Stepping mechanism for rotary motions

The invention relates to a stepping mechanism for rotary motions with a driven switching wheel (9) which comprises at least one wheel-side stop (10), with an escapement mechanism having at least one pawl (12) which cooperates with said wheel-side stop, and with an actuating device (3, 17) for the pawl. Pursuant to the invention, a miniaturizable stepping mechanism is provided which is of a simple design and which permits reliable positioning of the switching wheel into preselected individual rotational positions. According to the invention, this is achieved in that the escapement mechanism of the stepping mechanism comprises a brake (20) displaceable under the action of force, with a run-up edge (21) lying in the region of each pawl (12) on to which the wheel-side stop (10) runs up before striking the pawl (12) to thereby displace the brake. Preferably, the brake and the pawls are arranged on a rocker (20, 13) for each, these being pivotable about a common rotary shaft (14) not lying in the axis of rotation (A) of the stepping mechanism. The stepping mechanism can be used for the control (i.e. steering) of missiles. To this end the switching wheel is preferably connected with a rotary nozzle body (1) which, via a thrust nozzle (8), delivers a propellant jet approximately in a radial direction.

BACKGROUND AND SUMMARY OF THE INVENTION 
The invention relates to a stepping mechanism for rotary motions. 
Stepping mechanisms are known for a plurality of uses. In this connection, 
it is often desirable to have available a simply functioning stepping 
mechanism which is miniaturizable to a high degree, which can be stepped 
at high speed, and which occupies exact stepped positions. From DE-PS 33 
17 583 there is known, for example, a rotary nozzle arrangement, also 
miniaturizable to a high degree, which can be used for the control (e.g. 
steering) even of small-caliber shells. This rotary nozzle arrangement 
comprises a rotary nozzle body which is driven by the propellant stream, 
e.g. of a gas generator, continuously, at a high speed. The propellant 
stream issues from a thrust nozzle. The rotary nozzle arrangement is 
mounted in a missile so that the propellant stream is blown out 
approximately radially to the missile casing and hence exerts a steering 
force on the missile. The direction of the propellant stream can be 
defined with the aid of a brake which acts on the rotary nozzle body and 
can retain the latter in any desired position. The entire rotary nozzle 
arrangement can be miniaturized so that its diameter is in the millimeter 
range. Instead of using a brake for the retention of the rotary nozzle 
arrangement, also a stepping mechanism would be suitable which presets 
certain positions for the rotary nozzle body. 
A stepping mechanism is known from U.S. Pat. No. 4,463,921. With this 
stepping mechanism, the position of a gas distributor is adjusted. The gas 
distributor communicates with blow-out ports at the circumference of the 
casing of a missile and through which a propellant stream of a gas 
generator is blown out in different, approximately radial directions for 
the steering of the missile. This known stepping mechanism, however, is 
relatively expensive as to design and is not miniaturizable to the desired 
degree. 
It is the object of the present invention to provide a stepping mechanism 
for rotary motions which is miniaturizable to a high degree and which 
offers high setting speeds combined with the possibility of exact 
positioning. 
According to the invention, the objective is achieved through a novel brake 
which is engaged and displaced by a wheel-side stop of a switching wheel 
prior to the rest position of the switching wheel, as will appear. 
In the stepping mechanism of the invention, a continuous drive of the 
switching wheel is necessary. This continuous drive can take place e.g. by 
means of the above-mentioned rotary nozzle arrangement if the rotary 
nozzle body is connected coaxially with the drive shaft of the switching 
wheel. The continuous drive provides a very high stepping speed in the 
operation of the stepping mechanism. For the switching wheel, which 
carries at least one wheel-side stop, an escapement mechanism with at 
least one pawl is provided. To obtain exact positioning of the switching 
wheel and an optimally delayed entry of the switching wheel into the 
respective stepped position, there is provided, in the region of the pawl, 
a brake with a run-up edge on which the wheel-side stop of the switching 
wheel runs up before its entry into the final stepped position. The brake 
is thereby displaced and the switching wheel is delayed in entering into 
the final stepped position. Preferably, the braking action, i.e. the force 
needed to displace the brake, is adjustable, e.g. by means of compression 
springs or by magnetic pressing, in that the brake is arranged between the 
pawl and a magnet. Depending on the strength of the magnet, the brake will 
be pressed more or less against the magnet or a friction disk, and the 
braking force is thereby adjustable. 
