US3776046A - Inertia balancing means for power presses - Google Patents

Inertia balancing means for power presses Download PDF

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US3776046A
US3776046A US3776046DA US3776046A US 3776046 A US3776046 A US 3776046A US 3776046D A US3776046D A US 3776046DA US 3776046 A US3776046 A US 3776046A
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counterweight
slide
respect
counterweight means
inertia forces
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C Jones
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Niagara Machine and Tool Works
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Niagara Machine and Tool Works
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    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/28—Counterweights, i.e. additional weights counterbalancing inertia forces induced by the reciprocating movement of masses in the system, e.g. of pistons attached to an engine crankshaft; Attaching or mounting same
    • F16F15/283—Counterweights, i.e. additional weights counterbalancing inertia forces induced by the reciprocating movement of masses in the system, e.g. of pistons attached to an engine crankshaft; Attaching or mounting same for engine crankshafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0064—Counterbalancing means for movable press elements
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18248—Crank and slide
    • Y10T74/18256—Slidable connections [e.g., scotch yoke]
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2173—Cranks and wrist pins
    • Y10T74/2183—Counterbalanced
    • Y10T74/2184—Vibration dampers
    • 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
    • Y10T83/00—Cutting
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8821—With simple rectilinear reciprocating motion only
    • Y10T83/8824—With provision for dynamic balance

