CA1229243A - Timer drive mechanism - Google Patents
Timer drive mechanismInfo
- Publication number
- CA1229243A CA1229243A CA000474810A CA474810A CA1229243A CA 1229243 A CA1229243 A CA 1229243A CA 000474810 A CA000474810 A CA 000474810A CA 474810 A CA474810 A CA 474810A CA 1229243 A CA1229243 A CA 1229243A
- Authority
- CA
- Canada
- Prior art keywords
- drive
- pawl
- cam
- mechanism according
- drive pawl
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000007246 mechanism Effects 0.000 title claims abstract description 29
- 230000003247 decreasing effect Effects 0.000 description 2
- 241001674048 Phthiraptera Species 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002674 ointment Substances 0.000 description 1
Classifications
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
- H01H43/00—Time or time-programme switches providing a choice of time-intervals for executing one or more switching actions and automatically terminating their operations after the programme is completed
- H01H43/10—Time or time-programme switches providing a choice of time-intervals for executing one or more switching actions and automatically terminating their operations after the programme is completed with timing of actuation of contacts due to a part rotating at substantially constant speed
- H01H43/101—Driving mechanisms
- H01H43/102—Driving mechanisms using a pawl and ratchet wheel mechanism
Abstract
TIMER DRIVE MECHANISM
ABSTRACT
A drive mechanism for a timer includes a drive paw having a pin which is trapped between two camming surfaces of a continuously driven drive cam. The drive paw is slidably mounted in the timer frame so that it is linearly reciprocated when the drive cam is rotated. A spring biases the drive paw against the ratchet track.
ABSTRACT
A drive mechanism for a timer includes a drive paw having a pin which is trapped between two camming surfaces of a continuously driven drive cam. The drive paw is slidably mounted in the timer frame so that it is linearly reciprocated when the drive cam is rotated. A spring biases the drive paw against the ratchet track.
Description
~LD/lm pa 22~Z~3 TIMER DRIVE MECHANISM
DESCRIPTION
BACKGROUND OF THE INVENTION
This invention relates to timers of the type advanced in a step-by-step manner by a drive mechanism and, more par-titularly, to the drive mechanism itself When designing a drive mechanism for a switching device in a program timer, a number of criteria must be taken into consideration. For example, it is desirable to advance the switching device at a relatively rapid rate for fast switch-in action. Prior designs have resulted in an indexing mock-anise which drives -the switching device in a step-by-step manner by providing a ratchet track on -the switching device and a drive paw which cooperates with the ratchet track to index the switching device Ever, these designs have not proven -to be entirely satisfactory for a number of reasons. For example, the movement profile of the drive paw has generally been limited to a sinusoidal motion.
Also, these mechanisms have required a relatively large number of parts, increasing the cost of production.
It is therefore an object of this invention to provide a drive mechanism for advancing the switching device in a ;
#
Jo . ?.`~
.. .. .
~2~32~3 program timer in a step-by-step manner wherein -the movement profile of the drive paw can be -tailored as desired.
It is another object of this invention to provide such a mechanism which comprises a relatively small number of parts.
SUMMARY OF THE INVENTION
The foregoing and additional objects are attained in accordance with the principles of this invention by provide in a drive mechanism for a program timer which includes a drive paw having a cam follower which is trapped between two gemming surfaces of a continuously driven drive cam.
The drive paw is yield ably biased against the ratchet track of the switching device and is guided for substantially linear reciprocation tangentially to the ratchet track.
In accordance with an aspect of this invention, the drive cam comprises a disc having a channel formed in one of its faces, with the first wall of the channel forming the first gemming surface and the second wall of the channel forming the second gemming surface.
BRIEF DESCRIPTION OF THE DRAWINGS
The foregoing will be more readily apparent upon read-in the following description in conjunction with the draw-ins in which lice elements in different figures thereof have the same reference character applied thereto and wherein:
FIG. 1 is a plan view through the front plate of a program timer showing the drive mechanism according to this invention;
FIG. 2 is a plan view showing -the underside of the drive cam of the drive mechanism shown in FIG. 1;
FIG. 3 is a perspective view of a drive cam constructed in accordance with this invention;
FIG. is a perspective view of a drive paw construct-Ed in accordance with this invention;
FIG. 5 is a detailed cross-sectional view taken along the line 5-5 in FIG. l; and FIGS. 6A-6F show the sequence of operation of the drive mechanism according -to this invention.
