US2734387A - Jansen - Google Patents

Jansen Download PDF

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Publication number
US2734387A
US2734387A US2734387DA US2734387A US 2734387 A US2734387 A US 2734387A US 2734387D A US2734387D A US 2734387DA US 2734387 A US2734387 A US 2734387A
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United States
Prior art keywords
spring
lever arm
lever
arm
torque
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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.)
Expired - Lifetime
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English (en)
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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H9/00—Details of switching devices, not covered by groups H01H1/00 - H01H7/00
    • H01H9/0005—Tap change devices
    • H01H9/0027—Operating mechanisms
    • 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
    • Y10T74/18888—Reciprocating to or from oscillating
    • 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
    • Y10T74/20—Control lever and linkage systems
    • Y10T74/20576—Elements
    • Y10T74/20582—Levers
    • Y10T74/2063—Stops

Definitions

  • Both kinds of spring drives show a power or torque versus travel diagram in which the movable parts of the load changeover switch obtain their greatest velocity only after completing half or more ofi their total travel;
  • the current interruptingprocess on the maincontacts of the load changeover-switch which is especially. important at great current intensity; must be mastered. however in the first quarter of the total movement.
  • the safe arc breaking eifect' ishowever dependent on. the opening velocity of the interrupting eontactswhich in turn depends on the velocity which the spring drive has imparted to the movable load changeover switclrpa'tts up to the-interrupting moment.
  • Both drives must, therefore, be considerably overdirnensioned in order to have discharged to themovable load changeover switch part at this deciding moment as much accelerating power, as is required for safe arc extinguishing.
  • This entails considerable stresses of' the mechanical construction elements of the. load changeover switch, if the remaining 85% or 70% respectively of'the spring drive working power are discharged and must be annihilated. by braking,
  • this disadvantage is removed by discharging the spring action driving gear F to the driving shaft M of the load changeover switch through a lever gear which from the initial position to the final position, produces a continually variable torque ratio, either by means of variable lever arm lengths or by means of variable effective angles of the driving lever in relation to the driven one. It is with good result that these two effects (variable lever arm and variable eflective 2. angle) can be used at the same time.
  • the variationof the leverlengths and-the effective angles can be influenced by the design in such a way that with a given spring power curve (e. g. continually decreasing from 100% force in.
  • Fig. 1 is a part elevational andpart diagrammatic view of spring actiondriving gear. with variable torque en1bodying the invention.
  • Figs. 2 and 3 are views of charts showing various torque conditions present during the operationv of the driving gear.
  • Fig. 1 shows the lever mechanism of such a. spring action driving gear.
  • the driven organ A of the lever transmission .gear connected with the shaft of the movable load changeover switch. part, revolves around the axis M of the load changeover switch; in theillustrated example from the initial position to the final position by an angle of Thesaid organconsistsof a lever with an oblong hole guiding L, in which a roller R is gliding which in turn is mounted on the driving.
  • lever B rotatable around. the auxiliary axis m.
  • the driving lever B In the position represented in Fig. l, the driving lever B is fixed on one side by the spring butter Em, and on the other side by the latch Kli.
  • the force of the spring action driving gear F is acting in the direction of the arrow Pf on the driving lever B, but can only become eifective if the latch K11 is disengaged. This is done, as customary on other spring drives too, by the organ C effecting the charging motion of the gear spring F, after the full' spring tension is attained, After the latch is disengaged, the spring force Pf turns the driving lever B from left to. right until resting on the right, bufier Epa. In this position, B is locked by the right latch Klz. During this movement, the roller R has proceeded on a circular path. to the right position. During this action, the lever arm m-R of the driving lever B remained unchanged.
  • the lever arm M-R, however, of the driven organ A was shortened, at first quicker, then slower, by gliding of the roller R in the oblong hole L to the middle position, and prolonged again, first slower, thenquicker, by gliding from there to the final'position.
  • the hereby eflfected torque transmission ratio Uh varies as shown, the conditions being as drafted in Fig. 2, between. in the initial and final positions and 50% in the middle position.
  • Parallel with the variation of the lever arm MR a variation of the effective angle has taken place, the roller R acting upon the radial flank of the. oblong hole L.
  • variable torque transmission ratio arises which varies, under the conditions shown in Fig:- 2, in the sameway between 100% and 50%.
  • the two variable transmission ratios and Uw compose in the total transmission ratio AwM Ami representing. a portion, varying from one position to the other, of the angle of the driving lever B, and Aw representing the respective portion of the angle of the driven lever A.
  • the torque ratio U which is shown in Fig. 3 by a dotted line, varies from the initial position through the middle position to the final position in the proportion 100%:25%:100%.
  • the operation of the mechanism is as follows:
  • the crank 1 rotates in a clockwise direction, as indicated by the arrow. It is driven by hand or motor.
  • the arm C is pivoted.
  • This arm is in pivoted engagement with one end of a lever 2 which is rotatably supported at its other end at m.
  • the drive lever arm B is also rotatably supported at 111.
  • These two arms 2 and B are loaded by a substantially V-shaped spring P which presses against pins B and 2 respectively, and strives to push these two arms 2 and B together, i. e. to cause them to coincide.
  • On the free end of drive arm B there is provided a projection 3 which serves to work alternately with the pawls Klr and Klz. These two pawls turn around a common fulcrum 4. In the position shown, the arm B is locked by the pawl Kli and the stationary end stop Epr.
  • the driven lever arm A is pivoted to the drive lever arm B by a pin R and a longitudinal slot L in the arm A.
  • This lever arm A acts directly on the load switch, not shown, the shaft of which is designated M and is perpendicular to the plane of the sheet of drawing.
  • the load switch is also moved about 90 or more from one operating position into the next operating position.
  • the drive lever arm B is now held fast by the pawl K12 and the stationary end stop Epz.
  • the same operation now takes place in reverse in such manner that a projection on lever C releases the pawl Klz in the same manner as the projection 5 previously released pawl K11.
  • the stop 8 on the trip-lever 7 acts in an analogous manner by means of a counterstop 11 on pawl Klz.
  • Spring-pressed driving mechanism with variable torque for load changeover switches including, in combination, a crank, a fixed shaft member, a lever arm having one end pivotally mounted on said shaft member, another lever arm having one end pivotally mounted on shaft member and spaced from said first-named lever arm, a spring member supported on the shaft member and operatively connected to said lever arms for continually pressing said lever arms into alignment with each other, another lever arm flexibly connected to one end of the first-named lever arm and to a changeover switch, an actuating arm connected at one end to said crank and at its other end to one end of said second-named lever arm, latching devices for holding said first-named lever arm in moved position when moved by said spring, and tripping means operatively connected to said actuating arm and means for releasing the latter.
  • Spring-pressed driving mechanism with variable torque for load changeover switches including, in combination, a fixed shaft member, a driving lever arm having one end pivotally mounted on said shaft member, a pin carried adjacent the free end of said arm, a projection on the free end of said arm, another lever arm having one end pivotally mounted on said shaft member and spaced from said driving lever arm, a spring member supported on the shaft member and operatively connected to the lever arms for continually pressing said lever arms into alignment with each other, a driven lever arm having a slotted portion at one end flexibly connected to the pin on said driving lever arm, the other end of said driven lever arm being operatively connected to a rotatable shaft of a load changeover switch, an elongated actuating arm pivotally connected at one end to said crank and pivotally connected at its other end to the other end of said second-named lever arm, spaced projections on one edge of said actuating arm, spaced stop members at the ends of the path of movement of said driving lever arm, pivotal pawl members interposed between said top members
US2734387D 1951-03-22 Jansen Expired - Lifetime US2734387A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB6936/51A GB705845A (en) 1951-03-22 1951-03-22 Spring action driving gear with variable torque for on-load changeover switches of regulating transformers

