is created between the outer surface of the piston, the inner surface of the cylinder and the two mutually facing boundary surfaces of the stop collars, which can be acted upon hydraulically.
  • a pressing device which is actuated by a double-acting piston.
  • the pressing device is thus moved both forward and backward by hydraulic force.
  • an inner and an outer cylindrical element are provided, two annular chambers being formed between these two elements. be formed.
  • the inner element acts as a hydraulic cylinder and the outer element as a hydraulic piston.
  • a correspondingly large, inwardly projecting collar must be provided to achieve the necessary piston area.
  • this piston since this piston must also form a cylinder wall, a large dimension is necessary, at least in the transition area between this outer wall and the inwardly projecting collar.
  • a relatively thick design is required for the cylinder, since the projecting collar has to absorb the enormous forces. There is no possibility of reaching a support from an opposite wall, since this collar is freely cantilevered.
  • the object of the invention is therefore to create a device of the type described at the outset which enables a simple construction which is small in terms of space.
  • the effective piston area for the return of the double-acting piston is only a fraction of the piston area for the advance of the same, that the end of the piston facing away from the clamping jaws engages in an annular hydraulic cylinder and that the effective piston area for the advance of the piston is formed at the free end thereof facing away from the clamping jaws and runs parallel to the bottom of the annular cylinder, the piston having the largest cross-sectional area at its end forming the effective piston surface for the feed.
  • FIG. 1 shows a device according to the invention in an oblique view
  • 2 shows a section through the device for pressing
  • Fig. 3 shows schematically an adjustable device for switching a hydraulic valve when a certain compression diameter is reached.
  • the device shown in Fig. 1 consists essentially of a Zylinderk ⁇ rper 1, in which the jaws 2 and the actuators for the same are housed, as well as a housing 3 supporting this cylinder body 1
  • a hydraulic valve is housed, via which the supply of the pressure medium the actuator can be regulated.
  • the necessary pressure can be achieved via a hand pump 4 or corresponding external connections.
  • an adjusting device 5 with an adjusting button 6 and a scale is provided.
  • Part can be set.
  • An actuating handle 7 is also provided, by means of which the hydraulic valve can be switched over.
  • the device according to the invention can be manufactured in a very small but compact design, so that such a device for both stationary use and for individual use in any operation, at any location and at any point suitable is.
  • an electrically operated pump can also be accommodated in the housing 3 in order to build up the necessary pressure.
  • the construction of the device according to the invention can essentially be seen in the longitudinal section through the device according to FIG. 2.
  • Sector-like adjoining jaws 2 are provided, various inserts being able to be attached to the inner boundaries of these jaws, depending on the desired end diameter range.
  • These jaws 2 are adjustable in the radial direction and spring-loaded against each other, with springs 8 being inserted into corresponding bores 9 between two jaws.
  • the clamping jaws are designed with conical lateral surfaces 10 and 11 falling off towards the two ends.
  • the conical surface 11 is supported on a conical extension 12 of a cone ring 14 and the conical surface 10 on a conical extension 13 of the piston 15.
  • the piston 15 acts as an actuator for the jaws 2, so that when the piston 15 is moved in the direction of arrow 16 Clamping jaws 2 are pushed against each other in the radial direction and are also slightly moved in the axial direction, since they perform a uniform relative movement both to the piston 15 and to the cone ring 14.
  • the piston 15 is annular and used in the embodiment shown in an annular hydraulic cylinder.
  • the effective piston surface 18 for the advance of the piston 15 is formed on the free end of the piston 15 facing away from the clamping jaws 2 and runs parallel to the bottom 19 of the annular hydraulic cylinder 17.
  • the entire cross-sectional area of the piston 15 can thereby be utilized without additional stop bars or a corresponding large stop collar should be provided to form a piston surface.
  • the effective piston surface 18 is therefore attached to the area of the largest cross-sectional area of the piston 15, so that the structural dimensions of the piston 15 can also be kept very small.
  • the ring-shaped hydraulic cylinder 17 can also if it's very easy to set up. This is formed by an outer cylinder sleeve 20 and a coaxially inserted pipe section, the cylinder base 19 connecting in one piece to the pipe section 21 used. This enables very simple production with turned parts.
  • the piston At its end facing the piston surface 18, the piston has a circumferential collar 22 with an outer diameter that is larger than the remaining area of the piston 15.
  • the outer boundary 23 of the hydraulic cylinder 17 is designed at least over the displacement area of the collar 22 with an enlarged inside diameter corresponding to the outside diameter of the collar 22. This creates an annular cylinder space which is enclosed on the one hand by the inner boundary 23 of the outer cylinder sleeve 20 and on the other hand the piston outer surface 24.