DETAILED DESCRIPTION
FIG. 1 shows the relevant portions of a program timer necessary for an understanding of the present invention.
Thus, as is well known, the program timer includes a plural-fly of timing cams 10 located on a rotating member for con-trolling the operation Of switches 12 in a p~edeterminedprogram. In particular, the rotating member is a hollow cam drum, sometimes referred to as a monoblock, which is rotatable journal led between a rear plate (not shown) and a front plate 14, shown in phantom. The details of the moo-block with respect to the timing cams 10 and the swishes are well known in the art and form no par-t of the pros-en invention.
The present invention is concerned with the mechanism for driving the monoblock. Accordingly, there is provided a ratchet track 16 on the monoblock. A drive paw 18 is operatively associated with the ratchet track 16 to drive the monoblock in a step-by-step manner, as will become clear from the following discussion.
The drive power source is a motor 20 mounted on a motor frame 22 secured to the front plate. As is conventional, the motor 20 is a reduction motor having an output shaft.
The output shaft of the motor 20 fits into an opening 2 provided therefore in a boss 26 formed on a drive cam 28.
The other side of the drive cam 28 is formed with a stub shaft 30 which is journal led for rotation in a suitable opening provided in the front plate. Accordingly, the motor 20 rotates the drive cam 28 in a clockwise direction, as viewed in FIG. 1.
As may be clearly seen prom FIG. 3, the drive cam 28 comprises a disc having a channel 32 formed in one face aye 3 thereof. The channel 32 forms a closed path surrounding the center of rotation of the drive cam 28 and has a fist, or inner, wall 34 and a second, or outer, wall 36. The inner wall 34 forms a first gemming surface for the drive paw 18 and the outer wall 36 forms a second gemming sun-face for the drive paw 18.
As is clearly shown in FIG. 4, the drive paw 18 is formed with a pin 38 which extends transversely to the direction of reciprocation of the drive paw 18, which direction of reciprocation is along the major longitudinal axis of the drive paw 18. The pin 38 acts as a cam follow-or and is adapted to extend into the channel 32 between the walls 34 and 36. The drive paw 18 is further formed with a tail section 40 which extends beyond the pin 38, the tail section 40 being of sufficient dimension so that it always spans the channel 32, irrespective of the rotative angle of the drive cam 28. This insures that an end of the drive paw 18 does not get jammed against one of the walls 34, 36. It will be noted from FIG. 4 that the thick-news of most of the tail Saxon is greater than the thickness of the remainder ox the drive paw 18. This allows the tail section 40 to provide a sliding bearing surface between the "land" areas of the drive cam 28 and -the front plate. Additionally, the driving end of the drive paw 18 is formed with a small stub 42 which pro-vises another bearing surface against the front plate of the timer.
The drive paw 18 is further formed with a guide pin 44 on the opposite side of the drive paw 18 from the cam 30 follower pin 38. As shown in FIG. 5, the guide pin 44 co-operates with an elongated slot 46 formed in the front plate 14 and a depending tab 48 formed from the front plate material cut away when the slot 46 was formed to keep the drive paw 18 reciprocating in a linear direction sub Stan-tidally parallel to its major longitudinal axis. The size ~229;29L3 of the guide pin 44 in the direction transverse to tune direction of reciprocation of the drive paw 18 is sub Stan-tidally the same as the width of the slot 46. A leaf spring 50 which is folded at 52 to be held by a portion of the motor frame 22 is cantilevered away from the motor frame 22 and toward the ratchet track 16 so as to yield ably bias the drive paw 18 against the ratchet track 16.
As is typical with a program timer, some means must be provided for preventing the monoblock from rotating in a direction opposite from that in which it is driven by the drive paw 18 Accordingly, an anti-reverse, or stop, paw 54 is provided. The anti-reverse paw 54 is formed with an enlarged extension 56 having an opening 58 encircle in the boss 26 to be carried whereby. The anti-reverse paw 54 is yield ably biased against the ratchet track 16 by means of a leaf spring 60 which, like the spring 50, is cantilevered away from the motor frame 22 and toward the ratchet track 16. Illustratively, the springs 50 and 60 are separate fingers of a bifurcated unitary spring assembly.
Alternatively, each of the paws 18 and 54 may be formed with an integrally molded cantilever spring. These molded springs would bear against a bent -tab formed from the front plate.
