Circuit Breaker Motor and Handle Clutch

Reference is made to the below listed copending applications which are assigned to the same assignee as the present invention.

1. "Stored Energy Circuit Breaker" by A. E. Maier et al, Ser. No. 755,768, filed Dec. 30, 1976.

2. "Circuit Breaker Having Improved Movable Contact" by H. Nelson et al., Ser. No. 755,767, filed Dec. 30, 1976.

3. "Circuit Breaker Utilizing Improved Current Carrying Conductor System" by H. A. Nelson et al., Ser. No. 755,769, filed Dec. 30, 1976.

4. "Circuit Breaker With Current Carrying Conductor System Utilizing Eddy Current Repulsion" by J. A. Wafer et. al., Ser. No. 755,776, filed Dec. 30, 1976.

5. "Circuit Breaker Having Insulation Barrier" by A. E. Maier et al., Ser. No. 755,765, filed Dec. 30, 1976.

6. "Circuit Breaker With High Speed Trip Latch" by A. E. Maier et al., Ser. No. 755,766, filed Dec. 30, 1976.

7. "Circuit Breaker With Dual Drive Means Capability" by W. V. Bratkowski et al., Ser. No. 755,764, filed Dec. 30, 1976.

This invention relates generally to single or multi-pole circuit breakers, and more particularly to stored energy circuit breakers having manual and motor operated drive means.

The basic functions of circuit breakers are to provide electrical system protection and coordination whenever abnormalities occur on any part of the system. The operating voltage, continuous current, frequency, short circuit interrupting capability, and time-current coordination needed are some of the factors which must be considered when designing a breaker. Government and industry are placing increasing demands upon the electrical industry for interrupters with improved performance in a smaller package and with numerous new and novel features.

Stored energy mechanisms for use in circuit breakers of the single pole or multi-pole type have been known in the art. A particular construction of such mechanisms is primarily dependent upon the parameters such as rating of the breaker. Needless to say, many stored energy circuit breakers having closing springs cannot be charged while the circuit breaker is in operation. For that reason, some circuit breakers have the disadvantage of not always being ready to close in a moment's notice. These circuit breakers do not have, for example, an open-close-open feature which users of the equipment find desirable.

Another problem present in some prior art circuit breakers is that associated with matching the spring torque curve to the breaker loading. These prior art breakers utilize charging and discharging strokes which are each 180.degree.. The resulting spring torque curve is predetermined, and usually cannot be matched with the breaker loading. Such a predetermined curve mandates that the elements associated with the breaker be matched for this peak torque rather than be matched with the breaker load curve.

A desirable characteristic in these circuit breakers is for the current carrying parts to be electrically isolated from the operating mechanism of the breaker. By so isolating the current carrying parts, temporary emergency repairs to the operating mechanism may be undertaken.

Another desirable characteristic in these circuit breakers is to provide for both manual and motor driven operation of the operating mechanism. This dual capability should be provided so that critical alignment of the connection of the motor to the operating mechanism is not necessary, and this connection of the motor to the operating mechanism should also be capable of being easily installed in the field in the unlikely event of a motor failure.

In accordance with this invention, it has been found that a more desirable stored energy circuit breaker is provided which comprises stationary and movable contacts operable between open and closed positions with respect to the stationary contact. Means for effecting movement of the movable contact between the open and closed positions are included, and these movement effecting means include a rotatable drive shaft, a drive handle and a motor operator having a rotatable output shaft. A motor and handle clutch is secured to the drive shaft and permits rotation of the drive shaft in one direction and prohibits rotation of the drive shaft in a second direction opposite to the first direction. The motor and handle clutch also prohibits rotation of the drive handle upon rotation of the motor operator, and prohibits rotation of the motor operator upon rotation of the drive handle.

Reference is now made to the description of the preferred embodiment, illustrated in the accompanying drawings, in which:

FIG. 1 is an elevational sectional view of a circuit breaker according to the teachings of this invention;

FIG. 2 is an end view taken along line II--II of FIG. 1;

FIG. 3 is a plan view of the mechanism illustrated in FIG. 4;

FIG. 4 is a detailed sectional view of the operating mechanism of the circuit breaker in the spring discharged, contact open position;

FIG. 5 is a modification of a view in FIG. 4 with the spring partially charged and the contact in the open position;

FIG. 6 is a modification of the views illustrated in FIGS. 4 and 5 with the spring charged and the contact open;

FIG. 7 is a modification of the view of FIGS. 4, 5, and 6 in the spring discharged, contact closed position;

FIG. 8 is a modification of the view of FIGS. 4, 5, 6 and 7 with the spring partially charged and the contact closed;

