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Claims  |
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We claim:
1. In a firearm of the type having: a frame; a hammer mounted on the frame
for movement between normal and fired positions; a trigger mounted on the
frame for movement between normal and pulled positions; and a main spring
interposed between the hammer and the trigger for driving the hammer to
the fired position, the main spring being adapted to be compressed by
moving the trigger from the normal position thereof toward the pulled
position thereof without substantial hammer movement from the normal
position thereof, the improvement comprising:
a toggle spring device interposed between the hammer and the frame for
resisting substantial hammer movement from the normal position thereof
while the main spring is being compressed and for urging return movement
of the hammer from the fired position thereof to the normal position
thereof; and
means responsive to movement of the trigger for contacting and buckling the
toggle spring device to change the resistance thereof such that the
compressed main spring may drive the hammer to the fired position thereof.
2. The improvement of claim 1, further comprising:
the hammer and the trigger being mounted on the frame for pivoting movement
about a common axis.
3. The improvement of claim 1, wherein the main spring comprises:
a V-shaped leaf spring having an apex and two legs, the apex of the main
spring being positioned in the trigger.
4. The improvement of claim 3, wherein the end of one of the legs of the
main spring is mounted on the trigger and the other of the legs has its
end in sliding engagement with the hammer.
5. The improvement of claim 1, wherein the toggle spring device comprises:
a leaf spring having a portion of its length thicker than the remaining
portion; and wherein the frame comprises:
surface means to prevent deflection in a first direction of the toggle
spring device during the trigger pull, the resistance of the toggle spring
device being reduced by buckling in a second direction opposite to the
first direction.
6. The improvement of claim 5, wherein the trigger movement responsive
means comprises:
a surface on the trigger.
7. The improvement of claim 1, further comprising:
means to withdraw the hammer from the fired position during return movement
of the trigger from the pulled position to the normal position.
8. In a revolver of the type having: a frame; a cylinder mounted in the
frame for rotation between discrete index positions, the cylinder having a
plurality of locking recesses on the periphery thereof; a cylinder spring
operatively connected to the cylinder for producing rotation thereof; a
trigger mounted in the frame for movement between normal and pulled
positions; a cylinder stop having a projection thereupon mounted in the
frame forwardly of the trigger such that the projection is adapted to be
received within a locking recess; and a cylinder stop spring mounted in
the frame and connected to the cylinder stop for urging the projection
against the cylinder and for urging the cylinder stop rearwardly toward
the trigger; the improvement comprising:
each of the locking recesses being constituted by a primary locking notch
with an abutment wall and a secondary locking notch with an abutment wall
circumferentially and axially spaced forwardly from the abutment wall of
the primary locking notch; and
a surface on the trigger adapted to engage the cylinder stop during trigger
return and push the cylinder stop forwardly such that the projection
leaves the primary locking notch and enters the secondary locking notch
and adapted to disengage from the cylinder stop during further trigger
return such that the cylinder stop may move rearwardly under the impetus
of its spring urging out of the secondary locking notch and onto the
periphery of the cylinder, whereby the cylinder can rotate to the
succeeding index position.
9. The improvement of claim 8, further comprising:
a plurality of safety notches on the periphery of the cylinder; and
an extension on the trigger adapted to enter a safety notch during movement
of the trigger from the normal position thereof to the pulled position
thereof when the cylinder is in an index position, the extension
contacting the periphery of the cylinder during trigger movement to the
pulled position thereof when the cylinder is not at an index position to
prevent further trigger movement and possible firing of the revolver.
10. In a cylinder assembly of the type adapted to be placed within a frame
of a revolver and of the type having a cylinder with a plurality of
cartridge chambers and a central bore extending therethrough, the
improvement comprising:
a cylindrical cylinder guide positioned in one end of the bore, the guide
having an extension thereupon for receipt in cavities in the frame;
a cylindrical ratchet, having a plurality of teeth, positioned in the other
end in driving connection with the cylinder;
a spring mounted in the central bore in engagement with the guide and
ratchet, the spring being adapted to urge the guide and ratchet away from
the cylinder and to urge rotation of the cylinder;
a yoke for mounting in the frame having two legs with respective apertures
therein, the extensions of the guide and ratchet being respectively
received in the apertures such that the guide is prevented from rotating
in its aperture and the ratchet is free to rotate in its aperture; and
means on the yoke to engage the teeth when the assembly is out of the frame
to prevent rotation of the cylinder relative to the yoke under the impetus
of the spring while permitting rotation of the cylinder relative to the
yoke to store energy in the spring.