FIG. 6A-6F show the sequence of operation of -the thus-treated drive mechanism. As viewed therein, the drive comma rotates in the clockwise direction. In the angular orientation shown in FIG. PA, the drive paw 18 is in an undriven state because the cam follower pin 38 is between a constant radius portion of the inner wall 34 and a con-slant radius portion of the outer wall 36 of the chenille of the drive cam 28. In -the angular orientation depict-Ed in FIG. 6B, the drive paw 54 is moved outwardly, as shown by the arrow thereon, from -the center of rotation of the drive cam 28 because the cam follower pin 38 is against a portion of the inner wall 34 having an increasing radius.
32~L3 The driving end of the paw 18 therefore moves against a wall 62 of a tooth on the ratchet track 16. In the post-lion depicted in FIX. 6C, the drive paw 18 has been moved further out due to the increasing radius of the inner wall S 34 which bears against the cam follower pin 38 so as to move the monoblock in a clockwise direction. At this time, the anti-reverse paw 54 slides out of the tooth notch where it has previously been. In the angular orientation depicted in FIG. I the cam follower pin 38 is against that portion of the inner wall 34 having the greatest radius so that the drive paw 18 is at its greatest extent of travel. At this -time, the anti-reverse paw 54 drops into the same tooth notch occupied by the drive paw 18 and bears against the wall 62 to prevent reverse movement of the monoblock. In lo the angular position depicted in FIG. YE, -the cam follower pin 38 comes under the influence of the outer wall 36 which is now in a region of decreasing radius. The drive paw 18 is therefore pulled inwardly, as depicted by the arrow thereon, by the inner wall 36. In the annular position depicted in FIG. OF, the cam follower pin 38 is still under the influence of the outer wall 36 and is almost to the end of -the region of decreasing radius and has retracted surf-ficiently to engage the following tooth of the ratchet track 62 for its next drive stroke.
Thus, the contour of the inner wall 34 controls the driving portion of -the stroke of the paw 18 and -the con-tour of the outer wall 36 controls -the return portion of the stroke of the paw 18. This arrangement possesses a number of advantages. For example, there are relatively few parts to this drive mechanism, thereby lowering the cost to produce it. Another advantage is that the drive paw 18 is positively driven by cam surfaces throughout its entire stroke. Since these cam surfaces can take on almost any contour, the motion of -the drive paw 18 is not restricted to a particular type (i.e., sinusoidal).
. I, ..
Therefore, virtually any ratio of impulse to interval time can be achieved which allow for tighter switch sequence in with respect to time (shorter impulse) while conserving angular movement of the cam assembly (longer dwell or in-terval -time). Further, the same drive mechanism can be utilized for different applications by merely replacing the drive cam 28 with one having a more appropriate con fig-unction of the walls 34 and 36. Additionally, since the motion of the drive paw 18 more closely follows a straight line tangent to the ratchet track, different choices are available to the designer for a spring to bias the drive and anti-reverse paws against the ratchet track, as disk cussed above.
An alternative construction to the one described above would be to have the drive cam 28 rotate in a counter clock-wise direction and bias the pin 38 against the other side of the slot 46.
Accordingly, there has been disclosed a drive mechanism for a timer. It is understood that the above-described embodiment is merely illustrative of the application of the principles of this invention. Numerous other embodiments may be devised by those skilled in -the art without depart-in from the spirit and scope of this invention, as defined by -the appended claims.
DESCRIPTION
BACKGROUND OF THE INVENTION
This invention relates to timers of the type advanced in a step-by-step manner by a drive mechanism and, more par-titularly, to the drive mechanism itself When designing a drive mechanism for a switching device in a program timer, a number of criteria must be taken into consideration. For example, it is desirable to advance the switching device at a relatively rapid rate for fast switch-in action. Prior designs have resulted in an indexing mock-anise which drives -the switching device in a step-by-step manner by providing a ratchet track on -the switching device and a drive paw which cooperates with the ratchet track to index the switching device Ever, these designs have not proven -to be entirely satisfactory for a number of reasons. For example, the movement profile of the drive paw has generally been limited to a sinusoidal motion.
Also, these mechanisms have required a relatively large number of parts, increasing the cost of production.
It is therefore an object of this invention to provide a drive mechanism for advancing the switching device in a ;
#
Jo . ?.`~
.. .. .