Publications (1)

Publication Number Publication Date
US2734387A true US2734387A (en) 1956-02-14

Family

ID=9823547

Family Applications (1)

Application Number Title Priority Date Filing Date
US2734387D Expired - Lifetime US2734387A (en) 1951-03-22 Jansen

Country Status (5)

Country Link
US (1) US2734387A (fr)
BE (1) BE501371A (fr)
CH (1) CH296808A (fr)
FR (1) FR1034833A (fr)
GB (1) GB705845A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3092344A (en) * 1961-05-11 1963-06-04 Ampex Strip tensioning apparatus
US20160258385A1 (en) * 2015-03-02 2016-09-08 The Boeing Company Dual-Cam Bellcrank Mechanism

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US164212A (en) * 1875-06-08 Improvement in treadle mechanisms for printing-presses and other purposes
US795235A (en) * 1904-04-09 1905-07-18 Charles M Gould Electrical switch and operating mechanism therefor.
US876355A (en) * 1907-04-29 1908-01-14 Sheffield Car Co Transmission-gear.
US1540247A (en) * 1922-11-08 1925-06-02 Charles L Bowman Clutch-shifting device
USRE18933E (en) * 1933-09-05 Lever mechanism
US2009383A (en) * 1934-11-01 1935-07-30 Gen Electric Transformer tap-changing apparatus
US2177109A (en) * 1935-04-29 1939-10-24 Allis Chalmers Mfg Co Voltage regulator
US2231696A (en) * 1938-12-28 1941-02-11 Fisher Governor Co Gas pressure booster system
US2427621A (en) * 1943-09-11 1947-09-16 Automatic Elect Lab Remote-control system
US2453560A (en) * 1943-09-28 1948-11-09 Republie Aviat Corp Airfoil operating mechanism
GB621078A (en) * 1946-11-18 1949-04-04 British Thomson Houston Co Ltd Improvements in and relating to mechanism for operating speed varying means for rotating devices
US2513677A (en) * 1949-03-05 1950-07-04 Mcgraw Electric Co Multiple step switch

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US164212A (en) * 1875-06-08 Improvement in treadle mechanisms for printing-presses and other purposes
USRE18933E (en) * 1933-09-05 Lever mechanism
US795235A (en) * 1904-04-09 1905-07-18 Charles M Gould Electrical switch and operating mechanism therefor.
US876355A (en) * 1907-04-29 1908-01-14 Sheffield Car Co Transmission-gear.
US1540247A (en) * 1922-11-08 1925-06-02 Charles L Bowman Clutch-shifting device
US2009383A (en) * 1934-11-01 1935-07-30 Gen Electric Transformer tap-changing apparatus
US2177109A (en) * 1935-04-29 1939-10-24 Allis Chalmers Mfg Co Voltage regulator
US2231696A (en) * 1938-12-28 1941-02-11 Fisher Governor Co Gas pressure booster system
US2427621A (en) * 1943-09-11 1947-09-16 Automatic Elect Lab Remote-control system
US2453560A (en) * 1943-09-28 1948-11-09 Republie Aviat Corp Airfoil operating mechanism
GB621078A (en) * 1946-11-18 1949-04-04 British Thomson Houston Co Ltd Improvements in and relating to mechanism for operating speed varying means for rotating devices
US2513677A (en) * 1949-03-05 1950-07-04 Mcgraw Electric Co Multiple step switch

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3092344A (en) * 1961-05-11 1963-06-04 Ampex Strip tensioning apparatus
US20160258385A1 (en) * 2015-03-02 2016-09-08 The Boeing Company Dual-Cam Bellcrank Mechanism
US9885314B2 (en) * 2015-03-02 2018-02-06 The Boeing Company Dual-cam bellcrank mechanism

Also Published As

Publication number Publication date
CH296808A (de) 1954-02-28
FR1034833A (fr) 1953-08-03
BE501371A (fr)
GB705845A (en) 1954-03-17

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