WO1996005930A1 - Appareil modulaire de coupage de tuyaux - Google Patents

Appareil modulaire de coupage de tuyaux Download PDF

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Publication number
WO1996005930A1
WO1996005930A1 PCT/US1994/009516 US9409516W WO9605930A1 WO 1996005930 A1 WO1996005930 A1 WO 1996005930A1 US 9409516 W US9409516 W US 9409516W WO 9605930 A1 WO9605930 A1 WO 9605930A1
Authority
WO
WIPO (PCT)
Prior art keywords
recited
cutting apparatus
link
cutting element
cutting
Prior art date
Application number
PCT/US1994/009516
Other languages
English (en)
Inventor
John J. Borzym
Original Assignee
Borzym John J
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
Priority to US07/924,185 priority Critical patent/US5347901A/en
Priority claimed from US07/924,185 external-priority patent/US5347901A/en
Application filed by Borzym John J filed Critical Borzym John J
Priority to AU76728/94A priority patent/AU7672894A/en
Priority to PCT/US1994/009516 priority patent/WO1996005930A1/fr
Publication of WO1996005930A1 publication Critical patent/WO1996005930A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D21/00—Machines or devices for shearing or cutting tubes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D25/00—Machines or arrangements for shearing stock while the latter is travelling otherwise than in the direction of the cut
    • B23D25/02—Flying shearing machines
    • B23D25/04—Flying shearing machines in which a cutting unit moves bodily with the work while cutting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D33/00—Accessories for shearing machines or shearing devices