To obtain a dynamically balanced operation of the stepping mechanism, the 
escapement mechanism preferably comprises two pawls located on opposite 
sides of the switching wheel and also two brakes. The pawls, as well as 
the two brakes can be formed by a rocker, both of which are pivotable 
about a common axis. The axis here lies in the center between the pawls or 
the run-up edges, respectively. As a result, practically no imbalances 
occur during operation. 
The escapement mechanism can be brought into the required position by an 
external actuating device, but it is advantageous to utilize for this 
purpose, at least in part, the drive force for the switching wheel, which 
is available anyway. The wheel-side stops and the pawls are formed so 
that, during the abutment of a wheel-side stop, a force acts on a pawl 
which force pressurizes the pawl in the direction of release of the 
wheel-side stop. A releasable holding device must then also be provided 
for the pawl. If the pawl is thereby released, it is pushed away by the 
wheel-side stop, the wheel-side stop being released. If then, e.g., two 
pawls are provided jointly on a rocker, the other pawl can thereby be 
brought into a position in which a wheel-side stop is retained in the next 
stepped position. The actuation of the pawl by the drive force can be 
further supported by a compression spring. 
On the same principle also, the brake can be positioned accordingly by the 
switching wheel, in particular, if the brake is designed as a rocker with 
two opposite run-up edges. To obtain an exact positioning of the pawls, 
fixing means may be provided in which the pawl is retained in the desired 
two positions in each instance. Such fixing can occur for instance, by 
means of lock balls. 
The masses to be moved in the stepping operation of the stepping mechanism 
are very small, so that, on the whole, a stepping mechanism with small 
inertia is made possible. 
It is also an objective of the present invention to provide a straight 
forward design for a stepping switch, of the type described above, which 
functions with few component parts. 
This objective is achieved according to a further embodiment of the present 
invention, by providing two connecting links, a pawl link and a clamping 
link, which move in simple shifting movements, into respective two 
switching positions, perpendicular to the axis of rotation of the rotary 
operating mechanism. This provides the use of simple bearing and guide 
means for the connecting links, for example with the use of pins and 
slotted holes. The spring supported movement of the pawl link is 
accomplished with the help of an annular spring, which encircles both 
connecting links and abuts against only one of the connecting links, at 
any one time, on opposite sides in the area of the guide means. This 
annular spring is deformed by the clamping link, which is actuated by the 
ratchet wheel, and is thereby tensioned, so that it exerts a force, in the 
direction of the axis of rotation of the rotary operating mechanism, on 
the pawl link, which is retained in one switching position. If the pawl 
link is released, it is then shifted by the annular spring into the other 
switching position, in which it now abuts against the annular spring on 
the opposite side. When the ratchet wheel is rotated further, the clamping 
link is simultaneously pressed into the other switching position, so that 
it again lies on the now other side of the annular spring, and tensions it 
once more with deformation. This exchange cycle repeats itself. 
In the case of the stepping switch, according to the further embodiment of 
the present invention, it is not essential that any self-arresting action 
occurs during the operation of the escapement mechanism. On the contrary, 
the pawls and the end stops on the ratchet wheel can be made 
conventionally, so that self-arresting action occurs. Of course, a 
functioning without self-arresting action is also possible, whereby as in 
the case of the above described embodiment of the invention, the shifting 
of the pawl link into the other switching position, at the time, is 
supported by the ratchet wheel. 
The escapement mechanism of the stepping switch according to the further 
embodiment of the invention, features only three simple component parts, 
namely the two plate-shaped connecting links, as well as an annular 
spring. These parts are simple to manufacture, so that, to a great extent, 
the stepping switch can be miniaturized. 
The invention will now be described in greater detail in the following 
detailed description with reference to the accompanying drawings.

DETAILED DESCRIPTION 
In FIG. 1, the reference numeral 1 denotes a rotary nozzle body, 2 a 
stepping module, and 3 an electrically actuated pot magnet, which together 
form a stepping mechanism. This stepping mechanism is installed, for 
instance, in a missile and serves for the control (i.e. steering) thereof. 
The rotary nozzle body consists of a neck portion 4 and a head portion 5 
and is rotatably mounted in a wall 6 of the missile. In the head portion 
5, a recess 7 open on the front of the rotary nozzle body is provided, 
from which there originates a thrust nozzle 8 which traverses the wall of 
the head portion 5. Flowing into the recess 7 is a propellant, e.g. hot 
gas, from a gas generator (not specifically illustrated). This propellant 
is represented schematically by an arrow and G. The propellant is blown 
off through the thrust nozzle 8, namely so that there results a thrust 
jet, the thrust direction of which does not pass through the axis of 
rotation A of the rotary nozzle body. A torque is thereby exerted on the 
rotary nozzle body 1, so that the rotary nozzle is set in rapid rotation 
about the axis of rotation without impediment. 
