The invention disclosed herein pertains to a multiple position rotary switch.

Rotary switches are used in many applications for switching electric current values of 1mA to 25 amperes. Rotary switches of the indicated ratings are freguently used as control and function selectors in major domestic appliances such as dish and clothes washing machines and clothes dryers. The environment in these machines is usually wet, humid and soapy and is, therefore, hostile to electrical devices such as switches, connectors, and so forth. In the case of a rotary switch in such appliance, it is highly desirable for it to be sealed against entry of moisture. One difficulty in preexisting rotary switches is that they often have backlash or freeplay which gives the user a poor feel as if there is elasticity in the parts when the switch is indexed by turning the operating shaft. A corollary to this is that the shaft feels unstable and, often is actually unstable, when the switch is being indexed rotationally from one position to another. Another difficulty has been to properly seal the switch against entry of contaminants along the switch operating shaft and where the lead wires enter and exit the switch. If the lead wires are not properly sealed and anchored, besides allowing entry of

_n „, _nM „ PCT US96/13452 97/08721

- 2 -

contaminants, physical forces on the lead wires externally of the switch housing can distort or dislocate the contacts inside of the housing, thereby causing the switch to operate erratically or fail completely.

Summary of the Invention

The rotary switch described herein overcomes the above mentioned and other difficulties and problems experienced in preexisting rotary switches.

According to the invention, the new switch design comprises a base composed of nonconductive material such as synthetic resin. A common electric contact strip or bar is mounted fixedly to the base interiorly of the switch housing. A plurality of deflectable or bendable contacts composed of flat spring metal are mounted to the base such that the tips of the contacts are positioned above the stationary common electric contact bar. The switch includes a basically conventional rotor comprised of a disk having an operating shaft extending axially from it in one direction and a plurality of concentric curved riser cam segments extending in the opposite direction from the disk such that when the rotor is turned the cam segments press on the flexible spring contacts in a predetermined sequence. Pressing a spring contact causes its tip, to touch the metal stationary contact bar and make electrical contact therewith. The rotor disk has a toothed index wheel molded integrally with the shaft and disk. A plastic double-legged spring is mounted to the base and has facing convex offsets, constituting detents, on the long legs of the spring on opposite sides of the index wheel and in contact with the index wheel.

The index wheel has equiangularly arranged grooves in its periphery. The grooves are spaces between index teeth. The two convex detents have, according to one feature of the invention, radii that are greater than the radii of the grooves between index wheel teeth so only two tips of two teeth at one time can stay in contact with the spring detents when the rotor turns. Several variations of the spring are presented, all of which assure elimination of hysteresis, the feeling of elasticity, freeplay and backlash from the switch.

Springs are known which have two parallel legs that exert a detent force on an index wheel in a rotary switch so the wheel and rotationally driven cams increment rotationally in discrete switch contact operating steps. Applicants have discovered that it is the parallel legged springs used in conventional ways that causes the freeplay, the loose and the unstable feeling that is unpleasant to one rotating the switch shaft. Applicants have also discovered that maintaining the legs of the spring in tension at all shaft rotational angles overcomes the shaft rotational instability problems. Several modified forms of a two legged spring that experiences tension are disclosed herein. Description of the Drawings

FIGURE 1 is a perspective view of the new rotary switch as it appears when it is ready for installation; FIGURE 2 is an exploded perspective view showing the major parts of the rotary switch;

FIGURE 3 is a perspective view of one model of several alternative models of a unitary rotor used in the new switch; FIGURE 4 is a sectional view taken on a

line corresponding to 4-4 in FIGURE 1;

FIGURE 5 is a vertical sectional view taken on a line corresponding to 5-5 in FIGURE 4;

FIGURE 6 is a vertical sectional view taken along a line corresponding to 6-6 in FIGURE 4;

FIGURE 7 is a fragmentary sectional view taken on a line corresponding to 7-7 in FIGURE 5 showing one of the movable switch contacts in detail and in unoperated position and showing the cam on the depicted rotor in readiness for deflecting the movable switch contact for its tip to make contact with the stationary common contact bar;

