U.S. patent application number 14/979143 was filed with the patent office on 2016-06-30 for operating system utilizing an articulated bolt train to manage recoil force.
The applicant listed for this patent is Jorge Pizano. Invention is credited to Jorge Pizano.
Application Number | 20160187082 14/979143 |
Document ID | / |
Family ID | 56163736 |
Filed Date | 2016-06-30 |
United States Patent
Application |
20160187082 |
Kind Code |
A1 |
Pizano; Jorge |
June 30, 2016 |
OPERATING SYSTEM UTILIZING AN ARTICULATED BOLT TRAIN TO MANAGE
RECOIL FORCE
Abstract
An Operational System for Firearms founded on the use of the
synchronic controlled motion and cooperative interaction of
elements of a Pivotally Articulated Bolt Train displacing
reciprocatingly within a compliant receiver, along guiding means,
disposed according to a purposely engineered Path, capable of
generating anticipated adjustable dynamic reactions, and to execute
mechanical actions, due to pre-calculated movements of
interconnecting mechanisms within said Train members, when they
pivot one relative to the other. The alternate divergent and
converging motion of the Train Bolt and A Firing Mechanism Carriage
subassembly, along a horizontal path, and a transverse path,
modifies and splits the linear bearing of the recoil force, and
generates a Gyroscopic Effect or Angular Moment, decreasing the
Barrel Torque magnitude, conveying a unique tailored dynamic
behavior, while performing different functions and achieving the
eleven different purposes of this invention. Numerous motion
parameters are adjustable to attain the distinctive recoil Dynamic
reaction.
Inventors: |
Pizano; Jorge; (Cordova,
TN) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Pizano; Jorge |
Cordova |
TN |
US |
|
|
Family ID: |
56163736 |
Appl. No.: |
14/979143 |
Filed: |
December 22, 2015 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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13385262 |
Feb 10, 2012 |
9217614 |
|
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14979143 |
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61463034 |
Feb 11, 2011 |
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Current U.S.
Class: |
89/194 |
Current CPC
Class: |
Y10T 29/49826 20150115;
F41A 5/24 20130101; F41C 23/16 20130101; F41A 3/26 20130101; F41A
3/36 20130101 |
International
Class: |
F41A 3/12 20060101
F41A003/12; F41A 5/18 20060101 F41A005/18 |
Claims
1. An Operating System for a firearm to manage a recoil force
effect utilizing a Pivotally Articulated Bolt Train of planar
motion displacing along a cooperative receiver.
2. The Operating System of claim 1 having: A Pivotally Articulated
Bolt Train Mechanism functioning within a cooperative receiver,
displacing, track mounted, along a pre-determined Path to partially
redirect the initial bore axial recoil force into a transversally
directed recoil force and to perform several functions; A Firing
Mechanism Subassembly incorporated to the Bolt Train that displaces
altogether as part of the recoiling train; A Firing Mechanism
Subassembly incorporated to the Bolt Train that cocks in response
to the recoil displacement along a predetermined Path, and to the
angular rotation motion of the components of said Train while
displacing rearwards. A Cam Delay Blowback mechanism to retard the
opening of a barrel breech after firing; An array, within the
cooperative receiver, of mechanisms, paths, tracks subassemblies
reducing the total weight, volume and lowers of the center of
gravity of said firearm; An independent, optional Recoil Damper
Mechanism attachable to the Bolt Train sub assembly: A quick Jaws
opening and closing Array of the Upper and Lower receivers pivoting
about a hinge joint, like jaws, to facilitate the access to
internal components of the bolt train mechanisms for assemble and
disassemble of the train components; A pre-calculated planar
angular motion of certain train members to generate a gyroscopic
effect and an Angular Moment which reduces a Barrel Torque rotation
effect of the firearm after firing; A pre-calculated motion along a
portion of said path and tracks, through a tunnel handle of the
firearm; A number of identified and engineerable parameters
involved in the functioning of the Articulated Bolt Train
Operational System, to set the desired values for the preferred
objective Dynamic reactions; and A number of interactive mechanisms
to perform inter-dependent mechanical actions, occurring in
mechanisms housed within separated train members, said actions
being: 1) To cock a firing mechanisms, 2) To create a delay in a
barrel breech opening, and 3) To actuate an optional recoil damper
mechanism.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application is a Continuation-in-Part of co-pending
U.S. patent application Ser. No. 13/385,262, filed on Feb. 2, 2012,
which claims the benefit of Provisional Patent Application Ser. No.