By the end of its neck portion 4, the rotary nozzle body 1 is firmly 
connected with a switching wheel 9 disposed in the stepping module 2. As 
can be seen from FIG. 3, this switching wheel 9 comprises three stops 10a, 
10b and 10c, arranged at angular distances of 120.degree. each. The 
wheel-side stops 10a to 10c cooperate with two opposite pawls 12a and 12b 
of a pawl rocker 13. This pawl rocker 13 embraces the switching wheel and 
is mounted laterally on a rotary shaft 14. The rotary shaft 14 is parallel 
to the axis of rotation A of the switching wheel. On the side opposite the 
rotary shaft 14, the pawl rocker 13 has two recesses 15, into which a 
detent ball 16 can engage which lies on a beam bracket 17. This beam 
bracket 17 is situated on the side of the stepping module 2 toward the pot 
magnet 3, is mounted on the rotary shaft 14, and is fixed in its position 
by the arrangement of a bore 18 coaxial to the axis of rotation A through 
which the bracket 17 embraces an axle stub 19 of the stepping module 2. 
This axle stub 19 may be e.g. an extension of the neck portion 4 of the 
rotary nozzle body 1. The recesses 15 in the pawl rocker 13 are situated 
so that in both positions of the pawl rocker 13 one of the two pawls 12a 
or 12b can come in engagement with one of the wheel-side stops 10. In FIG. 
3, as well as in FIG. 5a, the wheel-side stop 10a applies against pawl 
12a; in the other position of the pawl rocker 13, the wheel-side stop 10b 
can run up onto the pawl 12b, as shown in FIGS. 5b and 5e. The pawl rocker 
13 is stamped from a thin magnetic sheet. 
On the bottom of the stepping module 2, between the pawl rocker 13 and the 
pot magnet 3, a brake rocker 20 is mounted. The brake rocker 20 is also 
stamped from a magnetic sheet and has more or less the form of a half 
annulus. The brake rocker 20 is centered and mounted on the rotary shaft 
14. At both its ends the brake rocker 20 has teeth pointing inwardly in 
the direction of the axis of rotation A, which teeth are provided with a 
run-up edge 21a, 21b. These run-up edges 21a, 21b are situated in the 
vicinity of the pawls 12a, 12b. Just as the pawl rocker 13, the brake 
rocker 20 swings between two positions, for which appropriate stops 22 and 
23 are provided. In the region of the teeth 21 of the brake rocker 20 
there are further provided guide slots 24 for a compression spring 25, 
which takes support at one end on the bottom of the respective guide slot 
and by its other end on the outer edges of the pawl rocker 13. 
Contiguous to the stepping module 2 is the pot magnet 3, the ring poles of 
which are marked 26 and 27. The position of the ring poles 26 and 27 and 
the form of the pawl rocker 13 and of the brake rocker 20 are matched in 
such a way that the outer ring pole 26 runs approximately along the outer 
edge of the pawl rocker 13 and of the brake rocker 20, while the inner 
ring pole 27 runs along the inner edge of the pawl rocker and brake 
rocker, respectively. In addition, the wheel-side stops 10a to 10c of the 
switching wheel 9, the pawls 12a and 12b, as well as the run-up edges 21a 
and 21b are arranged so that the wheel-side stops can cooperate both with 
the pawls and with the run-up edges. Further, the stop edges of the 
wheel-side stops 10a to 10c as well as of the pawls 12a and 12b are formed 
so that when a wheel-side stop runs off from a pawl, the pawl rocker 13 is 
pushed out of the respective holding position toward the respective other 
position, both positions being determined by the engagement of the detent 
ball 16 in recess 15. 
The operation of the described stepping mechanism will be explained with 
reference to FIGS. 5a to 5e. 
In one holding position, as illustrated in FIG. 5a, the wheel-side stop 10a 
applies against pawl 12a of the pawl rocker 13; the brake rocker 20 is 
pressed by the wheel-side stop 10a against its stop 22. The pot magnet 3 
is energized, so that the pawl rocker 13 is attracted and retained by the 
ring poles 26 and 27. The holding force is greater than the rotary force 
acting on the switching wheel as a result of the rotary nozzle body being 
supplied with the propellant. If the pot magnet is now deenergized, the 
switching wheel begins to rotate, in this case clockwise, pushing the pawl 
rocker 13 upward counterclockwise in the figure. The moment when the 
wheel-side stop 10a runs off the tip of pawl 12a is illustrated in FIG. 