Definitions

  • This application in general relates to tube cutting apparatus in which each major component may be easily replaced relative to the others. Further, improvements to the components are also disclosed.
  • Modern tube cutting apparatus typically include a number of separate components.
  • a track bed supports a die set which typically includes a clamp and cutting blade.
  • a drive or accelerator accelerates the die set on the bed up to the speed of a tube to be cut.
  • a ram is forced downwardly onto the die set by a ram drive to actuate the clamp and cutting blade to cut the tube during movement of the die set.
  • the basic components could be said to include a bed, a die set, an accelerator, a ram and a ram drive.
  • the ram and ram drive may be collectively referred to as a powerhead.
  • Apparatus for cutting other materials may not need each of the above components. As one example, some materials may not have needed a clamp. However, they still would require the other components.
  • the prior art powerheads also have deficiencies.
  • a pair of eccentric shafts are driven to selectively drive the ram into the die set.
  • These systems were deficient in that the mounting for the bearings of the first and second shafts were not readily accessible.
  • gear teeth on the eccentric shaft underwent large cyclic stresses, such that the large stresses were borne by certain teeth, which were prone to failure.
  • the two shafts are always synchronized such that the ram remains parallel to the bed. In practice, due to gear tooth and bearing clearances, there is often slippage, or relative misalignment between the two shafts, such that parallelism between the shafts is lost. This is undesirable. Ideally, exact parallelism must be maintained.
  • a pair of spaced plates mount the powerhead and the tracks.
  • an accelerator for the die set is preferably mounted between the spaced plates.
  • the modular mounting of these various components to the spaced plates allows the various components to be easily interchanged.
  • the vertical and lateral position of the powerhead between the spaced plates is adjustable.
  • the accelerator for the die set may be a hypocycloidal drive. In this type of drive, a pair of equal length links are driven and connected to the die set. The die set moves through direct linear movement due to this connection.
  • a rotary motor for driving a first of the links is electrically controlled, and feedback of the actual die set position is given to this rotary motor. This feed back allows control of the speed of the rotary motor to control the speed and position of the die set. It is desirable for the die set to quickly reach the exact speed of the tube, such that the tube may be cut by the die set.
  • a belt is fixed to the die set, and a reversible motor moves the belt to move the die set through its path of travel.
  • This second disclosed accelerator also preferably uses a feedback to control its motor.
  • a drive for a ram in the powerhead includes two spaced shafts which are connected by at least one synchronizing link.
  • the synchronizing link is preferably offset from the eccentric mounts of the shafts to the ram. In positions where the shafts are likely to slip relative to each other, thus losing parallelism between the shafts, the link is preferably in a position where it does not allow any slippage. This maintains parallelism through the critical portions of the cyclic path of the ram.
  • there are two links which are offset by a first angle relative to each other, with one of the links being offset by a second angle relative to the eccentric mount of the shafts to the rams.
  • Figure 1 is a largely schematic perspective view of a modular tube cutting apparatus.
  • Figure 2 is a largely schematic view of an accelerator for the inventive apparatus.
  • Figure 3 is an end view of the accelerator illustrated in Figure 2.
  • Figure 4 is a cross-sectional view showing the accelerator.
  • Figure 5 is a top view showing a powerhead.
  • Figure 6 is an end view showing the accelerator and the powerhead drive.
  • Figure 7 is a cross-sectional view through the entire apparatus.
  • Figure 8 A is an end view of a portion of the powerhead.
  • Figure 8B is a top view of the portion shown in Figure 8A.
  • Figure 8C is a cross-sectional view through one shaft as shown in Figure 8B.
  • Figure 8D is a cross-sectional view through the powerhead.
  • Figures 8E-8H show a problem in the prior art.
  • Figure 9A is a graphic representation of various portions of the powerhead in a first position.
  • Figure 9B is a view similar to Figure 9A, but showing a subsequent position.
  • Figure 9C shows a position subsequent to that shown in Figure 9B.
  • Figure 9D shows another subsequent position.
  • Figure 9E shows another subsequent position.
  • Figure 9F shows yet another subsequent position.
  • Figure 9G shows another subsequent position, which is then returned to the position show in Figure 9A.
  • Figure 10 is an end view of the powerhead drive.
  • Figure 11 is a cross-sectional view through the bed of the present invention.
  • Figure 12 is a top view of the bed shown in Figure 11.
  • Figure 13 is a top view similar to Figure 12, but showing an alternative accelerator.
  • a modular cutting system 28 is schematically illustrated in Figure 1 and incorporates a pair of side plates 29 and 30.
  • An accelerator 34 has a link 36 connected to drive die set 32.
  • a track assembly 37 guidably supports die set 32 and includes two spaced tracks 38 and two track supports 132, shown schematically.
  • a powerhead 40 has a ram which is forced downwardly into die set 32 at selected times to actuate a clamp and cutting blade to cut a workpiece.
  • the powerhead 40, accelerator 34 and track assembly 37 are all mounted between plates 29 and 30.
  • the device has been disclosed as a tube cutting apparatus, however, it has benefits in any cutting application.
  • the present invention incorporates improvements to the individual components, and is also an improvement in that each of the above individual components which are mounted to side plates 29 and 30 may be easily modified or replaced such that the various components can be utilized as modular systems.
  • each of the above individual components which are mounted to side plates 29 and 30 may be easily modified or replaced such that the various components can be utilized as modular systems.
  • the configuration or position of the powerhead may also be easily modified.
  • the inventive system thus is an improvement over the prior art in that it is easily modified to replace the various components.
  • Figure 2 shows a simplified view of accelerator with rotating member 42 which drives a first link 44.
  • First link 44 is connected to link 36 at shaft 48, which is in turn connected at shaft 50 to a member 43 which is connected to drive die set 32 along the track assembly 37.
  • the length of links 44 and 36 are equal.
  • Figure 3 is a graphic representation of the actual shape of the various accelerator members.
  • member 43 is connected by shaft 50 to one end of link 36, which is in turn connected by shaft 48 to member 44.
  • Member 44 is connected to drive shaft 42.
  • the distance between centers of shafts 50 and 48 is equal to the distance between centers of shafts 42 and 48.
  • Concentric with shaft 42 is a non-rotating gear 45
  • integral with shaft 48 is a pinion with half the number of teeth as gear 45.
  • Gear 45 drives pinion of shaft 48 by means of idler gear 46.
  • shaft 50 is directly connected to the die set, this translates into a direct linear movement from the die set.
  • shaft 42 be driven by an electronically-controlled motor such that its speed may be instantaneously adjusted to control the speed of shaft 50.
  • feedback be associated with the track assembly 37, such that feedback signals can be sent to a motor for member 42 so that its speed can be adjusted to control the speed of point 50.
  • a relatively simple drive is utilized to drive shaft 50 and die set 32, while at the same time ensuring that a tight control is achieved over the speed of die set 32.
  • the plural relatively small links replace the prior art slider crank configurations with relatively long links, which may flex undesirably.
  • Figure 4 is a cross-sectional view through the overall system and shows a motor 19 for driving member 42 which drive first link 44, which hypocycloidally drives link 36, which is in turn connected to member 43, which is to be connected to the die set.
  • a planetary gear system 47 may be inserted between motor 19 and link 44. As disclosed above, the distance between points 43 and 48 is equal to the distance between points 48 and 50. This results in point 50 having direct linear movement.
  • powerhead 40 includes a motor 85 driving a shaft 74, which drives a follower shaft 72.
  • a pair of keys 76 and adapter 77 secure the powerhead assembly 40 between plates 29 and 30.
  • housing 93 is split horizontally and bolted together by bolts 80. If one desires to gain access to the interior of powerhead 40, one merely removes bolts 80 and the top half of housing 93. One would then have access to the shafts and bearings for the powerhead 40 on both shafts 72 and 74.
  • Ram 45 is driven by shafts 72 and 74 to actuate die set 32.
  • rotating member 42 drives link 44, which drives link 36, which is connected to point 50.
  • keys 82 secure adapters 77 and lower adapters 84 to side plates 29 and 30.
  • the vertical position of powerhead 40 may be easily adjusted.
  • the angular orientation of powerhead 40 and the die set may be varied. In this way, one can achieve a die set and powerhead which cuts at an angle relative to the vertical and horizontal. This is valuable when cutting non-cylindrical members such as square tubing.