~2~32~3 program timer in a step-by-step manner wherein -the movement profile of the drive paw can be -tailored as desired.
It is another object of this invention to provide such a mechanism which comprises a relatively small number of parts.
SUMMARY OF THE INVENTION
The foregoing and additional objects are attained in accordance with the principles of this invention by provide in a drive mechanism for a program timer which includes a drive paw having a cam follower which is trapped between two gemming surfaces of a continuously driven drive cam.
The drive paw is yield ably biased against the ratchet track of the switching device and is guided for substantially linear reciprocation tangentially to the ratchet track.
In accordance with an aspect of this invention, the drive cam comprises a disc having a channel formed in one of its faces, with the first wall of the channel forming the first gemming surface and the second wall of the channel forming the second gemming surface.
BRIEF DESCRIPTION OF THE DRAWINGS
The foregoing will be more readily apparent upon read-in the following description in conjunction with the draw-ins in which lice elements in different figures thereof have the same reference character applied thereto and wherein:
FIG. 1 is a plan view through the front plate of a program timer showing the drive mechanism according to this invention;
FIG. 2 is a plan view showing -the underside of the drive cam of the drive mechanism shown in FIG. 1;
FIG. 3 is a perspective view of a drive cam constructed in accordance with this invention;
FIG. is a perspective view of a drive paw construct-Ed in accordance with this invention;
FIG. 5 is a detailed cross-sectional view taken along the line 5-5 in FIG. l; and FIGS. 6A-6F show the sequence of operation of the drive mechanism according -to this invention.
DETAILED DESCRIPTION
FIG. 1 shows the relevant portions of a program timer necessary for an understanding of the present invention.
Thus, as is well known, the program timer includes a plural-fly of timing cams 10 located on a rotating member for con-trolling the operation Of switches 12 in a p~edeterminedprogram. In particular, the rotating member is a hollow cam drum, sometimes referred to as a monoblock, which is rotatable journal led between a rear plate (not shown) and a front plate 14, shown in phantom. The details of the moo-block with respect to the timing cams 10 and the swishes are well known in the art and form no par-t of the pros-en invention.
The present invention is concerned with the mechanism for driving the monoblock. Accordingly, there is provided a ratchet track 16 on the monoblock. A drive paw 18 is operatively associated with the ratchet track 16 to drive the monoblock in a step-by-step manner, as will become clear from the following discussion.
The drive power source is a motor 20 mounted on a motor frame 22 secured to the front plate. As is conventional, the motor 20 is a reduction motor having an output shaft.
The output shaft of the motor 20 fits into an opening 2 provided therefore in a boss 26 formed on a drive cam 28.
The other side of the drive cam 28 is formed with a stub shaft 30 which is journal led for rotation in a suitable opening provided in the front plate. Accordingly, the motor 20 rotates the drive cam 28 in a clockwise direction, as viewed in FIG. 1.
As may be clearly seen prom FIG. 3, the drive cam 28 comprises a disc having a channel 32 formed in one face aye 3 thereof. The channel 32 forms a closed path surrounding the center of rotation of the drive cam 28 and has a fist, or inner, wall 34 and a second, or outer, wall 36. The inner wall 34 forms a first gemming surface for the drive paw 18 and the outer wall 36 forms a second gemming sun-face for the drive paw 18.
As is clearly shown in FIG. 4, the drive paw 18 is formed with a pin 38 which extends transversely to the direction of reciprocation of the drive paw 18, which direction of reciprocation is along the major longitudinal axis of the drive paw 18. The pin 38 acts as a cam follow-or and is adapted to extend into the channel 32 between the walls 34 and 36. The drive paw 18 is further formed with a tail section 40 which extends beyond the pin 38, the tail section 40 being of sufficient dimension so that it always spans the channel 32, irrespective of the rotative angle of the drive cam 28. This insures that an end of the drive paw 18 does not get jammed against one of the walls 34, 36. It will be noted from FIG. 4 that the thick-news of most of the tail Saxon is greater than the thickness of the remainder ox the drive paw 18. This allows the tail section 40 to provide a sliding bearing surface between the "land" areas of the drive cam 28 and -the front plate. Additionally, the driving end of the drive paw 18 is formed with a small stub 42 which pro-vises another bearing surface against the front plate of the timer.