5b. The pivoting motion of the pawl rocker 13 counterclockwise is 
supported by what in the figure is the lower compression spring 25. At the 
same time the lower pawl 12b is thereby brought into a position relative 
to the brake rocker 20 in which the run-up edge 21b of rocker 20 lies in 
the direction of rotation of the switching wheel--in front of the pawl and 
extends to the tip of pawl 12b. The brake rocker 20 is thereby pivoted 
clockwise and owing to its inertia brakes the switching wheel 9. The start 
of the run-up of the wheel-side stop 10b onto the run-up edge 21b is 
illustrated in FIG. 5c. Upon further rotation of the switching wheel 9 
according to FIG. 5d, the brake rocker 20 is pivoted clockwise by the 
contact of the wheel-side stop 10b with the run-up edge 21b, until 
according to FIG. 5e the brake rocker applies against the lower stop 23. 
In this position then also the braked wheel-side stop 10b strikes against 
the pawl 12b. During the pivoting of the brake rocker, the upper 
compression spring 25 in the figures is tensioned. In the meantime the pot 
magnet 3 has been energized again, so that it retains the pawl rocker 13, 
and the position per FIG. 5e determines the new rotational position of the 
stepping mechanism. 
If the stepping mechanism is to be actuated anew, the pot magnet is again 
deenergized, so that the pawl rocker 13 is pivoted clockwise again into 
the starting position per FIG. 5a, the run-up edge 21a being then in the 
corresponding brake position again with respect to pawl 12a, as is shown 
in FIG. 5c. The pivoting movement of pawl rocker 13 is now supported by 
the upper compression spring 25. 
With the illustrated stepping mechanism six fixed rotational positions of 
the switching wheel can be obtained, at angular distances of 60.degree.. 
If the number of wheel-side stops is greater, naturally additional 
rotational positions can be obtained. 
The braking forces exerted by the brake rocker 20 on the switching wheel 
when a wheel-side stop runs onto one of the run-up edges are preferably 
brought about solely by the inertia of the brake rocker. This ensures that 
the wheel-side stops will always run into the end position up to abutment 
on a pawl. This braking force, however, can be increased, e.g. adjusted to 
a base force, or even varied. This can be done in several ways. If the 
brake rocker itself is of magnetic material, the braking force can be 
influenced by the attraction force of the pot magnet and can thus also be 
varied. Further, a friction force can act on the brake rocker, e.g. by 
appropriate friction linings of the brake rocker or by pressurization with 
springs or other dampers. In this case, of course, the brake rocker need 
not be of magnetic material. The braking force should, however, be 
increased only to a base force for which it is assured that a wheel-side 
stop will always run into the end position to abutment on a pawl. 
In FIG. 6 an exploded view of the essential parts of an additional stepping 
mechanism is illustrated. It differs from the above described embodiment 
in that the stepping module 2' comprises two switching wheels 9' and 9" 
firmly connected together, which in turn comprise two sets of wheel-side 
stops 10', 10". The two switching wheels are of the same design but are 
rotated relative to each other by 180.degree.. Both switching wheels are 
again firmly coupled with a rotary nozzle body 1'. The stepping module 2' 
again comprises one pawl rocker 13', but 
two brake rockers 20' and 20". Pawl rocker 13' is structurally identical 
with the above described design and the brake rockers 20' and 20" are 
identical in design with the above described brake rocker 20. The brake 
rockers 20' and 20", however, lie in front of the pawl rocker 13', so that 
the latter abuts directly on the pot magnet 3'. For the positioning of the 
pawl rocker 13' again a brake bracket 17' with appropriate detent balls, 
is provided. The switching wheel 9' toward the pot magnet 3' cooperates 
with the pawl rocker 13' and with the brake rocker 20', as has been 
described above. The brake rocker 20" cooperates only with the switching 
wheel 10" turned toward the rotary nozzle body 1', namely so that, 
whenever the brake rocker 20' is displaced by a stop 10' of the switching 
wheel 9', the brake rocker 20" is pivoted oppositely to the brake rocker 
20' by a stop 10" of switching wheel 9' located exactly opposite. 