FIGURE 8 is similar to FIGURE 7 except that the rotor is rotated sufficiently for one of its cams to deflect a movable switch contact;

FIGURE 9 is a fragmentary sectional view showing how a spring, complying with the general nature of the spring embodiments disclosed herein, deforms as the index wheel of the rotor is halfway between two angularly adjacent index positions;

FIGURE 10 is a magnified view of a part of FIGURE 7 showing how the contours of the double- legged spring detent and the index wheel mate when the index wheel is in a quiescent angular position; FIGURE 11 is a vertical sectional view taken on a line corresponding to 11-11 in FIGURE 4 with some parts omitted and showing one form of the double-legged spring;

FIGURE 12 is a fragmentary vertical sectional view taken on a line corresponding with 12-12 in FIGURE 11;

FIGURE 13 is a front elevational view of a double-legged spring of conventional type but is used in accordance with the invention; FIGURE 14 is a side elevational view of the

spring depicted in FIGURE 13;

FIGURE 15 is a vertical sectional view taken on a line corresponding to ll-ll in FIGURE 4 but a different double-legged spring is substituted for the spring shown in FIGURE 11 although all other parts of the FIGURE 15 switch are the same as in the FIGURE 11 switch;

FIGURE 16 is a vertical sectional view taken on a line corresponding with 11-11 in FIGURE 4 but a different style of the double-legged spring is substituted for the spring in FIGURE 11 although other parts of the FIGURE 16 switch are the same as the FIGURE 11 switch;

FIGURE 17 is a vertical sectional view taken on a line corresponding to 11-11 in FIGURE 4 but the double-legged spring differs from the spring in FIGURE 11 by reason of the FIGURE 17 spring having diagonally opposite ends of the legs T-shaped and restrained in slots that have elements for preventing the spring legs from moving longitudinally when the spring legs are stressed longitudinally by the rotating index wheel;

FIGURE 18 is a fragmentary section taken on a line corresponding with 18-18 in FIGURE 17; FIGURE 19 is a vertical sectional view comparable to FIGURE 17 except that the spring in

FIGURE 19 has both ends of both legs terminated in

T-shaped ends which are restrained in slots that differ in configuration from the slots in FIGURE 4; FIGURE 20 is a vertical sectional view taken on a line corresponding with 11-11 in FIGURE

4 but the double-legged spring differs from the spring in FIGURE 11 by reason of each of the legs of the spring in FIGURE 20 terminating in L-shaped ends;

FIGURE 21 is similar to FIGURE 17 except that in FIGURE 21 the toothed index wheel is rotated to where the tips of diametrically opposite teeth on the index wheel are passing the midpoints of the convex detent formations on legs of the spring;

FIGURE 22 is a vertical sectional view taken on a line with 11-11 in FIGURE 4 but the configuration of the ends of the spring legs and the configuration of the slots which contain the spring ends differ from other of the embodiments; and

FIGURE 23 is a vertical sectional view taken on a line corresponding with 11-11 in FIGURE 4 but the configuration of the ends of the spring legs and the configuration of the slots which contain the spring , ends differ from most of the embodiments except FIGURE 22. Description of a Preferred Embodiment

FIGURE 1 shows the improved operably stable switch fully assembled. The switch comprises a molded plastic housing 10 from which four lead wires marked 1, 2,3 and 4 extend. The switch is operated by rotating a shaft 11. The depicted model of the switch described herein responds to rotation of shaft 11 by changing the digital logic signal levels of the individual output leads between 0 and 1. The switch has many uses such as in major home appliances, including clothes washers, dryers and dishwashers, for example. Major appliances using state-of-the-art technology usually have a microprocessor based controller, not shown, controlling the functions of the machine that are to be performed at the proper times. The new rotary switch provides digital signals that the processor interprets and causes a programmed function to be performed.

FIGURE 2 is provided for identifying the major parts of the rotary switch. The switch includes a molded base member 13 comprised of plastic insulating material. Base member 13 has a flat back wall 14. A stub shaft 15 projects integrally from the back wall 14. An elongated contact element or bar 16 is shown in position for being inserted and installed stationarily on the back wall 14 of base member 13. Stationary contact element 16 is basically a flat, rectangular bar 17 having a stop edge 18 formed at a right angle to the flat bar 17. The contact element or bar 16 has a hole 19 which fits onto a plastic nib 20 projecting from the back wall 14 of base 13. After contact element 16 is fitted on the nib, the nib is heat swaged or flared to retain the contact element stationarily.