  • the powerhead may also be mounted beneath the die set.
  • Drive 85 is connected by belt 86 to a flywheel 88 which actually drives shaft 70.
  • Shaft 70 is connected to, and my be integral with, shaft 74.
  • a tube 90 is receive within die set 32.
  • a ram 45 is movable between the illustrated position and a lower position shown in phantom at 94, where it forces components of the die set 32 to clamp and cut tube 90.
  • die set 32 is mounted on tracks 38.
  • Ram 45 is overhung mounted from housing 93 which is bolted to plate 30.
  • shafts 72 and 74 are connected by a pair of offset links 106 and 110. These links are offset by 30 degrees. As shown in Figure 8B, shafts 72 and 74 extend through these offset links 106 and 110. As shown in Figure 8C, shaft 72 has a pair of eccentric mounts 108 and 112 which receive links 106 and 110, respectively. Shaft 74 has corresponding structure.
  • a clutch and brake combination 100 connects flywheel 88 to shaft 70.
  • taper mounted bearings 102 and 104 mount shaft 74 within housing 93. Taper mounted bearings allow bearing clearance to be adjusted to a minimum.
  • shafts 70 and 74 may be one integral shaft. As discussed above, when the top plate is removed, one has access to the shaft and its bearings.
  • ram 45 is connected to shaft 74 by eccentric 103. Shaft 72 has a similar eccentric connection to ram 45.
  • both shafts 72 and 74 drive ram 45.
  • the shaft eccentric mount to ram 45 is angularly offset from one of the links, as an example link 106. It is shown offset by 90 degrees.
  • Link 106 is in turn offset by an additional angle from link 110. It is shown offset by 30 degrees.
  • the purpose of the links is to resist slippage, and maintain parallelism between ram 45 and the other components.
  • the eccentric mount of the shafts 72 and 74 to ram 45 is at a position where slippage may occur, preferably at least one of the links 106 and 110 is in positions which resist any slippage. This acts to maintain parallelism between the shafts.
  • the ability of a link to resist slippage between two cranks is a function of the angle by which the link is displaced from the common centerline between points 72 and 74 of the two cranks. The larger the angle, the greater the ability of the crank to resist slippage.
  • the link When the link is on the common centerline X of the two shafts, the link has a minimum ability to resist slippage. Slippage is also a function of the clearance in the attachment between the link and the crank.
  • Figure 8E schematically shows the link located on the common centerline X of shafts 72 and 74 and schematically shows the clearance between eccentric mount 108 on shaft 72, and link 106. Clearance between the eccentric mount 108 and link 106 is eliminated.
  • This rotation angle is the slippage, and will increase as the clearance between the eccentric mount of shaft 74 and link 106 increases.
  • Figure 8G when the link is located 90 degrees from the common centerline of shafts 72 and 74, the angle of slippage is reduced to the minimum for a specific clearance. Clearance between the eccentric mount on shaft 74 and link 106 will further increase the shown angle of slippage.
  • Figure 8H shows the relationship between horizontal clearance, various angular locations of the eccentric mount and slippage. Slippage can be seen to be reduced as the distance from the horizontal centerline increases.
  • a top dead center position TDC for the eccentric connection point of the shafts to the ram would be at twelve o'clock. This position is shown in phantom, and is merely a reference point in this figure.
  • the connection point of the eccentric mount of the shafts to the ram is shown schematically as R.
  • Link 106 is shown offset by 90 degrees from R.
  • Link 110 is shown offset by an additional 30 degrees.
  • none of the members R, 106 or 110 are in positions which typically lead to slippage.
  • the particular position shown is a critical one during the cycle of the ram, since it is on the downstroke of the ram when the die set is being actuated to clamp and cut a tube. The largest stresses are placed on the powerhead during this portion of movement. Essentially, the most critical portions occur from the position illustrated in Figure 9A to a position just before that shown in Figure 9C.
  • connection point R of the eccentric mount and the ram has reached the position where it is at 90 degrees from the top dead center position. This is a critical position, as slippage of the rams on the eccentric mounts is possible, and most likely at this position.
  • link 106 is at the position where it is least likely to allow slippage. This is true since the link is at its lowermost position.
  • link 110 is also at a position close to that of link 106, and thus also resists slippage. At this position, links 106 and 110 ensure that the shafts 72 and 74 do not slip and maintain parallelism of the ram.
  • connection point R, and link 106 are both in positions resisting slippage.
  • link 106 is in a position where it may allow slippage.
  • link 110 is in a position not far from link 106, and may also allow some slippage.
  • the connection point R is in a position which is most likely to resist slippage, however, and it is unlikely that any slippage between shafts 72 and 74 could occur. Further, this position is not a high stress position, and thus there is less likelihood of slippage.
  • Link 110 is in a position resisting slippage and connection point link 106 is moving towards that position.
  • connection point R is moving towards the position where it might allow slippage in the absence of links 106 and
  • connection point R is at a position where it may allow slippage.
  • Link 106 is at the position where it has a great resistance to slippage, however, and link 110 is not far from that position. Thus, any slippage between shafts 72 and 74 is resisted.
  • Figure 9G shows the subsequent position.
  • Link 110 is now at a position where it may allow slippage.
  • the positions of link 106 and connection point R are both close to positions where they have a great resistance to slippage. They thus tend to resist slippage between shafts 72 and 74. Further, this is not a critical or high stress portion of the cycle of the powerhead, and thus slippage is unlikely.
  • the shafts which drive the ram are eccentrically mounted to the ram.
  • synchronizing links connect the two shafts and are positioned offset from the eccentric mount to the ram to overcome the weak portions of the cycle of the ram drive. In this way, the inventive system allows the use of the two shaft eccentric drive for the ram, while addressing and eliminating any slippage during critical portions of the cycle.
  • links 106 and 110 are shown in compression, they may also be in tension. Preferably, if the links are relatively short they will be utilized in compression, whereas if they are relatively long they may be utilized in tension. Further, although only two links are shown, it is envisioned that additional links could be utilized to further reduce the likelihood of any slippage between shafts 72 and 74.
  • FIG 10 is an end view of motor 85 connected to belt 86 which in turn drives flywheel 88.
  • motor 85 may be connected to a plate 120 which includes bolts 122 received in slots 124.
  • the position of motor 85 may be adjusted to adjust the tension on belt 86.
  • motor 85 and its associated structure can be removed with the powerhead.
  • tracks 38 receive die set 32.
  • Tracks 38 are mounted on track supports 132.
  • a spacer member 130 extends between track supports 132.
  • Supports 132 are in turn mounted to the side plates.
  • the side plates may either have alternate bolt holes as required such that the location of tracks 38 and track supports 132 may be changed, or the track supports may be replaced entirely to change the distance between the tracks.
  • member 134 is attached to die set 32 and member 136 is attached to the machine frame, here shown attached to track support 132.
  • members 134 and 136 interact to continuously provide a signal which is a function of die position to the accelerator control.
  • the accelerator controls the position and velocity of die set 32, and a relatively simple rotary motor can be used while still achieving tight control over the position and speed of the die set.
  • tracks 38 are mounted on track supports 132 which extend between side plates 29 and 30.
  • member 43 is connected to die set 32, and drives it along guide tracks 38. Further, member 136 provides a feedback signal.
  • FIG 13 shows an alternative accelerator 140.
  • Accelerator 140 includes a belt 142 which is fixed to die set 32.
  • a pair of spaced rollers 146 and 148 drive belt 142.
  • Belt 142 is bolted at 150 to die set 32.
  • a motor 152 drives roller 146 through a coupling 154.
  • Tracks 156 mount die set 32.
  • Motor 152 rotates in a first direction to move belt 142 and die set 32 moves along in that direction. At the end of the cutting operation, motor 152 is reversed, reversing the position of die set 32.
  • belt 142 is a steel belt. It is relatively easy to control the speed of belt 142 by this combination, and consequently to control the speed of die set 32.
  • the size of the assembly is reduced since the accelerator is incorporated into the track assembly.
  • the motor for the accelerator is an electronically controlled motor available from Unico Corporation.
  • a steel belt available from Belt Technologies is utilized.
  • a feedback device available under the tradename Temposonics was preferably utilized to provide the position feedback discussed above.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

