CA1135794A - Clutch mechanism for time of day watt demand meter registers - Google Patents
Clutch mechanism for time of day watt demand meter registersInfo
- Publication number
- CA1135794A CA1135794A CA000383829A CA383829A CA1135794A CA 1135794 A CA1135794 A CA 1135794A CA 000383829 A CA000383829 A CA 000383829A CA 383829 A CA383829 A CA 383829A CA 1135794 A CA1135794 A CA 1135794A
- Authority
- CA
- Canada
- Prior art keywords
- clutch
- closing part
- driving
- driving part
- driven
- 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
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01R—MEASURING ELECTRIC VARIABLES; MEASURING MAGNETIC VARIABLES
- G01R11/00—Electromechanical arrangements for measuring time integral of electric power or current, e.g. of consumption
- G01R11/02—Constructional details
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01R—MEASURING ELECTRIC VARIABLES; MEASURING MAGNETIC VARIABLES
- G01R11/00—Electromechanical arrangements for measuring time integral of electric power or current, e.g. of consumption
- G01R11/56—Special tariff meters
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01R—MEASURING ELECTRIC VARIABLES; MEASURING MAGNETIC VARIABLES
- G01R11/00—Electromechanical arrangements for measuring time integral of electric power or current, e.g. of consumption
- G01R11/56—Special tariff meters
- G01R11/57—Multi-rate meters
- G01R11/58—Tariff-switching devices therefor
Abstract
14 48,239 ABSTRACT OF THE DISCLOSURE
A clutch mechanism for watt demand meter regis-ters includes a clutch driving part continuously driven by a rotating measuring element so as to be freely rotatable when the clutch is open. The driving part is mounted between a clutch driven part and a clutch closing part which clamps the clutch parts together when the clutch mechanism is closed.
A clutch mechanism for watt demand meter regis-ters includes a clutch driving part continuously driven by a rotating measuring element so as to be freely rotatable when the clutch is open. The driving part is mounted between a clutch driven part and a clutch closing part which clamps the clutch parts together when the clutch mechanism is closed.
Description
9 ~357~
1 48,239 A~ IMPROVED CLUTCH MECHANISM
FOR TIME OF DAY WATT DEMAND METE~ REGISTE~S
BA~KGROU~D OF THE INVENTION
This invention relates to a watt demand dial register having a clutch mechanism for periodically un-coupling a dial indicator from a rotatable measuring element dri~en in response to variations of a quantity to be measured.
Dial registers are typically used in various types of meters for indicating the consumption of differ-ent quantities to be measured. In electric energy meters, a disk and shaft assembly that is electromagnetically driven. The assembly forms a measuring element which is rotatable at the rate of consumption of electric energy.
The rotations are coupled by one or more register gear trains to dial pointers indicating kilowatt demand of !5 power usage. When measurements are to be made only during preselected time intervals, such as for only a part of each day, the dial pointers must remain uncoupled from the measuring element while it continues to rotate. A clutch mechanism is required to be provided in the register to selectively couple and uncouple the dial pointers. Many prior art register clutch mechanisms produced additional frictional drag or additional rotational torque loading on the rotatable measuring element while the clutch is un-coupled. The mechanical loading on the register gear trains cause them to wear excessively and substantially shorten the operational lifetime of the register. The substantial variations in loads on the rotatable measuring 7~L
element during measuring and non-measuring times can cause il to ~>ec(>me unstable, pro(luct excessive wear >rl the disc stldft ~earing and substantially reduce the operational lifetime of the measuring element.
In U.S. Patent No. 3,406,338, issued October 15, 1968, a maximum watt demand meter is disclosed including a block interval demand register having a clutch mechanism which is open briefly at the end of each demand measuring interval, which may be every fifteen, thirty or sixty minutes. A clutch driving member includes a sleeve which carries an input gear at one end and a frictional clutch surface at the other end. The driving member is uncoupled from a driven member when it is engaged by an operator 'member formed by a trip lever or arm member having a fork configuration. The driving member is shifted axially by the trip lever to be disengaged and uncoupled from the driven clutch member. The clutch is only opened or disen-gaged for two to five seconds. The additional frictional and rotational forces on the driven member due to being shifted to the open position is not applied sufficiently long to take up the backlash on the associated gear train connected to it. If the clutch mechanism were to be held open for a substantial time, as required in on and off peak or time of day demand registers, for example, the additional loading on the clutch driving member would be coupled to the gear train and/or the rotations of the measuring element.
One example of an on-peak off-peak watt demand register is described and claimed in U.S. Patent No.
3,913,014, issued October 14, 1975. The register in the aforementioned patent includes selective coupling and uncoupling with the demand measuring gear train by de-meshing a pai,r of gears in accordance with a programmed cam surface. Misalignment of mating gears can retard the return to the mutually meshed relationship. A pusher drive and reset mechanism utilizing an additional clutch mechanism is suggested for use in the aforementioned patent in which such clutch mechani,sm is described in U.S.
7 ~
3 4~ g Patent No. 2,~59,31/~, issued October 14s 1941.
UMMARY OF THE INVENTION
An improved clutch mechanis-m for time of day watt demand registers made in accordance with this inven-tion, includes a three part arrangement mounted along acommon axls provided by a shaft. A clutch driven part has a fixed axial position and is rotatable for effecting movement of a watt demand dial pointer indicator. A
clutch driving part is continuously coupled through a gea-r train to a rotatable measuring element and the driving part is axially shiftable for disengagement and frictional engagement of the clutch driven part while heing freely rotatable about the common axis. A clutch closing part is axially biased toward the clutch driving part for effect-ing the coupled engagement between the clutch driving anddriven parts. The clutch closed position effects rota-tional coupling through the clutch between the rotatable measuring element and the dial pointer indicator. A
clutch operator is effective to axially shift the clutch closing part and release the clutch driving part from its driving engagement with the driven part.