Definitions

  • This invention relates to power presses and, particularly, to means for substantially reducing the inertia forces developed therein.
  • one of the cooperating die members is secured to the bed of the press and the upper die member is secured to the usual reciprocating slide or ram of the press.
  • the weight of the slide itself, the movable die attached thereto, the connection between the slide and the crankshaft or eccentric shaft which reciprocates the same, and the eccentric portion of the shaft all make up a reciprocating mass of very substantial magnitude.
  • the heavy vibrations generated by this rapid reciprocation and the shaking forces developed in the machine and transmitted to the building structure present very severe problems.
  • the present invention provides means whereby a very large percentage of the inertia forces developed by the reciprocating mass of the press is neutralized in a very effective and practical manner.
  • counterweight means fixed to the crankshaft or eccentric shaft of the press having a center of gravity offset from the axis of the shaft and oriented so that the eccentric mass of the counterweight is in a lower dead center position when the slide is in an up position, and vice versa, will tend to balance out a portion of the inertia effect of the reciprocating slide and its connected reciprocating parts, but this solution presents a collateral problem since the rotating eccentric mass of this counterweight means introduces lateral inertia forces which increase rapidly with increased mass of the eccentric counterweight and thus greatly limit the use of this expedient and militate against its effectiveness.
  • the use of such a counterweight means is rendered feasible to much more fully neutralize the inertia effect of the reciprocating slide and its connected parts by providing a second counterweight means rotating in a direction opposite to that of the first counterweight means but arranged so that the eccentric masses of both counterweight means are at bottom dead center at the same time and at top dead center at the same time.
  • the eccentric masses of the two oppositely rotating counterweight means act cumulatively in opposition to the inertia forces of the reciprocating mass comprising the power press slide and its connected parts.
  • the second counterweight means introduces lateral inertia forces in opposition to the lateral inertia forces of the first counterweight means to subtract from lateral inertia forces developed by the first counterweight means.
  • the second oppositely rotating counterweight means will be of less mass, or of less inertia effect, than the first means. This is due to the fact that a portion of the lateral effect of the first counterweight means is cancelled out by the opposite lateral effect of the drive means for the slide, that is, the rotating or revolving parts of such drive means.
  • the second counterrotating counterweight means need only be of suffrcient mass or inertia to balance out the excess of lateral inertia forces of the first counterweight means, for optimum results.
  • the foregoing eccentric counterweight means will be in addition to the usual primaryflywheel of the machine although the rotational inertia forces of the counterweight means of the present invention may somewhat reduce the requirement for rotational inertia energy in the principal flywheel of the machine.
  • FIG. 1 is a general front elevational 'view of one type of power press to which the principles of the present DESCRIPTION OF THE ILLUSTRATED EMBODIMENT
  • FIG. 1 shows a conventional straight side power press having a bed 10, side frames 11 and 12, a crown l3, and a vertical reciprocable slide 14 driven from a main shaft 15 by reciprocable connections 16 and 17.
  • the numeral 18 designates a housing which contains a conventional flywheel mounted on main shaft 15 and the usual clutch and brake mechanism (not shown) is interposed between the flywheel and main shaft 15.
  • a die set will be employed in the power press of FIG. 1 with the stationary unit thereof secured to a bolster plate 20 on bed 10 and with a movable member of the die set secured to the under side of slide 14.
  • crown 13 includes upper and lower walls 22 and 23 and, as shown in FIG. 3, front and rear walls 24 and 25.
  • main shaft 15 is supported by a series of six bearings 27 which are carried by vertical wall members designated 28, 29-and 30 in FIG. 2, the wall membersbeing welded to top wall 22 and front and rear walls 24 and 25.
  • the press shown herein by way of example has a pair of driving eccentrics 32 on main shaft 15 which are provided with connections 33 to slide 14 for reciprocating the latter vertically.
  • a conventional counterbalancing cylinder which is fixed to upper wall 13 is shown at 35 and has a shaft connection 36 to slide 14. All of the foregoing is conventional construction in power presses of this general type.
  • main shaft is provided with a pair of semi-circular counterweights 40 which are fixed to the main shaft by bearing caps 41.
  • the eccentrics 32 and slide 14 are at top dead center and the semi-circular counterweights 40 are at bottom dead center.
  • a countershaft 43 supported in the left-hand vertical wall member 29 and a further similar vertical wall member 44, is connected to main shaft 15 by gears 45 and 46 of equal pitch diameters so that countershaft 43 rotates synchronously with main shaft 15 but in the opposite direction.
  • a further semi-circular counterweight 50 is fixed to countershaft 43 by means of a bearing cap 51 and is likewise in its bottom dead center position when eccentrics 32 and slide 14 are in their upper positions.
  • the two counterweights 40 and counterweight 50 will all move upwardly as the slide 14, the eccentrics 32 and the connections 33 move downwardly, and vice versa.
  • the vertical inertia components of the three counter weights act in opposition to the vertical inertia of slide 14, eccentrics 32, connections 33 and the movable die member carried by slide 14.
  • the lateral component of counterweight 50 acts in opposition to the lateral components of counterweights 40.
  • the lateral components of counterweights 40 are in part counterbalanced by the lateral components of the eccentrics 32 and the connections 33 and, accordingly, the mass of counterweight 50 will be substantially less than the mass of counterweights 40.
  • a power press having a frame including a bed, a slide reciprocable with respect to said bed and connectible with a movable die member to effect working strokes thereof, a continuously rotating shaft having eccentric drive means and means connecting the same to said slide for reciprocating the same; first counterweight means rotatable with said drive shaft and having its center of gravity opposite to that of said eccentric drive means whereby said first counter-weight means moves in opposition to the movement of said slide, and second counterweight means synchronized with said first counterweight means to rotate continuously at the same speed but in the opposite direction, the center of gravity of said second counterweight means being offset from its axis of rotation in the same direction as that of the first counterweight means with respect to the direction of the slide, whereby said two counterweight means move in unison with respect to the direction of said slide but oppositely with respect to a direction at right angles thereto.
  • Apparatus according to claim 1 including'a countershaft and transmission means connecting the same to said drive shaft for rotation at a one to one ratio therewith but in the opposite direction, said second counterweight means being mounted on said countershaft for rotation therewith.
  • Apparatus according to claim 2 including a countershaft and transmission means connecting the same to said drive shaft for rotation at a one to one ratio therewith but in the opposite direction, said second counterweight means being mounted on said countershaft for rotation therewith.

Abstract

In power presses such as are used for stamping sheet metal and the like, the inertia forces of the reciprocating slide of the press and its attached parts set up very heavy and objectionable vibrations, particularly in high speed presses. The present invention provides primary and secondary counterweights. The primary counterweights rotate with the crankshaft or eccentric shaft of the press but with the center of gravity of the counterweight moving in a direction opposite to the direction of movement of the slide to neutralize at least a portion of the inertia forces of the slide and its connected parts. The secondary counterweight rotates opposite to the first counterweight but with its center of gravity moving in the same direction with respect to the vertical, so that the second counterweight has a cumulative effect with respect to the primary counterweight in neutralizing vertical inertia forces but has a subtractive effect with respect to lateral inertia forces produced by rotation of the primary counterweight.