11. The improvement, as defined in claim 10, further comprising:
a cartridge plate mounted for limited rotation on the ratchet for
preventing rearward movement of cartridges in the chambers and covering
exposed primers thereof.
12. In a revolver of the type having: a frame; a trigger mounted on the
frame for movement between normal and pulled positions; a cylinder, having
a plurality of locking recesses for indexing, mounted in the frame for
rotation between discrete index positions during trigger return from the
pulled position to the normal position, the improvement comprising:
a plurality of safety notches on the periphery of the cylinder; and
an extension upon the trigger adapted to enter one of the safety notches
during movement of the trigger from the normal position thereof to the
pulled position thereof when the cylinder is in an index position and
adapted to contact the periphery of the cylinder during trigger movement
to the pulled position thereof when the cylinder is not at an index
position to prevent further trigger movement and possible firing of the
revolver.
13. In a method for rotating a cylinder between index positions in a
revolver of the type which includes the steps of: urging rotation of the
cylinder with a spring; maintaining contact with a first abutment wall on
the cylinder to prevent the cylinder from rotating from an index position;
and terminating contact with the first abutment wall to permit the
cylinder to rotate, the improvement comprising:
establishing contact with a second abutment wall on the cylinder after the
cylinder has rotated through an angular increment smaller than that
between adjacent index positions to stop cylinder rotation at a location
between index positions;
terminating contact with the second abutment wall to permit the cylinder to
rotate; and
establishing contact with a third abutment wall to stop cylinder rotation
at another index position.
14. The improvement, as defined in claim 13, wherein the terminating of
contact with the first abutment wall comprises:
moving a cylinder stop from a first axial station on the cylinder to a
second axial station on the cylinder; and wherein the terminating of
contact with the second abutment wall comprises:
moving the cylinder stop from the second axial station to the first axial
station.
15. In a method of operating a firearm of the type which includes the steps
of: compressing a main spring against a striking device to bias the device
toward a cartridge while substantially maintaining the position of the
striking device relative to the cartridge; and releasing the striking
device after the main spring has been compressed to allow the main spring
to drive the striking device toward the cartridge, the improvement
comprising:
buckling a toggle spring device connected to the striking device to effect
the releasing of the striking device, the toggle spring device serving to
maintain the position of the striking device before the buckling thereof
and to bias the striking device away from the cartridge after the buckling
thereof.
16. The improvement, as defined in claim 15, wherein the firearm has a
trigger mounted thereupon connected to the mainspring and wherein the
compressing comprises pulling the trigger; and wherein the buckling
comprises:
bringing the trigger and toggle spring device into engagement. |
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Claims |
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Description |
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BACKGROUND OF THE INVENTION
This invention relates to double action revolvers.
Present day revolvers are relatively expensive to manufacture. This is due
in large part to the great amount of hand fitting which is required.
Typically, the searing surfaces of the hammer and trigger must be hand
filed in addition to the pawl and cylinder ratchet.
Also, present double action revolvers require a large force to pull the
trigger. Such a large force militates against accuracy and ease of
operation.
SUMMARY OF THE INVENTION
The invention provides a double action revolver which has a construction
that readily lends itself to low-cost manufacture. The hammer and trigger
are devoid of searing surfaces which normally require hand fitting. Also,
provision is made for the automatic indexing of the cylinder during
trigger return, thereby obviating the usual pawl and ratchet arrangement
for turning the cylinder between discrete index positions. Because the
trigger is relieved of supplying the energy to turn the cylinder and the
unique means to bias the hammer toward the fired position during trigger
pull, a revolver of the invention can exhibit a significantly reduced and
smoother trigger pull.
In an embodiment of the invention, a hammer or main spring, interposed
between the hammer and the trigger, is compressed during trigger pull to
bias the hammer toward the fired position. A toggle spring device
interposed between the hammer and the frame resists substantial hammer
movement until buckled or deflected by a surface on the trigger, which
action occurs after sufficient compression of the hammer spring. After
buckling, the resistance offered by the toggle spring device is reduced to
such an extent that the compressed hammer spring drives the hammer to its
fired position with sufficient energy to fire a cartridge. The hammer is
returned to its normal position by the toggle spring device while the
trigger is returned to its normal or released position by the hammer
spring.