An important feature of the present inven-tion is to provide an improved clutch mechanism for watt demand registers that couples and uncouples a rotatable measuring element with a dial indicator so that a clutch driving part produces low or negligible torque on the register gear train and measuring element when the clutch is held open for extended periods.
BRIEF DESCRIPTION OF THE DRAWING
Figure 1 is a top plan view of a portion of a tirne of day watt demand register including an improved clutch mechanism made in accordance with the present invention and further includes a diagrammatic showing of associated parts of an electric energy meter utilizing the register;
Fig. 2 is a top plan view of a portion of Fig. 1 showing the improved clutch mechanism in a different operative position; and i799!~
4 4~23g Flg. 3 is an enlarged top plan ~iew, with part~
broken away, of an alternative embodiment oP the olutch mechanlsm sho~m in Figs. 1 and 2.
DETAILED DESCRIPTION OF THE PREFERRED ~E~D~TS
Re~erring now to the drawing and more particu-larly to Fig. 1, an electric energy meter 10 ls shown therein including a time of day maximum watt demand regis-ter 12 including an improved clutch mechanism 14 made in accordance with the present invention~ For purposes o~
description and not limitation, the clutch mechanism 14 is shown replacing the clutch of a maximum demand device aisclosed and claimed in the aforementioned U.S. Patent No. 3?406,338.
me meter 10 includes a watthour metering move-ment of the induction or electromechanical type h~ving arotatable measuring element 16 formed by a shaft supported conductive disk~ As is ~nderstood by those skilled in the watthour meter art, the disc and shaft are rotated or driven electromagnetically at a rate proportional to the rate of consumption of an electric energy quantity to be measured. In a known manner, a worm wheel 18 is driven by the shaft of the measuri~g element 16 to couple its rota-tion~ to a gear train 20 of the register 12. me gear train 20 includes a wide gear Z6 belng continuously coupled to the lnput of the clutch mechanism 14 as descr1bed herein-below.
The clutch mechanism 14 has a three part ar-rangement and is oarried on a shaft 28 æo as to be coax-ially aligned with the longi~udinal axis o~ the shaft 28.
A olutch driving part 30 is axially slidable and rotatably mountad on the shaft 28. me drlvlng part 30 is substan- -tially a thin dlsc having the outer periphery thereof formed by gear teeth continuously meshing with the gear 26. A clutch driven part 32 is rotatable and axially restrained on the for~rard end of the shaft 28 between a pair of shaft mounted retaining rings so as to rotate on the shaft while having a ~ixefl a~ial pos~tlon thereon. A
resettable pusher member 36 ls fixedly carried on a for-11~357~
~g, ~3g ward part of the driven part 32 and extends through a dialplate 38 of the register 12. The pusher member 36 is engageable w-ith and actuates a maximum wa~t demand dial pointer indicator 40 pivotally mounted on the front face of the dial plate 38. The forward end of the shaft 28 is mounted in a thrust bearing rearward of the pivotal mount-ing of the indicator 40. The clutch mechanism l~ further-generally includes a clutch closing member 42 mounted in a rotatable and axially shiftable relationship on the shaft l() 28. In the closed position of the clutch mechanism 14 as shown in Fig. 1, the clutch driving part 30 is clarnped ~etween the closing part 42 and the clutch driven part 32 to couple the continuous metering responsive rotations of the gear 26 to the pusher member 36.
The shaft 28 is supported in the register 12 for being rotatable and carrying the clutch mechanism 14 and extends rearward of the dial plate 38 as described herein-above. A fur~her retainer ring 44 is provided at the rear end of the shaft 28 and is applied to one of a series of grooves in the rear end of the shaft 28. A helical spring 46 is compressed between the retainer 4~ and the clutch part 42. The spring 46 normally biases the clutch part 42 toward and against the driving part 30 to produce a clamp-ing force or pressure to effect the clutch closed posi-tion.
The clutch parts 30, 32 and 42 of the clutchmechanism 14 are arranged so that the driving part 30 provides a gear input to the clutch mechanism as described above, and has a thin gear configuration for continuously 3~ meshing with the gear 26 as it is shifted on the shaft 28.
The continuous meshing of the gear teeth around the outer periphery of the part 30 with the teeth of the gear 26 when the clutch is moved between the axial extents of the axial slidable movement thereof avoids any problem of initially meshing the gear teeth which could occur if they become separated. Thus, Lhe gear train 20 is continuously coupled to the rotations of the rotatable measuring ele-ment 16 and to the clutch driving part 30. Only the = ~1 3 ~7 ~ ~
6 4~,2~9 eccentricity o~ the -thin clutch part 30 is critical ~o that the clutch mechanlsm 14 is simple to assemble and has more accuracy than if the clutch driving part includes an extended sleeve carrying an actuating end and an input gear.