The drive paw 18 is further formed with a guide pin 44 on the opposite side of the drive paw 18 from the cam 30 follower pin 38. As shown in FIG. 5, the guide pin 44 co-operates with an elongated slot 46 formed in the front plate 14 and a depending tab 48 formed from the front plate material cut away when the slot 46 was formed to keep the drive paw 18 reciprocating in a linear direction sub Stan-tidally parallel to its major longitudinal axis. The size ~229;29L3 of the guide pin 44 in the direction transverse to tune direction of reciprocation of the drive paw 18 is sub Stan-tidally the same as the width of the slot 46. A leaf spring 50 which is folded at 52 to be held by a portion of the motor frame 22 is cantilevered away from the motor frame 22 and toward the ratchet track 16 so as to yield ably bias the drive paw 18 against the ratchet track 16.
As is typical with a program timer, some means must be provided for preventing the monoblock from rotating in a direction opposite from that in which it is driven by the drive paw 18 Accordingly, an anti-reverse, or stop, paw 54 is provided. The anti-reverse paw 54 is formed with an enlarged extension 56 having an opening 58 encircle in the boss 26 to be carried whereby. The anti-reverse paw 54 is yield ably biased against the ratchet track 16 by means of a leaf spring 60 which, like the spring 50, is cantilevered away from the motor frame 22 and toward the ratchet track 16. Illustratively, the springs 50 and 60 are separate fingers of a bifurcated unitary spring assembly.
Alternatively, each of the paws 18 and 54 may be formed with an integrally molded cantilever spring. These molded springs would bear against a bent -tab formed from the front plate.
FIG. 6A-6F show the sequence of operation of -the thus-treated drive mechanism. As viewed therein, the drive comma rotates in the clockwise direction. In the angular orientation shown in FIG. PA, the drive paw 18 is in an undriven state because the cam follower pin 38 is between a constant radius portion of the inner wall 34 and a con-slant radius portion of the outer wall 36 of the chenille of the drive cam 28. In -the angular orientation depict-Ed in FIG. 6B, the drive paw 54 is moved outwardly, as shown by the arrow thereon, from -the center of rotation of the drive cam 28 because the cam follower pin 38 is against a portion of the inner wall 34 having an increasing radius.
32~L3 The driving end of the paw 18 therefore moves against a wall 62 of a tooth on the ratchet track 16. In the post-lion depicted in FIX. 6C, the drive paw 18 has been moved further out due to the increasing radius of the inner wall S 34 which bears against the cam follower pin 38 so as to move the monoblock in a clockwise direction. At this time, the anti-reverse paw 54 slides out of the tooth notch where it has previously been. In the angular orientation depicted in FIG. I the cam follower pin 38 is against that portion of the inner wall 34 having the greatest radius so that the drive paw 18 is at its greatest extent of travel. At this -time, the anti-reverse paw 54 drops into the same tooth notch occupied by the drive paw 18 and bears against the wall 62 to prevent reverse movement of the monoblock. In lo the angular position depicted in FIG. YE, -the cam follower pin 38 comes under the influence of the outer wall 36 which is now in a region of decreasing radius. The drive paw 18 is therefore pulled inwardly, as depicted by the arrow thereon, by the inner wall 36. In the annular position depicted in FIG. OF, the cam follower pin 38 is still under the influence of the outer wall 36 and is almost to the end of -the region of decreasing radius and has retracted surf-ficiently to engage the following tooth of the ratchet track 62 for its next drive stroke.
Thus, the contour of the inner wall 34 controls the driving portion of -the stroke of the paw 18 and -the con-tour of the outer wall 36 controls -the return portion of the stroke of the paw 18. This arrangement possesses a number of advantages. For example, there are relatively few parts to this drive mechanism, thereby lowering the cost to produce it. Another advantage is that the drive paw 18 is positively driven by cam surfaces throughout its entire stroke. Since these cam surfaces can take on almost any contour, the motion of -the drive paw 18 is not restricted to a particular type (i.e., sinusoidal).
. I, ..
Therefore, virtually any ratio of impulse to interval time can be achieved which allow for tighter switch sequence in with respect to time (shorter impulse) while conserving angular movement of the cam assembly (longer dwell or in-terval -time). Further, the same drive mechanism can be utilized for different applications by merely replacing the drive cam 28 with one having a more appropriate con fig-unction of the walls 34 and 36. Additionally, since the motion of the drive paw 18 more closely follows a straight line tangent to the ratchet track, different choices are available to the designer for a spring to bias the drive and anti-reverse paws against the ratchet track, as disk cussed above.