Description

D United States Patent [1 1 Jones, Jr. Dec. 4, 1973 [5 INERTIA BALANCING MEANS FOR POWER Primary ExaminerCharles J. Myhre PRESSES Assistant ExaminerWesley S. Ratliff, Jr. [75] Inventor: Clarence 0. Jones, Jr., Eggertsville, Atmmey chnste l & Bean N.Y. [57] ABSTRACT [73] Ass1gnee: Niagara Machine & Tool Works,
Buffalo, In power presses such as are used for stamping sheet metal and the like, the inertia forces of the reciprocat- [22] Fled: Sept 1971 ing slide of the press and its attached parts set up very [21] Appl 184,040 heavy and objectionable vibrations, particularly in high speed presses. The present invention provides primary and secondary counterweights. The primary [52] US. Cl 74/50, 83/615, 74/604 countel-weights lUtate with the k h ft or eccentric [5 1] Int. Cl. Fl6h 21/18 Shaft of the press but i the center of gravity of the [58] Field of Search 74/50, 44, 586, 587, counterweight moving in a direction opposite to the 74/588 589, 604; 83/615 628 direction of movement of the slide to neutralize at least a portion of the inertia forces of the slide and its [56] References Cited connected parts. The secondary counterweight rotates UNITED STATES PATENTS opposite to the first counterweight but with its center 2,407,102 9/1946 Ryder 74/604 of gravity moving in the Same direction. with respect to 3,203,274 8/1965 Barth et a], 74/604 the vertical, so that the second counterweight has a 2,188,146 1/1940 Fraula 83/628 cumulative effect with respect to the primary counter- 2,32l,325 6/ Sherman et 83/615 weight in neutralizing vertical inertia forces but has a 2,819,618 1/1958 slflsher 74/590 subtractive effect with respect to lateral inertia forces 3,085,457 4/1963 Fischer et al.. 83/615 produced by rotation of the pn-mary counterweight 3,422,688 1/1969 Bruderer 74/44 4 Claims, 3 Drawing Figures PAIENTEDuEc 4mm 3776046 sum 1m 3 n n nu Fl6.'l'.
INVENTOR- CLARENCE O. JONES ATTORNEYS PATENTEDDEB 4:915 SHEET w 3 3.776046 PIC-5.5.
INVENTOR. 4 CLARENCE o. JONES,JR.
j /g mw/w AT TOR N EYS INERTIA BALANCING MEANS FOR POWER PRESSES BACKGROUND OF THE INVENTION This invention relates to power presses and, particularly, to means for substantially reducing the inertia forces developed therein.
In conventional power presses one of the cooperating die members is secured to the bed of the press and the upper die member is secured to the usual reciprocating slide or ram of the press. Thus the weight of the slide itself, the movable die attached thereto, the connection between the slide and the crankshaft or eccentric shaft which reciprocates the same, and the eccentric portion of the shaft, all make up a reciprocating mass of very substantial magnitude. In present day high speed presses the heavy vibrations generated by this rapid reciprocation and the shaking forces developed in the machine and transmitted to the building structure present very severe problems.
Such means as have been proposed in the prior art for ameliorating these conditions have only slightly improved the situation and the requirement for everincreasing operating speeds of power presses renders a better solution to the questions of vibration as of prime importance in power press design.
SUMMARY OF THE INVENTION The present invention provides means whereby a very large percentage of the inertia forces developed by the reciprocating mass of the press is neutralized in a very effective and practical manner.
counterweight means fixed to the crankshaft or eccentric shaft of the press having a center of gravity offset from the axis of the shaft and oriented so that the eccentric mass of the counterweight is in a lower dead center position when the slide is in an up position, and vice versa, will tend to balance out a portion of the inertia effect of the reciprocating slide and its connected reciprocating parts, but this solution presents a collateral problem since the rotating eccentric mass of this counterweight means introduces lateral inertia forces which increase rapidly with increased mass of the eccentric counterweight and thus greatly limit the use of this expedient and militate against its effectiveness.
In the present invention, in its broadest aspect, the use of such a counterweight means is rendered feasible to much more fully neutralize the inertia effect of the reciprocating slide and its connected parts by providing a second counterweight means rotating in a direction opposite to that of the first counterweight means but arranged so that the eccentric masses of both counterweight means are at bottom dead center at the same time and at top dead center at the same time. Thus the eccentric masses of the two oppositely rotating counterweight means act cumulatively in opposition to the inertia forces of the reciprocating mass comprising the power press slide and its connected parts. On the other hand, due to the opposite rotation of the two counterweight means, the second counterweight means introduces lateral inertia forces in opposition to the lateral inertia forces of the first counterweight means to subtract from lateral inertia forces developed by the first counterweight means.
In general, or in most instances, the second oppositely rotating counterweight means will be of less mass, or of less inertia effect, than the first means. This is due to the fact that a portion of the lateral effect of the first counterweight means is cancelled out by the opposite lateral effect of the drive means for the slide, that is, the rotating or revolving parts of such drive means. A major part of the connection between the crankshaft or eccentric shaft and the slide and the eccentric mass of the driving cranks or eccentrics themselves, all develop lateral reciprocating inertia forces which are opposed to the lateral inertia forces of the first counterweight means, by reason of the fact that the eccentric mass of the first counterweight means is at bottom dead center when the slide and its driving connection is in uppermost position, and vice versa. Since the first eccentric counterweight means and the slide drive means rotate in the same direction, this places their effective masses at an angular spacing of at all times.
For the foregoing reason, the second counterrotating counterweight means need only be of suffrcient mass or inertia to balance out the excess of lateral inertia forces of the first counterweight means, for optimum results.