The forward radial side o~ the clutch part 30 includes a flat friction clutch surface for coupling engagement with a mating flat friction clutch surface of a rear flat radial side surface ~ormed on a plate portion 50 (shown in Fig. 2) o~ the driven part 32. A pinion gear 52 is carried in an integrally attached relationship w~th the plate portion 50 of the part 32. The pinion gear 52 is en- -gaged by a sector gear 560 The clutch part 32 is held axi-ally in place relative to the shaft 28 by a snap ring7 not shown, fitted into a center recess of the plate portion 507 mus, the plate 50, gear 52 and pusher member 36 rotate in uni~on. me sector gear 56 returns the clutch part 32 and pusher member 36 to a reset or an initial measuring posi-tion when the clutch mechanism is opened. me resetting operation is in accordance with the operation o~ a ~lock interval demand register in which the pusher member 36 is reset at the end of a predetermined demand mea~urlng inter-val or period such as fifteen, thirty or sixty minutes. me pusher resetting operation is described in the a~ore-mentioned U.S. Patent Nos4 3,405,338 and 2,259,314.
me clutch clo~ing member 42 includes a sleeve58 having a ~orward pressure applying plate 60 having substantially the æam~ diameter as the plate 50 of the clutch part 32. A forward flat radial side sur~ace o~ the plate 60 engages and presses against the rearward side radlal surface o~ the driving part 30. Thus engaged, the clutch part 30 is clamped in a sandwiched relationship between the clutch parts 32 a~d 42 in the closed position and coupling conditio~ of the clutch mechani~m 14. me eccentricity o~ the center hole o~ the sleeve 58 of the clutch part 42 is not critical since it is only required to provide rota~ing and slidable movement ~or applying ~xlal pressure to the mutually engaging surface~ of the , j .
S~
7 ~,~, 2 clwtch parts 30 and 32. The rearward end of the clutch part 42 includes a flange 64 in~egrally carried on t'ne rear end of the sleeve 58 and the helical spring 44 en-gages it to thereby bias the clutch part 42.
A clutch operating arrangement is provided by a trip lever or arm 66 mounted at a pivot 68 carried by a mounting plate 70 of the register 12. The right-hand or driving end of the lever 66 has a fork configuration defining tines extending over the sleeve 58 so that the ends of the tines are releasably engageable with a front flat radial surface of t ~ flange 64. The left-hand or driven end of the lever ~ is rotated by a solenoid act-uator 72 including a reciprocally movable cam 74 carried by a plunger armature 76. The armature 74 is reciprocally movable so that an increasing diameter or frustoconical camming surface of the cam 74 and a smaller straight diameter surface move the left-hand or driven end of the lever 66 to counter clockwise and clockwise positions, respectively. The solenoid actuator 72 includes a coil 78 which is energized by suitable electrical signals having opposite polarities as indicated by the d-irectinal arrows 80 and ~2 in Figs. 1 and 2, respectively. The electric signals move the armature 76 to an extended and right-hand most position as shown in Fig. 2 or to a retracted and left-hand most position shown in Fig. 1. The clutch closed position is produced by the armature 76 being electromagnetically shifted to the left or retracted position so that the lever arm 66 assumes a clockwise rotated position to be released from the flange 64 of the clutch part 42. The spring 46 biasingly urges the clu~ch part 42 and the clutch driving and driven parts 30 and 32 together so that the rotations of the gear train 20 are transmitted through the clutch mechanism 14 to the pusher member 36. The clutch open position and uncoupling condi-tion is illustrated in Fig. 2 when the armature 76 isshifted to the righ-t and extended position so that the lever arm 66 assumes a counterclockwise rotated position to drive the flange 64 rearwardly so that the clutch part , .. . .
:
, .13~j7~
8 ~ 4~ g 42 compresses the spring ~ and is spaced from the clutch driving part 30. The mutually engaging clutch friction surfaces of the clutch parts 30 and 32 are released and disengaged so that no torque is coupled thereacross.
The operation of the clutch mechanism 14 in a time of day or on-peal~ off-peak manner of watt demand metering provides coupling and extended uncoupling of the rotating measuring element 16 from the pusher member 36 which provides an actuating means for the indicator 40.
Typically, the predetermined times of day are selected for measuring which coincide with the peak demand periods of an electric utility supplying the electric energy being monitored by the meter 10. A locally or remotely gener-ated signal produces the electric signals having the polarity or direction of current flow indicated by the directional arrows 80 and 82. When the solenoid actuator 72 is electrically operated to shift the cam 74 to the retracted position as shown in Fig. 1, the lever 66 is rotated 6s~ that the end thereof is released from the flange ~ so that the clutch part 42 effects pressure against the clutch parts 30 and 32. The rotations of the rotatable measuring element 16 are then coupled through the gear train 20 and the clutch mechanism 14 to the pusher member 36 and indicator 40, as noted hereinabove.
The shaft 28, the spring 46 and clutch parts 30, 32 and 42 and the pusher member 36 all rotate in unison. There is negligible or low amount of mechanical loading or torque i~ applied on the gear train 20 and the measuring element 16 by the clutch mechanism to produce measuring movement of the indicator l~0, As is understood in the maximum demand metering art, the pusher member 36 engages and drives the indicator 40 upscale when the measuring element 16 rotates more in one demand interval than it has in any previous demand interval.
When it is desired to open the clutch mechanism 14 to either effect resetting of the pusher member 36, at the end of a predetermined demand interval, or to suspend or interrupt watt demand measurements for an extended ~3 9 4~,Z~
t-irne, the soleno-id actuator 72 is electrically op~rated ~y an eleclrical signal having the direction or polarity as indicated by the directional arrow 82 in Fig. 2. The cam 74 is extended and the larger diameter cam surface urges the lever arm 66 co~nterclockwise to slide the clutch part 42 rearward and release the clutch driving part 30 from the clutch driven part 32. The clutch part 42 is spaced and isolated from the clutch part 30 so it is freely rotatable in response to the rotatable measuring element 16 without any appreciable mechanical loading or torque being applied to the gear train 20 or the measuring ele-ment 16 due to the clutch opening operation producing the uncoupling condition of the clutch mechanism 14. In the ~i pusher resetting operation, the solenoid actuator 72 is .~ 15 energized to close the clutch after the sector ~Yg~m 56 drives the pinion gear 52 to the zero position after two to five seconds.