  • the supply line 35 for the pressure medium for resetting the piston 15 opens near the cylinder-side sealing ring 29 into the annular cylinder space 31, so that a proper supply for the pressure medium is possible even when the piston 15 is fully extended.
  • the design according to the invention also has a particular advantage in terms of construction in that no particularly dimensioned spoilings are required.
  • the outer cylinder sleeve would have to have a substantially larger cross section and the other parts would also have to be correspondingly larger.
  • Grooves 37 are provided in the cylinder sleeve, into which locking rings 37 'engage. These locking rings have an L-shaped cross section, one leg abutting the wall of the cylinder sleeve 20 and the other leg engaging in the groove 37 on the same.
  • these locking rings 37 'into the grooves 37 are severed once or several times in their scope. Especially then if only one separating point is provided, the separating surfaces of the locking rings run at an acute angle to a radial plane of the locking ring 37 ', in order to thereby enable insertion. Furthermore, it is also provided that the component 36 and the conical ring 14 are preferably offset at their outer edge regions over a length which corresponds to the leg of the locking ring 37 'resting on the cylinder sleeve by the thickness of this leg.
  • an adjustable switching device for switching an e-hydraulic valve also engages in the displacement area of the piston 15. This makes it possible, depending on the closed state of the jaws 2 and thus in the position of the exactly calculable Piston 15 fine valve switching to make so that the device works automatically.
  • the piston surface 18 is thus acted upon up to the required pressing diameter, whereupon the hydraulic valve is switched over after a previously adjustable displacement away from the piston 15, so that the annular space 31 is then acted upon and causes the piston 15 to return to the rest position.
  • a control rod 38 engages in the displacement area of the piston 15, which can be brought into operative connection with a stop 40 ', the distance of which from the piston end on the clamping jaw side can be adjusted.
  • this control rod 38 is guided displaceably in a bore 39 of the fixed cone ring 14.
  • the switchover can take place by mechanical transmission or also by electrical switching means.
  • a simple embodiment can be seen in FIG. 3.
  • the stop 40 'for the control rod 38 can be adjusted in the axial direction, so that, depending on the desired end diameter, the piston 15 sooner or later abuts the free end of the control rod 38 and thus the stop 40 'shifted.
  • a scale 41 with a corresponding display element in order to make the adjustment visible from the outside.
  • a fine adjustment is possible, which can be regulated as a function of the thread pitch of the threaded bolt 40, so that, for example, with a corresponding thread pitch it is achieved that the compression diameter is changed by 1 mm when the adjusting knob is turned .
  • the operating rod 47 can in turn return to the position shown in FIG. 3, so that the connecting rod 49 or the bolt 52 in turn fixes the same becomes.
  • the control rod 35 could also be designed to be spring-loaded, so that it rests against the stop 40 'in its rest position.
  • a particular advantage of the configuration according to the invention lies in the relatively short overall length of the device, which is achieved by the special design of the double-acting piston. This eliminates the essential structural lengths, which are given, for example, by springs which are intended to cause a piston to be returned. The return can also be carried out hydraulically in a simple manner according to the invention, so that these additional components can be omitted.
  • the device according to the invention also has a particular advantage in that the piston 15 can be moved relatively easily as long as no pipe connection has yet been pressed. This is very easy because there are no special opposing forces. This has made it possible to seal the storage tank for the pressure medium, which will generally be oil, in an airtight manner, so that a pressure can be built up within the storage tank. It is sufficient if in the free space of the Ratstankes compressed air is introduced so that the actual pressure medium is preloaded. There is therefore the possibility, without actuating a pump, to supply the pressure medium solely through the pressure built up in the storage tank via the supply line 34, so that the piston 15 up to that starting position, in which it comes into contact with the parts to be pressed, in one Overdrive is advanced.
  • the pressure medium which will generally be oil
  • This fast forward gear which is only possible due to the smooth running of the embodiment according to the invention, means that there are no additional means here which are intended to limit the return movement of the piston.
  • the device according to the invention is practically fault-free and therefore also maintenance-free.
  • the parts in which there is a risk of damage are covered entirely or are not accessible from the outside when the parts to be pressed are inserted. It is thus also a very simple handling of this device.
  • the construction is simple and, despite achievable high pressures, can be carried out in a relatively small dimension, so that the device becomes very light and therefore also easy to transport. Of course, the simple construction also results in an inexpensive construction.