A revolver of the invention may also incorporate a cylinder which
automatically indexes to the next cartridge position during trigger
return. In an embodiment of the invention, rotation of the cylinder is
urged by a torsion spring. A unique cylinder stop-locking recess
arrangement allows the cylinder stop to clear the locking recess and
permits cylinder rotation while being adapted to be received in the
succeeding locking recess for terminating cylinder rotation at a discrete
index position.
It will also be appreciated that the invention provides a useful method of
operating a revolver with respect to hammer movement and cylinder
rotation.
Accordingly, it is a primary object of the invention to provide a double
action revolver without searing surfaces on the hammer and the trigger
thereof.
Another object of the invention is to provide a method and apparatus for
indexing a revolver cylinder.
A further object is to provide methods for operating the hammer and
cylinder of a revolver.
These and other objects and advantages of the invention will become more
readily apparent from the following detailed description, when taken in
conjunction with the accompanying drawings, in which:
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a perspective view of a revolver according to the invention.
FIG. 2 is a perspective view of the cylinder assembly of the revolver of
FIG. 1.
FIG. 3 is a top plan view of the revolver of FIG. 1.
FIG. 4 is a sectional side elevational view of the revolver of FIG. 1
showing the components of the firing mechanism in their normal positions
prior to trigger pull.
FIG. 5 is a view similar to that of FIG. 4 showing the positions of the
components of the firing mechanism where the trigger is displaced to a
position just prior to that which buckles the toggle spring device and
releases the hammer for falling movement.
FIG. 6 is a view similar to those of FIGS. 4 and 5 showing the positions of
the components of the firing mechanism where the trigger is in the pulled
position and the hammer has fallen to the fired position.
FIG. 7 is a view similar to those of FIG. 4, 5, and 6 showing the positions
of the components of the firing mechanism where the trigger is positioned
somewhere between its pulled and normal positions during return movement.
FIGS. 8a, 9a, 10a, 11a, 12a, 13a, and 14a are sequential views showing the
interaction between the trigger, the cylinder stop and the cylinder during
trigger pull and trigger return.
FIGS. 8b, 9b, 10b, 11b, 12b, 13b, and 14b are sequential views, which
respectively correspond to the previously described views with similar
numeral prefixes, showing the relationship between the locking projection
of the cylinder stop and a locking recess on the cylinder.
FIG. 15, is a perspective view of a locking recess on the cylinder.
FIG. 16 is a side elevational view of the lower frame member.
FIG. 17 is a top plan view of the lower frame member, taken along the line
17--17 of FIG. 16.
FIG. 18 is a side elevational view of the upper frame member.
FIG. 19 is a bottom plan view of the upper frame member taken along the
line 19--19 of FIG. 18.
FIGS. 20, 21 and 22 are respectively top plan, side elevational and rear
elevational views of the cylinder stop, per se.
FIGS. 23 and 24 are respectively perspective and fragmentary rear
elevational views of the trigger, per se.
FIGS. 25 and 26 are respectively side and front elevational views of the
hammer, per se.
FIG. 27 is a view of the hammer return projection, taken along the line
27--27 of FIG. 25.
FIGS. 28 and 29 are side and plan views of the hammer spring, respectively.
FIGS. 30 and 31 are respective plan and side views of the toggle spring
device.
FIG. 32 is a side view of the cylinder.
FIGS. 33 and 34 are respective sectional views of the cylinder, taken along
the lines 33--33 and 34--34 of FIG. 32.
FIGS. 35 and 36 are respective side and rear views of the cylinder ratchet.
FIGS. 37 and 38 are respective side and front views of the cylinder guide.
FIG. 39 is a view of the cylinder guide, taken along the line 39--39 of
FIG. 38.
FIG. 40 is a fragmentary perspective view of the cylinder guide.
FIGS. 41, 42, 43 and 44 are respectively side, top plan, rear end and front
end views of the cylinder yoke in association with the cartridge retaining
plate.
FIGS. 45 and 46 are rear and sectional views, respectively, of the
cartridge retaining plate, per se.
FIG. 47 is a view of the cartridge plate biasing spring.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
Referring now to the drawings and more particularly to FIG. 1, there is
shown a firearm according to the invention in the form of a revolver. The
revolver comprises a frame, generally shown at 10, to which is secured a
barrel 12 and a handgrip 14. The frame 10 is constituted by an upper frame
member 16 and a lower frame member 18. Mounted in the upper frame member
16 is a cylinder assembly 20 adapted to be quickly removed from and
inserted into the revolver.