Fig. 3 illustrates an alternative clutch mecha-nism 110 that is capable of replacing the clutch mechanism 14 shown in Fig. 1. Accordingly, the shaft 28 has mounted thereon the clutch parts 30 and 32 in substantially the identical manner as they provided in the clutch mechanism 14. The clutch closing part 112 has the same general configuration as does the corresponding clutch closing part 42 excepting that a low strength permanent magnet 114 is carried in a recess 116 in the pressure plate portion 11~ of the clutch part 112. The pressure plate 118 is otherwise the same as the plate 60 and the remaining sleeve and fLange portions of the clutch part 112 are the same as in the clutch part 42.
When the mechanism 14 is closed, the flux of the magnet 114 will cause a temporary magnetic coupling be-tween the ~nagnetic material forming the driving part 30 and the magnet 114. When the clutch opening operation is provided, the lever 66 urges the clutch part 112 rearward against the spring 46 and the effect of the magnet 114 is to releasably attract the clutch part 30 so that positive disengagernent with the clutch driven part 32 is provided.
: ~ 1357~9~
~8,~g Any ~ ectx ~ausing cohesion o~ sticking between the nutually engaging fr-iction surfaces of the par~s 30 and 3~
are ~hereby overcome. The force of atLraction of the magnet 114 for the clutch part 30 is substantially smaller than the frictional force and retarding torque due to the engagement of the tines of the lever 66 with the flange 64. Thus, as the gear train 20 rotates the clutch part 30, the frlctional force of the lever 66 on the flange 64 is grea-ter than the magnetic attraction force between the clutch part 112 and the clutch part 30 to cause the clutch part 30 to break free of the clutch part 112 as it is shifted rearward and continue to rotate freely on the shaft 28. Thus, during the initial clutch opening opera-tion produced by the lever 66, the driving part 30 is pulled axially away from the driven par~ 32 by the attrac-tion of the magnet 114 as the part 110 slides rearward.
Further rearward axial movement of the part 110 and the rotations of the part 30 then cause the coupling between t~ dri~in~ part ~0 and closing part 112 to be broken.
1 48,239 A~ IMPROVED CLUTCH MECHANISM
FOR TIME OF DAY WATT DEMAND METE~ REGISTE~S
BA~KGROU~D OF THE INVENTION
This invention relates to a watt demand dial register having a clutch mechanism for periodically un-coupling a dial indicator from a rotatable measuring element dri~en in response to variations of a quantity to be measured.
Dial registers are typically used in various types of meters for indicating the consumption of differ-ent quantities to be measured. In electric energy meters, a disk and shaft assembly that is electromagnetically driven. The assembly forms a measuring element which is rotatable at the rate of consumption of electric energy.
The rotations are coupled by one or more register gear trains to dial pointers indicating kilowatt demand of !5 power usage. When measurements are to be made only during preselected time intervals, such as for only a part of each day, the dial pointers must remain uncoupled from the measuring element while it continues to rotate. A clutch mechanism is required to be provided in the register to selectively couple and uncouple the dial pointers. Many prior art register clutch mechanisms produced additional frictional drag or additional rotational torque loading on the rotatable measuring element while the clutch is un-coupled. The mechanical loading on the register gear trains cause them to wear excessively and substantially shorten the operational lifetime of the register. The substantial variations in loads on the rotatable measuring 7~L
element during measuring and non-measuring times can cause il to ~>ec(>me unstable, pro(luct excessive wear >rl the disc stldft ~earing and substantially reduce the operational lifetime of the measuring element.
In U.S. Patent No. 3,406,338, issued October 15, 1968, a maximum watt demand meter is disclosed including a block interval demand register having a clutch mechanism which is open briefly at the end of each demand measuring interval, which may be every fifteen, thirty or sixty minutes. A clutch driving member includes a sleeve which carries an input gear at one end and a frictional clutch surface at the other end. The driving member is uncoupled from a driven member when it is engaged by an operator 'member formed by a trip lever or arm member having a fork configuration. The driving member is shifted axially by the trip lever to be disengaged and uncoupled from the driven clutch member. The clutch is only opened or disen-gaged for two to five seconds. The additional frictional and rotational forces on the driven member due to being shifted to the open position is not applied sufficiently long to take up the backlash on the associated gear train connected to it. If the clutch mechanism were to be held open for a substantial time, as required in on and off peak or time of day demand registers, for example, the additional loading on the clutch driving member would be coupled to the gear train and/or the rotations of the measuring element.
One example of an on-peak off-peak watt demand register is described and claimed in U.S. Patent No.
3,913,014, issued October 14, 1975. The register in the aforementioned patent includes selective coupling and uncoupling with the demand measuring gear train by de-meshing a pai,r of gears in accordance with a programmed cam surface. Misalignment of mating gears can retard the return to the mutually meshed relationship. A pusher drive and reset mechanism utilizing an additional clutch mechanism is suggested for use in the aforementioned patent in which such clutch mechani,sm is described in U.S.
7 ~
3 4~ g Patent No. 2,~59,31/~, issued October 14s 1941.
UMMARY OF THE INVENTION
An improved clutch mechanis-m for time of day watt demand registers made in accordance with this inven-tion, includes a three part arrangement mounted along acommon axls provided by a shaft. A clutch driven part has a fixed axial position and is rotatable for effecting movement of a watt demand dial pointer indicator. A
clutch driving part is continuously coupled through a gea-r train to a rotatable measuring element and the driving part is axially shiftable for disengagement and frictional engagement of the clutch driven part while heing freely rotatable about the common axis. A clutch closing part is axially biased toward the clutch driving part for effect-ing the coupled engagement between the clutch driving anddriven parts. The clutch closed position effects rota-tional coupling through the clutch between the rotatable measuring element and the dial pointer indicator. A
clutch operator is effective to axially shift the clutch closing part and release the clutch driving part from its driving engagement with the driven part.