One edge 21 of base 13 in the illustrative embodiment of the switch in FIGURE 2 has five notches 22-26. Not all of the notches are used in this version of the switch. In any version, a notch such as notch 26 is for accepting an insulated lead wire 3 which is also shown in FIGURE 1. Typical lead wire 3 is electrically connected to a flat portion 27 of a thin spring metal contact 28. The typical deflectable spring contact 28 is preferably composed of phosphor-bronze. Typical spring contact 28 has two essentially flat portions 29 and 30 that are mutually angulated to create an offset which is herein called a knee 32. Contact 28 has a contact tip 31.

Observe in FIGURE 2 that typical spring contact 28 has a hole 33. There is a row of molded pins, such as the pin marked 34, shown in FIGURES 2 and 4, projecting from base member 13. The hole 33

and contact 28 slides over typical pin 34. By placing the hole 33 on pin 34, the flat portion 27 of contact 28 becomes captured between ribs 35 and 36 which project from base member 13. When the spring contact 28 is in place, for example, its lead wire 3 is pressed into a notch 26 on the upper rim of base 13. Ultimately, when base member 13 is fitted into housing 10, the back of the base is sealed around its edges with a resin, such as an epoxy resin, so the lead wire 3 becomes bonded in notch 26 and the epoxy seals around the joint between the perimeter 13 of the base and the interior perimeter of the housing as will be explained in more detail later. In FIGURE 2, a rotor 41 is molded unitary with shaft 11, with a rotor disk 42 and with a toothed index wheel 43. A shaft end portion 44 has an axial bore 37, not visible in FIGURE 2, but shown in FIGURE 3, which constitutes a journal bearing fitting on a fixed stub shaft 15 which projects integrally from base 13. The side of rotor 41 to which the arrowheaded line 45 points has a plurality of concentric spring contact operating riser cams which will be exhibited in other views and will be discussed later.

Rotor 41 has a stop element segment 46 on a side facing the viewer in FIGURE 1. The angle subtended by segment 46 determines the angle through which the shaft 11 and, hence, rotor 41 can rotate in either direction between stops which are not visible in FIGURE 2. This angle can differ among different versions of the rotary switch used in different applications.

A double-legged detent spring 50 composed of plastic is shown in FIGURE 2. Springs of this

configuration are known per se but the spring is modified and applied, according to the invention in such a way that is vital to eliminating rotor freeplay and backlash. Expressed in another way, in the new rotary switch the spring is mounted in a manner that eliminates backlash and takes away the poor feel that a user perceives when turning many preexisting rotary switches. The particulars of various embodiments of the spring and its application will be discussed later. It is sufficient to mention at this time that the spring 50 coacts with index wheel 41 in the new assembled rotary switch to give the user who turns the shaft a feeling of constancy with an absence of any freeplay or backlash.

As shown in FIGURE 2, an O-ring 51 is sized to fit on shaft 11 next to index wheel 43 to effect a seal between shaft 11 and an annular channel 52 surrounding a hole 53 for the shaft 11 in housing 10. The inside diameter of the o-ring is less than the outside diameter of the shaft so the o-ring is stretched to effect a tight seal between the ring and shaft. The outside diameter, being greater than the inside diameter of channel 52, results in the o- ring experiencing a compressive force when the o- ring is urged into channel 52 so a tight seal is formed between the outside diameter of the o-ring and channel wall.

A single piece rotor 41 is shown in FIGURE 3. All of the so-called versions of the rotor have in common shaft 11, end shaft journal 44 with the journal bore 37 for fitting rotatably on base stub shaft 15, a rotor disk 42 and an index wheel 43. Various versions of the rotor used in different applications of the switch differ in respect to the

number of and angular length of the switch contact operating concentric cams 60-64 which the rotor has. The illustrative rotor 41 in FIGURE 3 has formed on its axially remote of disk 42 from shaft 11, a plurality of concentric cam segments 60, 61, 62, 63 and 64. Both ends of each cam segment are tapered as typified by the tapered end marked 65 on cam 60. The tapered ends provide for the cams to ride onto the knees 32 of the spring contacts smoothly to urge the spring contact tips 31 into contact with the stationary common metal contact bar 16.