This has the following advantage: In the first embodiment there is exerted 
on the switching wheel upon run-up on one of the run-up edges of the brake 
rocker a force in the direction of the axis of rotation of the switching 
wheel. This may cause imbalances, especially if the stepping mechanism is 
highly miniaturized. These shocks in the direction of the axis of rotation 
are compensated by counter-forces that are generated by the run-up of a 
wheel-side stop 10" of switching wheel 9" onto the run-up edge of the 
second brake rocker 20" on the respective opposite side. Thereby an 
absolutely true running of the stepping mechanism is ensured. As in the 
above embodiment, the braking force of the brake rockers 20' and 20" can 
be preset to a certain value, e.g. by pressurization with compression 
springs. Here, too, it must be ensured that the switching wheel 9' always 
runs into the end position. 
In the described operation of the two stepping mechanisms the pawl rocker 
was held in its position by the force of the pot magnet. It is possible 
also to let a permanent magnet supply this holding force. For release of 
the rocker, the pot magnet need then be energized only briefly with a 
pulse by which the holding force of the permanent magnet is reduced. With 
such a design, a stepping mechanism of low energy consumption is possible. 
Besides, the coils of the pot magnet can be correspondingly small, as they 
no longer need to supply the actual holding force and will not heat up. 
In FIG. 7, a rotary nozzle body is designated with 101, an escapement 
mechanism with 102, and an electrically actuated pot magnet with 103; 
which together form a stepping switch. The stepping switch is, for 
example, installed in a missile, which it serves to control. The rotary 
nozzle body 101 consists of a neck piece 104 and a headpiece 105, and is 
rotatably supported in a wall 106 of the missile. An open recess 107 is 
provided in the headpiece 105, on the front end of the rotary nozzle body 
101. A propelling nozzle 108 leads out from this recess and penetrates the 
wall of the headpiece 105. A propellant, for example hot gas, from a gas 
generator (not shown) flows into the recess 107. This propellant is 
discharged through the propelling nozzle 108, so that a propelling jet 
results, with a direction of thrust, which does not run through the axis 
of rotation A of the rotary nozzle body 101. An angular momentum is 
thereby exerted on the rotary nozzle body 101, setting it into a fast 
rotation, with no retardation, around the axis of rotation A. 
A shaft 109 is connected to the neck piece 104 of the rotary nozzle body 
101, coaxially to the axis of rotation. A clamping wheel 110 and a ratchet 
wheel 111, which are directly joined together, are attached to the shaft 
109. The clamping wheel 110 and the ratchet wheel 111 can also be 
manufactured as a single component part. As illustrated in FIG. 8, the 
ratchet wheel 111 has three end stops 112a, 112b and 112c, which are 
arranged around its circumference at angular distances of 120.degree.. The 
clamping wheel 110 includes cams 113, which are aligned with the three end 
stops 112a to 112c of the ratchet wheel 111, respectively. 
Two connecting links, including a clamping link 114 and a pawl link 115, 
work together with the clamping wheel 110 and the ratchet wheel 111, 
respectively, as will be described. The plate-shaped clamping link 114 
includes a ring area 116, which encircles the ratchet wheel and has two 
outwardly extending lugs 117 on opposite sides. Two slotted holes 118 are 
formed in the lugs 117, perpendicular to the axis of rotation A, and guide 
pins 119 are received in the slotted holes. The clamping link 114 can be 
shifted back and forth, perpendicular to the axis of rotation A, between 
an upper switching position, as shown in FIG. 7, and a lower switching 
position. The clamping link 114 includes two cams 120 on the inner 
circumference of the ring area 116, which lie on opposite sides of the 
clamping wheel 110, in the shifting direction of the clamping link, and 
which work together with the cams of the clamping wheel 113. 
The pawl link 115 is of a similar construction and includes a ring area 
121, which encircles the ratchet wheel and has two lugs 122, as well as 
slotted holes 123 formed therein, in which the guide pins 119 likewise 
engage. Two pawls 124a and 124b are mounted on the inner circumference of 
the ring area. They work together with the pawls 112a to 112c of the 
ratchet wheel 111. 
The clamping link 114 and the pawl link 115 are surrounded by an annular 
spring 125, which has a width corresponding to the thickness of both 
pawls, as illustrated in FIG. 7. In each switching position of the 
escapement mechanism, the annular spring abuts against a lug of one 
connecting link, on the one side, and against a lug of the other 
connecting link, on the other side. In FIGS. 7 and 8, the clamping link 
114 is in the upper switching position and the pawl link 115 is in the 
lower switching position, so that the annular spring 125 abuts against the 
upper lug 117 of the clamping link 114 and against the lower lug 122 of 
the pawl link 115. The annular spring 125 is deformed and exerts a force, 
which acts on both connecting links in the direction of the axis of 
rotation A. 