An important feature of the present inven-tion is to provide an improved clutch mechanism for watt demand registers that couples and uncouples a rotatable measuring element with a dial indicator so that a clutch driving part produces low or negligible torque on the register gear train and measuring element when the clutch is held open for extended periods.
BRIEF DESCRIPTION OF THE DRAWING
Figure 1 is a top plan view of a portion of a tirne of day watt demand register including an improved clutch mechanism made in accordance with the present invention and further includes a diagrammatic showing of associated parts of an electric energy meter utilizing the register;
Fig. 2 is a top plan view of a portion of Fig. 1 showing the improved clutch mechanism in a different operative position; and i799!~
4 4~23g Flg. 3 is an enlarged top plan ~iew, with part~
broken away, of an alternative embodiment oP the olutch mechanlsm sho~m in Figs. 1 and 2.
DETAILED DESCRIPTION OF THE PREFERRED ~E~D~TS
Re~erring now to the drawing and more particu-larly to Fig. 1, an electric energy meter 10 ls shown therein including a time of day maximum watt demand regis-ter 12 including an improved clutch mechanism 14 made in accordance with the present invention~ For purposes o~
description and not limitation, the clutch mechanism 14 is shown replacing the clutch of a maximum demand device aisclosed and claimed in the aforementioned U.S. Patent No. 3?406,338.
me meter 10 includes a watthour metering move-ment of the induction or electromechanical type h~ving arotatable measuring element 16 formed by a shaft supported conductive disk~ As is ~nderstood by those skilled in the watthour meter art, the disc and shaft are rotated or driven electromagnetically at a rate proportional to the rate of consumption of an electric energy quantity to be measured. In a known manner, a worm wheel 18 is driven by the shaft of the measuri~g element 16 to couple its rota-tion~ to a gear train 20 of the register 12. me gear train 20 includes a wide gear Z6 belng continuously coupled to the lnput of the clutch mechanism 14 as descr1bed herein-below.
The clutch mechanism 14 has a three part ar-rangement and is oarried on a shaft 28 æo as to be coax-ially aligned with the longi~udinal axis o~ the shaft 28.
A olutch driving part 30 is axially slidable and rotatably mountad on the shaft 28. me drlvlng part 30 is substan- -tially a thin dlsc having the outer periphery thereof formed by gear teeth continuously meshing with the gear 26. A clutch driven part 32 is rotatable and axially restrained on the for~rard end of the shaft 28 between a pair of shaft mounted retaining rings so as to rotate on the shaft while having a ~ixefl a~ial pos~tlon thereon. A
resettable pusher member 36 ls fixedly carried on a for-11~357~
~g, ~3g ward part of the driven part 32 and extends through a dialplate 38 of the register 12. The pusher member 36 is engageable w-ith and actuates a maximum wa~t demand dial pointer indicator 40 pivotally mounted on the front face of the dial plate 38. The forward end of the shaft 28 is mounted in a thrust bearing rearward of the pivotal mount-ing of the indicator 40. The clutch mechanism l~ further-generally includes a clutch closing member 42 mounted in a rotatable and axially shiftable relationship on the shaft l() 28. In the closed position of the clutch mechanism 14 as shown in Fig. 1, the clutch driving part 30 is clarnped ~etween the closing part 42 and the clutch driven part 32 to couple the continuous metering responsive rotations of the gear 26 to the pusher member 36.
The shaft 28 is supported in the register 12 for being rotatable and carrying the clutch mechanism 14 and extends rearward of the dial plate 38 as described herein-above. A fur~her retainer ring 44 is provided at the rear end of the shaft 28 and is applied to one of a series of grooves in the rear end of the shaft 28. A helical spring 46 is compressed between the retainer 4~ and the clutch part 42. The spring 46 normally biases the clutch part 42 toward and against the driving part 30 to produce a clamp-ing force or pressure to effect the clutch closed posi-tion.
The clutch parts 30, 32 and 42 of the clutchmechanism 14 are arranged so that the driving part 30 provides a gear input to the clutch mechanism as described above, and has a thin gear configuration for continuously 3~ meshing with the gear 26 as it is shifted on the shaft 28.
The continuous meshing of the gear teeth around the outer periphery of the part 30 with the teeth of the gear 26 when the clutch is moved between the axial extents of the axial slidable movement thereof avoids any problem of initially meshing the gear teeth which could occur if they become separated. Thus, Lhe gear train 20 is continuously coupled to the rotations of the rotatable measuring ele-ment 16 and to the clutch driving part 30. Only the = ~1 3 ~7 ~ ~
6 4~,2~9 eccentricity o~ the -thin clutch part 30 is critical ~o that the clutch mechanlsm 14 is simple to assemble and has more accuracy than if the clutch driving part includes an extended sleeve carrying an actuating end and an input gear.