Landscapes

  • Mechanical Engineering (AREA)
  • Engineering & Computer Science (AREA)
  • Earth Drilling (AREA)
  • Reduction Or Emphasis Of Bandwidth Of Signals (AREA)
  • Actuator (AREA)
  • Analysing Materials By The Use Of Radiation (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
  • Shaping Of Tube Ends By Bending Or Straightening (AREA)
  • Magnetic Resonance Imaging Apparatus (AREA)
  • Measurement Of Radiation (AREA)
  • Surgical Instruments (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • Fats And Perfumes (AREA)
  • Springs (AREA)
  • Processing Of Meat And Fish (AREA)
  • Forging (AREA)
  • Jigs For Machine Tools (AREA)
  • Jellies, Jams, And Syrups (AREA)
  • Control And Other Processes For Unpacking Of Materials (AREA)
  • Massaging Devices (AREA)
  • Investigating Or Analyzing Materials By The Use Of Ultrasonic Waves (AREA)
  • Pipe Accessories (AREA)
  • Clamps And Clips (AREA)
  • Lining Or Joining Of Plastics Or The Like (AREA)
  • Making Paper Articles (AREA)
  • Manufacturing Of Electrical Connectors (AREA)
  • Quick-Acting Or Multi-Walled Pipe Joints (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Pens And Brushes (AREA)
  • Automatic Assembly (AREA)

Abstract

Appareil de pressage de parties tubulaires, notamment pour presser ou pour serrer des raccords de tuyaux contre des tuyaux rigides ou flexibles et des douilles. L'on prévoit plusieurs mâchoires de serrage (2) à ressort et radialement déplaçables connectées à un piston annulaire (15). Le piston (15) se déplace hydrauliquement vers les mâchoires de serrage (2) et revient à sa position de repos. La surface (25) du piston qui effectue le retour du piston (15) ne représente qu'une fraction de la surface du piston (18) qui effectue l'avance du piston (15). L'extrémité du piston (15) adjacente aux mâchoires de serrage (2) s'engrène dans un cylindre hydraulique annulaire (17), l'ensemble de la section transversale du piston (15), plus grande à cette extrémité, formant la surface (18) du piston qui en effectue l'avance.
EP83900555A 1982-02-04 1983-02-01 Appareil de pressage de parties tubulaires Expired EP0100334B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0042482A AT376589B (de) 1982-02-04 1982-02-04 Vorrichtung zum verpressen rohrfoermiger teile
AT424/82 1982-02-04

Publications (2)

Publication Number Publication Date
EP0100334A1 true EP0100334A1 (fr) 1984-02-15
EP0100334B1 EP0100334B1 (fr) 1986-05-28

Family

ID=3490242

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83900555A Expired EP0100334B1 (fr) 1982-02-04 1983-02-01 Appareil de pressage de parties tubulaires

Country Status (17)

Country Link
US (1) US4696085A (fr)
EP (1) EP0100334B1 (fr)
JP (1) JPS59500091A (fr)
AT (2) AT376589B (fr)
AU (1) AU561471B2 (fr)
BR (1) BR8305746A (fr)
CA (1) CA1207991A (fr)
DE (1) DE3363630D1 (fr)
DK (1) DK455983A (fr)
ES (1) ES8402409A1 (fr)
FI (1) FI833575A0 (fr)
HU (1) HUT36734A (fr)
IT (1) IT1167313B (fr)
NO (1) NO154185C (fr)
NZ (1) NZ203168A (fr)
WO (1) WO1983002737A1 (fr)
ZA (1) ZA83745B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004058601A1 (fr) 2002-12-31 2004-07-15 Hellenic Environmental Systems Industry S.A. Conteneur de dechets a bras basculants relies pivotants au couvercle de ce conteneur

