MXPA99004247A

MXPA99004247A - Set of closure and closure for mechanism of energy operation stored of electro switch

Info

Publication number: MXPA99004247A
Application number: MXPA/A/1999/004247A
Authority: MX
Inventors: Anthony Wehrli Henry Iii; Clyde Doran Raymond
Original assignee: Eaton Corporation
Priority date: 1998-05-07
Filing date: 1999-05-07
Publication date: 2000-07-01

Abstract

The present invention relates to an electrical switch apparatus such as an energy circuit breaker, a network protector or switch has a self-supporting operating mechanism module that includes a cage formed by a pair of side plates rigidly fastened on relationship spaced by spacers. The cage supports all components of the operating mechanism that include a helical compression closure spring fully mounted between the side plates and coupled to a cam member via a rocker arm in a manner that maintains longitudinal forces to the spring. The leva element has a loading cam with a loading profile for compressing the closing spring and a closing profile through which the spring drives the cam element to effect a controlled release of stored energy to close the contacts of the apparatus. A locking strut, spring-loaded to an unlocked position, is locked to secure the closing spring in the state loaded by a locking assembly restored by a separate reset lever of the closing strut which in turn is reset by the rotation of the cam element during loading. An interlock prevents the release of the closing spring when the contacts are closed or the trigger release is activated. An indicator actuated by an actuator pivoted against the cam shaft passes from a discharged indication to a loaded one as the closing spring becomes fully loaded and the actuator falls into a notch stripe by a slab on the cam shaft. An open / closed pressure action indicator for switch contacts is also provided. Both indicators are rotatably mounted on a front plate bolted to the side plates and are connected to the operating mechanism by shaped wires. The pressure buttons of closing and opening are linked by pressure to a common axis and have actuating fingers that trigger releases in the operating mechanism. The rotary closing shafts are connected only in confronted openings in the side plates. The camshaft is captured between bushings seated in non-circular openings in the side plates eliminating the need for fasteners. Likewise, other parts mounted between the side plates and joined by bolts having enlarged heads retained by the side plates do not require detents. Several axes extending between the side plates have ends of reduced diameter of progressive lengths for successive insertion into a side plate to assist in the assembly of the operating mechanism.

Description

CLOSURE AND CLOSURE SCREW SET FOR STORED ENERGY OPERATING MECHANISM OF ELECTRICAL SWITCH APPARATUS Background of the Invention Field of the Invention The invention relates to electrical switching devices such as protective devices and switches used in electric power distribution circuits carrying large currents. Such apparatuses use a large spring to store sufficient energy to close the contacts of the apparatus against the considerable magnetic repulsion forces generated by the large current while simultaneously charging opening springs. More particularly, the invention is directed to the operating mechanism that assembles, and controls the storage and release of energy, by the closing spring. Specifically, it refers to the closing strut which retains the closing spring in the charged state ready for closing, the bolt assembly that releases the closing strut to initiate closure, and a resetting device that resets the closing strut assembly and bolt. BACKGROUND INFORMATION Electrical circuit breakers for opening and closing electrical power circuits typically use an energy storage device in the form of one or more large springs to close the contacts of the device in the large currents that may exist in those circuits. This electrical switch apparatus includes power circuit breakers and network protectors that provide protection, and electrical switches that are used to energize and de-energize parts of the circuit or to effect the transfer between alternative power sources. These power circuit breakers, network protectors, and switches also include an open spring (s) that quickly separates the contacts to interrupt the current flowing in the power circuit. The springs to open are loaded during closing by the closing spring which, therefore, must store enough energy both to overcome the mechanical and magnetic forces to close, and to load the springs to open. As indicated, each or both of the closing spring and opening spring can be a single spring or multiple springs and it should be considered that both are referred to herein although the singular is mentioned for convenience reasons. An operating mechanism assembles and controls the loading and unloading of the closing spring. Typically, the operating mechanism includes a cam member that rotates in a single direction and is coupled to the closing spring to load the spring when the cam is rotated either manually, by means of a handle, or automatically, by means of a engine, through a ratchet mechanism. The ratchet mechanism introduces some retraction when the cam is rotated in increments during the load cycle. As the closing spring becomes fully loaded, the cam passes over the center and the energy stored in the spring tends to drive the cam. A closing strut keeps the spring in the loaded state. Typically, the closing strut is spring biased to this closed state, and a releasing mechanism removes the closing strut when the stored energy is to be released to close the contacts of the electrical apparatus. Since the closing strut is typically biased to the closed state, it is restored automatically after the spring is released and the cam is driven to a closing position from which a new charging cycle can be initiated. This polarization of the closing strut to the closed position increases the required release force. Therefore, there is room for improvements in the closing struts and the associated operation mechanism of circuit breakers, network protectors and switches. There is therefore a need for an improved operating mechanism for electrical switching devices such as power circuit breakers, network protectors and switches, and particularly the closing strut which retains the closing spring in the loaded state. In this regard, there is a need for an operating mechanism with a closing strut that has a lower release force than typically provided. There is also a need for an improved operating mechanism in which the closure strut is not biased to the closed position. There is also an additional need for such an operating mechanism having an arrangement for restoring the closing strut to the closed position. SUMMARY OF THE INVENTION These and other needs are met by the invention, which is directed to an operating mechanism for electrical switching devices such as power circuit breakers, network protectors and switches having a closing spring mechanism that includes a closing spring and means for loading the closing spring incorporating a cam member coupled to and urged by the closing spring as the closing spring becomes fully loaded. The operating mechanism also includes a pivotally mounted locking strut having a closed position that links and prevents rotation of the cam member, and a non-closed position in which it disengages from the cam member so that the cam member is free to be rotated by the closing spring. Polarization means polarize the closing strut to the non-closed position. A bolt assembly is connected to the closing strut and closes the closing strut in the closed position when it is restored. Restoration means reset the bolt assembly by rotating the cam member towards the closure strut. Preferably, the reset means is a pivotally mounted reset lever having a reset finger that is engaged by the cam member when the cam member is rotated. The reset lever links the closing strut and rotates the closing strut against the polarization applied to the closing strut in the closed position. The bolt assembly preferably includes a bolt plate pivotally mounted with a bolt spine. A bolt link connects the bolt plate to the closing strut for joint rotation. The bolt assembly also includes a lock arrow capable of rotating having a release notch. The lock spine links the lock arrow when the lock arrow is in a loaded position but falls off the lock spine so that the lock plate is pulled through the notch by the biasing means and the closing post is turned to the non-closed position when the closing arrow is rotated to a release position. Also preferably the closing strut and the reset lever are mounted on a common pivot shaft. The reset lever or locking tip has a lateral projection that links the other to rotate the locking strut to the lock position when the finger on the reset lever is engaged by the cam member during reset. This lateral projection also places the reset lever to be linked by the cam member when the bolt arrow is rotated to the release position and the polarization means rotate the closure strut to the non-closed position. The cam member of the operating mechanism has a stop member that is engaged by the closing strut and a reset member in front of the stop member that engages and actuates the resetting means when the cam member is rotated during the loading of the closing spring. When the loading means includes a pawl that produces retraction of the cam member during loading, a spring biases the reset lever to engage with the closing strut, but allows the reset lever to be moved away from the closing strut by the reset member on the cam member in response to the retraction of the cam member. BRIEF DESCRIPTION OF THE DRAWINGS The invention may be fully understood based on the following description of the preferred embodiments., taken in conjunction with the accompanying drawings, in which: Figure 1 is an isometric exploded view of a high current, low voltage power circuit breaker, according to the invention. Figure 2 is a vertical section through a circuit breaker pole of Figure 1 illustrated as the contacts separate during opening.