The poles of the pot magnet 103 are directed toward the pawl link 115. The 
pawl link 115 can be retained in its current switching position by 
switching on the pot magnet 103 or it can be released, by switching off 
the pot magnet. Other magnetic systems can also be used, such as, for 
example, two magnets or a polarized magnetic system. With an appropriate 
formation of the poles in the magnetic arrangement, the pawl link is 
retained either by a magnetic force or, as in the case of the present 
embodiment, by the magnetic force and, for the most part, by the 
frictional force between the poles and the pawl link 115. Of course, it is 
also possible to use other retaining and releasing devices for the pawl 
link 115. 
The described stepping switch functions as follows: 
In the switching position of the stepping switch depicted in FIGS. 7 and 8, 
the end stop 112a of the ratchet wheel 111 abuts against the upper pawl 
112a of the connecting link 115, which is retained in its lower switching 
position with the help of the pot magnet 103. Its lower lug 122 abuts 
against the inner circumference of the annular spring 125. The cam 113 of 
the clamping wheel 110, which is aligned with the end stop 112a on the 
ratchet wheel, abuts against the upper cam 120 of the clamping link, so 
that this clamping link is pushed into its upper switching position and, 
with its upper lug 117, abuts against the annular spring 125. The annular 
spring 125 is deformed by the lugs 117, 122 and consequently tensioned 
against both connecting links, as shown. 
If the pot magnet 103 is switched off, then the pawl link 115 is released. 
The pawl link in FIG. 8 is pushed upwards by the force of the annular 
spring 125 toward the opposite switching position. As soon as the pawl 
124a of the pawl link 115 comes off the end stop 112a, the ratchet wheel 
111 and the clamping wheel 110 in FIG. 8 are released to rotate counter 
clockwise. At this moment, however, the upper lug 122 of the pawl link 
abuts against the upper inner circumference of the annular spring 125. The 
pawl link is retained, by again turning on the pot magnet 103. Instead of 
turning the magnet on and off, this switching operation can be replaced by 
reversing the voltage on the magnet. When the ratchet wheel 11 continues 
to turn and rotate 60.degree., its end stop 112b runs up against the 
advancing pawl 124b, now moved inwards, of the pawl link 115, so that the 
rotary motion is once again interrupted. However, the cam 113 of the 
clamping wheel, which is aligned with the end stop 112b, also runs up 
against the lower cam 120 of the clamping link 114, so that the clamping 
link is pushed downwards and, with its lower lug 117, is positioned 
against the annular spring 125, and again deforms and tensions the spring 
125. 
This working cycle repeats itself when the pot magnet 103 is actuated 
again, so that now the end stop 112c of the ratchet wheel 111 abuts 
against the upper pawl 124a of the pawl link. The two connecting links are 
then situated once again in the initial state, as shown in FIG. 8. 
In the illustrated embodiment, when the ratchet wheel runs into the next 
stopping position, it is already braked as a result of the shifting of the 
clamping link into the other switching position, so that the current end 
stop of the ratchet wheel runs up smoothly against the assigned pawl of 
the pawl link 115. In this case, additional measures can still be taken to 
intensify the cushioning effect, when the ratchet wheel runs into the 
stopping position. 
Another specific embodiment of an escapement mechanism 102 is shown in FIG. 
10. This specific embodiment differs from the escapement mechanism of 
FIGS. 7 and 8, only in that two superposed annular springs 125a and 125b 
are provided, instead of one annular spring. The other component parts as 
well as the functioning of the escapement mechanism remain the same. With 
this type of spring arrangement, the spring characteristic can be 
influenced accordingly. Furthermore, it is possible to insert an 
attenuator 131 between the two annular springs 125a and 125b, at least in 
their upper and lower contact areas, above or below the guide pins 19. The 
shifting of the clamping link 114 by the clamping wheel into the other 
switching position can be, hereby, damped accordingly, as a result of 
energy absorption in the attenuator 131, so that the end stops on the side 
of the wheel run up smoothly against the assigned pawls of the pawl link 
115. 
With good spring qualities, the annular springs used for the escapement 
mechanisms can have a small and compact design. They are easy to replace 
and especially guarantee a symmetry with regard to the movements of both 
connecting links into the switching positions.