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3611253A1 (de) * 1986-04-04 1987-10-08 Peter Dipl Ing Schroeck Radialpresse
JPH0248092Y2 (fr) * 1987-12-29 1990-12-18
WO2003057385A1 (fr) * 2001-12-31 2003-07-17 Eaton Corporation Appareil de sertissage de manchons, procede de sertissage de manchons, et necessaire de sertissage
US6993953B2 (en) * 2003-02-04 2006-02-07 Interface Associates, Inc. Swaging die and method of use
JP2009519770A (ja) 2005-12-16 2009-05-21 インターフェイス・アソシエイツ・インコーポレーテッド 医療用の多層バルーン及びその製造方法
US20100229617A1 (en) * 2009-03-13 2010-09-16 Freudenberg-Nok General Partnership Swaging Operation For Relieving Stress From A Bushing Flange
AU2013251238B2 (en) * 2012-11-01 2018-05-17 Betaswage Pty Ltd Indexing die shoes in a swage press
CN114310180B (zh) * 2021-12-30 2024-01-05 辽宁美托科技股份有限公司 一种航空用新型35MPa轴向挤压管路连接件制造装配方法

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US2999405A (en) * 1957-12-24 1961-09-12 Smith Corp A O Apparatus for radially compressing articles
US3370451A (en) * 1965-06-28 1968-02-27 Blaw Knox Co Apparatus and method for pointing tubes
US3879834A (en) * 1973-03-01 1975-04-29 Wyle Laboratories Crimping Machine
US3977065A (en) * 1973-03-01 1976-08-31 Wyle Laboratories Crimping machine
FR2229479A1 (en) * 1973-05-15 1974-12-13 Peeters Etude Realisat Eng Crimping machine for flexible tube end fittings - has hydraulic piston assembly and automatic stroke regulation
US3851514A (en) * 1973-07-18 1974-12-03 Weatherhead Co Swing-open crimper
US3972112A (en) * 1974-11-25 1976-08-03 Parker-Hannifin Corporation Method and apparatus for forming tube coupling joint
SE7513288L (sv) * 1975-01-27 1976-07-28 Wyle Laboratories Pressningsmaskin, foretredesvis for montering av ett beslag pa en slang eller liknande
GB1484515A (en) * 1975-04-16 1977-09-01 Imp Eastman Ltd Crimping apparatus
GB1569126A (en) * 1976-02-24 1980-06-11 Andrew Hydraulics Int Device for crimping tubular elements
DE2613240A1 (de) * 1976-03-27 1977-10-06 Schauz Ind Handel Gmbh Vorrichtung zum festpressen von armaturen auf schlauchenden
US4034593A (en) * 1976-04-09 1977-07-12 The Weatherhead Company Crimping machine with automatic swing open pushers
DE2844475C2 (de) * 1978-10-12 1983-09-29 Peter Ing.(grad.) 6380 Bad Homburg Schröck Radialpresse für Werkstücke mit zylindrischer Außenfläche
JPS55100835A (en) * 1979-01-29 1980-08-01 Matsutani Seisakusho:Kk Constantly loaded staking apparatus
US4314706A (en) * 1979-05-07 1982-02-09 Cushman Industries, Incorporated Chucks of constant jaw force
GB2059840B (en) * 1979-10-08 1983-03-02 Andrew Hydraulics Internatonal Crimping device
US4331019A (en) * 1979-10-12 1982-05-25 Andrew Hydraulics International Limited Device for crimping tubular elements
US4432559A (en) * 1981-12-16 1984-02-21 Robert Rasmussen Hydraulic chuck having ring collet

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See references of WO8302737A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004058601A1 (fr) 2002-12-31 2004-07-15 Hellenic Environmental Systems Industry S.A. Conteneur de dechets a bras basculants relies pivotants au couvercle de ce conteneur

Also Published As

Publication number Publication date
BR8305746A (pt) 1984-01-10
NO154185B (no) 1986-04-28
HUT36734A (en) 1985-10-28
AU561471B2 (en) 1987-05-07
ATA42482A (de) 1984-05-15
AU1158683A (en) 1983-08-25
FI833575A (fi) 1983-10-03
DK455983D0 (da) 1983-10-03
ATE19967T1 (de) 1986-06-15
NO154185C (no) 1986-08-06
NZ203168A (en) 1986-01-24
DE3363630D1 (en) 1986-07-03
EP0100334B1 (fr) 1986-05-28
NO833584L (no) 1983-10-03
CA1207991A (fr) 1986-07-22
WO1983002737A1 (fr) 1983-08-18
IT1167313B (it) 1987-05-13
ZA83745B (en) 1983-11-30
JPS59500091A (ja) 1984-01-19
ES519509A0 (es) 1984-02-01
ES8402409A1 (es) 1984-02-01
DK455983A (da) 1983-10-03
AT376589B (de) 1984-12-10
IT8367114A0 (it) 1983-02-03
FI833575A0 (fi) 1983-10-03
US4696085A (en) 1987-09-29

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