The forward radial side o~ the clutch part 30 includes a flat friction clutch surface for coupling engagement with a mating flat friction clutch surface of a rear flat radial side surface ~ormed on a plate portion 50 (shown in Fig. 2) o~ the driven part 32. A pinion gear 52 is carried in an integrally attached relationship w~th the plate portion 50 of the part 32. The pinion gear 52 is en- -gaged by a sector gear 560 The clutch part 32 is held axi-ally in place relative to the shaft 28 by a snap ring7 not shown, fitted into a center recess of the plate portion 507 mus, the plate 50, gear 52 and pusher member 36 rotate in uni~on. me sector gear 56 returns the clutch part 32 and pusher member 36 to a reset or an initial measuring posi-tion when the clutch mechanism is opened. me resetting operation is in accordance with the operation o~ a ~lock interval demand register in which the pusher member 36 is reset at the end of a predetermined demand mea~urlng inter-val or period such as fifteen, thirty or sixty minutes. me pusher resetting operation is described in the a~ore-mentioned U.S. Patent Nos4 3,405,338 and 2,259,314.
me clutch clo~ing member 42 includes a sleeve58 having a ~orward pressure applying plate 60 having substantially the æam~ diameter as the plate 50 of the clutch part 32. A forward flat radial side sur~ace o~ the plate 60 engages and presses against the rearward side radlal surface o~ the driving part 30. Thus engaged, the clutch part 30 is clamped in a sandwiched relationship between the clutch parts 32 a~d 42 in the closed position and coupling conditio~ of the clutch mechani~m 14. me eccentricity o~ the center hole o~ the sleeve 58 of the clutch part 42 is not critical since it is only required to provide rota~ing and slidable movement ~or applying ~xlal pressure to the mutually engaging surface~ of the , j .
S~
7 ~,~, 2 clwtch parts 30 and 32. The rearward end of the clutch part 42 includes a flange 64 in~egrally carried on t'ne rear end of the sleeve 58 and the helical spring 44 en-gages it to thereby bias the clutch part 42.
A clutch operating arrangement is provided by a trip lever or arm 66 mounted at a pivot 68 carried by a mounting plate 70 of the register 12. The right-hand or driving end of the lever 66 has a fork configuration defining tines extending over the sleeve 58 so that the ends of the tines are releasably engageable with a front flat radial surface of t ~ flange 64. The left-hand or driven end of the lever ~ is rotated by a solenoid act-uator 72 including a reciprocally movable cam 74 carried by a plunger armature 76. The armature 74 is reciprocally movable so that an increasing diameter or frustoconical camming surface of the cam 74 and a smaller straight diameter surface move the left-hand or driven end of the lever 66 to counter clockwise and clockwise positions, respectively. The solenoid actuator 72 includes a coil 78 which is energized by suitable electrical signals having opposite polarities as indicated by the d-irectinal arrows 80 and ~2 in Figs. 1 and 2, respectively. The electric signals move the armature 76 to an extended and right-hand most position as shown in Fig. 2 or to a retracted and left-hand most position shown in Fig. 1. The clutch closed position is produced by the armature 76 being electromagnetically shifted to the left or retracted position so that the lever arm 66 assumes a clockwise rotated position to be released from the flange 64 of the clutch part 42. The spring 46 biasingly urges the clu~ch part 42 and the clutch driving and driven parts 30 and 32 together so that the rotations of the gear train 20 are transmitted through the clutch mechanism 14 to the pusher member 36. The clutch open position and uncoupling condi-tion is illustrated in Fig. 2 when the armature 76 isshifted to the righ-t and extended position so that the lever arm 66 assumes a counterclockwise rotated position to drive the flange 64 rearwardly so that the clutch part , .. . .
:
, .13~j7~
8 ~ 4~ g 42 compresses the spring ~ and is spaced from the clutch driving part 30. The mutually engaging clutch friction surfaces of the clutch parts 30 and 32 are released and disengaged so that no torque is coupled thereacross.
The operation of the clutch mechanism 14 in a time of day or on-peal~ off-peak manner of watt demand metering provides coupling and extended uncoupling of the rotating measuring element 16 from the pusher member 36 which provides an actuating means for the indicator 40.
Typically, the predetermined times of day are selected for measuring which coincide with the peak demand periods of an electric utility supplying the electric energy being monitored by the meter 10. A locally or remotely gener-ated signal produces the electric signals having the polarity or direction of current flow indicated by the directional arrows 80 and 82. When the solenoid actuator 72 is electrically operated to shift the cam 74 to the retracted position as shown in Fig. 1, the lever 66 is rotated 6s~ that the end thereof is released from the flange ~ so that the clutch part 42 effects pressure against the clutch parts 30 and 32. The rotations of the rotatable measuring element 16 are then coupled through the gear train 20 and the clutch mechanism 14 to the pusher member 36 and indicator 40, as noted hereinabove.
The shaft 28, the spring 46 and clutch parts 30, 32 and 42 and the pusher member 36 all rotate in unison. There is negligible or low amount of mechanical loading or torque i~ applied on the gear train 20 and the measuring element 16 by the clutch mechanism to produce measuring movement of the indicator l~0, As is understood in the maximum demand metering art, the pusher member 36 engages and drives the indicator 40 upscale when the measuring element 16 rotates more in one demand interval than it has in any previous demand interval.
When it is desired to open the clutch mechanism 14 to either effect resetting of the pusher member 36, at the end of a predetermined demand interval, or to suspend or interrupt watt demand measurements for an extended ~3 9 4~,Z~
t-irne, the soleno-id actuator 72 is electrically op~rated ~y an eleclrical signal having the direction or polarity as indicated by the directional arrow 82 in Fig. 2. The cam 74 is extended and the larger diameter cam surface urges the lever arm 66 co~nterclockwise to slide the clutch part 42 rearward and release the clutch driving part 30 from the clutch driven part 32. The clutch part 42 is spaced and isolated from the clutch part 30 so it is freely rotatable in response to the rotatable measuring element 16 without any appreciable mechanical loading or torque being applied to the gear train 20 or the measuring ele-ment 16 due to the clutch opening operation producing the uncoupling condition of the clutch mechanism 14. In the ~i pusher resetting operation, the solenoid actuator 72 is .~ 15 energized to close the clutch after the sector ~Yg~m 56 drives the pinion gear 52 to the zero position after two to five seconds.
Fig. 3 illustrates an alternative clutch mecha-nism 110 that is capable of replacing the clutch mechanism 14 shown in Fig. 1. Accordingly, the shaft 28 has mounted thereon the clutch parts 30 and 32 in substantially the identical manner as they provided in the clutch mechanism 14. The clutch closing part 112 has the same general configuration as does the corresponding clutch closing part 42 excepting that a low strength permanent magnet 114 is carried in a recess 116 in the pressure plate portion 11~ of the clutch part 112. The pressure plate 118 is otherwise the same as the plate 60 and the remaining sleeve and fLange portions of the clutch part 112 are the same as in the clutch part 42.
When the mechanism 14 is closed, the flux of the magnet 114 will cause a temporary magnetic coupling be-tween the ~nagnetic material forming the driving part 30 and the magnet 114. When the clutch opening operation is provided, the lever 66 urges the clutch part 112 rearward against the spring 46 and the effect of the magnet 114 is to releasably attract the clutch part 30 so that positive disengagernent with the clutch driven part 32 is provided.
: ~ 1357~9~
~8,~g Any ~ ectx ~ausing cohesion o~ sticking between the nutually engaging fr-iction surfaces of the par~s 30 and 3~
are ~hereby overcome. The force of atLraction of the magnet 114 for the clutch part 30 is substantially smaller than the frictional force and retarding torque due to the engagement of the tines of the lever 66 with the flange 64. Thus, as the gear train 20 rotates the clutch part 30, the frlctional force of the lever 66 on the flange 64 is grea-ter than the magnetic attraction force between the clutch part 112 and the clutch part 30 to cause the clutch part 30 to break free of the clutch part 112 as it is shifted rearward and continue to rotate freely on the shaft 28. Thus, during the initial clutch opening opera-tion produced by the lever 66, the driving part 30 is pulled axially away from the driven par~ 32 by the attrac-tion of the magnet 114 as the part 110 slides rearward.
Further rearward axial movement of the part 110 and the rotations of the part 30 then cause the coupling between t~ dri~in~ part ~0 and closing part 112 to be broken.
2~ clutch mech~ni~m 1~ elos~ su~ n-tia~y same manner as d~sc~osed ~ereinabove f~r the c1utch mechanism 14. Accordingly, clockwise pivoting of the lever 66 permits the spring 46 to bias the clutch parts 112, 30 and 32 together to couple the rotations of the gear train gear 26 to the the associated pusher member 36 and when appropriate, ~he indicator 40.
While the clutch mechanisms 14 and 110 are described hereinabove for meter registers having a sin~le pointer indicator the clutch mechanisms can be used in a multiple dial pointer register or a cumulative demand type regis~er. Accordingly, preferred embodiments of the invention have been described hereinabove while contem-plating that other obvious alternatives and equivalents which would be understood by those skilled in the art may be employed without departing from the spirit and scope of this invention.
While the clutch mechanisms 14 and 110 are described hereinabove for meter registers having a sin~le pointer indicator the clutch mechanisms can be used in a multiple dial pointer register or a cumulative demand type regis~er. Accordingly, preferred embodiments of the invention have been described hereinabove while contem-plating that other obvious alternatives and equivalents which would be understood by those skilled in the art may be employed without departing from the spirit and scope of this invention.
Claims (7)
1. A watt demand meter register for indicating accumulated values of measured electric energy usage, comprising:
a rotatable measuring element rotated at a rate corresponding to the consumption of the measured electric energy usage quantity;
a gear train continuously driven by said rotatable measuring element;
a clutch driven part freely rotatable about an axis of rotation and carrying a pusher member for actuating a watt demand indicator means;
a clutch closing part freely rotatably about said axis of rotation and being axially shiftable;
a clutch driving part coaxially mounted between said clutch closing part and said clutch driven part, said clutch driving part freely rotatable about said axis of rotation and being axially shiftable, said clutch driving part being continuously driven by said gear train; and a clutch operator means for shifting said clutch closing part between one axial position spaced from said clutch driving part so as to disengage said parts and pre-sent minimal loading on said gear train, and another axial position wherein said clutch closing part engages said clutch driving part for effecting a common coupling engage-ment between said parts.
a rotatable measuring element rotated at a rate corresponding to the consumption of the measured electric energy usage quantity;
a gear train continuously driven by said rotatable measuring element;
a clutch driven part freely rotatable about an axis of rotation and carrying a pusher member for actuating a watt demand indicator means;
a clutch closing part freely rotatably about said axis of rotation and being axially shiftable;
a clutch driving part coaxially mounted between said clutch closing part and said clutch driven part, said clutch driving part freely rotatable about said axis of rotation and being axially shiftable, said clutch driving part being continuously driven by said gear train; and a clutch operator means for shifting said clutch closing part between one axial position spaced from said clutch driving part so as to disengage said parts and pre-sent minimal loading on said gear train, and another axial position wherein said clutch closing part engages said clutch driving part for effecting a common coupling engage-ment between said parts.
2. The watt demand meter register as claimed in claim 1 including means releasably coupling said driving part and said closing part so that when said closing part is shifted between said another and said one axial posi-tions said driving part is temporarily shifted rearward by said closing part to effect separation of said driving and said driven parts.
3. The watt demand meter register as claimed in claim 2 wherein said clutch operating means includes a pivotally mounted lever arm selectively engaging and disengaging said clutch closing part to selectively shift said clutch closing part between said one and another axial positions.