In most adaptations of the principles of the presen invention the foregoing eccentric counterweight means will be in addition to the usual primaryflywheel of the machine although the rotational inertia forces of the counterweight means of the present invention may somewhat reduce the requirement for rotational inertia energy in the principal flywheel of the machine.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a general front elevational 'view of one type of power press to which the principles of the present DESCRIPTION OF THE ILLUSTRATED EMBODIMENT FIG. 1 shows a conventional straight side power press having a bed 10, side frames 11 and 12, a crown l3, and a vertical reciprocable slide 14 driven from a main shaft 15 by reciprocable connections 16 and 17. In FIG. 1 the numeral 18 designates a housing which contains a conventional flywheel mounted on main shaft 15 and the usual clutch and brake mechanism (not shown) is interposed between the flywheel and main shaft 15.
It will be understood that a die set will be employed in the power press of FIG. 1 with the stationary unit thereof secured to a bolster plate 20 on bed 10 and with a movable member of the die set secured to the under side of slide 14.
Referring now to FIG. 2, crown 13 includes upper and lower walls 22 and 23 and, as shown in FIG. 3, front and rear walls 24 and 25. In the present instance, main shaft 15 is supported by a series of six bearings 27 which are carried by vertical wall members designated 28, 29-and 30 in FIG. 2, the wall membersbeing welded to top wall 22 and front and rear walls 24 and 25.
The press shown herein by way of example, has a pair of driving eccentrics 32 on main shaft 15 which are provided with connections 33 to slide 14 for reciprocating the latter vertically. A conventional counterbalancing cylinder which is fixed to upper wall 13 is shown at 35 and has a shaft connection 36 to slide 14. All of the foregoing is conventional construction in power presses of this general type.
In the machine shown and described herein to illustrate the principles of the present invention, main shaft is provided with a pair of semi-circular counterweights 40 which are fixed to the main shaft by bearing caps 41. In the position of parts illustrated in FIGS. 2 and 3, the eccentrics 32 and slide 14 are at top dead center and the semi-circular counterweights 40 are at bottom dead center.
A countershaft 43, supported in the left-hand vertical wall member 29 and a further similar vertical wall member 44, is connected to main shaft 15 by gears 45 and 46 of equal pitch diameters so that countershaft 43 rotates synchronously with main shaft 15 but in the opposite direction. A further semi-circular counterweight 50 is fixed to countershaft 43 by means of a bearing cap 51 and is likewise in its bottom dead center position when eccentrics 32 and slide 14 are in their upper positions.
From the foregoing it will be noted that the two counterweights 40 and counterweight 50 will all move upwardly as the slide 14, the eccentrics 32 and the connections 33 move downwardly, and vice versa. Thus the vertical inertia components of the three counter weights act in opposition to the vertical inertia of slide 14, eccentrics 32, connections 33 and the movable die member carried by slide 14. Furthermore, since counterweight 50 rotates reversely to counterweights 40, the lateral component of counterweight 50 acts in opposition to the lateral components of counterweights 40. As indicated earlier herein, the lateral components of counterweights 40 are in part counterbalanced by the lateral components of the eccentrics 32 and the connections 33 and, accordingly, the mass of counterweight 50 will be substantially less than the mass of counterweights 40.
For ease of description and by way of example, reference has been had herein to a vertical movable slide and to counterweight means movable to properly neutralize the inertia forces of a vertically movable slide. However, it is to be understood that the same principles may be applied to a power press slide which reciprocates in a horizontal direction, or in any other direction. Furthermore, while the counterweight arrangement of the present invention may aim at substantially full counter-balancing of the objectionable inertia forces of the slide of a power press, various conditions and limitations may dictate something less than such full neutralization without departing from the principles of the present invention.
A preferred embodiment has been described herein and shown in the accompanying drawings to illustrate the underlying principles of the invention but it is to be understood that numerous modifications may be made without departing from the broad spirit and scope of the invention.
I claim:
1. In a power press having a frame including a bed, a slide reciprocable with respect to said bed and connectible with a movable die member to effect working strokes thereof, a continuously rotating shaft having eccentric drive means and means connecting the same to said slide for reciprocating the same; first counterweight means rotatable with said drive shaft and having its center of gravity opposite to that of said eccentric drive means whereby said first counter-weight means moves in opposition to the movement of said slide, and second counterweight means synchronized with said first counterweight means to rotate continuously at the same speed but in the opposite direction, the center of gravity of said second counterweight means being offset from its axis of rotation in the same direction as that of the first counterweight means with respect to the direction of the slide, whereby said two counterweight means move in unison with respect to the direction of said slide but oppositely with respect to a direction at right angles thereto.
2. Apparatus according to claim 1 wherein said first counterweight means is mounted on said drive shaft for rotation therewith.
3. Apparatus according to claim 1 including'a countershaft and transmission means connecting the same to said drive shaft for rotation at a one to one ratio therewith but in the opposite direction, said second counterweight means being mounted on said countershaft for rotation therewith.
4. Apparatus according to claim 2 including a countershaft and transmission means connecting the same to said drive shaft for rotation at a one to one ratio therewith but in the opposite direction, said second counterweight means being mounted on said countershaft for rotation therewith.