Attention is now invited to FIGURES 5-10. FIGURE 5 shows four spring contacts, generally designated by 28, installed on base member 13 on typical pins 34. A lead wire 3 extends from the typical contact A. A part of the flat area 27 of the spring contact A is stabilized against misalignment and turning on swaged plastic pin 34 by the end portion of the flat area being captured between the previously mentioned T-shaped ribs 35 and 36. The electric current interchange tip 31 of movable spring contact A overhangs the stationary contact bar 16. The rotor disk 42 is omitted but is symbolized by a phantom circle in FIGURE 5. Stationary contact bar 16 is electrically a common terminal for being contacted by all movable spring contacts 28. Bar 16 is blocked against shifting by reason of its upstanding margin 18 abutting a pair of stops 66 which project inwardly of a rim 67 of base 13. The swaged plastic anchor pin 20 holds the stationary contact 16 in a fixed position.

The profile of a typical contact A is shown supported in cantilever fashion in FIGURE 7. Cam 60 on disk 42 of rotor 41 has not been rotated onto

knee 32 of the movable or deflectable spring contact as yet in FIGURE 8. Hence, the tip 31 of the spring contact is not making electrical contact with the flat portion of stationary contact 16 as yet. In FIGURE 8, rotor 41 has rotated or has been indexed sufficiently for the tapered leading end 65 of cam 60 to apply a force on knee 32 which causes contact tip 31 to make physical and electrical contact with stationary bar contact 16. All spring contacts in FIGURE 5 are identical structurally to the spring contact which was just discussed. Contact B is a common contact. Its lead 4 is an input lead that is fed from a voltage source, not shown. The tip of power infeed common contact B makes contact with stationary contact 16 as soon as rotor 41 is turned through its first angular step from fully off position, that is, from an angular position where all spring contacts are not touching stationary contact bar 16 and the contact between spring contact B and stationary contact bar 16 is maintained until the switch is operated back to off position wherein none of the spring contact tips 31 are in electrical contact with stationary contact 16. If the housing 10 with the cams of the rotor 41 facing toward the observer in FIGURE 6 is flipped over and superimposed on the base 13 in FIGURE 5, the cams on the rotor become properly related to their cooperating contacts which the cams operate. Thus, voltage infeed contact B in FIGURE 5 is in the circular rotational path of radially innermost cam 63 in FIGURE 6. The first angular step of the rotor from off position results in connecting infeed common spring contact B to stationary contact 16 so that contact 16 is electrified at a voltage

corresponding to customary digital logic voltage of about five volts, for example. As is evident in FIGURE 6, the spring contacts are arranged in phantom mirror image to what they are in FIGURE 5, so as soon as the leading end of cam 63 is turned to an angle of 45 degrees in the direction of arrow 73, spring contact B makes contact with common stationary contact 16. In this particular version of the switch, cam 63 intercepts a central angle total 270° and would return to the angular position in which it is shown in FIGURE 6 after the rotor 41 has been rotated to 270°.

The next radially outwardly displaced cam 62 in FIGURE 6 acts on spring contact B when the rotor and, hence, cam 62 is rotated three angular increments of 45° each. Cam 62 subtends an angle of 135°.

The next radially outwardly displaced cam 61 in FIGURE 6 begins to act on spring contact C when the rotor and cam 61 rotate 45° from switch off position or 000. Cam 61 subtends and angle of 135°.

Radially outermost cams 60 and 64 operate spring contact B. When rotor 41 has turned two angular increments from switch off position, cam 64 operates spring contact D. After the next 45° increment of rotation, rotor 41 rotation, spring contact D opens because cam 64 subtends an angle of 45° which is one angular step. After the rotor rotates 270°, the cam 60 operates the spring contact to a conductive state again.