An alternative construction to the one described above would be to have the drive cam 28 rotate in a counter clock-wise direction and bias the pin 38 against the other side of the slot 46.
Accordingly, there has been disclosed a drive mechanism for a timer. It is understood that the above-described embodiment is merely illustrative of the application of the principles of this invention. Numerous other embodiments may be devised by those skilled in -the art without depart-in from the spirit and scope of this invention, as defined by -the appended claims.
Claims (9)
1. A mechanism for driving a switching device in a timer or the like in a step-by-step manner, comprising:
a ratchet track on said switching device;
a motor;
a drive cam coupled to said motor for continuous rota-tion therewith, said drive cam having opposed first and second camming surfaces thereon;
a drive pawl operatively associated with said ratchet track;
a cam follower mounted on said drive pawl and trapped between said first and second camming surfaces;
means for yieldably biasing said drive pawl against said ratchet track; and guide means for limiting the motion of said drive pawl to substantially linear reciprocation tangential to said ratchet track.
a ratchet track on said switching device;
a motor;
a drive cam coupled to said motor for continuous rota-tion therewith, said drive cam having opposed first and second camming surfaces thereon;
a drive pawl operatively associated with said ratchet track;
a cam follower mounted on said drive pawl and trapped between said first and second camming surfaces;
means for yieldably biasing said drive pawl against said ratchet track; and guide means for limiting the motion of said drive pawl to substantially linear reciprocation tangential to said ratchet track.
2. The mechanism according to Claim 1 wherein said drive cam comprises a disc having a channel formed in one face thereof, a first wall of said channel forming said first camming surface and a second wall of said channel forming said second camming surface.
3. The mechanism according to Claim 2 wherein said channel forms a closed path surrounding the center of rota-tion of said disc.
4. The mechanism according to Claim 3 wherein the contour of the inner wall of said channel defines the drive stroke of said drive pawl and the contour of the outer wall of said channel defines the return stroke of said drive pawl.
5. The mechanism according to Claim 4 wherein said cam follower comprises a pin extending from said drive pawl transversely to the direction of reciprocation of said drive pawl.
6. The mechanism according to Claim 5 wherein said drive pawl is formed with a tail section extending beyond said pin, said tail section being of sufficient dimension to span said channel throughout the entire rotation of said drive cam element.
7. The mechanism according to Claim 1 wherein said drive cam is formed with a circular boss concentric with the center of rotation of said drive cam, said mechanism further comprising:
an anti-reverse pawl cooperating with said ratchet track to prevent movement thereof in a direction opposite to that imparted thereto by said drive pawl, said anti-reverse pawl being formed with an opening encircling said boss to be carried thereby; and means for yieldably biasing said anti-reverse pawl against said ratchet track.
an anti-reverse pawl cooperating with said ratchet track to prevent movement thereof in a direction opposite to that imparted thereto by said drive pawl, said anti-reverse pawl being formed with an opening encircling said boss to be carried thereby; and means for yieldably biasing said anti-reverse pawl against said ratchet track.
8. The mechanism according to Claim 1 wherein said timer includes a plate and said guide means comprises:
an open elongated slot in said plate; and a pin mounted on said drive pawl and extending through said slot, the dimension of said pin in the direction trans-verse to the direction of reciprocation of said drive pawl being substantially the same as the width of said slot.
an open elongated slot in said plate; and a pin mounted on said drive pawl and extending through said slot, the dimension of said pin in the direction trans-verse to the direction of reciprocation of said drive pawl being substantially the same as the width of said slot.