Claims (4)

1. In a power press having a frame including a bed, a slide reciprocable with respect to said bed and connectible with a movable die member to effect working strokes thereof, a continuously rotating shaft having eccentric drive means and means connecting the same to said slide for reciprocating the same; first counterweight means rotatable with said drive shaft and having its center of gravity opposite to that of said eccentric drive means whereby said first counter-weight means moves in opposition to the movement of said slide, and second counterweight means synchronized with said first counterweight means to rotate continuously at the same speed but in the opposite direction, the center of gravity of said second counterweight means being offset from its axis of rotation in the same direction as that of the first counterweight means with respect to the direction of the slide, whereby said two counterweight means move in unison with respect to the direction of said slide but oppositely with respect to a direction at right angles thereto.
2. Apparatus according to claim 1 wherein said first counterweight means is mounted on said drive shaft for rotation therewith.
3. Apparatus according to claim 1 including a countershaft and transmission means connecting the same to said drive shaft for rotation at a one to one ratio therewith but in the opposite direction, said second counterweight means being mounted on said countershaft for rotation therewith.
4. Apparatus according to claim 2 including a countershaft and transmission means connecting the same to said drive shaft for rotation at a one to one ratio therewith but in the opposite direction, said second counterweight means being mounted on said countershaft for rotation therewith.
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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2806584A1 (en) * 1978-02-16 1979-08-23 Kaiser Kg Otto Eccentric press counterbalance mechanism - has movable mass element with assembly driven in opposite phase relative to press main shaft
FR2523508A1 (en) * 1982-03-16 1983-09-23 Aida Eng Ltd BALANCING DEVICE FOR MECHANICAL PRESS
US4800852A (en) * 1986-05-12 1989-01-31 Tecumseh Products Company Inline counterbalance weight system for a single cylinder engine
US5316519A (en) * 1992-05-07 1994-05-31 Johnson Farm Machinery Company, Inc. Multiple weight drum shaker
US6330848B1 (en) * 1998-05-30 2001-12-18 Kanefusa Kabushiki Kaisha Circular saw cutting machine
US20060037490A1 (en) * 2004-08-18 2006-02-23 Fmc Technologies, Inc., Corporation Of The State Of Delaware Juice extractor with counterweight operatively engaged with camshaft
US20070000224A1 (en) * 2004-09-14 2007-01-04 Westside Equipment Small scale tomato harvester

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2188146A (en) * 1937-06-08 1940-01-23 American Brake Shoe & Foundry Machine for manufacturing brake shoe inserts
US2321325A (en) * 1940-08-03 1943-06-08 Henry & Wright Mfg Company Dieing machine
US2407102A (en) * 1943-06-04 1946-09-03 Ryder Elmer Internal-combustion engine
US2819618A (en) * 1953-05-04 1958-01-14 Slusher Frank Counterbalancing apparatus for reciprocating slide
US3085457A (en) * 1960-03-11 1963-04-16 Champlain Company Inc High speed web stopping mechanism
US3203274A (en) * 1961-06-29 1965-08-31 Linde Eismasch Ag Balance weight arrangement for reciprocating engines
US3422688A (en) * 1965-12-02 1969-01-21 Bruderer Ag Arrangement for counterbalancing the forces in crankshaft driven machines

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2188146A (en) * 1937-06-08 1940-01-23 American Brake Shoe & Foundry Machine for manufacturing brake shoe inserts
US2321325A (en) * 1940-08-03 1943-06-08 Henry & Wright Mfg Company Dieing machine
US2407102A (en) * 1943-06-04 1946-09-03 Ryder Elmer Internal-combustion engine
US2819618A (en) * 1953-05-04 1958-01-14 Slusher Frank Counterbalancing apparatus for reciprocating slide
US3085457A (en) * 1960-03-11 1963-04-16 Champlain Company Inc High speed web stopping mechanism
US3203274A (en) * 1961-06-29 1965-08-31 Linde Eismasch Ag Balance weight arrangement for reciprocating engines
US3422688A (en) * 1965-12-02 1969-01-21 Bruderer Ag Arrangement for counterbalancing the forces in crankshaft driven machines

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2806584A1 (en) * 1978-02-16 1979-08-23 Kaiser Kg Otto Eccentric press counterbalance mechanism - has movable mass element with assembly driven in opposite phase relative to press main shaft
FR2523508A1 (en) * 1982-03-16 1983-09-23 Aida Eng Ltd BALANCING DEVICE FOR MECHANICAL PRESS
US4481834A (en) * 1982-03-16 1984-11-13 Aida Engineering, Ltd. Balance device for a mechanical press
US4800852A (en) * 1986-05-12 1989-01-31 Tecumseh Products Company Inline counterbalance weight system for a single cylinder engine
US5316519A (en) * 1992-05-07 1994-05-31 Johnson Farm Machinery Company, Inc. Multiple weight drum shaker
US6330848B1 (en) * 1998-05-30 2001-12-18 Kanefusa Kabushiki Kaisha Circular saw cutting machine
US20060037490A1 (en) * 2004-08-18 2006-02-23 Fmc Technologies, Inc., Corporation Of The State Of Delaware Juice extractor with counterweight operatively engaged with camshaft
WO2006023217A1 (en) * 2004-08-18 2006-03-02 Fmc Technologies, Inc. Juice extractor with counterweight operatively engaged with camshaft
US7305918B2 (en) 2004-08-18 2007-12-11 Fmc Technologies, Inc. Juice extractor with counterweight operatively engaged with camshaft
US20070000224A1 (en) * 2004-09-14 2007-01-04 Westside Equipment Small scale tomato harvester
US7921628B2 (en) 2004-09-14 2011-04-12 Westside Equipment Company Small scale tomato harvester

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