There are versions or models of the new switch where more or fewer cams and spring contacts are used in which case, fewer or more bits, respectively, for representing a binary number are needed. In the illustrative embodiment, three bit

digital numbers are sent to a microprocessor based controller, not shown, which means that, excluding zero position of the rotor, seven unique digital signals or logic states can be produced, and the processor could dictate execution of eight functions by a machine where all zero bit digital numbers are included.

A significant feature of the new rotor is that it gives a good feel to the user when shaft 10 is rotated because the rotor is stabilized at all times. This is achieved by the way a generally known double-legged spring 50 and cooperating index wheel 43 are refined structurally, in accordance with the invention, and in respect to the way they cooperate. One form of spring 50 is shown installed in switch housing 10 in FIGURE 13. The housing, as shown in FIGURE 11, has four interior slots 80, 81, 82 and 83. Typical leg tip portions 84 and 85 are shown registered in slots 82 and 83. Typical side legs 86 and 87 of spring 50 have centrally positioned curved convex detents 88 and 89, respectively. Legs 86 and 87 may be but are not necessarily tied together by lateral struts 79. In FIGURE 11 it is evident that, in a sense, the index wheel 43 is sufficiently large diametrically, compared to the distance between detents 88 and 89 so that legs 86 and 87 of the spring become deflected when the spring is pressed onto the index wheel 43. In other words, the spring 50 is prestressed even when the rotor shaft and, hence, the index wheel 43 are not rotating. In accordance with the invention, however, the convex radii of curvature of the detents 88 and 89 on the spring side legs are greater than the radius of curvature of the arc 90 between the tips 91 and 92 of any

consecutive index wheel teeth so a gap 93 exists between the convex typical detent 89 and the concave surface existing between two consecutive tips such as 91 and 92, of the index wheel 43. The gap 93 and the way the tooth tips 91 and 92 of the index wheel 43 bear on a detent 88 are more easily visualized in the FIGURE 10 magnified view. The tips 91 and 92 make line contact on the typical spring detent 88 as a consequence of the difference in radii between the typical detent 88 and index wheel tips 91 and 92 though no freeplay is present nor could any be felt, when a knob, not shown on shaft 11 is grasped manually to start rotation of rotor disk 42.

FIGURE 13 shows one type of double-legged spring that fulfills the antibacklash and zero freeplay objectives achieved with the spring and index wheel in accordance with the invention. The spring in this FIGURE appears on first impression to be comparable to a conventional spring of this type but it is not when used in the way it is used in FIGURE 12. A conventional spring would have side legs 86 and 87 of such length that the spring would drop freely into the slots 80-83 in the FIGURE 11 base and the legs would be parallel. Then when the index wheel 43 is inserted, according to prior practice, the legs would bulge outward away from each other and the tips of the legs would, respectively, pull away from the bottoms of the slots 80-83. Thus, there would be a gap between each leg to tip and the slot bottom. The consequence of this prior practice is that when the index wheel starts to turn the legs are stressed in opposite directions. The spring distorts, gaps at diagonally opposite ends of the legs get larger depending on the direction of rotation, and the

person turning the shaft 11 gets the unpleasant feeling of freeplay and looseness.

Applicants have discovered that the feeling of variable resistance and freeplay incidental to turning the shaft can be eliminated if the spring is stabilized at all times. Stabilization has been achieved in FIGURE 11 by making the legs, such as typical leg 87 of the spring, longer than the distance between the bottoms of the slots 80 and 81 so the spring must be forced into the slots 80-83. To facilitate accomplishing the forced fit and preloading of the spring legs, the ends 86A and 86B of typical spring leg 86 are beveled as shown in FIGURE 14. Alternatively, if one wants to limit the bevel angle to no more than is required for the draft a plastic spring needs to withdraw it from a mold one may resort to what is done in FIGURE 12 to facilitate forcing the spring into the slots. In FIGURE 12 the slot 83, which is isolated from FIGURE 11, has a beveled edge 100 so the square end of the spring leg tip 85 can be forced into slot 83.