4. A watt demand meter register including an in-dicator for indicating totalized amounts of rotation of a rotable measuring element during predetermined demand intervals and a clutch mechanism for selectively coupl-ing and uncoupling the indicator with the rotations of the measuring element wherein said clutch mechanism comprises:
a shaft;
a driving part freely rotatable and axially shift-able on said shaft and including a thin disc having an outer gear periphery continuously coupled with the rotations of said measuring element and a side surface;
a driven part mounted in a freely rotatable axially fixed position on said shaft adjacent one side of said driving part and having a side surface frictionally engage-able by said side surface of said driving part;
a clutch closing part freely rotatable and axially shiftable on said shaft on the other side of said driving part, said closing part being slidable into engagement with said driving member for clamping said driving member to said driven member to effect coupling therebetween and further slidable away from said driving member to disengage said driving member;
spring biasing means carried on said shaft and urging said clutch closing part toward engagement with said clutch driving part;
a clutch operator including means engageable with said clutch closing part so as to axially slide said closing part to one position against the force of said biasing means to open said clutch mechanism and present minimal loading on 13 48,239 said gear train, and to another position releasing said clutch closing part so that said biasing means is effective to close said clutch mechanism; and pusher means fixedly carried by said driven part so as to provide measuring indications at said indicator in response to maximum numbers of the rotations of said measuring element occurring during said demand intervals exclusively when said clutch mechanism is closed.
a shaft;
a driving part freely rotatable and axially shift-able on said shaft and including a thin disc having an outer gear periphery continuously coupled with the rotations of said measuring element and a side surface;
a driven part mounted in a freely rotatable axially fixed position on said shaft adjacent one side of said driving part and having a side surface frictionally engage-able by said side surface of said driving part;
a clutch closing part freely rotatable and axially shiftable on said shaft on the other side of said driving part, said closing part being slidable into engagement with said driving member for clamping said driving member to said driven member to effect coupling therebetween and further slidable away from said driving member to disengage said driving member;
spring biasing means carried on said shaft and urging said clutch closing part toward engagement with said clutch driving part;
a clutch operator including means engageable with said clutch closing part so as to axially slide said closing part to one position against the force of said biasing means to open said clutch mechanism and present minimal loading on 13 48,239 said gear train, and to another position releasing said clutch closing part so that said biasing means is effective to close said clutch mechanism; and pusher means fixedly carried by said driven part so as to provide measuring indications at said indicator in response to maximum numbers of the rotations of said measuring element occurring during said demand intervals exclusively when said clutch mechanism is closed.
5. The watt demand meter register as claimed in claim 4 wherein said clutch closing part includes a weak magnetic means carried in a facing relationship to said driving part for effecting a releasable coupling between said closing part and said driving part.
6. The watt demand meter register as claimed in claim 4 wherein said clutch operator includes a recipro-cally movable cam member for selectively actuating said means engagable with said closing part.
7. The watt demand meter register as claimed in claim 6 including a solenoid actuator for effecting recip-rocal movement of said cam.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US06/102,499 US4307341A (en) | 1979-12-11 | 1979-12-11 | Clutch mechanism for time of day watt demand meter registers |
| CA000383829A CA1135794A (en) | 1979-12-11 | 1981-08-13 | Clutch mechanism for time of day watt demand meter registers |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US06/102,499 US4307341A (en) | 1979-12-11 | 1979-12-11 | Clutch mechanism for time of day watt demand meter registers |
| CA000383829A CA1135794A (en) | 1979-12-11 | 1981-08-13 | Clutch mechanism for time of day watt demand meter registers |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1135794A true CA1135794A (en) | 1982-11-16 |
Family
ID=54207216
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000383829A Expired CA1135794A (en) | 1979-12-11 | 1981-08-13 | Clutch mechanism for time of day watt demand meter registers |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US4307341A (en) |
| CA (1) | CA1135794A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4364009A (en) * | 1980-07-14 | 1982-12-14 | Westinghouse Electric Corp. | Clutch mechanism for time of day watthour meter registers |
| US4686461A (en) * | 1984-07-12 | 1987-08-11 | Westinghouse Electric Corp. | Auxiliary equipment mounting ring for electric meter |
| US4852030A (en) * | 1984-09-24 | 1989-07-25 | Westinghouse Electric Corp. | Time-of-use-meter with a calendar of cyclic events |
| US6386116B1 (en) * | 2000-06-23 | 2002-05-14 | Storage Technology Corporation | Propulsion decoupling method and system for multiple track mounted robots of an automated storage library |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1405927A (en) * | 1920-02-14 | 1922-02-07 | Lauth Jacob | Clutch mechanism |
| US1985422A (en) * | 1932-03-28 | 1934-12-25 | Twin Dise Clutch Company | Clutch |
| US2259314A (en) * | 1938-07-01 | 1941-10-14 | Westinghouse Electric & Mfg Co | Demand register |
| US2859924A (en) * | 1955-09-30 | 1958-11-11 | Enterprise Mfg Co | Free spool fishing reel |
| US3406338A (en) * | 1965-09-14 | 1968-10-15 | Westinghouse Electric Corp | Maximum-demand device with clutch having adjustable open time |
| US3913014A (en) * | 1974-06-13 | 1975-10-14 | Westinghouse Electric Corp | Demand meter for on-peak maximum demand metering |
-
1979
- 1979-12-11 US US06/102,499 patent/US4307341A/en not_active Expired - Lifetime
-
1981
- 1981-08-13 CA CA000383829A patent/CA1135794A/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| US4307341A (en) | 1981-12-22 |
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| Date | Code | Title | Description |
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| MKEX | Expiry |