The cylinder assembly 20, which is shown alone in perspective in FIG. 2 and
from above in FIG. 3 when inserted in the revolver, comprises a cylinder
22, an embracing yoke 24, and a cartridge plate 26. The cylinder assembly
20, which permits automatic indexing of the cylinder 22 in its discrete
firing positions, is shown and described in greater detail in the
succeeding views and description.
Turning now to FIG. 4, the components of the firing mechanism are shown in
their respective normal positions prior to trigger pull. A trigger 28 is
mounted for pivotal movement upon the lower frame member 18 by means of a
pin 30. The rear portion of the trigger 28 is provided with a recess 28a
in which the apex 32a of a somewhat V-shaped hammer spring 32 is
positioned. The trigger 28 comprises a rearwardly extending arm 28b, the
end of which receives the end of a leg 32b of the hammer spring 32. The
other leg 32c has its end in sliding abutment with the head 34a of a
hammer 34 which is mounted for pivotal movement upon the pin 30. On a pin
in the head of the hammer 34 is mounted a pivoted striker 34b. The hammer
spring 32 generally acts as a leaf spring.
A toggle spring device 36 has one end thereof seated in a recess 34c in the
lower part of the hammer 34 and the other end thereof seated in a recess
18a in the lower frame member 18. The toggle spring device 36 resists
substantial hammer movement while the trigger 28 is being initially pulled
back from its normal or released position but permits hammer 34 to fall
from the normal to the fired position when its resistance to such hammer
movement is substantially reduced by buckling or deflection caused by
contact with a surface 28c of the trigger 28. The buckled toggle spring
device 36 urges the hammer 34 to return from the fired position thereof to
the normal position thereof while the hammer spring 32 urges the trigger
28 to return from the pulled position to the normal position. In addition,
hammer return is aided by the engagement between the returning trigger 28
and a projection 34d on the hammer 34. As shown in FIG. 4, the toggle
spring device 36 comprises a portion of increased cross section caused by
bending over a strip of the metal from which it is formed. The detailed
construction and mounting of the illustrated toggle spring device 36 is
discussed more fully hereinafter. For purposes of this part of the
description, suffice it to say that the toggle spring device 36 is
essentially a leaf spring which buckles in the manner of a column when a
transverse force is applied thereto. When the hammer 34 moves into the
fired position, the end of the striker 34b, which forms a part thereof,
passes through a tapered opening 16a in the frame and contacts the primer
of a cartridge in the cylinder 22.
The manner of operation of the firing mechanism may be best appreciated by
reference to FIGS. 5, 6, and 7. In FIG. 5, the trigger has been pulled to
a position where the hammer spring 32 has been practically completely
compressed and the surface 28c of the trigger 28 is just about to contact
the toggle spring device 36. A further small increment of trigger rotation
causes contact between the surface 28c and the lower side of the toggle
spring device 36 whereupon still further slight trigger rotation causes
the toggle spring device 36 to buckle. Such buckling permits the hammer
spring 32 to then drive the hammer to its fired position, as is depicted
in FIG. 6. It will be noted that the pulled (i.e., fully rearward)
position of the trigger 28 is only slightly angularly displaced from its
position in which the surface 28c initially contacts the toggle spring
device 36. However, it will be seen that, in FIG. 6, the toggle spring
device 36 has assumed a bowed configuration after deflection such that it
is markedly spaced from the surface 28c.
When the hammer 34 is in the fired position and the trigger 28 is in the
pulled or fully depressed position (as shown in FIG. 6), the hammer spring
32 is urging the trigger 28 to return to its normal position and is also
urging the hammer 34 toward its fired position. Although, in this FIG. 6
configuration, the toggle spring device 36 is urging the hammer 34 to
return from the fired position, such urging is at first insufficient to
overcome the urging of the hammer spring and produce withdrawal of the
striker 34b from engagement with the chambered spent cartridge. This is
because the moment on the hammer 34 attributable to the hammer spring 34
is greater than the opposing moment on the hammer 34 generated by the
toggle spring device 36. Since the cylinder 22 is indexed during trigger
return, it is necessary in the illustrated embodiment to move the hammer
34 whereby it does not impede the travel of rotating cartridges. To this
end, an abutment surface 28d is provided on an extension 28e of the
trigger 28. The abutment surface 28d is adapted to engage the projection
34d on the hammer 34 during initial trigger return to withdraw the hammer
34 from the fired position and permit untrammeled rotation of the cylinder
22. This engagement is depicted in FIG. 7. As trigger return continues the
moment exerted on the hammer 34 by the toggle spring device 36 increases
while the moment exerted by the hammer spring 32 decreases. Eventually,
during trigger return, the toggle spring device 36 snaps into its unbowed
or normal configuration whereby the hammer 34 assumes its normal position.
Trigger return then continues under the bias of the hammer spring 32 until
the trigger leg 28b hits the frame, whereby the trigger assumes its normal
position.
It will be understood that the firing mechanism of the invention need not
be utilized only in conjunction with a cylinder that is automatically
indexable but could be used with conventional cylinders which have
ratchets driven by a trigger connected pawl. The firing mechanism may also
find utility in firearms other than revolvers. In addition, the spring
designs which are illustrated could be replaced by other spring designs.
Moreover, a different spring arrangement may make it possible to dispense
with the engagement between the trigger and hammer during trigger return.
Furthermore, the hammer 34 could engage a conventional spring biased
firing pin, if desired.
Returning now to FIG. 4, the cylinder assembly 20 will now be described in
detail. The cylinder 22 has a central bore 22a passing therethrough and a
keyway 22b communicating therewith. Partially contained within the central
bore 22a at opposite ends thereof are a cylinder guide 38 which the
cylinder 22 rotates over and a cylinder ratchet 40 which transmits torque
thereto. The interiors of the guide 38 and ratchet 40 are hollowed to
furnish a space for a torsion spring 42, which extends therebetween and
has its ends respectively inserted in suitable sockets 38a and 40a in the
guide 38 and the ratchet 40, respectively. The spring 42 also acts as a
compression spring in that it biases the guide 38 and ratchet outwardly or
away from the center of the cylinder and also urges relative rotation
between the guide 38 and the cylinder 22 when wound. The torque
transmitted by the spring 42 is applied to the cylinder 22 by means of a
key 40b which is fashioned on the periphery of the ratchet 40 and received
in the keyway 22b.
From FIGS. 1-4, it will be seen that the yoke 24 embraces the cylinder 22
and has two apertures 24c and 24d through which respective integral
extensions 38b and 40c of the guide 38 and the ratchet 40 extend. The legs
24a and 24b of the yoke 24 extend through and rest against the respective
vertical walls 16a and 16b of the cavities 16c and 16d which extend across
the frame-barrel assembly in a transverse manner. The extensions 38b and
40c are, in turn, received within respective cavities 16e and 16f of the
upper frame member 16. It will be seen that an intermediate annular
surface 40d on the extension 40c is formed by an enlarged diameter segment
of the extension. This annular surface 40d is urged by spring 42 against
the upper frame member 16 and bears thereagainst during cylinder rotation.
The cylinder guide 38 bears against the yoke 24 and engages therewith (as
explained hereinafter) such that relative rotation therebetween is
prevented both when the cylinder assembly 20 is in the frame 10 and out of
the frame 10. When the cylinder assembly 20 is inserted in the frame 10,
as shown in FIG. 4, the cylinder is constantly being urged to rotate.
However, when the cylinder assembly is taken out of the frame by squeezing
the legs of the yoke 24, a plurality of teeth 40e move into contact with
the inboard surface of leg 24b which has a protrusion (shown hereinafter)
thereupon. The engagement between the protrusion of the yoke 24 and the
teeth 40e prevents the ratchet 40, and, hence, cylinder 22, from being
turned by the spring 42 relative to the yoke 24. It will be noted,
however, that such engagement does not prevent relative rotation in the
opposite direction, whereby energy can be stored in the spring 42 when the
cylinder 22 is turned during loading. It will be understood, in this
respect, that the contact between annulus 40d and the wall 16b precludes
engagement between the teeth 40e and the inboard surface of leg 24b when
the cylinder assembly is mounted in the frame.
In order to keep cartridges in the cylinder 22 from engaging the upper and
lower walls of the cavity 16d and interfering with cylinder rotation and
also for safety reasons, the plate 26 is mounted upon the ratchet 40. The
plate 26 is biased (when the cylinder assembly 20 is out of the revolver)
against a stop on the yoke 24 by means of a spring 27 attached to the stop
on the yoke 24 and the plate 26. To load (when the cylinder assembly 20 is
removed) a cartridge in the cylinder 22 of FIG. 2, the plate 26 is
manually rotated about 45.degree. counterclockwise from the position
thereshown and a cartridge inserted in the exposed cylinder chamber. The
cylinder is then incrementally turned against the bias of the spring 42
and the succeeding cylinder chambers are loaded. As the cylinder assembly
20 is being inserted in the revolver, a surface 16L (FIGS. 1 and 18) on
the upper frame member 16 engages the plate 26 and causes about a
45.degree. rotation, thereby to expose the primer of the upper cartridge.
The cylinder 22 is provided with a plurality of locking recesses 22d (best
shown in FIGS. 1-4, 15, and 32-34) which are adapted to engage the locking
projection 44a of a cylinder stop 44 for maintaining the cylinder 22 in a
plurality of discrete index positions in which a chamber 22c thereof is
aligned with the barrel 12. The locking recesses 22d are not of
conventional geometry since they are each constituted by a primary notch
22e and a secondary notch 22f. The primary notch 22e is not conventional
in shape as it only locks the cylinder against rotation in one direction.
The recess 22d has a sloping entrance cut leading to an abutment wall 22g
which is adapted to engage the projection 44a and terminate cylinder
rotation in a discrete index position. The secondary notch 22f is
shallower in depth than the primary notch 22e and begins just slightly
forward the center line of the primary notch 22e. The secondary notch 22f
extends to a circumferential station beyond that of the primary notch 22d
such that its abutment wall 22h is circumferentially offset from the
abutment wall 22g of the primary notch.
The reason for utilizing the illustrated locking recess design is to permit
reciprocating (forward and rearward) movement of the cylinder stop 44 to
index the cylinder 22 while the projection 44a always remains in contact
with the surface thereof. Obviously, a cylinder stop which at some point
in the trigger movement departed from the surface of the cylinder would be
unsuitable as the cylinder would quickly rotate past the succeeding index
positions under the bias of the spring 42.
In brief, what occurs is that during forward movement of the cylinder stop
44 the projection 44a clears the abutment wall 22g of the notch 22e,
whereby the cylinder 22 rotates a few degrees until the projection 44a
contacts the abutment wall 22h of the notch 22f. Then return or rearward
movement of the cylinder stop 44 causes the projection 44a to slide out of
the secondary notch 22f (and out of engagement with abutment wall 22h) to
the outer periphery of the cylinder 22. The cylinder 22 now rotates until
the projection 44a engages the abutment wall 22g of the succeeding locking
recess 22d.
The cylinder stop 44 is biased upwardly and rearwardly by a compression
spring 46 seated in respective cavities 44b and 18b in the cylinder stop
44 and lower frame member 18. In FIG. 4, the top of the projection 44a is
being urged against the sloping entrance cut of the primary notch 22e and
a shoulder 44c on the cylinder stop 44 bears against the upper frame
member 16. The cylinder stop 44 also has a cam surface 44d fashioned upon
a rear extension 44e thereof. During trigger pull (i.e., counterclockwise
trigger movement) the nose 28f of the trigger 28 engages the cam surface
44d so as to cause the cylinder stop 44 to generally pivot about the end
of the projection 44a while locking engagement is maintained; and during
trigger return, the nose 28f of the trigger 28, which is contoured to
engage the rear extension 44e of the cylinder stop 44, pushes the cylinder
stop 44 forwardly until the nose 28f disengages from the end of the
extension whereupon the cylinder stop 44 returns rearwardly with a snap
action.
The cylinder 22 is also provided with a plurality of safety notches 22i
which are adapted to partially receive the trigger extension 28e during
trigger pull. The safety notches 22i are so positioned on the periphery of
the cylinder 22 that the extension 28e can enter a notch only when a
cylinder chamber is properly aligned with the barrel 12. If such alignment
is not present, the trigger 28 cannot be pulled back far enough to produce
hammer fall since the movement of the extension 28e will be impeded by the
periphery of the cylinder 22.
The interaction between the trigger 28, the cylinder 22 and the cylinder
stop 44 may best be understood by reference to FIGS. 8a-14a, and to FIGS.
8b-14b. The latter FIGS. (8b-14b) show the relationship of the projection
44a to the locking recess 22d. Also, each of the views of the former group
of figures corresponds to a view in the latter group of figures which has
the same numeral (e.g., the position of the projection in FIG. 12a is
shown in FIG. 12b).
In FIGS. 8a and 8b, the depicted elements are in their normal positions
awaiting a pulling of the trigger 28. It will be noted that the projection
44a is received within the notch 22e in engagement with the abutment wall
22g, such engagement being urged by the spring 42.
In FIGS. 9a and 9b, the trigger 28 is being pulled. The nose of 28f of the
trigger 28 has engaged the cam surface 44d and produced a pivoting of the
cylinder stop 44 about the end of its projection 44a. As shown in FIG. 9b,
the relative positions of the projection 44a and the locking notch 22e
remain substantially unchanged.
FIG. 10a shows the trigger 28 in the pulled position after the revolver has
been fired and a V-shaped cut on the nose 28f of the trigger 28 engages
the rear end of the rear extension 44e of the cylinder stop 44. The end of
the rear extension 44e snaps into the V-shaped cut after the base of the
nose 28f has cleared the cam surface 44d. Again with reference to FIG.
10b, the relationship between the projection 44a and the notch 22e has not
been substantially changed, although the cylinder stop has pivoted further
about the end of its projection 44a.
FIGS. 11a and 11b show the cylinder stop 44 being pushed forward by the
trigger 28 during trigger return. It will be seen that the V-shaped cut in
the nose 28f of the trigger is still in engagement with the end of
extension 44e. FIG. 11b illustrates the position of projection 44a
relative to the locking recess 22d just before it disengages from the
abutment wall 22g and enters the secondary notch 22f.
In FIGS. 12a and 12b, with trigger return continuing, the projection 44a
has cleared the abutment wall 22g and the cylinder 22 has been rotated
under the bias of spring 42 an amount sufficient to beget engagement
between the projection 44a and abutment wall 22h. It should be mentioned
at this point that an indexing rotation of the cylinder 22 cannot take
place until the projection 44a clears the abutment wall 22h which is now
being urged by spring 42 into contact therewith.
With reference now to FIGS. 13a and 13b, the rear extension 44e of the
cylinder stop 44 has snaped rearwardly under the urging of the spring 46
and the cam surface 44d now bears against the underside of the nose 28f of
the trigger 28. As soon as the nose 28f has cleared the end of the
extension 44e, the above described rearward motion is occasioned. This
rearward movement has caused the projection 44a to slide out of the
secondary notch 22f, out of engagement with the abutment wall 22h and onto
the periphery of the cylinder 22.
When the projection clears the abutment wall 22h, the cylinder 22 begins to
rotate as shown in FIGS. 14a and 14b. The projection is now in position to
enter the next sloping entrance cut of the succeeding primary locking
notch 22e and be contacted by the abutment wall 22g thereof. Further
trigger return merely causes a slight pivoting of the cylinder stop 44
until the shoulder 44c engages the upper frame member 16.
FIGS. 16-47 are detailed views of certain parts of the illustrated revolver
which should be referred to in conjunction with the other figures.
With reference to FIGS. 16 and 17, the lower frame member 18 is shown as
having aligned bores 18e, 18f, and 18g extending laterally therethrough
which receive a pin 48. The pin 48 is adapted to secure the frame members
16 and 18 together. Yet another set of aligned bores 18h and 18i in the
sides of the frame member 18 are adapted to mount the trigger pin 30 about
which the trigger 28 and hammer 34 pivot. The front portion of the lower
frame member 18 is also recessed at 18j such that, together with the side
of the upper frame member 16, a channel is defined for partially receiving
the front extension 44f of the cylinder stop 44 for ease of assembly. The
front end of the lower frame member 18 is also stepped at 18k to mate with
a surface on the upper frame member 16 such that a relatively flush
contour is provided therebetween. From FIG. 17, it will also be observed
that the surfaces 18c and 18d, upon which the toggle spring device 36 is
supported, are relatively narrow in width and are formed by a raised
portion of the lower frame member 18. This support is essential to
restrict downward deflection of the toggle spring device 36 during trigger
pull.
FIGS. 18 and 19 show the upper frame member 16. It can be seen therefrom
that the upper frame member 16 also has a set of aligned bores 16g and 16h
which receive the pin 48. The upper frame member 16 also has windows 16i
and 16j formed therein through which the trigger extens | | |