Figure 3 is an isometric exploded view of a cage assembly that forms part of the operating mechanism of the circuit. Figure 4 is an isometric exploded view illustrating the assembly of the operating mechanism. Figure 5 is a partial vertical section through an armed operating mechanism taken through the rocker assembly. Figure 6 is an isometric view illustrating the assembly of the closing spring that forms part of the operating mechanism. Figure 7 is a side elevational view of the cam assembly that is part of the operating mechanism. Figure 8 is an elevational view illustrating the relationship of the main components of the illustrated operating mechanism with the open contacts and the discharged closing spring. Figure 9 is a view similar to Figure 8 with the contacts open and the closing spring loaded. Fig. 10 is a view similar to Fig. 8 with closed contacts and discharged closing spring. Figure 11 is a view similar to Figure 8 with the contacts closed and the closing spring loaded. Figure 12 is an elevational view of the closure strut which controls the release of the closing spring illustrated in relation to the cam member of the operating mechanism with the discharged closing spring and the release strut released. Figure 13 is a view similar to that of Figure 12 illustrated during loading of the closure spring as the closure strut is being restored. Figure 14 is a view similar to Figure 12 illustrating the closure strut that holds the spring in the loaded state. Figure 15 is a view similar to Figure 12 illustrating the closure strut immediately after it has been released to close the contacts. Figure 16 is an end view of the closure strut assembly. Fig. 17 is an isometric view of the interlocking assembly that interlocks the operation of the trip lock D and the lock lock D. Figure 18 is a side elevational view of the interlock of Figure 17 with the contacts in the open state. Figure 19 is a view similar to Figure 18 illustrating the operation of the interlock when the closing solenoid is actuated. Figure 20 is a view similar to that of Figure 18 in the "trigger" condition which prevents the closing spring from being triggered repeatedly by the continuous actuation of the closing solenoid Figure 21 is a view similar to that of Figure 18 illustrating the condition of the lock assembly when the main contacts of the circuit breaker are closed Figure 22 is a front elevation illustrating the assembly of the keypads in the operating mechanism Figure 23 is an isometric view illustrating the coupling of the keypads to the lock assembly Figure 24 is a front elevational view of the operating mechanism illustrating the faceplate and the mounting of the keypads and indicator flags.Figure 25 is an isometric view of the back of the door. front plate illustrating the assembly of the indicator flags Figure 26 is a vertical section through the front plate taken along line 26 in figure 24. Figure 27 is an isometric view of the flag indicating the status of the closing spring. Figure 28 is a side elevational view of the operating mechanism illustrating the spring action of the status indicator of the closing spring in the discharged state of the spring. Fig. 29 is a view similar to Fig. 28 illustrating the state of the flag indicating the closing spring just before the spring becomes fully loaded. Figure 30 is a view similar to Figure 28 illustrating the indicator flag of the closing spring in the loaded state.

Figure 31 is a side elevational view of the operating mechanism of the contact status indicator flag when the main contacts of the circuit breaker are closed. Figure 32 is similar to Figure 31 and illustrates the operating mechanism of the open / closed indicator flag when the main contacts of the circuit breaker are open. Figure 33 is an isometric view of the armed operating mechanism particularly illustrating the manual and electric charging system. Figure 34 is an exploded isometric view of the manual loading mechanism for the closing spring. Figure 35 is an enlarged elevation view of a section of a ratchet wheel that forms part of the spring loading mechanism. Figure 36 is a side elevational view of the operating mechanism illustrating the loading mechanism of the armed closing spring and with a portion of the engine load unit removed for clarity. Figure 37 is an isometric view of the motor operator for electrically charging the closing spring. Figure 38 is a fragmentary elevational view illustrating an alternative embodiment of the loading mechanism. Figure 39 is a schematic illustration of a feature that simplifies the assembly of the operating mechanism. Description of Preferred Embodiments The invention will be described as applied to an air-to-air circuit breaker; however, it also has application in other electrical switching devices to open and close electric power circuits. For example, it has application in switches that provide a disconnection for power branches and transfer switches used to select alternative energy sources for a distribution system. The main difference between an energy circuit breaker and these various switches is that the circuit breaker has a tripping mechanism that provides overcurrent protection. The invention can also be applied to network protectors that provide protection and isolation for distribution circuits in a specific area. With reference to Figure 1, the air power circuit breaker 1 of the invention has a housing 3 that includes a molded front box 5 and a rear case 7, and a cover 9. The circuit breaker of example 1 has three poles 10 forming the front and rear boxes 5, 7 three pole chambers 11. Each pole 10 has an arc chamber 13 which is enclosed by a ventilated arc chamber cover 15. The circuit breaker 1 has an operating mechanism 17 which is mounted on the front of the front box 5 and is enclosed by the cover 9. The operating mechanism 17 has a front plate 19 which is accessible through an opening 21 in the cover . The operating mechanism 17 includes a large spring 18 which is charged to store energy to close the circuit breaker. The faceplate 19 mounts a push-open button 25 to open the circuit breaker. The indicators 27 and 29 represent the condition of the closing spring and the open / closed state of the contacts, respectively. The closing spring 18 is loaded by the operation of the loading handle 31 or remotely by a motor operator (not shown). The common operating mechanism 17 is connected to the individual poles by a polar axis 33 with a lobe 35 for each pole. As is conventional, the circuit breaker 1 includes an electronic trip unit 37 supported on the cover 9 which operates the operating mechanism 17 to open all the poles 10 of the circuit breaker through the rotation of the polar axis 33 in response to characteristics default of the current flowing through the circuit breaker. Figure 2 is a vertical section through one of the pole chambers. Pole 10 includes a side edge conductor 39 projecting outward from the rear case 7 to be connected to a source of electrical power c.a. (not illustrated). A charging conductor 41 also projects out of the rear case 7 to be typically connected to the conductors of the charging network (which is also not illustrated).

Each pole 10 also includes a pair of main contacts 43 that include a stationary main contact 45 and a moving main contact 47. The moving main contact 47 is carried by a moving conductor assembly 49. This movable conductor assembly 49 includes a plurality of fingers of contact 51 which are mounted in axially spaced relation on a pivoting bolt 53 secured in a contact carrier 55. The contact carrier 55 has a molded body 57 and a pair of legs 59 (only one illustrated) having pivots 61 supported rotatably in the housing 3. The contact carrier 55 is rotated about the pivots 61 by the drive mechanism 17 which includes a drive pin 63 received in the transverse passage 65 in the carrier body 57 through a slot 67 to which the actuator pin 63 is keyed by plates 69. The actuator pin 63 is fixed on an actuator link 71 which is received in a groove 73. in the carrier body. The other end of the actuator link is rotatably connected by a bolt 75 to the associated pole arm 35 on the polar axis 33 similarly connected to the carriers (not shown) at the other poles of the circuit breaker. The polar axis 33 is rotated by the operating mechanism 17 in a manner to be described. A movable main contact 47 is fixed to each of the contact fingers 51 at a point spaced from the free end of the finger. The portion of the contact finger adjacent the free end forms an arc contact or "arch foot" 77. A stationary arc contact 79 is provided on the confronting face of an integral arc and slider contact 81 mounted on the lateral conductor of the arc. line 39. The stationary arcing contact 79 and the arc foot 77 together form a pair of arcing contacts 83. The arc contact and integral slider 81 extends upwards towards a channel 85 mounted in the arc chamber 13. contact fingers 51 are pushed clockwise as can be seen in figure 2 on the pivoting bolt 53 of the carrier 55 by pairs of helical compression springs 87 seated in the recesses 89 in the carrier body 55. The operating mechanism 17 rotates the polar axis 33 which in turn rotates the contact carrier 55 clockwise to a closed position (not shown) to close the main contacts 43. To open the contacts, the operating mechanism 17 releases to the polar axis 33 and to the compressed springs 87 for accelerating the carrier 55 in a counter-clockwise direction to an open position (not shown). As the carrier is rotated clockwise to the closed position, the arch feet 77 contact the stationary arcing contacts 79 first. As the carrier continues to move clockwise, the springs 87 are compressed as the contact fingers 51 oscillate about the pivot pin 53 until the main contacts 43 close. The additional clockwise rotation to the fully closed position (not shown) results in the opening of the arcing contacts 83 while the main contacts 43 remain closed. In that closed position, a circuit is completed from the line conductor 39 through the closed main contacts 43, the contact fingers 51, the flexible leads 91, and the load conductor 41. To open the circuit breaker 1, the operating mechanism 17 releases the polar axis 33 so that the compressed springs 87 accelerate the carrier 55 in counter-clockwise relationship, as seen in Fig. 2. Initially, as the carrier 55 moves out of the line conductor 39, the contact fingers 51 perform a tilting movement so that the arcing contacts 83 close while the main contacts 43 remain closed. As the carrier 55 continues to move counterclockwise, the main contacts 43 open and all current is transferred to the arcing contacts 83 which is the condition illustrated in FIG. 2. If a dimensionable current is being carried by the switch of circuit such as when the circuit breaker trips to open in response to an overcurrent or short circuit, an arc is triggered between the stationary arcing contacts 79 and the movable arcing contacts or arc feet 77 as these contacts are separated with the rotation continued counterclockwise of the carrier 55. As the main contacts 43 have been separated, the arc is confined to the arc contacts 83 which preserves the life of the main contacts 43. The electromagnetic forces produced by the current sustained in the arc push the arc outwards towards the arc channel 85 so that the end of the arc in the stationary arcing contact 79 moves toward the arc contact and integral slider 81 and within the arc channel 85. At the same time, the rapid opening of the carrier 55 leads to the arc legs 77 adjacent to the free end of the plate arc upper 93 as illustrated in dotted lines in Figure 2, so that the arc extends from the arch feet 77 to the arc upper plate 93 and moves upward to the sup plate. arc arch inside the arc plates 94 that break the arc into shorter sections that are then extinguished. The operating mechanism 17 is a self-supporting module having a cage 95. As illustrated in Figure 3, the cage 95 includes two side plates 97 that are identical and interchangeable. The side plates 97 are held in spaced apart relation by four elongated elements 99 formed by spacer sleeves 101, and threaded shafts 103 and nuts 105 securing the side plates 97 against the spacer sleeves 101. Four main sub-assemblies and a large spring 18 form the power portion of the operating mechanism 17. The four main sub-assemblies are the cam assembly 107, the rocker assembly 109, the main link assembly 111 and a spring-loaded closure support assembly 113. All of these components fit together the two side plates 97. With reference to figures 3 and 4, the cam assembly 107 includes a camshaft 115 which is connected in non-cylindrical bushings 117 seated in the complementary non-cylindrical openings 119 in the side plates 97. The bushings 117 have tabs 121 which bear against the internal faces 123 of the side plates 97 and the camshaft 115 has shoulders 125 which position it nans between the bushings 117 so that the camshaft 115 and the bushings 117 are captured between the side plates 97 without the need for fasteners. Similarly, a pivoting bolt 127 of the rocker assembly 109 has shoulders 129 that capture it between the side plates as seen in Figures 3-5. Planchets 131 on the swing bolt 127 are linked with similar planks 133 in the openings 135 in the side plates 97 to prevent rotation of the swing bolt. The camshaft 115 and the swing bolt 127 add stability to the cage 95 which is self-aligning and does not require special accessories for alignment of the parts during assembly. Since the main components are "sandwiched" between the two side plates 97, most components do not need additional hardware for their support. As will be seen, this sandwich construction simplifies the assembly of the operating mechanism 17. The closing spring 18 is a heavy-duty, round, common, closed, wire-wound coil compression spring with flat ground at both ends. A compression spring is used because its energy density is higher than that of a tension spring. The helical compression closure spring 18 is very uniquely supported by the closure spring support assembly 113 to prevent voltage spikes and / or buckling. In such a high-energy application, it is important that the ends of the spring 18 remain parallel and uniformly supported and that the spring be held laterally in place. As particularly illustrated in Figures 4 and 6, and also in Figures 8-11, this is achieved by compressing the closing helical compression spring 18 between a U-support 137 which is free to rotate and also actuate the rocker assembly. 109 at one extreme, and a nearly square spring washer or guide plate 139 that can pivot against a spring stop or support pin 141 extending through the spring means, spring washer 139 and strut 145 of the U-shaped support 137 The elongated guide member 143 in turn is captured on one end by the spring stop bolt 141 extending through an opening 147, and at the other end by a support bolt 149 extending through the legs 151 on the U-shaped support 137 and an elongated slot 153 in the elongated element. The rocker assembly 109 includes a rocker 155 rotatably mounted on the swing bolt 127 by a pair of roller bearings 157 that are captured between the side plates 97 and held in spaced relationship by a sleeve 159 as best seen in Figure 5. The rocker 155 has a fork 161 on one end which rotatably connects the rocker 155 to the U-support 137 through the support bolt 149. A pair of legs 163 on the other end of the rocker 155 extending at an obtuse angle to the fork 161, form a pair of forks that support the tilting rollers 165. The tilting rollers 165 are rotatably mounted to the roller forks by the bolts 167. These bolts 167 have heads 169 facing outwards toward the side plates 97 so which are captured and held in place without the need for pressure rings or other separate seals. As the rocker 155 performs its oscillating movement about the swing bolt 127, the spring washer 139 rotates on the spring support shaft 141 so that the load on the spring 18 remains uniform regardless of the position of the rocker 155. spring 18, spring washer 139 and spring support pin 141 are the last parts that go into a finished mechanism 17 so that spring 18 can be correctly sized for the application. The U-bolt 149 transfers all the spring and energy load to the rocker fork 161 on the rocker 155. The translational loads on the rocker 155 are transferred on * the non-rotating rocker pin 127 and from there into the two side plates 97 while the rocker 155 is free to rotate between the plates 97. With reference to figures 4-11, the cam assembly 107 includes in addition to the cam shaft 115, a cam member 171. The cam member 171 it includes a load cam 173 formed by a pair of load cam plates 173a, 173b mounted on the camshaft 115. The load cam plates 173a, 173b ride on a drive cam 175 which is formed by a second pair of cam plates 175a, 175b. A cam spacer 177 establishes the spacing between the actuator cam plates 175a, 175b while spacer bushes 179 separate the load cam plates 173a, 173b from the actuator cam plates and from the side plates 97. The cam plates 173 , 175 are all secured together by rivets 181 which extend through rivet spacers 183 between the plates. A stop roll 185 is pivotally mounted between the drive cam plates 175a and 175b and a reset pin 187 extends between the drive cam plate 175a and the load cam plate 173a. The cam assembly 107 is a mechanism 360E which compresses the spring 18 to store energy during part of the rotation, and which is rotated by releasing the energy stored in the spring 18 during the rest of the rotation. This is achieved through the linking of the load cam plates 173a, 173b by the tilt rollers 165. The preload on the spring 18 keeps the tilt rollers 165 in engagement with the load cam plates 173a, 173b . The load cam 173 has a cam profile 189 with a loading portion 189a which at the point of attachment with the rollers tilting 165 increases its diameter with the clockwise rotation of the cam member 171. The camshaft 115 and therefore the cam member 171 is manually rotated by the handle 31 or by an electric motor 421 (see figure 33) of a way that will be described. The loading portion 189a of the load cam profile 189 is configured such that a substantially constant torque is required to compress the spring 18. This provides better detection for manual loading and reduces the size of the motor required for the given automatic load. that the constant torque is below the peak torque that would normally be required as the spring approaches the fully compressed condition. The cam profile 189 on the load cam 173 also includes a closing portion 189b that decreases in diameter as the load cam 173 rotates against the tilt rollers 165 so that the energy stored in the spring 18 drives the element. of cam 171 clockwise when the mechanism is released in a way to be discussed. The actuator cam 175 of the cam member 171 has a cam profile 191 which in certain rotational positions is linked by an actuator roller 193 mounted on a main link 195 of the main link assembly 111 by a rolling pin 197. The other end of the main link 195 is rotatably connected to an actuator arm 199 on the pole axis 33 by a bolt 201. This main link assembly 111 is coupled to the actuator cam 175 to close the circuit breaker 1 by a firing mechanism 203 which includes a hatchet plate 205 rotatably mounted on a hatchet bolt 207 supported by the side plates 97 and pushed counterclockwise by a spring 219. A banana link 209 is rotatably connected at one end to an extension on the rolling pin 197 of the assembly. the main link and at the other end is rotatably connected to one end of the hatchet plate 205. The Another end of the hatchet plate 205 has a locking shoulder 211 which is linked to a firing axis D 213 when the shaft is rotated to a locking position. With the tack plate 205 locked, the banana link 209 holds the drive roller 193 in engagement with the drive cam 175. During operation, when the trigger axis D is rotated to a firing position, the locking shoulder 211 slides off the axis D of shot 213 and the hatchet plate 205 passes through a notch 215 in the firing axis D which restores the pivot point of the banana link 209 connected to the hatchet plate 205 and allows the drive roller 193 to float independently of the actuating cam 175. The loading and unloading sequence of closing spring 18 can be understood by reference to FIGS. 8-11. In Figure 8 the mechanism is illustrated in the open discharged position, ie the closing spring 18 is discharged and the contacts 43 are open. It can be seen that the cam member 171 is positioned so that the load cam 173 has its smallest radius in contact with the tilting rollers 165. In this way, the rocker 155 is rotated to a fully counter-clockwise position and the spring 18 is in its maximum extension. It can also be seen that the firing mechanism 203 is not locked so that the drive roller 193 is floating but supported against the actuating cam 175. As the camshaft is rotated clockwise manually by means of the handle 31 or through from the operation of a load motor 421, the load portion 189a of the load profile on the load cam progressively increasing in diameter, is linked to the tilt roll 165 and rotates the rocker 155 clockwise to compress the spring 18. As mentioned, the configuration of this load portion 189a of the profile is selected such that a constant torque is required to compress the spring 18. During this spring loading 18, the drive roller 193 is in contact with a portion of the drive cam profile 191 having a constant radius so that drive roller 193 continues to float. Turning now to FIG. 9, as the spring 18 becomes fully loaded, the drive roller 193 falls out of the drive cam profile 191 in a recess 217. This allows the reset spring 219 to rotate the hatchet plate. 205 counterclockwise until the locking shoulder 211 passes slightly past the firing axis D 213. This raises the pivot point of the banana link 209 on the hatchet plate 205 so that the drive roller 193 is raised to a position where it rests under the notch 217 in the actuating cam 175. At the same time, the tilting rollers 165 arrive at a point just after the rotation 170E of the cam member where they enter the closing portion 189b of the load cam profile 189 In this portion 189b of the load cam profile, the radius of the load cam 173 in contact with the tilting rollers 165 decreases with the clockwise rotation of the cam member 171. Thus, the Closing spring 18 applies a force tending to continue rotation of cam member 171 in the clockwise direction. However, a closure strut (not shown in Figure 9) that is part of a locking strut mechanism to be described later, is linked to the stop roller 185 and prevents further rotation of the cam member 171. Thus, the spring 18 remains fully charged ready to close the contacts 43 of the circuit breaker 1. The contacts 43 of the circuit breaker 1 are closed by releasing the closure strut in a manner to be described. With the closing strut disengaged from the stop roller 185, the energy of the spring is released to rapidly rotate the cam member 171 to the position illustrated in FIG. 10. As the cam member 171 rotates, the drive roller 193 it is linked by the cam profile 191 of the actuator cam 175. The radius of this cam profile 191 increases with the rotation of the cam shaft and as the banana link 209 holds the actuator roller 193 in contact with this surface, the polar axis 33 is rotated to close the contacts 43 as described in relation to figure 2. At this point, the locking shoulder 211 is linked to the D lock 213 and the contacts are closed with a lock. If the circuit breaker is tripped at this point by the rotation of the firing axis D 213 so that this locking projection 211 is disconnected from the D-axis 213, the very large force generated by the compressed contact springs 87 (see FIG. ) exerted through the main link 195 pulls the pivot point of the banana link 209 in the hatchet plate 205 clockwise downward and the drive roller 193 falls free of the actuator cam 175 allowing the polar axis 33 to rotate and the contacts 43 open. With the contacts 43 open and the spring 18 discharged the mechanism would again be in the state illustrated in Fig. 8. Typically, when the circuit breaker is closed, the closing spring 18 is recharged, again by the rotation of the camshaft 115 either manually or electrically. This causes the cam member 171 to return to the same position as in Figure 9, but with the firing mechanism 203 locked, the banana link 209 keeps the drive roller 193 engaged with the actuator profile 191 of the actuator cam 175 as shown in FIG. illustrated in Figure 11. If the circuit breaker is tripped at this point by rotation of the trigger lock D 213 so that the hatchet plate 205 rotates clockwise, the drive roller 193 will fall into the slot 217 in the cam actuator 175 and the circuit breaker will open. As mentioned, during the first 180E of rotation of the cam member 171, the spring 18 is being loaded and during the second 180E of rotation the energy in the spring is being delivered to the contact structure in a controlled manner. In other words, during the last phase, the spring 18, the cam member 171 and the drive roller 193 are acting as a motor. As discussed, it is desirable to provide a constant load torque for manual loading because it provides better "detection" for the operator, and for the electrical operator that can be sized for a constant torque rather than for a peak torque. During the first 10E of load, the torque is raised to the selected constant value. This provides the user with a friendly feeling rather than a person against a wall of constant torque. It also allows the charging motor, if used, to be brought to speed before reaching the maximum touch. During the last 10E of the load cycle, the torque is reduced from a maximum positive torque to a slightly negative torque. This allows the cam assembly 107, and specifically the stop roller 185 and the closure strut 223, to abut one another for half-cycle closure. The profile 189 of the loading cam 173 is designed so that the force between the roller 185 and the strut 223 is a negative of 5 to 15 pounds, depending on the size of the compression spring 18. Once the closing strut 223 is removed, the cam assembly 107 begins to rotate the remaining 180E due to the force of the spring 18 and the slope of the closing profile of the load cam 189b. The closing cam profile 189b between 180E and 360E is very critical for the optimal operation of the circuit breaker and is a unique feature of the invention. In the prior art mechanisms, without a drive cam 175, it is common to simply release the energy from the spring and let the contacts 43 close. The spring 18 is usually dimensioned to close the contacts 43 quickly and without contact rebound. These goals may be incompatible and compromises are made. However, with the closing cam 173 of the invention it is possible to control the release of energy to the mobile conductor assembly 49. This closing cam profile 189b can be selected so that the contacts can be quickly closed, firmly, and without contact bounce. We have found that at least 50% of the energy stored in the spring 18 must be released before contact closure, and certainly, before the contact of the arcing contacts 83. Preferably, approximately 70% of the energy is released before the contacts begin to touch. A computer simulation can be used to optimize the cam profiles 189, 190. In most applications, the load portion of the load cam profile 189a must be approximately the same. However, the closing portion of the load cam profile 189b is unique to the movable conducting assembly 49 (mass and geometry) and to the type of contacts 43, 83 that are being used. Due to the high energies and forces associated with the actuator mechanism, locking cams 173 and actuating cams 175 of hardened stainless steel are used. However, it should be noted that all forces are balanced around the center plane of the cam assembly 107 by the use of dual load cams 173 a, 173 b riding on the symmetrical drive cam 175 to prevent buckling and twisting. It is believed that symmetric loading is important to make a durable mechanism. The closing strut mechanism 221 is illustrated in Figures 12-16. This mechanism includes the closing strut 223, a locking assembly 225 and a resetting device 227. As mentioned, the closing strut 223 connects the stop roller 185 on the cam member 171 to keep the closed spring 18 in the loaded condition The pivot pin 229 for the closing strut 223 is located exactly in the line of force exerted by the stop roller 185 on the closing strut 223 to minimize the unlocking force and to reduce the possibility of impact (unintentional opening of the contacts due to vibration or shock). A large torsion spring 231 (see Figures 4 and 16) pushes the locking strut 223 into the release position against a stop 233 as illustrated in Figure 12. It is held in the locked position illustrated in Figure 14 by the assembly 225. This lock assembly 225 includes a lock latch plate 235 rotatably mounted on a support shaft of the latch plate 237 supported on the side plates 97, and a lock latch shaft D 239 connected to the plates. lateral The locking latch plate 235 has a locking shoulder 241 which is engaged with the latching locking shaft D 239 with the latter in the raised position, but falls through a notch 243 in the latching locking shaft D 239 when the shaft is rotated to a release position. The lock assembly 225 also includes a lock link 245 which connects the lock strut 223 to the lock lock plate 235. With the lock plate 235 linked by the lock pin D 239, the lock strut 223 is rotated to the stop or reset position illustrated in Figure 14. When the lock locking shaft D 239 is rotated to the release position, the lock locking plate 235 falls through the notch 243 and the spring Torque 231 rotates to closing strut 223 clockwise to the release position illustrated in Figure 15 by rotating to lock latch plate 235 therewith. The reset device 227 for the closing strut mechanism 221 includes a reset lever 247 that is rotatably mounted on the same axis 229 as the closure strut 223 but is rotatable independently of the closure strut. The reset device 227 also includes a reset member in the shape of the reset pin 187 provided between the lock cam plate 173 a and the drive cam plate 175 a in advance of the stop roller 185 in the direction of rotation. With the locking strut mechanism 221 unlocked as illustrated in FIG. 12, the locking strut 223 is urged against the stop 233 by the torsion spring 231. As the cam member 171 rotates to load the spring, the reset bolt 187 is connected with a finger 251 on the reset lever 247. As illustrated in FIG. 13, clockwise rotation of the cam member 171 causes rotation of the reset lever counterclockwise. The reset lever 247 has a flange 253 that engages the closure strut 223 so that the closure strut rotates with the reset lever. Alternatively, of course, the closure strut 223 may have a flange linked by the reset lever 247. The link 245 pushes the lock latch plate 235 towards the latch lock shaft D 239 and the rounded corner 235R on the plate lock latch 235 rotates latch locking shaft D 239 to allow the locking shaft to pass through notch 243. When latch lock plate 235 passes over latch locking shaft D 239, the latter rotates again so that the reset lever 247 slides from the reset bolt 187 and the torsion spring 231 pushes the closure strut 223 clockwise, the locking projection 241 engages with the locking axle D closing 239 to maintain the closure strut 223 in the reset or locked position illustrated in FIG. 14. As mentioned, the reset lever 247 can rotate independently of the closure strut 223, but is pushed against the closing strut by a second torsion spring 255 (see Figure 16). However, since the manual loading system has a ratchet that allows the cam assembly 107 to back off during the recycling of the handle 31, the reset pin 187 can be linked with the reset lever 247 and rotated clockwise against the force of thrust of the second torsion spring 25 and out of the locked locking strut 223. This is an important feature of the invention as it prevents damage to the closing strut mechanism 221. The trigger locking axis D 213, which as shown in FIG. describes a turn to open the circuit breaker, is fully supported by the two side plates 97 as illustrated in Figure 17. It is located in the uppermost part of the mechanism 17 and has a molded plastic platform held by pressure 257 at one end and two additional platforms 259 and 261 at the other end, all outside the side plates 97. The molded plastic platforms 257 and 259 are keyed on p lanchue-las at each end of firing pin D axis 213 outside the side plates 97. The platform 261 can rotate freely on the lock shaft D 213, but has an extension 249 that connects with the platform 259 to couple it to the D-axis of trigger lock. These molded platforms are connected by solenoids to rotate the locking shaft 213 to open the circuit breaker in the manner discussed above. Platform 257 is connected by a low voltage solenoid (if provided). The platform 259 is rotated by an auxiliary trip solenoid (not shown, and if provided) that can be operated from a remote location. The platform 261 is linked by a trip actuator (not shown, and if provided) energized by the trip unit 37 in response to an overcurrent or short circuit condition in the protected circuit. As can be seen in Figure 17, the lock locking shaft D 239 extends parallel to the axis 213 near the top of the mechanism 17 and is also fully supported by the side plates 97. With reference also to Figures 18 to 21 , a molded platform 263 for lock release is mounted but rotates freely on lock locking shaft D 239. This is because the lock release platform 263 is part of a latching mechanism 265 that gives preference to the firing of the contacts 43 so that they open. This interlocking mechanism 265 includes a pair of latch spring release levers 267 keyed to latch lock shaft D 239 off the latch release platform 263. These latch spring release levers 267 each have stops 269 extending transversely from the levers. The stops 269 are urged against a stop axis 271 to hold the lock locking shaft D in the engaged position by a tension spring 273 (see FIG. 4). The closure release platform 263 is pushed clockwise to the horizontal position illustrated in Figure 18 by a torsion spring 275 (also Figure 4). A locking element 277 in the form of a slide is interposed between the release platform 263 of the closing spring and the closing spring lever 267 on the one hand. The elongated slide 277 is loosely mounted on the locking shaft 213 which extends through an elongated slot 279. The slide 277 has a projection 281 on one end which, when the slide is in a first position illustrated in Figure 18, it is aligned with a finger 283 on the release platform 263 of the closing spring. Thus, with the slide 277 in this position, the rotation of the release platform 263 of the closing spring downward, such as by a closing solenoid 285, causes the finger 283 to engage with the projection 281 on the slide 277 that then it transmits the rotation of the release platform of the closing spring to the rotation of the release lever 267 of the closing spring as illustrated in FIG. 19. This rotates the locking bolt 239 D to release the assembly from locking bracket lock 225 allowing the locking bracket 223 to be removed which results in the release of the locking spring 18 and the closure of the contacts 43. The release platform 263 of the closing spring can also be rotated by the keypad of closure 23 as will be described. Adjacent to the projection on the slide 277, it is a recess 287. The continued downward rotation of the release platform 263 of the closing spring causes the finger 283 to slide out of the projection 281 on the slide and fall into the recess 287. This allows the release levers of the closing spring 267, and thus the closing locking pin D 239, to return to the locking position which results in the condition illustrated in FIG. 20. At this point, the spring Closing 18 can be recharged. If it were not for the interlocking mechanism 265 of the invention, the continued operation of the closed solenoid 285 or the closing snap button 23 would result in a "crossfire" or re-release of the closing spring. The condition illustrated in Figure 20 prevents this from happening and consequently provides an "anti-pumping" characteristic. As finger 283 begins to slide out of projection 281 and enters recess 287, it slides slide 277 to the right to reach the position illustrated in Figure 20. It is important that this condition does not take place until the lever 267 of the closing spring has rotated sufficiently to release the locking assembly 25 from the closure support by means of the rotation of the locking latch bolt D 239. This is ensured by dimensioning the finger 283 so that the edge of the latch finger does not pass beyond the edge of the projection 281 defining the recess 287 thus producing a component tending to pull the slider 277 to the right until the locking latch bolt D has rotated to release the strut assembly 25 from the strut closing. By moving the slide 277 to the right as illustrated in FIG. 21 to a second position, the finger 283 on the release platform 263 of the closing spring no longer engages the projection 281 on the slide but moves freely on the slide. recess 287 so that the release lever of the closing spring is not rotated with the release platform of the closing spring and consequently the closing spring 18 is not released. The slide 277 is urged by a spring 289 to the first position illustrated in FIG. 18 in which the actuation of the spring release platform 263 rotates the release lever 267 of the closing spring. The slide 277 is brought to a second position by a contact closure element in the form of a lobe 291 on the polar axis 33 that rotates to connect the end of the slide 277 and moves it to the second position in which the release of the closing spring is exceeded when the contacts 43 close. The slide 277 is also brought to the second position, overpassed, by a projection 293 on the firing platform 259 which projects normally into a notch 295 in the upper part of the slide 277. However, if the locking bolt D 213 is operated so that the firing platform 259 is rotated clockwise, the projection 293 is linked to the slider 277 at the end of the notch 295 and moves it to the second position illustrated in figure 21. Accordingly, if the trigger mechanism 203 is actuated, the closing spring assembly 225 does not it can be activated. It should be noted that neither the trigger mechanism 203 nor the closing spring lock assembly 225 require any adjustment. The holes in the side plates 97 in which the locking bolts 213 and 239 are received provide sufficient alignment so that a good locking engagement is ensured. It should also be noted that bearings are not used with any of the locks or their associated parts. The holes drilled in the side plates 97 provide all the support requirements due to the relatively light loads and low speeds of these parts. In addition, the interlocking mechanism does not require lubrication since the parts are made of a highly lubricated molded plastic. As mentioned, a closing pressure button 23 and an opening pressure button 25 are provided to close and open the contacts 43 of the circuit breaker, respectively. These buttons are mounted directly on and form part of the modular operating mechanism 17. As can be seen in Figures 22-24 and 26, the buttons 23 and 25 are molded, generally flat elements having a transverse internal hole 297 at the lower end thereof. it is open along a side edge 199 less than 180E and preferably about 160E. These two molded buttons 23 and 25 are rotatably mounted on a common pivoting element 301 which extends through the side plates 97. The portion of the common pivoting element 301 between the side plates 97 is formed by one of the spacers 101 which fix the spacing between the side plates, as previously discussed. The threaded shaft 103 extends beyond the right side plate 97 of FIG. 22 and supports a sleeve 303 that forms a cylindrical member of the same diameter as the spacer 101. An operating finger 305 secured to the top of the pressure button of closure 23 extends along the right side plate 97 transverse to the common pivot where it engages finger 283 on the release platform 263 of the closing spring to release the closing spring when it is pushed into the actuated position. This pressurized closing button 23 is pushed to the non-driven position by a torsion spring 307 (see figure 26) and the spring 231 pushes the spring release platform 263 (see figure 4). Similarly, the snap button 25 has an operating finger 309 that extends along the left side plate 97 in Figure 22, again transverse to the pivot axis, and is linked to a flap 311 on the firing platform 259 to open the contacts when it is activated. The pressurized opening button 25 is pushed to the non-driven position by a torsion spring (not shown) similar to the spring 307. As discussed previously, mounting the push buttons on the operating mechanism 17 can make it difficult to align the the same with the openings of the housing. The present invention avoids this difficulty by providing a front plate 19 through which there is access to buttons 23 and 25 at opening and closing pressure. The faceplate 19 is also fixed to the operating mechanism in a manner to be discussed, and therefore presents no alignment problems for the push button in relation to the faceplate. The faceplate 19 is aligned behind the opening 21 in the cover 9 that forms part of the housing 3 for the circuit breaker (see Figure 1). The front plate 19 has a larger area than the opening 21 so that taking into account the tolerances of the various components, the opening 21 is always filled by the front plate 19 when the cover is placed on the operating mechanism. Another unique feature of the invention is the manner in which the faceplate 19 is mounted in a fixed position on the front of the operating mechanism 17. Referring also to FIGS. 24 and 25, it can be seen that the faceplate 19 is a planar element molded with pairs of integral top and bottom mounting tabs 315t and 315b, respectively. The faceplate is secured to the side plates 97 by mounting rods 317 which extend through the flanges 315 and the side plates 97. The lower flanges 315b are laterally spaced so as to abut the side plates 97 and so on. both laterally fix the position of the faceplate 19. The molded projection 319 extending rearwardly from approximately the center of the faceplate 19 is linked with a notch 321 at the front edge of a side plate 97 for vertically fixing the position of the front plate. The invention also saves the problems usually associated with the alignment of the charge / discharge indicator 27 of the closing spring and the open / closed indicator 29 of the contacts with the openings in the housing. According to the invention, the indicators 27 and 29 are mounted directly in the openings 323 and 325 in the front plate 19 as illustrated in Figures 24-27. As illustrated in Figure 27, molded indicators such as the loaded / unloaded indicator 27 are molded with an arched front face 327. The first and second loading and unloading states of the loading spring are indicated by the DOWNLOADED legend and the symbol of a relaxed spring in the lower half of the arched face 327, and the CHARGE legend and the spring symbol compressed in the upper half. The detachable contact state is provided by the OPEN and CLOSED legends on the arched face of the indicator 29. The indicators 27 and 29 are rotatably mounted in the openings 323 and 325 in the front plate 19 by integral flanges 329 molded on the back of the faceplate along the openings and have pivoting pins 331 confronted. The indicators are rotatably supported on the bolts 331 by supports in the form of backward integral integral flanges 333 having openings 335 into which the bolts 331 engage to rotatably capture the indicators. The indicators 27 and 29 are rotated between their respective indications by "pressure action" actuators 337 and 339. By "pressure action" it is meant that the indicators 27 and 29 have discrete positions indicating the two states of the closing spring and the contacts. They do not change slowly from one indication to the other, but by a discrete movement jump from one to another. The "snap action" actuator 337 for the closing recess indicator 27 includes the camshaft 115. As previously described, the cam member 171 which is mounted on the cam shaft 115 loads the closing spring 18 a through half of its rotation and delivers the energy stored in the spring to close the contacts 43 during another portion of rotation. Accordingly, the rotational position of the cam shaft 115 to which the cam member 171 is attached, provides a positive and reliable indication of the state of charge of the spring 18. As illustrated in FIGS. 28-30, the outer end of the shaft cams 115 projecting beyond the side plate 97 have a cylindrical peripheral surface 341 with a radial discontinuity provided by a recess 343 formed by a plate on the camshaft 115. For coupling the rotary position of the camshaft 115 to the flag or loaded / unloaded indicator 27, an actuating element in the form of a lever 345 pivoted at one end to the swinging bolt 127 is urged towards the camshaft 115 by a tension spring 347. As can be seen in figure 28, the second end of the actuating lever 345 abuts against the cylindrical peripheral surface 341 of the camshaft 115 when the closing spring 18 is fully discharged. A wire shaped 349 linked in one end by the actuator element is mounted for vertical movement by a pair of guides 351 molded on the rear part of the front plate 19 (see also figure 25). A finger 353 on the upper end of the wire 349 is engaged with a notch 355 in the indicator tab 333 to the rear of the pivot for the indicator 27. The DISCHARGED legend is shown with the closing spring fully discharged. As the closing spring 18 is loaded through the rotation of the cam element 115, the camshaft rotates counterclockwise as illustrated by the arrow in figure 28. The actuator lever 345 remains at rest against the cylindrical peripheral surface 341 on the camshaft 115 as the camshaft rotates approximately 175E degrees to the position illustrated in Fig. 29. As discussed above, the load cam 173 reached a peak at 170 degrees and is now being driven by the loading spring. As illustrated in Figure 29, the actuator lever 345 is right over the edge of the recess 343 in the camshaft 115. As the spring 18 rotates the cam to the closed position illustrated in Figure 30, the second end of the cam actuating lever 345 falls from the cylindrical surface 341 on the camshaft 115 and into the recess 343. This sets the flag indicator 27 by discrete movement to the loaded position with the legend CHARGED at the advantage 323. The driving lever 345 is retained in the the recess 343 by a stop 357 formed by a notch in the bushing collar 117 of the cam shaft. The closing spring is released such as by pressing the closing button 29 or by actuating a closing solenoid. The sudden release of the energy stored in the closing springs 87 (see Figure 2) rapidly rotates the cam shaft 115 in the direction of the arrow illustrated in Figure 30 to the fully discharged position illustrated in Figure 28. It can be seen on the basis of FIG. 30, the planh on the cam shaft 115 pushes the actuator lever 345 downwards until the second end is connected to the cylindrical peripheral surface 341 again as illustrated in FIG. 28. The indicator flag of FIG. open / closed 29 which provides an indication of the state of the contacts 43 is driven by the polar axis 33 which provides a positive indication of the contact state. As illustrated in FIGS. 31 and 32, the pressure actuator 339 for the indicator 29 includes a generally L-shaped open / closed actuator 359 that is rotatably mounted on the pivoting pin 229 of the closure strut. A bolt 361 mounted on an arm of the open / closed actuator 359 is urged against a shoulder 363 in an open / closed slide 365 by a tension spring 367. The open / closed slide 365 is an elongate element that is slidably mounted on the pivoting pin 229 of the closing strut by a slot 369 at one end and on a pin 371 at the other end by an elongated slot 373. A second arm 375 in the open / closed actuator 359 has a slot 377 that is linked by the end folded bottom 379 of the wire 381. The upper end 383 of the wire 381 is bent laterally to engage with the notch 384 in the indicator 29. The wire 381 is supported between the ends by molded guides 385 on the back of the plate front 19. The open / closed slide 365, the open / closed actuator 359 and the shaped wire 381 comprise a drive link connected to the open / closed indicator 2 9. With the contacts 43 closed, the pressure actuator 339 for the open / closed indicator 29 is urged by the spring 367 to the position illustrated in figure 31 in which the open / closed indicator flag 29 is rotated downward to that the CLOSED legend be represented in the advantage 325. When the contacts 43 are opened, the polar axis 33 is rotated to the position illustrated in figure 32 where the lobe 387 of the polar axis is linked to the open / closed slide 365 and the drive to the right. This rotates the open / closed actuator 359 clockwise which in turn pulls the wire 381 down to rotate the open / closed indicator flag 29 counterclockwise which represents the legend OPEN in window 325. The polar axis 33 is rapidly rotated by the closing spring 18 from the open position illustrated in FIG. 32 to that illustrated in FIG. 31 to close the contacts. This rapid action causes the open / closed indicator flag 29 to be changed from the OPEN legend to the CLOSED status legend of the contacts under the influence of the spring 367., the pole axis 33 rapidly rotates to the position illustrated in FIG. 32 when the contacts are opened by the springs 87. It should be noted that the open / closed indicator is pushed to the "closed" position and only jumps to the open position during the last part of the rotation of the polar axis. Thus, if the contacts are closed soldiers, the indicator will continue to represent the "closed" indication unsafe. As discussed previously, the closing spring 18 can be manually or electrically charged by means of the rotation of the camshaft 115. The actuator mechanism 387 for manually or electrically rotating the camshaft 115 is illustrated in Figures 33-37. This actuator mechanism 387 includes a pair of ratchet wheels 389 a and 399b keyed to planks on the camshaft 115. Also keyed to the camshaft between the ratchet wheels 389 is a handle decoupler cam 391 and an engine decoupling cam 393 Bolts 395 engage the cams 391 and 393 to the ratchet wheels 389 so that torque is transmitted from the ratchet wheels on the camshaft 115 through the cams 391 and 393 as well as through the ratchet wheels directly. . The ratchet wheels 389 are rotated by the loading handle 31 through a handle actuator link 397 formed by two links 397 a and 397 b having only the link 397 b a cam surface 399 near the free end. This free end of the handle actuator link 397 extends between a pair of ratchet wheels 389 and has a handle actuator bolt 401 that can be engaged with peripheral ratchet teeth 403 on the ratchet wheels. The other end of the handle actuator link 397 is rotatably connected to the handle 31 by a pivot bolt 405. The handle 31 is rotatably mounted on an extension of the swing bolt 127 and is retained by a clamp at C 407. A latch lock 409 made of a pair of plates 409 a and 409b also rotates on the swing bolt 127. This stop lock 409 also extends between the ratchet plates 389 a and 389 b and has a transverse stop bolt 411 that is engaged with the ratchet teeth 403 A tension spring (see figure 36) pushes the handle actuator link 397 and the stop lock 409 toward each other and in engagement with the ratchet wheels 389. In addition, there is a torsion spring 415 mounted on the swing bolt. 127 and has a leg 415 which abuts against the underside of the handle and pushes it towards a stored position such as that illustrated in figure 33 and a second arm 415b which rests against the side d below the stop lock and also pushes it towards the ratchet wheels 389. Another unique feature of the invention is the configuration of the ratchet teeth 403 and the drive pin 401 and the stop bolt 411. As illustrated in the view FIG. 35, the ratchet teeth 403 are of arcuate configuration and have roots 403r having a radius that complements the spokes of the handle actuator bolt 401 and the stop bolt 411. This configuration reduces stress concentration in the roots of the ratchet teeth 403 and also facilitates the manufacture of the ratchet wheels 389 since they can be easily stamped starting from flat initial material. The use of turned bolts for the handle actuator bolt 401 and the stop bolt 411 also eliminates the stress concentrations created by the usual drive teeth and straight edge stop. The closing spring 18 is manually loaded by pulling the handle 31 downwards in a clockwise direction as seen in Figures 33, 34 and 36. As the handle is pulled down, the handle actuator bolt 401 is linked to a tooth 403 on each of the ratchet wheels 389a and 389b to rotate the camshaft 115 clockwise. The springs 413 and 415 allow the stop lock to pass over the ratchet teeth 403 that rotate clockwise. At the end of the handle race, the torsion spring 415 returns the handle 31 to the stored position. Again, the spring 413 allows the handle actuator bolt to pass over the teeth which are held stationary by the stop lock 409. As the handle 31 is mounted on the swing bolt 127 instead of the cam shaft 1156 so that it rotates about of an axle that is parallel but laterally spaced from the axle of the ratchet wheels, the actuator link 397 can be connected by the pin 405 to the handle 31 at a point that is closer to the axis provided by the pivot pin 127 than the spokes of the ratchet wheels 389 a and 389b. This arrangement provides a greater mechanical advantage for the handle 31 which, of course, is significantly longer than the spokes of the ratchet wheels 389 a and 389 b. The handle 31 has a reciprocating reciprocating motion to rotate in increments the ratchet wheels 389 and thus the cam shaft 115 to load the spring 18. As the spring 18 becomes fully loaded, the handle decoupler cam 391 rotates to a position where the cam lobe 391 a is linked to the cam surface 399 on the handle link plate 397b and lifts the drive link 397 upwardly so that the handle actuator bolt 401 is disengaged from the ratchet teeth 403 of the ratchet wheels 389. Thus, once the closing spring 18 has been loaded and the closing strut 223 is seated against the cam member 171 (as illustrated in Figure 14), the handle 31 is disconnected so that force can no longer be applied to try to rotate the cam shaft 115 against the locking strut 223. When the closing spring 18 is released, the camshaft 115 rotates rapidly. It has been found that as this occurs the rebound of the handle actuator bolt 401 by the rapidly rotating ratchet teeth 403 causes the handle 31 to spring from the stored position. This is prevented by an arrangement through which the actuator bolt 401 is disengaged from the ratchet teeth 403 with the handle in the stored position. In one embodiment, a lateral projection in the form of a cover plate 417 on the upper portions of the handle actuator link 397 accomplishes this function. This cover plate 417 rides on the upper portions of the ratchet teeth 403 with the handle in the stored position thereby lifting the handle actuator bolt 401 out of the ratchet teeth 403 as illustrated in Figure 33. This does not interfere with the normal operation of the handle 31, because as the handle is pulled downward the cover plate 417 slides along the teeth until the handle actuator bolt 401 falls in engagement with a tooth 463 on each of the ratchet wheels 389. Preferably, the cover plate 417 is molded into an elastic resinous material. The drive mechanism 387 also includes a motor operator 419 which includes a small high torque electric motor 421 with a gearbox 423. A mounting plate 425 connects the optional motor operator 419 to the side of the operating mechanism 17 at points of support including the spring support bolt 141. As can be seen in figures 36 and 37, the output shaft (not shown) of the gearbox has an eccentric 427 to which a link is mounted by the pivot bolt 429. motor actuator 431. The actuator link 431 is fabricated with two plates 431 a and 431b supporting adjacent a free end a transverse, motor-driven motor pin 433. A support 437 supports a tension spring 439 which urges the motor drive link 431 counterclockwise as can be seen in figure 37. A V-shaped plastic stop 432 supported by a flange on the support 437 centers the motor drive link 431 pair to an appropriate alignment to engage with the ratchet wheel 389. As can be seen in figure 36, with the motor operator 419 mounted on the side of the operating mechanism 17, the spring 439 urges the motor drive pin 433 in engagement with the ratchet teeth 403 of the ratchet wheels 389. The operation of the motor 421 rotates the eccentric 427 which reciprocates the motor drive link 431 to obtain the repetitive rotation in increments of the ratchet wheels 389. When the closing spring 18 becomes fully loaded, the uncoupling cam of the motor 393 rotates to a position (no illustrated) where the lobe 393 a is linked to the cam surface 435 on the motor drive link 413 a and lift the motor drive link 431 off the ratchet wheel 389 so that the motor drive pin 433 is disengaged from the ratchet teeth 403. Again, this prevents the continued application of torque to the camshaft which is prevented from rotating by the clamp 223. or time, a motor cutting cam 441 (see figure 33) mounted on the end of the camshaft 115 outside the ratchet wheels 389 rotates to a position where it is linked to an engine cut-off microswitch 443 mounted on a platform 445 secured to the mounting plate 425. The axially extending cam surface 441c drives the switch 443 to shut down the engine 421. An alternative arrangement for uncoupling the handle actuator bolt 401 from the ratchet teeth 403 and the ratchet wheels 389 is illustrated in Figure 38. In this embodiment, a lifting element or stop in the shape of, for example, a sleeve 447 is fixed to the side plate 97 adjacent to the ratchet wheel 389 by a screw 449. As the handle 31 is returned to the stored position, illustrated with full line in figure 38, the cam surface 399 on the actuator link 397b is linked to an elevator element 447 and rotates to the actuator link in a clockwise direction, as illustrated in the figure, to disassociate the actuator bolt 401 from the ratchet teeth 403. Thus, when the closing spring is released and the ratchet wheels rotate rapidly, the actuator link is kept apart from the wheel of ratchet and the handle 31 is not disturbed. When the handle is pulled clockwise, rotate approximately 15 degrees to the position shown in dotted line in figure 38 in which the actuator bolt 401 is reattached to the ratchet teeth 403. Both this elevator element 447 and the cover plate 417 provide this movement of approximately 15 degrees of the handle before the ratchet tooth is attached. This allows the user to obtain a firm grip on the handle before the handle is loaded. As previously discussed, the main components of the operating mechanism 17 are mounted between the side plates 97 and supported thereon. This produces a modular operating mechanism that can be assembled separately. All the components are standard, only the closing spring being different for the different current values. In this way, the operating mechanisms can be fully assembled and maintained in the inventory except the closing spring that is selected and installed for a specific application when it is identified. This mounting arrangement of all components between or to the side plates also eliminates the need for many fasteners, since the parts are captured between the side plates as discussed above. Also, to rotate the axles with light loads, separate bearings are not required since the fixed alignment of the side plates ensures shaft alignment, and the openings in the side plates provide sufficient support. In this regard, the axle openings are punched which, as is known, produces a thin annular surface in the punched opening thinner than the thickness of the plate which serves as a bearing. This modular construction also simplifies the assembly of the operating mechanism 17. As illustrated in Figure 4, the operating mechanism can be built on one of the side plates 97. With all the parts installed, the other side plate is located on top and is secured by the nuts 105 (see figure 3). To facilitate assembly, the various all axes, all of which have the same length to be captured between the side plates, have varying lengths of ends of reduced diameter that are received in openings in the side plates. Thus, as schematically illustrated in Figure 39, the bolts 451 a-451d all have a reduced diameter end 453 a-453d of the same length inserted into the openings 455 a-455d of one of the side plates 97x. After all the other components (not illustrated in Figure 40) have been installed, the second plate 972 is placed in the upper part so that the second ends 457 a-457d of the axes 451 a-451d can be in register with the openings 459 a-459d. In order for all the bolts to have to be inserted into the openings in the upper plate 972 simultaneously, the reduced diameter end 457 a is longer than the others and can be inserted into its associated opening by itself first. As the plate 972 is lowered, the shorter end 457b of the bolt 451b is inserted into its opening 459b. Each axis is also connected to the plate 972 as the plate is successively lowered, but all the pins do not have to be aligned simultaneously. Although specific embodiments of the invention have been described in detail, those skilled in the art will appreciate that various modifications and alternatives to these details can be developed by considering the teachings of the disclosure. Accordingly, the particular provisions described are only illustrative and not limiting with respect to the scope of the invention that is given by the scope of the appended claims and any or all equivalents thereof.

Claims

CLAIMS 1. An operating mechanism for electrical switching devices, comprising: a closing spring mechanism comprising a closing spring, and means for loading said closing spring and including a cam member coupled to and driven by said closing spring. when the closing spring becomes fully loaded; a pivotally mounted locking strut having a bolt position in which it links and prevents rotation of said cam member and a non-closed position in which it disengages from said cam member so that said cam member is free to to be rotated by said closing spring; biasing means biasing said closing strut to said non-closed position; a bolt assembly connected to said closing strut and locking said closing strut in said bolt position when it is reset; and resetting means that reset said bolt assembly by rotating said cam member toward said closing strut. The operating mechanism of claim 1, wherein said resetting means comprises a pivotally mounted reset lever having a reset finger linked by said cam member when said cam member is rotated, said reset lever engaging said strut closing and rotating said closing strut against the polarization applied by the polarization means to said bolt position and resetting said bolt assembly to close said closing strut in the bolt position. 3. The operating mechanism of claim 2, wherein said bolt assembly includes a pivotally mounted bolt plate having a bolt spine, a bolt link connecting said bolt plate to said bolt strut for joint rotation, and a bolt lock arrow capable of turning having a release notch, said bolt spine connecting said bolt lock arrow with said bolt lock arrow in a loaded position and said bolt lock arrow falling from said bolt arrow of closure so that said lock plate is pulled through said notch by said biasing means and said closure strut rotates to said non-closed position when the lock latch arrow is rotated to a release position. 4. The operating mechanism of claim 3, wherein said closing strut and said reset lever are mounted on a common pivot shaft. The operating mechanism of claim 4, wherein said reset lever or said closing strut has a lateral projection that links the other to rotate said closing strut to the closed position when the finger on said reset lever is linked by said cam member and which lateral projection places the reset lever to be linked by said cam member when the bolt arrow is rotated to the release position and the polarization means rotates the closure strut to the non-closed position. The operating mechanism of claim 5, wherein said cam member has a stop member that is engaged by said closing strut, and a reset member in front of said stop member that links and actuates said restoring means. The operating mechanism of claim 2, wherein said cam member has a stop member that is engaged by said closing strut, and a reset member in front of said stop member that links and actuates said restoring means. The operating mechanism of claim 7, wherein said loading means includes ratchet means that produce retraction of said cam member and including spring means that bias said reset lever to engage said closure strut but allow said The reset lever is moved away from said closing strut by said reset member in said cam member in response to the retraction of said cam member. 9. The operating mechanism of claim 8, wherein said closing strut and said reset lever are mounted on a common pivot shaft. The operating mechanism of claim 9, wherein said reset lever or said closing strut has a lateral projection which links the other to rotate said closing strut to the closed position when the finger on said reset lever is linked by said cam member and which lateral projection places the reset lever to be linked by said cam member when the bolt arrow is rotated to the release position and the polarization means rotates the closure strut to the non-closed position. SUMMARY An electrical switch apparatus such as an energy circuit breaker, network protector or switch has a self-supporting operating mechanism module that includes a cage formed by a pair of side plates rigidly held in space spaced relation. The cage supports all components of the operating mechanism that include a helical compression closure spring fully mounted between the side plates and coupled to a cam member via a rocker arm in a manner that maintains longitudinal forces to the spring. The cam member has a load cam with a load profile for compressing the closing spring and a closing profile through which the spring drives the cam element to effect a controlled release of stored energy to close the contacts of the apparatus . A locking strut, spring-loaded to an unlocked position, is locked to secure the closing spring in the state loaded by a locking assembly restored by a separate reset lever of the closing strut which in turn is reset by the rotation of the cam element during loading. An interlock prevents the release of the closing spring when the contacts are closed or the trigger release is activated. An indicator actuated by an actuator pivoted against the cam shaft passes from a discharged to loaded indication as the closing spring becomes fully loaded and the actuator falls into a notch created by a flat on the camshaft. An open / closed pressure action indicator for switch contacts is also provided. Both indicators are rotatably mounted on a front plate bolted to the side plates and are connected to the operating mechanism by shaped wires. The pressure buttons of closing and opening are linked by pressure to a common axis and have actuating fingers that trigger releases in the operating mechanism. The rotary closing shafts are connected only in confronted openings in the side plates. The camshaft is captured between bushings seated in non-circular openings in the side plates eliminating the need for fasteners. Likewise, other parts mounted between the side plates and joined by bolts having enlarged heads retained by the side plates do not require detents. Various axes extending between the side plates have ends of reduced diameter of progressive lengths for successive insertion into a side plate to aid in the assembly of the operating mechanism.