Appareil (28) de coupage de tuyaux qui comporte des plaques espacées (29, 30) permettant un montage modulaire des pièces principales dudit appareil. Les différentes pièces peuvent être remplacées et appariées à d'autres pièces, soit par modification de la position dans laquelle les pièces sont montées sur les plaques, soit par remplacement desdites plaques. Un accélérateur (34) utilise une connexion excentrique à un moteur rotatif pour fournir un entraînement relativement simple de l'outil de coupe (32). Dans un autre mode de réalisation de l'accélérateur, une bande d'acier peut tourner dans les deux sens et est fixée de manière à entraîner l'outil de coupe. Dans un ensemble (4) tête d'alimentation destiné à actionner l'outil de coupe (32), une paire d'arbres espacés sont connectés par l'intermédiaire de deux liaisons décalées afin de synchroniser lesdits arbres et de maintenir le parallélisme du coulisseau lorsqu'il est poussé vers le bas dans l'outil de coupe.
PCT/US1994/009516 1992-08-03 1994-08-23 Appareil modulaire de coupage de tuyaux WO1996005930A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US07/924,185 US5347901A (en) 1992-08-03 1992-08-03 Modular tube cutting apparatus
AU76728/94A AU7672894A (en) 1992-08-03 1994-08-23 Modular tube cutting apparatus
PCT/US1994/009516 WO1996005930A1 (fr) 1992-08-03 1994-08-23 Appareil modulaire de coupage de tuyaux

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US07/924,185 US5347901A (en) 1992-08-03 1992-08-03 Modular tube cutting apparatus
PCT/US1994/009516 WO1996005930A1 (fr) 1992-08-03 1994-08-23 Appareil modulaire de coupage de tuyaux

Publications (1)

Publication Number Publication Date
WO1996005930A1 true WO1996005930A1 (fr) 1996-02-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1994/009516 WO1996005930A1 (fr) 1992-08-03 1994-08-23 Appareil modulaire de coupage de tuyaux

Country Status (1)

Country Link
WO (1) WO1996005930A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4228706A (en) * 1976-08-18 1980-10-21 Alpha Industries, Inc. Swinging ram cut-off machine
US4354409A (en) * 1981-02-03 1982-10-19 Riera John F Flying cutoff machine
US4411182A (en) * 1981-04-27 1983-10-25 Borzym John J Belt driven flying cutoff apparatus
US4489634A (en) * 1982-07-28 1984-12-25 Volk Michael J Portable power tool table
US4542670A (en) * 1983-05-27 1985-09-24 Borzym John J Cutoff die set seat accelerator using rotary to linear motion converter
US4614139A (en) * 1985-07-12 1986-09-30 Alpha Industries, Inc. Rotary link driven cutoff machine
US4947673A (en) * 1989-04-13 1990-08-14 Connell Limited Partnership Removable slide presses
US4964325A (en) * 1988-12-27 1990-10-23 Alpha Industries, Inc. Cut-off machine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4228706A (en) * 1976-08-18 1980-10-21 Alpha Industries, Inc. Swinging ram cut-off machine
US4354409A (en) * 1981-02-03 1982-10-19 Riera John F Flying cutoff machine
US4411182A (en) * 1981-04-27 1983-10-25 Borzym John J Belt driven flying cutoff apparatus
US4489634A (en) * 1982-07-28 1984-12-25 Volk Michael J Portable power tool table
US4542670A (en) * 1983-05-27 1985-09-24 Borzym John J Cutoff die set seat accelerator using rotary to linear motion converter
US4614139A (en) * 1985-07-12 1986-09-30 Alpha Industries, Inc. Rotary link driven cutoff machine
US4964325A (en) * 1988-12-27 1990-10-23 Alpha Industries, Inc. Cut-off machine
US4947673A (en) * 1989-04-13 1990-08-14 Connell Limited Partnership Removable slide presses

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