FIG. 9 is a modification of the view of FIGS. 4, 5, 6, 7, and 8 with the spring charged and the contact closed;

FIG. 10 a plan view of a current carrying contact system;

FIG. 11 is a side, sectional view of the current conducting system;

FIG. 12 is a detailed view of the movable contact;

FIG. 13 is a side view of the cross arm structure;

FIG. 14 is a modification of the multi-pole contact structure;

FIG. 15 is an end view of the connection of the motor operator shaft to the drive shaft;

FIG. 16 is a modification of the view of FIG. 15;

FIG. 17 is a side view of the connection of the motor operator to the drive shaft;

FIG. 18 is a modification of the view of FIG. 17;

FIG. 19 is a modification of the view of FIG. 18, and

FIG. 20 is a detailed view of the motor and handle clutch.

Referring now more particularly to FIG. 1, therein is shown a circuit breaker utilizing the teachings of this invention. The circuit breaker 10 includes support 12 which is comprised of a mounting base 14, side walls 16, support walls 13, 15, and a frame structure 18 (see FIG. 2). The mounting base 14 and support walls 13, 15 are, in the preferred embodiment, molded of an electrically insulating material such as plastic. A pair of stationary contacts 20, 22 are disposed within the support 12, with the support walls 13, 15 disposed between adjacent pairs of stationary contacts 20, 22. Stationary contact 22 would, for example, be connected to an incoming power line (not shown), while the other stationary contact 20 would be connected to the load (not shown). Electrically connecting the two stationary contacts 20, 22 is a movable contact structure 24. The movable contact structure 24 comprises a movable contact 26, a movable arcing contact 28, a contact carrier 30 and crossbar insulator 64. The movable contact 26 and the arcing contact 28 are pivotally secured to the stationary contact 20, and are capable of being in open and closed positions with respect to the stationary contact 22. Throughout this application, the term "open" as used with respect to the contact positions means that the movable contacts 26, 28 are spaced apart from the stationary contact 22, whereas the term "closed" indicates the position wherein the movable contacts 26, 28 are contacting both stationary contacts 22 and 20. The movable contacts 26, 28 are mounted to and carried by the contact carrier 30 and crossbar insulator 64.

Also included within the circuit breaker 10 is an operating mechanism 32, a toggle means 34, and an arc chute 36 which extinguishes any arc which may be present when the movable contacts 26, 28 change from the closed to open position. A current transformer 38 is utilized to monitor the amount of current flowing through the stationary contact 20.

Electrically insulating the live elements, such as the contacts 26, 28 from the operating mechanism 32 and toggle means 34 is an insulating barrier 33. The barrier 33 is disposed intermediate the crossbar insulator 64 and the operating mechanism 32 and toggle means 34.

Referring now to FIG. 12, there is shown a detailed view of the movable contact 26. The movable contact 26 is of a good electrically conducting material such as copper, and has a contact surface 40 which mates with a similar contact surface 42 (see FIG. 1) of stationary contact 22 whenever the movable contact 26 is in the closed position. The movable contact 26 has a circular segment 44 cut out at the end opposite to the contact surface 40, and also has a slotted portion 46 extending along the movable contact 26 from the removed circular segment 44. At the end of the slot 46 is an opening 48. The movable contact 26 also has a depression 50 at the end thereof opposite the contact surface 40.

The circular segment 44 of the movable contact 26 is sized so as to engage a circular segment 52 which is part of the stationary contact 20 (see FIG. 11). The circular segment 44 and the slot 46 are utilized to clamp about the circular segment 52 to thereby allow pivoting of the movable contact 26 while maintaining electrical contact with the stationary contact 20. As shown in FIG. 11, the arcing contact 28 is designed similarly to the movable contact 26, except that the arcing contact 28 extends outwardly beyond the movable contact 26 and provides an arcing mating surface 54 which contact a similarly disposed surface 56 on the stationary contact 22. The arcing contact 28 and the movable contact 28 are mounted to, and carried by a contact carrier 30. A pin 58 extends through the openings 48 in the movable contact 26 and the arcing contact 28, and this pin 58 extends outwardly to, and is secured to, the contact carrier 30. The contact carrier 30 is secured by screws 60, 62 to a crossbar insulator and spring holder 64. The crossbar insulator and spring holder 64 is typically of a molded plastic. By so constructing the connections of the movable contact 26 to the contact carrier 30, the movable contacts 26 are permitted a small degree of freedom with respect to each other. To maintain contact pressure between the movable contact surface 40 and the stationary contact surface 42 when the movable contact 26 is in the closed position, a spring 66 is disposed within the recess 50 of the movable contact 26 and is secured to the spring holder 64 (see FIG. 10). The spring 66 resists the forces which may be tending to separate the movable contacts 26 from the stationary contact 22.

Also shown in FIG. 10 is a cross arm 68 which extends between the individual contact holders 64. The cross arm 68 assures that each of the three poles illustrated will move simultaneously upon movement of the operating mechanism 32 to drive the contacts 26, 28 into closed or open position. As shown in FIG. 13, the cross arm 68 extends within an opening 70 in the crossbar insulator 64 and through openings 69, 71 in support walls 13, 15 (see FIG. 2). A pin 72 extends through an opening 74 in the crossbar insulator 64 and an opening 76 in the cross arm 68 to prevent the cross arm 68 from sliding out of the crossbar insulator 64. Also attached to the cross arm 68 are pusher rods 78. The pusher rods 78 have an opening 80 therein, and the cross arm 68 extends through the pusher rod openings 80. The pusher rod 78 has a tapered end portion 82, and a shoulder portion 84. The pusher rod 78, and more particularly the tapered portion 82 extends into openings 86 within the support walls 13, 15 (see FIG. 2) and disposed around the pusher rods 78 are springs 88. These springs 88 function to exert a force against the shoulder 84 of the pusher rod 78, thereby biasing the cross arm 68 and the movable contacts 26 in the open position. To close the movable contacts 26, it is necessary to move the cross arm 68 such that the pusher rods 78 will compress the spring 88. This movement is accomplished through the operating mechanism 32 and the toggle means 34.

Referring now to FIGS. 2-4, there is shown the toggle means 34 and the operating mechanism 32. The toggle means 34 comprise a first link 90, a second link 92, and a toggle lever 94. The first link 90 is comprised of a pair of spaced-apart first link elements 96, 98, each of which have a slot 100 therein. The first link elements 96, 98, extend through an opening 87, 89 respectively in the insulating barrier 33, and within openings 75, 77 in the support walls 13, 15 respectively. The first link elements 96, 98 and the slot 100 engage the cross arm 68 intermediate the three crossbar insulators 64, and provide movement of the cross arm 68 upon the link 90 going into toggle position. The location of the link elements 96, 98 intermediate the crossbar insulators 64 reduces any deflection of the cross arm 68 under high short circuit forces. Also, the use of the slot 100 to connect to the cross arm 68 provides for easy removal of the operating mechanism 32 from the cross arm 68. Although described with respect to the three-pole breaker illustrated in FIG. 2, it is to be understood that this description is likewise applicable to the four-pole breaker illustrated in FIG. 14. With the four-pole breaker, the first link elements 96, 98 are disposed between the interior crossbar insulators 186, 188 and the exterior insulators 187, 189. Also, if desired, additional links or additional springs (not shown) may be disposed between the interior insulators 186, 188. The second link 92 comprises a pair of spaced-apart second link elements 102, 104 which are pivotally connected to the first link elements 96, 98, respectively at pivot point 103. The toggle lever 94 is comprised of a pair of spaced-apart toggle lever elements 106, 108 which are pivotally connected to the second link elements 102, 104 at pivot point 107, and the toggle lever elements 106, 108 are also pivotally connected to the mechanism frame 18 at pivotal connection 110. Fixedly secured to the second link elements 102, 104 are aligned drive pins 112, 114. The drive pins 112, 114 extend through aligned openings 116, 118 in the side walls 18 adjacent to the follower plates 120, 122.

The operating mechanism 32 is comprised of a drive shaft 124 rotatable about its axis 125 having a pair of spaced apart aligned cams 126, 128 secured thereto. The cams 126, 128 are rotatable with the drive shaft 124 and are sgaped to provide a constant load on the turning means 129. The turning means 129 comprise a drive handle 131 which is secured to the drive shaft 124, and a motor operator 133 having an output shaft 135 which is capable of engaging the end 137 of the drive shaft 124 to impart rotation thereto. For most efficient operation, means 139 for preventing rotation of the drive handle 131 upon rotation of the drive shaft 124 by the motor operator 133 are included

FIG. 20 illustrates in detail the prevention means 139. The preventing means 139 comprises a motor and handle clutch which has a drive shaft drum 201 secured to the drive shaft 124 by the pin 203. Secured to the drive shaft drum 201, and thereto the drive shaft 124, is the drive sleeve 205. Disposed on the drive shaft 124 adjacent to the drive shaft drum 201 is the motor drum 207. Positioned at one end of the motor drum 207 are connection means 209 typical of which is a pin, which is utilized for connecting the motor drum 207 to the output shaft 135 of the motor operator 133, as will hereinafter be explained in greater detail. Coupling the drive shaft drum 201 and the motor drum 207 is a motor drive spring 211 which is typically a clutch spring. The typical clutch spring which couples two elements together operates so that, upon rotation in one direction, the two elements rotate together whereas, upon rotation of one element in the opposite direction, only that element rotates freely and the other element remains stationary. This is the result of the winding of the helical spring, for the rotation of the element in the direction which causes the spring to tighten and attempt to become smaller, it will grab both elements and cause them to rotate together, while rotation in the other direction against the helical winding will cause the spring to expand, thereby permitting free-wheeling movement, or slipping, of the element with respect to the spring. Throughout this application, the term "grabbing" will be utilized whenever the two elements are rotated in a manner where the spring is contracted and therefore rotating both elements, whereas the term "slipping" will be utilized for those applications where the element is rotating so as to expand the spring and is free-wheeling therein, with the result that the element to which it is coupled remains stationary.

The coupling of the motor drum 207 to the drive shaft drum 201 is such that, if the motor drum 207 is rotating first in the positive direction, the motor drive spring 211 will grab the drive shaft drum 201 and cause it to rotate with the motor drum 207, and the rotation of the drive shaft drum 201 will cause the drive shaft 124 to which it is secured to rotate therewith. This occurs whenever the motor operator 133 is operating and causing rotation of the motor operator output shaft 135. The motor drive spring 211 is also coupled to the motor drum 207 and the drive shaft drum 201 such that, if the drive shaft drum 201 is the first to rotate, the motor drive spring 211 will slip with respect to these two elements, thereby maintaining the motor drum 207 in its stationary position. This prevents rotation of the motor operator output shaft 135 upon rotation of the drive shaft 124 by the handle 131.

Disposed adjacent to the drive sleeve 205 is a rotatable handle drive drum 213. Coupling the drive sleeve 205 and the handle drive drum 213 is a handle drive spring 215 which likewise will typically be a clutch spring. The handle drive spring 215 grabs the handle drive drum 213 and the drive sleeve 205 upon rotation of the handle 131 as it is charging up the drive shaft 124, and the handle drive spring 215 slips upon initial rotation of the drive sleeve 205 so as to maintain the handle drive drum 213 in its stationary position. The handle drive drum 215 is fixedly secured to a hub 217, which in turn is fixedly secured to the drive handle 131. Also coupled to the drive sleeve 205, by an anchor spring 219, is a brake drum 221, which is stationary and does not rotate. The brake drum 221 would be, for example, physically secured to the side wall 18 of the circuit breaker to maintain its spatial location. The anchor spring 219 would likewise be a clutch spring and operate similarly to the motor drive spring 211. A biasing spring 223 would be disposed adjacent to the hub 217, and would bias the hub 217, and the drive handle 131 secured thereto, for rotation in the direction opposite to the direction of rotation for charging up of the drive shaft 124.

The operation of the prevention means 139 is as follows, assuming that charging of the spring means 148 occurs while turning the drive shaft 124 in the clockwise direction (into the top of the drawing as shown). The drive shaft 124 would, to charge the spring means 148 completely, rotate about 360.degree.. This rotation would be accomplished, for example, by moving the drive handle 131 through an arc distance of 90.degree. four times, although other length of strokes and the number thereof may be utilized. Upon movement of the drive handle 131 for the first stroke, the hub 217 and the handle drive drum 213 which is secured thereto also rotate clockwise. As the handle drive drum 213 is the member initially rotating, the handle drive spring 215 is contracted and grabs the drive sleeve 205, causing it to rotate with the handle drive drum 213. The clockwise rotation of the drive sleeve 205 causes a corresponding clockwise rotation of the drive shaft drum 201 and the drive shaft 124 which are secured thereto by the pin 203. At the same time, since the drive shaft drum 201 is the initial rotating element, the motor drive spring 211 slips with respect to the drive shaft drum 201 and the motor drum 207, with the result that the motor drum 207 remains stationary and does not cause a rotation of either the motor drum 207 itself, nor the motor operator output shaft 135 to which it is engaged.

After the drive handle 131 has completed its initial stroke, it is rotated in a counterclockwise direction so as to enable it to be moved back into position to continue charging of the spring means 148. Upon this counterclockwise rotation, the hub 217 and the handle drive drum 213 likewise move in a counterclockwise direction. However, the counterclockwise rotation of the handle drive drum 213 expands the handle drive spring 215, causing it to slip with respect to the handle drive drum 213 and the drivesleeve 205. This slipping of the handle drive spring 215 prevents counterclockwise rotation of the drive sleeve 205, so that the drive sleeve 205, the drive shaft drum 201, and the drive shaft 124 do not move in a counterclockwise direction, which would then tend to discharge the spring means 148. As an added precaution against the possibility of discharging the spring means 148 upon cocking of the drive handle 131, any counterclockwise movement of the drive sleeve 205 will cause a contraction and grabbing of the anchor spring 219 against the drive sleeve 205 and the brake drum 221. As the brake drum 221 is fixed in its location, by means such as a pin (not shown) secured to the side wall 18, the drive sleeve 205 is again prohibited from counterclockwise rotation. After the drive handle 131 has been cocked, it again is rotated in the clockwise direction to charge the spring means 148 as has been heretofore described.

If, instead of utilizing the drive handle 131 to rotate the drive shaft 124, the motor operator, and more particularly the motor operator output shaft 135 is utilized, the operation proceeds as follows. The clockwise rotation of the motor operator output shaft 135, which engages the pin 209, causes a clockwise rotation of the pin 209 and the motor drum 207 which is secured thereto. The clockwise rotation of the motor drum 207 causes a contraction of the motor drive spring 211, causing it to grab both the motor drum 207 and the drive shaft drum 201. This grabbing by the motor drive spring 211 causes the drive shaft drum 201 to rotate with the motor drum 207, and also causes the drive shaft 124 secured to the drive shaft drum 201 to rotate, thereby causing a charging of the spring means 148. Additionaly, the rotation of the drive shaft drum 201 in the clockwise direction causes a clockwise rotation of the drive sleeve 205, which is secured to the drive shaft drum 201. This initial rotation of the drive sleeve 205 causes an expansion of both the anchor spring 219 and the handle drive spring 215, which causes these springs to slip with respect to the brake drum 221 and the handle drive drum 213 respectively. This slipping prevents a clockwise rotation of the handle drive drum 213, the hub 217, and the drive handle 131, resulting in the non-movement of the drive handle 131 upon rotation of the drive shaft 124 by the motor operator output shaft 135. As the motor operator output shaft 135 rotates in only the clockwise direction, there is no recocking requied to continue charging of the spring means 148. In the extremely unlikely event of a counterclockwise rotation of the motor operator output shaft 135, this counterclockwise rotation would cause a corresponding counterclockwise rotation of the pin 209 and the motor drum 207. However, this counterclockwise rotation of the motor drum 207, as the initial rotation, will expand the motor drive spring 211, causing it to slip and thereby not cause a counterclockwise rotation of the drive shaft drum 201. As the motor drum 207 is not fixedly secured to the drive shaft 124, its rotation does not cause a corresponding rotation of the drive shaft 124, but instead the drive shaft 124 only rotates upon rotation of the drive shaft drum 201, which does not occur as a result of rotation of the motor drum 207 unless the motor drive spring 211 grabs the two members. In this manner, the rotation of the drive shaft 124 can be accomplished by either the drive handle 131 or the motor operator output shaft 135 independently of each other, and the rotation is accomplished by not rotating either the drive handle 131 or the motor operator output shaft 135 upon rotation of the other member.

The motor operation 133 is comprised of a gear motor 141 which rotates a gear motor shaft 143 which is connected, for a simplified example, to a pair of cooperating gears 147, 149 within the gear box 145, The motoroperator output shaft 135 is connected to the gear 149, and is turned upon rotation of the gear 149. Upon activation of the gear motor 141, the gear motor shaft 143 is rotated, causing the rotation of gear 147 which is secured thereto. The interaction of gear 147 with gear 149 through gear teeth 113, 115 causes a corresponding rotation rotate the gear 149. The rotation of the gear 149 causes a rotation of the motor operator output shaft 135 which is secured thereto, and this motor operator output shaft 135 is capable of engaging the end 132, of the motor drum 207 to provide rotation thereto. The connection of the motor oprator output shaft 135 to the motor drum 207 is such that the motor operator 133 is capable of being plugged into the motor drum 207 with a minimum of effort. Referring to FIGS. 15-19, therein is shown a detailed view of some of the possible connections of the motor operator output shaft 135 to the end 137 of the motor drum 207. In FIGS. 15 and 17, it is shown that the end 137 of the motor drum 207 has a tongue 117 extending outwardly therefrom, and the motor operator output shaft 135 has a pair of space-apart, parallel fingers 119 which extends outwardly from the output shaft 135 and which engage the tongue 117 of the motor drum 207 on opposite sides thereof. The fingers 119 are such that, upon rotation of the output shaft 135, they engage the tongue 117 and cause it to rotte therewith. This rotation of the tongue 117 causes a rotation of the motor drum 207 of which the tongue 117 is a part, thereby providig rotation of the drive shaft 124 to power the operating mechanism 1132, as heretofore described.

FIGS. 16, 18 and 19 provide a modification of this tongue and finger arrangement previously described. In FIG. 16, it is shown that, instead of having a tongue 117, the output end 137 of the motor drum 207 is provided with a pair of openings 121, and disposed within these openings are a pair of pins 123 which are part of the motor operator output shaft 135 and which extend outwardly therefrom. The pins 123 cause rotation of the motor drum 207 upon rotation of the output shaft 135. FIG. 19 illustrates a modification of the pin and opening combination connection previously described. In this modification, the pins 157 are secured to, and extend outwardly from the end 137 of the motor drum 207, and openings 159 are included within the motor operator output shaft 135. This combination also functions to provide rotation of the motor drum 207 upon rotation of the motor operator output shaft 135. The pins 157 within the openings 159 are rotated upon rotation of the motor operator output shaft 135, causing a corresponding rotation of the motor drum 207. In these various means for connecting the motor operator 133 to the motor drum 207, it can be seen that the motor operator is capable of being plugged into the motor drum 207 in an easily installed manner, and one that does not require the dismantling of the circuit breaker 10 or operating mechanism 132.

The operating mechanism 32 also includes the follower plates 120, 122 which are fixedly secured together by the follower plate connector 130 (see FIG. 3). Fixedly secured to the follower plates 120, 122 is a cam roller 132 which also functions in latching the follower plates 120, 122 in the charged position, as will be hereinafter described. Also secured to each follower plate 120, 122 (FIG. 2) is a drive pawl 134, 136, respectively, which is positioned adjacent to the drive pins 112, 114. The drive pawls 134, 136 are pivotally secured to the follower plates 120, 122 by pins 138, 140, and are biased by the springs 142, 144.

The follower plates 122, 120 (FIG. 4) are also connected by a connecting bar 146 which extends between the two follower plates 120, 122, and pivotally connected to the connecting bar 146 are spring means 148. Spring means 148 is also pivotally connected to the support 12 by connecting rod 150. If desired, indicating apparatus 152 (see FIG. 2) may be incorporated within the breaker 10 to display the positions of the contacts 26, 28 and the spring means 148.

The operation of the circuit breaker can be best understood with reference to FIGS. 3-9. FIGS. 4-9 illustrate, in sequence, the movement of the various components as the circuit breaker 10 changes position from spring discharged, contact open, to spring charged, contact closed positions. In FIG. 4, the spring 148 is discharged, and the movable contact 26 is in the open position. Although the contacts 20, 22, and 26, 28 are not illustrated in FIGS. 4-9, the cross arm 68 to which they are connected is illustrated, and it is to be understood that the position of the cross arm 68 indicates the position of the movable contact 26 with respect to the stationary contact 22. To begin, the drive shaft 124 is rotated in the clockwise direction by the turning means 129. As the drive shaft 124 rotates, the cam roller 132 which is engaged therewith, is pushed outwardly a distance equivalent to the increased diameter portion of the cam. FIG. 5 illustrates the position of the elements once the cam 126 has rotated about its axis 125 approximately 180.degree. from its initial starting position As can be seen, the cam roller 132 has moved outwardly with respect to its initial position. This movement of the cam roller 132 has caused a rotation of the follower plate 120 about is axis 107, and this rotation has stretched the spring 148 to partially charge it. Also to be noted is that the drive pawl 134 has likewise rotated along with the follower plate 120. (The preceding, and all subsequent descriptions of the movements of the various components will be made with respect to only those elements viewed in elevation. Most of the components incorporated within the circuit breaker preferably have corresponding, identical elements on the opposite side of the breaker. It is to be understood that although these descriptions will not mention these corresponding components, they behave in a manner similar to that herein described, unless otherwise indicated.)

FIG. 6 illustrates the position of the components once the cam 126 has further rotated. The cam roller 132 has traveled beyond the end point 151 of the cam 126, and has come into contact with a flat surface 153 of a latch member 154. The follower plate 120 has rotated about its axis 107 to its furthest extent, and the spring 148 is totally charged. The drive pawl 134 has moved to its position adjacent to the drive pin 112. The latch member 154, at a second flat surface 156 thereof has rotated underneath the curved portion of a D-latch 158. In this position, the spring 148 is charged and would cause counterclockwise rotation of the follower plate 120 if it were not for the latch member 154. The surface 153 of latch member 154 is in the path of movement of the cam roller 132 as the cam roller 132 would move during counterclockwise rotation of the follower plate 120. Therefore, so long as the surface 153 of the latch member 154 remains in this path, the cam roller 132 and the follower plate 120 fixedly secured thereto cannot move counterclockwise. The latch member 154 is held in its position in the path of the cam roller 132 by the action of the second surface 156 against the D-latch 158. The latch member 154 is pivotally mounted on, but independently movable from, the drive shaft 124 (see FIGS. 2 and 3), and is biased by the spring 160. The force of the cam roller 132 is exerted against the surface 153 and, if not for the D-latch 158, would cause the latch member 154 to rotate about the drive shaft 124 in the clockwise direction to release the roller 132 and discharge the spring 148. Therefore, the D-latch 158 prevents the surface 156 from moving in a clockwise direction which would thereby move the first surface 153 out of the path of movement of the cam roller 132 upon rotation of the follower plate 120. To release the latch member 154, the releasable release means 162 are depressed, which causes a clockwise rotation of D-latch 158. The clockwise movement of the D-latch 158 disengages from the second surface 156 of the latch member 154, and the latch member 154 is permitted to rotate clockwise, resulting in the movement of the first surface 153 away from the path of the cam roller 132. The results of such release is illustrated in FIG. 7.

Once the latch member 154 is released, the spring 148 discharges, causing rotation of the follower plate 120 about its pivot axis 107. The rotation of the follower plate 120 moves the cam roller 132 into its position at the smallest diameter portion of the cam 126. At the same time, the rotation of the follower plate 120 causes the drive pawl 134 to push against the drive pin 112. This pushing against the drive pin 112 causes the drive pin 112, and the second link element 102 to which it is connected to move to the right as illustrated in the drawing. This movement causes the second link element 102 and the first link element 96 to move into toggle position with the toggle lever element 106. This movement into the toggle position causes movement of the cross arm 68, which compresses the shoulder 84 of the pusher rod 78 against the springs 88 (see FIG. 2), and moves the movable contacts 26 into the closed position in electrical contact with the stationary contact 22. The movable contact 26 will remain in the closed position because of the toggle position of the toggle means 34. Once the toggle means 34 are in toggle position, they will remain there until the toggle lever 94 is released. As can be noticed from the illustration, the drive pawl 134 is now in its original position but adjacent to the drive pin 112. The first link 90 and the second link 92 are limited in their movement as they move into toggle position by the limiting bolt 164. This bolt 164 prevents the two links 90, 92 from knuckling over backwards and moving out of toggle position. (Throughout this application, the term "toggle position" refers to not only that position when the first and second links are in precise alignment, but also includes the position when they are slightly over-toggled.) The status of the breaker at this position is that the spring 148 is discharged, and the contacts 26 are closed.

FIG. 8 then illustrates that the spring 148 can be charged while the contacts 26 are closed, to thereby store energy to provide an open-close-open series. FIG. 8 is similar to FIG. 5, in that the cam 126 has been rotated about 180.degree., and the follower plate 120 has rotated about its pivot point 107 to partially charge the spring 148. Again the drive pawl 134 has rotated with the follower plate. FIG. 9 illustrates the situation wherein the spring 148 is totally charged and the contacts 26 are closed. The drive pawl 134 is in the same position it occupied in FIG. 6, except that the drive pin 112 is no longer contacted with it. The latch member 154 and more particularly the surface 153, is in the path of the cam roller 132 to thereby prevent rotation of the follower plate 120. The second surface 156 is held in its location by the D-latch 158 as previously described. In this position, it can be illustrated that the mechanism is capable of an open-close-open series. Upon release of the toggle latch release means 166, the toggle lever 94 will no longer be kept in toggle position with links 90 and 92, but will instead move slightly in the counterclockwise direction. Upon counterclockwise movement of the toggle lever 94, the second link 92 will move in the clockwise direction, pivoting about the connection with the toggle lever 94, and the first link 90 will move in the counterclockwise direction with the second link 92. Upon so moving out of toggle, the force on the cross arm 68 which pushed the pusher rod 78 against the spring 88 will be released, and the release of the spring 88 will force the cross arm 68 and the movable contacts 26 into the open position. This then is the position of the components as illustrated in FIG. 6. To then immediately close the contacts 26, the latch member 154 is released, which, as previously described, causes rotation of the follower plate 120 such that the drive pawl 134 contacts the drive pin 112 to cause movement of the drive pin 112 and the second link element 102 to which it is fixedly secured to move back into toggle position. This then results in the position of the components as illustrated in FIG. 7. The breaker 10 then can immediately be opened again by releasing the toggle latch release means 166, which will position the components to the position illustrated in FIG. 4. Thus it can be seen that the mechanism permits a rapid open-close-open series.