9. The mechanism according to Claim 1 wherein said biasing means includes a leaf spring.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US616,092 | 1984-06-01 | ||
| US06/616,092 US4536626A (en) | 1984-06-01 | 1984-06-01 | Timer drive mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1229243A true CA1229243A (en) | 1987-11-17 |
Family
ID=24468000
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000474810A Expired CA1229243A (en) | 1984-06-01 | 1985-02-21 | Timer drive mechanism |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US4536626A (en) |
| JP (1) | JPH0610951B2 (en) |
| AU (1) | AU567394B2 (en) |
| CA (1) | CA1229243A (en) |
| DE (1) | DE3519156C2 (en) |
| FR (1) | FR2565312B1 (en) |
| IT (1) | IT1215648B (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4611103A (en) * | 1985-04-11 | 1986-09-09 | Emhart Industries, Inc. | Means providing intermittent motion to a cam means of a timing mechanism and having sub-interval switching means |
| US4599499A (en) * | 1985-07-26 | 1986-07-08 | Controls Company Of America | Fast impulse timer drive mechanism |
| US4649239A (en) * | 1985-10-04 | 1987-03-10 | Eaton Corporation | Program timer with variable time delay |
| US4755635A (en) * | 1987-05-29 | 1988-07-05 | Eaton Corporation | Electrical programmer |
| US5042311A (en) * | 1988-06-06 | 1991-08-27 | Eaton Corporation | Secondary timer for program timer |
| DE3918712C2 (en) * | 1989-06-08 | 1996-04-25 | Ako Werke Gmbh & Co | Electromechanical program switch |
| DE4441105A1 (en) * | 1994-10-17 | 1996-04-18 | Venta Vertriebs Ag | Fragrance evaporator, especially for toilets |
| US5637843A (en) * | 1995-09-28 | 1997-06-10 | Eaton Corporation | Electromechanical programmer/timer |
| US5739490A (en) * | 1996-05-28 | 1998-04-14 | Emerson Electric Co. | Cam-operated timer pawl drive |
| JP4004769B2 (en) * | 2001-10-17 | 2007-11-07 | Ｎｅｃトーキン株式会社 | Electrolytic solution and electrochemical cell using the same |
| US9533430B1 (en) * | 2011-10-18 | 2017-01-03 | Robert M. Kalb | Portable adjustable cutting apparatus for cutting and shaping sink holes in stone countertops |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| NL93780C (en) * | 1956-12-22 | |||
| US2868026A (en) * | 1957-08-22 | 1959-01-13 | Mallory & Co Inc P R | Intermittent driving mechanism |
| US3064891A (en) * | 1958-11-07 | 1962-11-20 | Lion Mfg Corp | Stepping switch mechanism |
| NL294083A (en) * | 1962-06-16 | |||
| US3857293A (en) * | 1974-02-07 | 1974-12-31 | Sarkes Tarzian | Timer |
| SE409176B (en) * | 1978-06-19 | 1979-08-06 | Gustavsson Jack | SECURITY SKI BINDING |
| US4311059A (en) * | 1979-08-31 | 1982-01-19 | Emhart Industries, Inc. | Means providing intermittent motion to a cam means of a timing mechanism |
| US4319101A (en) * | 1980-02-06 | 1982-03-09 | The Scott & Fetzer Company | Sequential timer with programmable dual frequency drive |
| US4467664A (en) * | 1981-09-28 | 1984-08-28 | The Singer Company | Timer drive mechanism |
| FR2520895A1 (en) * | 1982-01-29 | 1983-08-05 | Carpano & Pons | PROGRAMMER CONTROL DEVICE |
| US4500212A (en) * | 1984-07-02 | 1985-02-19 | The Singer Company | Expanded interval timer drive mechanism |
-
1984
- 1984-06-01 US US06/616,092 patent/US4536626A/en not_active Expired - Lifetime
-
1985
- 1985-02-13 AU AU38686/85A patent/AU567394B2/en not_active Ceased
- 1985-02-21 CA CA000474810A patent/CA1229243A/en not_active Expired
- 1985-03-27 IT IT8520084A patent/IT1215648B/en active
- 1985-04-08 JP JP60074149A patent/JPH0610951B2/en not_active Expired - Lifetime
- 1985-05-29 DE DE3519156A patent/DE3519156C2/en not_active Expired - Fee Related
- 1985-05-30 FR FR8508116A patent/FR2565312B1/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| DE3519156A1 (en) | 1985-12-05 |
| US4536626A (en) | 1985-08-20 |
| JPH0610951B2 (en) | 1994-02-09 |
| FR2565312A1 (en) | 1985-12-06 |
| AU567394B2 (en) | 1987-11-19 |
| IT8520084A0 (en) | 1985-03-27 |
| AU3868685A (en) | 1985-12-05 |
| IT1215648B (en) | 1990-02-22 |
| FR2565312B1 (en) | 1987-01-02 |
| DE3519156C2 (en) | 1994-02-24 |
| JPS60257028A (en) | 1985-12-18 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |