US3871204A - Machines for manufacturing bearing races by rolling - Google Patents

Machines for manufacturing bearing races by rolling Download PDF

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Publication number
US3871204A
US3871204A US378815A US37881573A US3871204A US 3871204 A US3871204 A US 3871204A US 378815 A US378815 A US 378815A US 37881573 A US37881573 A US 37881573A US 3871204 A US3871204 A US 3871204A
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Prior art keywords
machine
tool roller
set forth
die
spindle
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Expired - Lifetime
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US378815A
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English (en)
Inventor
Jean Gerat
Georges Gerbet
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NTN Europe SA
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Societe Nouvelle de Roulements SNR SA
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H1/00—Making articles shaped as bodies of revolution
    • B21H1/06—Making articles shaped as bodies of revolution rings of restricted axial length
    • B21H1/12—Making articles shaped as bodies of revolution rings of restricted axial length rings for ball or roller bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

Definitions

  • ABSTRACT A machine for rolling the outer races of bearings in an external die with the assistance of a rolling tool roller operating in overhanging relationship in a race blank to be rolled, and the roller is mounted to the end of an eccentric spindle fitted in a sleeve mounted in turn eccentrically in another sleeve, wherein the two sleeves are rotatably driven, the spindle and tool roller being rigidly assembled and rotatably driven from a motor at such speed that the apparent speed of the tool roller approaching the blank to be rolled is substantially zero, the sleeves being driven through an e'picyclic gear train connected through two of its rotating members to the sleeves, these two members coacting with a third member of the gear train which consists of a reaction member responsive to
  • SHEET UZUF 10 141 will! PATEHTED MAR] 8 I975 SHEET OBOF 10 PATENTED HAR I 8 I975 SHEET O7UF 10 Li I Lula-h ...w. x oq PATENTEBHAR 1 8 I975 SHEET 100F 10 MACHINES FOR MANUFACTURING BEARING RACES BY ROLLING
  • the present invention relates to a machine for manufacturing ring-shaped workpieces such as the outer races of bearings, by applying the so-called rolling operation to annular blanks cut from tubular stock.
  • the present invention is directed to provide a machine capable of rolling an annular workpiece, notably outer bearing races, according to the cold rolling technique, with the desired dimensional tolerances and surface conditions that are usually obtained in turning of workpieces of this general character.
  • both sleeves being responsive to drive means for rotating them and to other means capable of imparting an angular displacement thereto for rotatably driving the spindle and tool roller assembly and controlling the tool roller feed movement, is character- 1 ised in that the spindle and the tool roller are rigid with each other and rotatably driven from a motor atsuch speed that the apparent speed of the tool roller approaching the blank is substantially zero, and that the drive means comprise an epicyclic gear train operatively connected through two rotating members of said train to said sleeves, said rotating members co-acting with a third member of said gear train which is responsive to said angular displacement means, and consisting of a reaction member having its angular setting controlled as a function of the desired tool roller feed rate.
  • the means for producing the angular displacement of said reaction member may be easily controlled notably with the assistance of a hydraulic actuator.
  • the rolling feed rate of the tool roller can be controlled in a strict and reproductible manner, as a function of the programme contemplated and consistent with the workpiece to be rolled.
  • This control action is of primary importance, considering the magnitude of the pressures created in the roller-to-workpiece interface and applied to the roller and its spindle, these pressures being rather difficult to harmonize with the desired precision and production rates.
  • the preliminary driving of the spindle and roller at the rolling speed is advantageous in that it eliminates the risk of binding the parts at the points of contact between the roller and the workpiece, due to the absence of relative frictional engagement between the two surfaces involved.
  • This device is subsequently changed into the driving of the roller for rotation as a consequence ofits pressure contact with the blank during the rolling operation proper, under the control of the eccentric sleeves, but remains necessary at the beginning of each operation to avoid any relative and stray slip likely to produce any binding defect on the surface of the roller and also, of course, of the blank.
  • the kinematic chain contemplated herein for producing the above-defined roller feed movement may easily be constructed in a reversible form.
  • the rotation bearings are low-friction bearings such as rolling-contact bearings, especially those of the eccentric sleeves whereat the possibility of nonreversibility due to jamming or binding is most likely to develop, and at least one elastic coupling, for example a so-called Oldham joint permitting the absorption of possible axial misalignment during the operation with the sleeve in a pronounced eccentric relative position, may be provided on each sleeve driving line.
  • the fluid feed under constant hydraulic pressure produces a substantially constant pressure at the tool roller for only the nearly linear portion of the sine eccentricity law is utilized.
  • the output is adjusted from the onset and in any case has but a very moderate influence on the rolling time.
  • the feed curve is subordinate to the output and to the constant pressure. Nothwithstanding this, the kinematic chain is reversible since the eccentricity control and the stress transmission are accomplished through continuously moving members, the coefficients of friction are constantly dynamic and therefore moderate. This accounts for the fact that in the known, abovementioned hot-rolling method a passive drive through a hydraulic brake is utilized although the rolling pressures are lower than in the case of cold rolling.
  • FIG. I is a diagrammatic view of the kinematic chain of the device controlling the rolling tool roller feed
  • FIG. 2 is a recorded diagram of the rolling tool roller feed during a cycle of operation of a machine operating under constant stress condition
  • FIG. 3 is a wiring diagram illustrating the electrohy draulic control system of the machine
  • FIG. 4 is a sectional view showing the parallel gear trains connecting the epicyclic gear train to the eccentric sleeves;
  • FIG. 5 is an axial sectional view showing the mounting of the tool roller spindle and of the eccentric sleeves
  • FIG. 6 is a sectional view of the hydraulic ram operating in conjunction with the reaction member of the epicyclic gear train
  • FIG. 7 is an axial section showing the die carrier with its hydraulic control means for opening and closing the die. and for ejecting the workpiece and locking the die, together with the supply sump formed in the die carrier
  • FIG. 8 is a crosssectional view of the supply sump together with the means for controlling the locking of said die
  • FIG. 9 is a front view of the spindle supporting block provided with a deflector for protecting the tool roller
  • FIG. 10 is a view showing the base plate of the machine and means for controlling the tipping of the die carrier assembly, to facilitate the inspection thereof and the replacement of tools
  • FIGS. 11 to 14 are fragmentary axial sections illustrating the various steps of the blank rolling operation, and
  • FIGS. 15 and 16 are two cross-sectional view illustrating two steps of the rolling operation.
  • the rolling machine illustrated comprises in the whole (see notably FIG. 1) a spindle 1 receiving at its end a tool roller 2 and adapted to be driven at its other end by a motor 3 adapted to be reversed as a receiver operating without any antagonistic torque.
  • a hydraulic motor equipped with a non-return valve in parallel will serve the purpose very satisfactorily.
  • the spindle 1 is rotatably mounted in an eccentric position in a sleeve 4 (the eccentricity being designated by the reference numeral 5 in FIG.
  • any variation in the angular position of reaction sun gear 15 is attended by a relative angular displacement of sleeves 4 and 6 and therefore by a variation in the eccentricity or throw of the spindle l in relation to the axis 0, which corresponds to the feed movement of the tool roller 2, the operative rotation of the tool-roller carrier spindle 1 about the axis 0 corresponding in this case to the synchronous rotation of said sleeves.
  • the spindle motor 3 is provided for rotatably driving the spindle proper and, of course, the tool roller preliminary to the contact between this roller and the blank to be rolled, so that the apparent speed of the tool roller approaching and eventually contacting the blank is substantially zero.
  • the hydraulic motor 3 is then by-passed or short-circuited to operate as a pump during the rolling operation.
  • the angular position of the reaction sun gear 15 is controlled by means of a hydraulic ram designated in general by the reference numeral 18 via a rack 19 rigid with the cylinder 20 of this ram and co-acting with a pinion 21 rigid with said sun gear 15.
  • the cylinder 20 is slidably mounted to a piston rod 22 projecting from each end of the cylinder 20 and secured at its ends to the frame structure of the machine.
  • the ram movement is controlled by means of a variable-output hydraulic pump 23 responsive to an electro-hydaulic assembly 24 controlling the entire sequence of operations of the ma chine.
  • the spindle carrier block 7 (FIG. 5) carries about the tool roller a fixed element 25 of the die, the other element 26 of the openable die being an integral part of a movable device shown in detail in FIG. 7 and having its body 27 secured to the base plate 28 of the frame structure of the machine in front of the spindle carrier block 7.
  • this fastening is contemplated in this case about a pivot pin 29 and the bearing plate of body 27 which engages base plate 28 is pivotally connected on the other hand to the piston rod 30 of a hydraulic actuator having its cylinder 31 pivotally connected to said base plate.
  • the function of this actuator consists in tipping the movable die carrier device to the position shown in dash-and-dot lines in FIG. 10 for carrying out any inspection operation or changing the tool, which are thus greatly facilitated.
  • the die section 26 is secured to a structure movable in relation to the body 27 and comprising a hydraulic ram piston 32 having its cylinder formed in said body 27, and a hydraulic ram piston 33 having a greater cross-sectional surface area but a smaller stroke than the preceding piston, its cylinder 34 being provided with a collar 35 for mechanically locking same with respect to the spindle carrier block 7.
  • the block 7 carries in this form of embodiment three locking studs 36 adapted to constitute a bayonet coupling with the collar 35. Therefore, the latter comprises three arcuate slots 37 shaped at one end for receiving freely the heads of said studs 36, the remaining portions of these slots 37 being adapted to slide on the shanks of these studs.
  • the angular movement necessary for producing the locking bayonet coupling engagement is obtained by causing the mutual engagement of a toothed sector '35:: formed on said collar with a rack 38 slidably mounted in a guide 39 securedto the base plate 28 and connected to the piston of a hydraulic ram 40 having its cylinder secured to said base plate.
  • the movable assembly carrying the die section 26 also comprises a shoot 41 for supplying blanks to this die, such as the blank shown at 42.
  • This shoot opens into a bore of die section 26 which is adapted to receive the blank and has slidably mounted therein a push member 43 rigid with a bar 44 mounted in turn for sliding movement in the piston 32 of the movable assembly and constituting, at its rear end, the piston 45 of a hydraulic actuator having its cylinder 46 secured to a rear cover 27a of body 27.
  • the shoot 41 is slidably engaged between two positioning guides 47 secured to the spindle carrier block 7 and is provided in its portion not shown in the drawings with a sorting device of known type permitting the access of the blanks only one by one into the shoot portion illustrated.
  • FIG. 6 shows a typical mounting of the actuator 18 controlling the feed movement of the tool roller; it will be seen that the supply of hydraulic control fluid to the two chambers of the movable cylinder 20 takes place in this case through the inner passage of the piston rod 22.
  • the movable cylinder 20 also constitutes a sleeve 48 receiving therein a stop screw 49 co-acting therewith, said stop screw 49 being keyed at 50 in an axial groove 51 formed in a control rod 52 extending through said screw and adapted to be actuated by means of an external handwheel 53.
  • rotating this handwheel 53 will cause the screw 49 to move axially in relation to the sleeve 48 and thus adjust the permissible stroke of the cylinder of said actuator, within the limits permitted by the mutual engagement between said stop screw 49 and a limit stop 54 rigid with the frame structure, this adjustment permitting under these conditions the presetting of the feed stroke of the tool roller as a function of the desired inner diameter of the groove to be formed in the bearing race.
  • the screw 49 coacts with a movable stop member 55 adapted to produce the reversal ofthe stroke of actuator 18 at the end of a cycle and also to introduce a hydraulic damping or shock-absorbing action at the end of the stroke by throttling the corresponding exhaust of said actuator.
  • the rack 19 co-acts with a limit-stroke hydraulic damper 56 secured to the frame structure.
  • FIG. 4 A typical form of embodiment of the transmission provided between the epicyclic gear train and the sleeves 4 and 6 is illustrated in FIG. 4 with reference numerals corresponding to those of FIG. 1 and will not be described further in detail, except for emphasizing the interposition of Oldham coupling or joints 8a, 9a in the chain driving the interconnected trains 8 and 9. Furthermore, it will be noted, if reference is made to FIG. 5, that the tool roller carrier spindle 1 is mounted in sleeve 4 on bearings 57 and 58.comprising two rows of rollers, which are self-aligning under an axial thrust, to provide a relatively accurate centering between the tool roller and the die.
  • the sleeves are also mounted 'with a moderate coefficient of friction with the assis tance of needle rollers 59, 60 for sleeve 4 in sleeve 6, and 61, 62 for this sleeve 6 in said spindle carrier block 7.
  • the front face of the spindle carrier block 7 (FIGv 9) has pivotally mounted thereon by means of a pin 63 a deflector shutter 64 adapted to compel the finished race to emerge parallel to itself from the movable die section 26 so that it can slide freely during the ejection (for the ejected race may jump in any direction due to its inherent elasticity and may thus sometimes remain wedged between the two die sections), as will be explained presently, this deflector shutter being actuated by the piston rod of a pneumatic actuator 65 having its cylinder also pivotally mounted to said spindle carrier block 7.
  • Underlying the deflector shutter is an inclined shoot 66 for discharging the finished races, the lower end of said shoot beingsecured to the base plate 28.
  • FIG. 9 it will be seen (as in FIG. 5)-that the fixed section 25 of the die is centered without play in the spindle carrier block 7 with the assistance of an annular set of wedging elements 67 screwed in the front cover 7a of said block.
  • control means comprising the electro-hydraulic assembly or unit 24 illustrated, of which the component elements are shown in diagrammatic form or in'the form of symbols well known in the art, so that they will be mentioned only with reference to their specific functions illustrated in the drawings, in order to simplify the description, said control means being obvious to those skilled in the art and adapted to be replaced by other equivalent means without departing from.the basic principles of the invention.
  • FIG. 3 The positions of the various movable assemblies illustrated in FIG. 3 correspond to the waiting condition of the tool roller 2 in the axis 0 and to the state of the openable die which is illustrated in FIG. 7.
  • the hydraulic motor 3 is fed from pump 23 to drive the tool roller 2 for rotation about its axis; an output regulator 103 is inserted in the return line of the pump.
  • a single fluid pressure is utilized throughout the hydraulic network and adjusted at the level of said pump as a function of the necessary rolling effort.
  • This closing of the two component elements or sections of the die by means of a relatively high hydraulic pressure and by reacting against a bayonet mechanical locking and coupling device permits through a very short stroke and therefore in a minimum time of ob taining workpieces that are free of burrs at the joint between the fixed section 25 and movable section 26 of said die, while limiting the efforts to be transmitted to the other parts of the machine.
  • the limit switch 74 also controls the energization of the winding 77 of a solenoid-operated valve 78 of which the distribution pattern illustrated is reversed, whereby causing the forward stroke of the piston 45 of the actuator controlling the push member 43, the latter pushing the blank 42 into its rolling cavity formed in the aforesaid die section 25 and 26.
  • this push member At the end ofthe stroke of this push member another limit switch 79 is actuated for energizing the winding 80 of a solenoid-operated valve 81 monitoring the distributor 82 of which the distribution pattern illustrated is reversed, whereby the actuator 18 is supplied through an output regulator 102 in the direction to produce the approach movement of the tool roller 2 pressing the blank 42 against the peripheral surface of the die.
  • the actuator closes through a cam rigid with sleeve 48 a passage switch 83 controlling the energization of the winding 84 of solenoid-operated valve 78, thus reversing its distribution pattern and causing the push member 43 to recede; output limiters 105 are provided for controlling the supply of hydraulic fluid to the piston 45.
  • this 1st step terminates (as shown in the diagram of FIG. 2) as illustrated in FIG. 11 in which the blank 42, obtained by wheel-cutting tubular stock, has a distored trapezoidal cross-sectional contour as illustrated.
  • step 1 is now followed by the three operative or working steps, consisting in 2nd Step causing the tool roller 2 to penetrate into the blank 42 until it engages the entire rolling surface under constant-pressure conditions, by producing a gradually decreasing feed rate, after absorbing the elastic distortion of the blank (beginning of the step illustratcd in FIG. 12 and end of the step illustrated in FIGS. 13 and I) 3rd Step rolling without constant pressure the blank in the die by producing a gradually decreasing additional feed. until the blank fills completely the die with its outer surface (step illustrated in FIGS.
  • the circuit comprises a solenoid operated valve 106 and a deceleration valve 107 for adjusting the low-speed backward movement of the tool roller at the beginning of the backward stroke, said valve 106 being associated with an output regulator 108 adjusting the maximum backward rate of movement of the tool roller.
  • Actuator 40 at the end of its stroke, o'perates another limit switch controlling the energization of winding 91 of valve 69 monitoring the distributor 70, of which the distribution pattern resumes the state illustrated so that piston 32 is caused to recede and the die is opened.
  • the same limit switch 90 controls a solenoid-operated valve (not shown) for operating the actuator 65 and cause the deflector screen 61 to be lowered in front of the tool roller.
  • the movable assembly at the end of the backward stroke, actuates a limit switch 92 controlling the energization of the solenoid-operated valve controlling the actuator 65 in the direction to raise the deflector screen.
  • the push member 43 and bar 44 are provided with central passages 43a, 44a extending from end to end and through which a die washing, cooling and lubricating fluid is fed from the rear end of the bar and ejected through the front end of the push member. After re-feeding the shoot 41 with a fresh blank, another sequence identical with the one described hereinabove can be accomplished.
  • Output limiters 112 connect this valve 110 to the actuator cylinder 31.
  • a pressure gauge 113 is provided for checking the single control fluid pressure across pump 23.
  • the spindle carrier block 7 is inclined at about 45, in combination with a lubrication of the block bearings by means of lubricant flowing from feed means located at the top of this block and visible at 93 in FIG. 5, the oil exhaust being located at the lower point 91, and the oil return to an upper location is provided by pump means (not shown).
  • This inclined arrangement also assists in reducing the overall dimensions of the machine, notably as far as floor space is concerned, while reducing in the feed step the rate of fall of the blanks and pressing these blanks against the feed nose to prevent a improper feeding of such blanks.
  • Pressure oil inlet ports for dismantling purposes are also contemplated at the orifice 95 where a roller-holder 96 is fitted into the spindle 1 coupled by screw-threads to a traction rod 97 for pulling the roller-carrier member with the assistance of actuator 101 at the orifice 98 where the spindle is fitted into its ball-bearing adjacent the tool roller, and
  • the cylinder receives the traction rod 97 formed with an internal inlet duct 100 and carries a piston 101 to permit the easy dismantling and refitting of the roller carrier 96.
  • the tool roller is driven through the medium of motor 3, rod 97, actuator 101, the cross-pins connecting said actuator 101 to spindle 1, this spindle 1 proper, then the roller carrier 96 wedged in said spindle 1.
  • oil is injected at 95 and 100 (the tool roller is pulled on a film of lubricant).
  • first and second sleeves said first sleeve being disposed eccentrically in said second sleeve
  • said tool roller being rigidly connected to one end of said spindle
  • said second sleeve being rotatably mounted in said frame structure
  • said drive means comprising an epicyclic gear train operatively connected through two rotating members of said gear train to said sleeves, said rotating members being coactable with a third member of said gear train,
  • said third member being responsive to said angularly displacing means and constituting a reaction memher, the angular setting of which is controlled by said angularly displacing means as a function of the desired rate of feed movement of the tool roller.
  • the angular displacement imparting means comprise a hydraulic actuator having its fluid supply regulated for both pressure and output.
  • the hydraulic actuator comprises a stop adjustment device of the manual control screw type for adjusting the end of the permissible stroke, whereby the feed movement of the tool roller can be adjusted as a function of the predetermined inner diameter of the race.
  • a die comprising a first die section rigid with the frame structure and a movable device comprising a second openable die section carried by a movable assembly, means for closing and locking said die, a blank feed shoot and a central push member for positioning the blanks to be rolled and for ejecting the rolled blanks.
  • the means for closing and locking the die comprise a hydraulic actuator having a piston of large cross-sectional area and reduced stroke which reacts against a studand-slot mechanical locking device of the bayonet type operating by translation and then rotation of said movable assembly by means of corresponding rams.
  • said feed shoot comprises a sorting device capable of presenting only one blank per cycle.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Forging (AREA)
  • Rolling Contact Bearings (AREA)
US378815A 1972-08-09 1973-07-13 Machines for manufacturing bearing races by rolling Expired - Lifetime US3871204A (en)

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FR7228788A FR2195491B1 (enrdf_load_stackoverflow) 1972-08-09 1972-08-09

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US3871204A true US3871204A (en) 1975-03-18

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US (1) US3871204A (enrdf_load_stackoverflow)
JP (1) JPS49131945A (enrdf_load_stackoverflow)
DE (1) DE2340125C3 (enrdf_load_stackoverflow)
FR (1) FR2195491B1 (enrdf_load_stackoverflow)
GB (1) GB1434416A (enrdf_load_stackoverflow)
IT (1) IT992889B (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070085431A1 (en) * 2005-04-07 2007-04-19 Masamichi Hayakawa Motor, recording disk driving device using the same, and method of manufacturing thereof
CN102527800A (zh) * 2010-12-31 2012-07-04 杨岩顺 自动液压滚槽机
CN104148877A (zh) * 2014-08-07 2014-11-19 广州小出钢管有限公司 一种钢管全自动滚花系统
CN116871376A (zh) * 2023-07-31 2023-10-13 浙江长兴和良智能装备有限公司 一种管件旋沟加工装置及其加工方法

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2330477A1 (fr) * 1975-11-06 1977-06-03 Roulements Soc Nouvelle Dispositif de roulage de bagues de roulement
FR2332084A1 (fr) * 1975-11-20 1977-06-17 Le Politekhnic Institu Procede d'usinage d'ebauches annulaires par deformation
DE3717423A1 (de) * 1987-04-07 1988-10-27 Ragettli Christian Ag Verfahren zum profilformen von als rollkoerper ausgebildeten werkstuecken und einrichtung zur ausuebung des verfahrens
IT1236712B (it) * 1989-11-15 1993-03-26 Procedimento e apparecchiatura per la produzione di tubi in lega leggera a diametro maggiorato a partire da tubi a diametro inferiore.
IT1242945B (it) * 1990-12-12 1994-05-18 Bompani Ivaldo Mta Procedimento e mezzi per realizzare un mozzo in un disco di lamiera o simile
CN111872314B (zh) * 2020-07-31 2022-03-15 烟台吉森新材料科技有限公司 一种龙门式重型扩锻机组

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US253355A (en) * 1882-02-07 ecaubebt
US2139682A (en) * 1933-06-20 1938-12-13 American Can Co Container body forming and cutting mechanism
US2215731A (en) * 1937-09-28 1940-09-24 Hazel Atlas Glass Co Method and apparatus for forming metal closures
US2215845A (en) * 1937-11-01 1940-09-24 Hazel Atlas Glass Co Method and apparatus for forming metal closures
US3196651A (en) * 1960-12-17 1965-07-27 Karrberg Gustaf Herman Rolling mill for rings
US3654826A (en) * 1969-05-09 1972-04-11 Richard C Gersch Adjustable tool block assembly
US3700345A (en) * 1970-11-04 1972-10-24 Cross Europa Werk Gmbh Eccentric boring spindle

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US253355A (en) * 1882-02-07 ecaubebt
US2139682A (en) * 1933-06-20 1938-12-13 American Can Co Container body forming and cutting mechanism
US2215731A (en) * 1937-09-28 1940-09-24 Hazel Atlas Glass Co Method and apparatus for forming metal closures
US2215845A (en) * 1937-11-01 1940-09-24 Hazel Atlas Glass Co Method and apparatus for forming metal closures
US3196651A (en) * 1960-12-17 1965-07-27 Karrberg Gustaf Herman Rolling mill for rings
US3654826A (en) * 1969-05-09 1972-04-11 Richard C Gersch Adjustable tool block assembly
US3700345A (en) * 1970-11-04 1972-10-24 Cross Europa Werk Gmbh Eccentric boring spindle

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070085431A1 (en) * 2005-04-07 2007-04-19 Masamichi Hayakawa Motor, recording disk driving device using the same, and method of manufacturing thereof
CN102527800A (zh) * 2010-12-31 2012-07-04 杨岩顺 自动液压滚槽机
CN102527800B (zh) * 2010-12-31 2014-12-10 台州市黄岩图伟建筑设备制造有限公司 自动液压滚槽机
CN104148877A (zh) * 2014-08-07 2014-11-19 广州小出钢管有限公司 一种钢管全自动滚花系统
CN104148877B (zh) * 2014-08-07 2016-08-17 广州小出钢管有限公司 一种钢管全自动滚花系统
CN116871376A (zh) * 2023-07-31 2023-10-13 浙江长兴和良智能装备有限公司 一种管件旋沟加工装置及其加工方法

Also Published As

Publication number Publication date
GB1434416A (en) 1976-05-05
DE2340125A1 (de) 1974-02-21
JPS49131945A (enrdf_load_stackoverflow) 1974-12-18
DE2340125B2 (de) 1979-10-04
IT992889B (it) 1975-09-30
DE2340125C3 (de) 1980-06-12
FR2195491B1 (enrdf_load_stackoverflow) 1975-03-07
FR2195491A1 (enrdf_load_stackoverflow) 1974-03-08

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