FIGURE 15 illustrates restraining the tips of the spring legs in the slots in a manner that differs from the manner in which end-play of the spring legs is prevented in FIGURE 11. In FIGURE 15 typical tips 84 and 85 of typical spring leg 86 are anchored in the slots either by ultrasonic staking or with a bonding agent such as epoxy resin at places 101 and 102. The spring is installed in base 10 and then the index wheel 43 is pressed into the spring. If the slots are substantially larger than the size of the legs when ultrasound bonding is intended to be used, then it is desirable to insert a small fragment or powder composed of a compatible plastic to tighten the fit between the end of the

spring legs and the slot before applying the ultrasound.

In FIGURE 16 the spring 50 is stabilized by imparting tension to legs 86 and 87. In this embodiment the end portions, such as end portions 84A and 85A of spring leg 86, are provided with nominally T-shaped tips or extremities 103A. Slots 80A-83A are generally T-shaped. The end portions of the spring legs fit snugly through the slot openings 104. In this case, the T-shaped tips 103 have a crescent shaped cross sectional configuration such that two lines of contact 105 and 106 are made by the tips 103 on the wall of a slot as shown. Tension is maintained in legs 86 and 87 and pressure at the lines of contact 105 and 106 are enhanced by the forces developed when the legs are flexed apart by their detents 88 and 89 passing over the index wheel 43 during assembly of the spring to base 10. Although it is not apparent in FIGURE 16 there is, in fact, an increase in the radii of the detents 88 and 89 of the spring when the spring is fitted on the index wheel 43 so the detents do not bottom out in the grooves 90 of the index wheel as will be discussed in more detail later. In the FIGURE 16 embodiment, when the index wheel 43 is turned, the high points or teeth on the wheel must run along and finally toggle over the detents 88 and 89. However, since the legs 88 and 89 of spring 50 are flexed outwardly and prestressed even when the index wheel is at rest as depicted, the detents continuously apply a force on the index wheel as the wheel turns, thereby giving the person turning the shaft a solid feeling for all degrees of wheei rotation. As in all embodiments, in the FIGURE 16 embodiment, during assembly of the switch, the spring is installed in

the slots first and then the index wheel 43 is pushed into the spring.

In the FIGURE 17 embodiment the ends 103B of the spring 50 legs or sides 86 and 87 are T- shaped but the heads 103B of the T's are shaped slightly differently from the crescent shaped heads 103A in FIGURE 16. In FIGURE 17, the T-shaped ends 103B of the spring legs are disposed in slots 80B- 83B as are their counterparts in FIGURE 16. The ends 103B of the spring legs in FIGURE 17 are designated to develop a torsional moment of force on diagonally opposite ends of the spring to limit lateral motion of the spring. In this case, diagonally opposite slots 80B and 82B each have a pair of force concentrators 109 and 110 in them. The apexes of the triangularly shaped force concentrators engage the cross heads of the T's almost at the extremities of the heads. The head ends of the T's in diagonal slots 8IB and 83B do not require the cross heads but are provided to make the spring symmetrical so no attention need be given to which way the spring goes into the base slots 80B- 83B. In this embodiment, it is when the legs of the spring are flexed outwardly by assembly with index wheel 43 that the torque is applied to the T-head which torque is resisted by the force concentrators 109 and 110. The arrangement prohibits longitudinal motion of spring 50 for either direction of index wheel rotation. The presence of a T-head only on diagonally opposite spring ends is sufficient to prevent occurrence of any feeling of free play when the index wheel 43 is turned.

FIGURE 18 shows that the slots, such as 80B, have a bevel 112 to make insertion of the spring into the slots easier during switch assembly.

FIGURE 21 shows the desirable result of restricting the ends of the spring legs during passing of the peaks 91 of the teeth on the index wheel 43. The stabilizing force on the index wheel is the result of outward flexing of the spring legs

86 and 87. Regardless of the direction in which index wheel 43 turns in this case, the legs 86 and

87 will never go into tension because, although opposite diagonal spring ends in the slots 80B and 82B containing force concentrator 109 are fixed, the opposite spring ends in slots 8IB and 83B are free.

In the FIGURE 19 embodiment of the switch, all of the end portions of spring sides or legs 86 and 87 are T-shaped as indicated by numeral 103C. All of the slots 80C-83C are provided with force concentrators 109 and 110.

In the FIGURE 20 embodiment stability of the index wheel 43 throughout every rotational step is achieved by forming all end portions of spring legs 86 and 87 in the shape of the letter L. The end portions could also be characterized as being hook-shaped. A typical end portion of a spring leg has a part 120 which is at a right angle relative to typical leg 86. The legs or sides 86 and 87 of the spring are parallel before the index wheel 43 is inserted. When the index wheel is inserted the legs flex apart as shown in FIGURE 20 as well as in other FIGURES. Ends 120 reside in slots such as the slot marked 121. The end portion of a spring passes through the throat 122 of the slot with small clearance. The end 120 bears near its extremity on the apex 123 of a triangular force concentrator. Hence, when the index wheel 43 is installed, detent 88, deflects the legs 86 and 87 outwardly. The tension force acts through a moment arm constituted

by the short distance between straight leg portion 122 of the spring and the apex 123 of the force concentrator. When end 120 deflects by a small amount due to the tension force in the spring, the end 120 stores a force which tends to restore it to its undeflected state. Thus, when the tip 91 of the index wheel 43 passes beyond the center of a detent 88 or 89 during an indexing step the tension in the spring leg begins to decline. However, the stored force in the spring end 120 moment arm tends to keep the leg tension constant until the detents are fully registered in the recesses that are bounded by the teeth of the index wheel. As a result, the person turning the shaft of the rotary switch experiences a steady solid feeling throughout each indexing step with the complete absence of freeplay at the beginning and end of the step.

An alternative method of controlling end- play of spring legs 86 and 87 is shown in FIGURE 22 where one end of each spring leg 86 and 87 contains a circular compressible loop 124 with a radius about center 128 and fitting in circular recess 125 in base 10.

The other end of the spring leg 126 fits in a conventional manner in slot 127. It is to be understood that loop 124 may be oversize of recess 125 so that there is a slight compression in inserting the part during assembly thereby eliminating any free play at the beginning and end of the detent. This detail is repeated on spring leg 87.

Referring to FIGURE 23, spring legs 86 and 87 have at one of their ends a head 129 which fits snugly into recess 125 with the alternate end 126 being retained in a conventional fashion in slot

127. This is repeated on spring leg 87 and provides longitudinal restraint of the spring legs in spite of variations in molding tolerances and shrinkage to minimize free play at the beginning and the end of each detent step. The head 129 may be tapered to facilitate tight assembly into recess 125. Conversely, recess 125 may be tapered.

The fragmentary magnified view of the typical cooperating detent 88 of the spring and index wheel tooth tips 91 and 92 shows the gap 93 that results from the radii differences. According to prior practice, the contour of the detent is exactly complementary to the curve between typical index wheel tooth tips 91 and 92 and the convex contour of the detent. This results in an unstable feel on the shaft.

FIGURE 9 shows an index wheel 43A of slightly modified form as compared with wheel 43 in FIGURE 2. The wheel is half way through the process of indexing one angular step. When the index wheel 43A is at top dead center as it is in FIGURE 9, deflection of the spring legs 86 and 87 is substantial. Because the spring was prestressed by virtue of its tight fit on the index wheel at any time that the wheel is turned to a position where a cam on the disk is positively operating one of the spring contacts, the legs of the spring contact are stressed and deflected as exhibited in FIGURE 11.

FIGURE 4 illustrates the o-ring 51 in section on shaft 11. Observe that the o-ring is elongated axially of the annular cavity 52 in the housing and is also pressing snugly against the wall of cavity 52 and the shaft 11 to produce a very effective seal against water migrating into the switch housing along the shaft. The base member 13

is provided with four tabs 96 that snap into complementarily-shaped grooves in the housing 10 to retain the base member 13 in the housing.

The perimeter of the base member is configured such that in relation to the rim of the housing 10, a moat 97 is formed about the perimeter.

Moat 97 is filled with a sealant such as epoxy resin to form a water tight seal.

Refer now to FIGURE 6, which shows the cams 60-64 on disk 42 of illustrative rotor 41 in their entireties. That is, the cams are shown realistically as having tapered leading and trailing ends such as the typical end 65.