As can be appreciated from the foregoing, the operating mechanism 32 and the toggle means 34 are electrically insulated from the current carrying parts of the breaker. The movable contacts 26, 28 are held by, and carried by the crossbar insulator 64 which is of an electrically insulating material such as a molded plastic. The cross arm 68 is inserted within the crossbar insulator 64, and thereby is electrically insulated from the movable contacts 26, 28. The first link 90 contacts and engages the cross arm 68, and likewise is not in direct electrical contact with the current carrying movable contacts 26. All the other elements of the toggle means 34 and the operating mechanism 32 are disposed on the other side of the insulating barrier 33 distal from the moving contacts 26. Therefore, emergency repairs to the operating mechanism 32 or the toggle means 34 may be undertaken while the movable contacts 26 are in the closed or open position. Also, the arc chute 36 has an outer support 123 which likewise is of an insulating material such as plastic, and also electrically insulates the arcing contact 28 from the operating mechanism 32 and the toggle means 34.

In the preferred embodiment illustrated, the positions of the various components have been determined to provide for the most economical and compacted operation. The input shaft 124 to the operating mechanism 32 is through a rotation of approximately 360.degree.. However, the output torque occurs over a smaller angle, thereby resulting in a greater mechanical advantage. As can be seen from the sequential illustration, the output torque occurs over an angle of less than 90.degree.. This provides a mechanical advantage of greater than 4 to 1. For compactness and maximum efficiency, the pivotal connection of the second link 92 to the toggle lever 94 is coincident with, but on separate shafts from, the rotational axis of the follower plates 120, 122. Another mechanical advantage is present in the toggle latch release means 166 when it is desired to release the toggle means 34 from toggle position.

The toggle latch release means 166 are illustrated in FIGS. 3 and 4. The toggle latch release means 166 are comprised of the latch member release lever 168, the two D-latches 170 and 172, the catch 174, biasing springs 176 and 178 and the stop pin 180. To release the toggle means 34, the latch member release lever 168 is depressed. The depressing of this lever 168 causes a clockwise rotation of the D-latch 170. The catch 174 which has been resting on the D-latch 170 but was biased for counterclockwise rotation by the spring 176 is then permitted to move clockwise. The clockwise movement of the catch 174 causes a corresponding clockwise movement of the D-latch 172 to whose shaft 179 the catch 174 is fixedly secured. The clockwise movement on the D-latch 172 causes the latch lever 94, and more particularly the flat surface 182 upon which the D-latch 172 originally rested, to move, such that the surface 184 is now resting upon the D-latch 172. This then allows the toggle lever 94 to move in a counterclockwise direction, thereby releasing the toggle of the toggle means 34. After the toggle means 34 have been released, and the movable contact 26 positioned in the open position, the biasing spring 178 returns the toggle lever 94 to its position wherein the surface 182 is resting upon the D-latch 172. To prevent the toggle lever 94 from moving too far in the clockwise direction, the stop pin 180 is utilized to stop the toggle lever 94 at its correct location. The mechanical advantage in this release system occurs because of the very slight clockwise rotation of the D-latch 172 which releases the toggle lever 94 as compared to the larger rotation of the latch release lever 168.

As can be seen in FIG. 3, the D-latches 170 and 158 are attached to two levers each. Levers 183 and 190 are secured to D-latch 158, and levers 168 and 192 are secured to D-latch 170. The extra lever 190 is present to permit electromechanical or remote tripping of the breaker and spring discharge. An electromechanical flux transfer shunt trip 193 (see FIG. 3) may be secured to the frame 194 and connected to the current transformer 38 so that, upon the occurrence of an overcurrent condition, the flux transfer shunt trip 193 will move lever 192 in the clockwise direction to provide release of the toggle lever 94 and opening of the contacts 24. An electrical solenoid device may be positioned on the frame 194 adjacent to lever 190 so that the remote pushing of a switch (not shown) will cause rotation of lever 190 causing rotation of D-latch 158 and discharging of the spring 148 to thereby close the breaker.

Accordingly, the device of the present invention achieves certain new and novel advantages resulting in a compact and more efficient circuit breaker. A dual drive means capability is provided wherein a handle can be utilized for manual operation to turn the drive shaft, and where a motor operator is capable of engaging the drive shaft to provide rotation thereof. The motor operator can be plugged into the drive shaft without dismantling the circuit breaker.