61/463,034 filed on Feb. 11, 2011, now expired. The entirety of
both the co-pending non-provisional and expired provisional
applications are herein incorporated by reference.
FIELD OF THE INVENTION
[0002] This application relates generally to a firearm operational
system improvement, describing an Articulated Bolt Train mechanism
in which The Head Bolt moves linearly aligned with the axis of the
barrel and the second train member, the Firing Mechanism
Subassembly, may have a movement component perpendicular to the
barrel axis in certain sectors of the Motion path when it changes
the bearing, from horizontally aligned with the axis of the barrel,
to a transverse, through the handle direction. This redirection of
the path causes significant reaction forces over the guiding tracks
inserted in the receiver, which induces a dynamic behavior, unique,
predictable and manageable to the firearms utilizing this Operating
System. The Physical Mechanic and Dynamic Forces resulting from the
operation of firearms of this category are comprehended and
manageable under the concepts of Newtonian Mechanics and Dynamics
The identification of the parameters involved in the operation of
the Articulated Bolt Train Operating System Makes it possible to
select the proper values of such parameters to attain, to a certain
extent, the desired recoil resultant.
BACKGROUND OF THE INVENTION
[0003] The enormous majority of auto loading firearms made in prior
art are based on the pattern of reciprocating bolts (masses)
displacing linearly using the inertia mass and a spring to absorb
the energy of the reaction force produced in response to the firing
of a cartridge. Some mechanisms have used toggle articulated links
to create enough space, for the bolt, to travel enough to reach the
rear part of a new cartridge, in a magazine, in the backwards
motion, and reciprocate forward reloading a new cartridge in the
chamber. The toggle mechanism articulates at least two pivoted
links sideways, which produce a motion vector having a component
perpendicular to the axis of the barrel while producing a different
dynamic reaction. The Last link of the toggle array is pivotally
grounded to the receiver, condition which limits the total travel
of the bolt and delivers at the very beginning of the recoil
motion, a considerable portion of the energy to the receiver.
[0004] Previously, in firearms, the use of articulated or toggled
bolts and connecting masses to control recoil is very old. When
recoiling, these types of mechanisms displace in a different
direction of the barrel axis creating force vectors partially
diverting the initial recoil force, away from the bore axis. In
toggle mechanisms the last member of the articulated linkage is
pivotally grounded to the receiver limiting the range of the head
bolt to move in the horizontal direction towards the breech. The
use of this principle is present in the first known auto loading
pistol invented by Hugo Borchardt in the C-93 pistol (1893), and
the same principle for displacing the bolt rearwards and the heavy
connecting bars transversally to reduce the axial recoil is used by
Georg Luger in (1898) in the well known P-08 model. Both, Borchardt
and Luger, were following the even earlier design of Hiram Maxim
incorporating the toggle lock or knee principle. Borchardt and
Luger had an exterior articulating bolt fixedly hinged at the rear,
but never before a completely movable Interior Articulated Bolt
Train.
[0005] Several firearms recoil absorbing systems have been patented
recently using similar principles that cause an inertia mass to
move downwards or transversally by using the original recoil force,
transforming it into two force vectors; Like patent U.S. Pat. No.
7,201,094 of Jan Henrik Jebsen. However, none of the previous
patents uses the active firing mechanisms as part of the moving
recoiling mass displacing transversally. Nor it uses an active
recoil damper mechanism. It only moves inertia dead mass
downwards.
[0006] In previous inventions like patent U.S. Pat. No. 7,201,094
the firearm head bolt is attached to an independent body or mass
that contains no mechanisms inside. It is just dead mass. The two
bodies are connected by series of linked interconnected parts, some
of them requiring sufficient margin of play, like a slotted guide,
placed at an inclined angle at the end of one of the bodies. A rod,
belonging to the bolt, travels horizontally through a slotted
guide. A rod placed transversally becomes the contact point between
the bolt and the mass. As the bolt travels horizontally it pushes
the rod through the inclined slotted guide causing the effect of a
wedge by pushing the mass in a transverse direction. The oblique
displacement of the dead inertia mass is forced by a transverse
fixed guide bar passing through the mass. However the different
means used to achieve the recoil absorption are significantly
inefficient in terms of the volume and total weight required. None
of the design solutions involve the use of firing mechanisms
displacement or the use of the firing mechanisms mass as a part of
the recoiling inertial mass. U.S. Pat. No. 7,201,094 of Jan Henrik
Jebsen uses a complete conventional separate stationary fixed
firing mechanism assembly, placed conveniently that necessitates
significant volume and weight to operate. The latter mentioned
patent does not have any sort of internal recoil abatement
mechanisms inside the inertia mass as this invention has. It is
notorious for being voluminous and unwieldy. It is voluminous with
a very little barrel length. And furthermore, the array of
mechanisms condemns the operation, in practical reality, to small
pistol cartridges. With respect to the Delay Blowback breech
opening function that this invention has, the U.S. Pat. No.
3,283,345 of Theodor Koch is important to mention because it has
been extensively divulged and promoted by its use in the Heckler
and Koch G3 rifles and especially in the very well known MP 5 sub
machineguns. It causes a delay in the breech opening by means of a
complicated mechanism inside the bolt whereby a set of sprig loaded
rollers are forced to move along a pair of closing arc circle
surfaces generating a retention of the force produced by the
increasing gas pressure inside the barrel until the point where it
overcomes the force of the rollers mechanism, generating a delay.
The use of such mechanism has been successful, but has several
disadvantages: it is sensitive to dirt, it requires lubrication,
rollers break, springs fatigue, and does not lend to trimming.
Advantages of the Invention
[0007] The Operating System presented in this Patent application is
notoriously different than any other known art. The present
invention has at least one the following advantages.
[0008] For the first time, an Operating System utilizing a floating
Articulated Bolt Train, including a Firing Mechanism subassembly is
used to take advantage of the reaction forces that a Path bearing
change causes, in benefit of engineering a desired effect in the
final recoil behavior. The Articulated Bolt Train having a planar
motion, and capable of continuously changing path of some train
members, towards a transverse curved direction which generates
important manageable reaction forces over the receiver. [0009] This
invention integrates an Active Firing Mechanisms as a part of the
recoiling Bolt Train and places it for all time in the immediate
proximity to the firing pin. [0010] This invention is improved
because the firing mechanisms are contained in a compact,
volume-efficient, carriage that moves transversally along a by
design predetermined path. [0011] This invention is superior
because, when shooting, the firing mechanisms contained in a
compact, volume-efficient, carriage moves downwards, through the
handle or grip, producing a unique reaction movement of the
receiver resulting in a balanced dynamic behavior. [0012]
Conventionally, the Controlling Firing Mechanisms or Trigger Group
and its frame are placed in a fixed dedicated location. This
invention makes the Active Firing Mechanism movable and uses its
mass as part of the Bolt Train 90 mass needed to absorb the recoil,
saving volume, weight and lowering the center of gravity. [0013]
The active firing mechanisms operate linearly without rotating
parts inside a movable Carriage, which make it simple to
manufacture and volume effective. [0014] The Controlling Firing
Mechanisms subassembly 74 FIG. 5D is modular, easy to change if
needed. [0015] A part, the Mechanisms Carriage Housing, has
multiple functions. It frames the Active firing mechanisms; it
guides the recoil travel; and it displaces transversally with the
contained independent mechanisms in place. At the rear it may have
a protruding cam that slides over the inclined plane face of the
spring loaded, movable recoil compensator forcing it back, adding
additional restrain to the opening of the breech. All that in a
very dense compact package, making it efficient in terms of minimal
volume. [0016] The Mechanisms Carriage Housing optionally has a
rear protruding cam (40C) that works in conjunction with the Recoil
Damper sub assembly to produce additional restriction to the
rearwards motion, adding more delay to the breech opening. [0017]
When the firing mechanisms sub assembly works in conjunction with
the protruding delay cam of the Front Bolt 20, it creates a delay
on the blowback opening motion without requiring any additional
moving parts. [0018] The mechanisms carriage housing and mechanism
can slide roll down through the firearm handgrip, making it very
compact and volume efficient. [0019] The proximity of the compact
Bolt Train to the top of the shooter' grabbing first lowers the
center of gravity of the weapon creating an improved handling.
[0020] When the mechanisms carriage housing and mechanism slide
roll down through the firearm handgrip, the effect of the downwards
displacement is felt directly on the grip, eliminating any moments
about the grabbing point. [0021] This novel mechanism can be used
in many types of firearms; pistols; rifles, shotguns; machineguns;
sub-machineguns; heavy machineguns; sniper rifles, grenade
launchers, heavy weapons all the above semi automatic and full
automatic, gas operated, long or short stroke, blowback, delayed
blowback recoil, with rotary bolts and bolt carrier, electrical or
mechanical firing. [0022] These mechanisms can be used in bullpup
configuration. [0023] The front bolt can be used as a bolt carrier,
enabling the use of rotary locking bolts. [0024] The bolt carrier
can be used in conjunction with direct drive rods with gas operated
bolts. [0025] Firearms using this type of bolt lend to be
manufactured with polymer injected materials, which translates into
low production costs. [0026] The progressive displacement downwards
of the mechanisms carriage housing and mechanism provides a smooth
transition of the reaction force. [0027] Rollers can be added to
the guide rods to smooth the operation. [0028] Rollers can be adder
to the hammer to smooth the operation. [0029] The design of this
Operating System is outstanding because:to induce Dynamic reaction
forces on the receiver, and Mechanically, it uses the train members
interaction, occurring during train articulation to perform three
functions 1) To cock the firing mechanisms, 2) To create a delay in
the breech opening, and 3) To actuate a recoil damper mechanism.
[0030] The incorporation of a delay blowback breech opening
mechanism in the rearwards recoil motion, enhances the delivered
energy of the projectile, and reduces the pressure at the breech
when opening. [0031] The delay blowback breech opening system of
this invention achieves the same results of H&K delay opening
mechanism with a very simple interaction of two parts and lends to
be trimmed by producing a desired controlling surface in the front
face of the slider striking hammer. [0032] The delay opening
mechanism slows the rate of fire when used in full automatic mode.
[0033] This invention is far simpler and advantageous than the one
of Jebsen because it only uses only one displaced articulation or
hinge as the means of linkage between the front bolt and the
mechanisms carriage housing. The movement required at the
articulation is only rotational. [0034] No margin of play is
required between the front bolt and the mechanisms carriage
housing. [0035] This invention does not require any mobile breech
to interlock the front bolt and the mechanisms carriage housing.
[0036] This invention requires a smaller number of components in
comparison to any other gun. [0037] This invention has a moving
cylindrical extruded sear 58 housed inside the hammer and
integrated to the movable Firing Mechanism sub assembly. [0038]
Alternatively, this invention comprises a self sprigged sear-hammer
FIG. 3B. [0039] When required, internal sears can be used to
protrude laterally to outside of the Mechanism Carrier Housing 40
and 40B, and engage against it, to become operational with side
mounted column spring or pushing bar 78A FIG. 5D of the controlling
firing mechanisms. [0040] The Bolt Train 90 can be used in
conjunction of Gas piston systems [0041] The bolt train 90 can be
used in conjunction with rotary bolts. [0042] Optionally, when
additional kinetic energy absorption is desired, a third component
to the Bolt Train 90 can be attached: the Recoil Damper Subassembly
of FIG. 4B and FIG. 4C. [0043] A transient Gyroscopic Effect or
Angular Moment is generated in every shoot recoil motion by the
angular motion of some of the train components, while transitioning
from the bore axial path to the transverse path, in the curved zone
of the path. This angular motion of the Firing Mechanism Carriage
Subassembly is capable of compensating to some extent, the rotation
reaction (Barrel Torque) effect of the barrel and Firearm.
SUMMARY OF THE INVENTION
Terms Definitions
[0044] Train is a series of pivotally linked carriages that move
along a track in a reciprocating manner.
[0045] The terms Pivotally Articulated Bolt Train, Articulated
Bolt, Bolt Train, Bolt Train sub assembly, Bolt Train Assembly,
Bolt Train Mechanism, are used indistinctively.
[0046] The terms Front Bolt, Head Bolt, and Bolt refer to the first
member of the Bolt Train. These terms may be used
alternatively.
[0047] The terms Axial Force or axial recoil force refer to that
one occurring in the direction of the axis of the barrel of the
firearm or bore axis when the firearm is discharged.
[0048] The terms Carrier, Carriage, Carrier Housing, Mechanism
Carriage Housing, refer to hollow, track mounted box, capable of
containing and controlling mechanisms placed within, are used
indistinctively.
[0049] The term forward direction is referred as the one having the
direction of the projectile when fired.
[0050] The term rearward direction is the one opposite to forward
or muzzle wards.
[0051] The term transverse is used to define a course oblique to
the bore axis of the barrel.
[0052] The term Hammer is used to designate a moving part propelled
linearly at the impulse of a spring. This can be also referred as a
Striker, or slide striker hammer.
[0053] The terms Slot tracks guides, and Slot channel guides are
used indistinctively.
[0054] The terms Charging handle and Cocking handle are used
indistinctively.
[0055] The term Protruding Guides is used to refer to the
protruding elements that run and slide into the Slot tracks
guides.
[0056] The term Parameter a numerical or other measurable factor
forming one of a set that defines a system or sets the conditions
of its operation.
[0057] The term Jaws means two opposed hinged movable parts in a
mechanical device.
[0058] The term System: is a set of interacting or interdependent
component parts forming a complex/intricate whole.
[0059] The term "Operating System" is used to indicate in the field
of the specific art, the entirety of mechanisms enabling, once a
cartridge has been fired, the expulsion of the case of the fired
cartridge and the loading of a new cartridge while generating
innovative Dynamic reactions over the entire firearm.
SUMMARY
[0060] In accordance with one embodiment, this Operating System
generally relates to a firearm having a collection of mechanisms
and arrays, conceived to manage recoil by changing the dynamic
behavior of the weapon when firing, in a manner that redirects
forces, creates delays, decelerates motion, absorbs energy and
lowers significantly the center of gravity, resulting in an
improvement of the handling of the gun. All of the above is
attained by the motion of a Track mounted Pivotally Articulated
Bolt Train moving reciprocatingly along a pre calculated Path,
engineered to change bearings, to induce premeditated Dynamic
reactions, conceived to favor the recoil control.
[0061] Said firearm comprises several modular subassemblies, a
Barrel, a receiver, an Articulated Bolt Train that alternates
between a forward and backward position, an active firing
mechanism, a delay blowback method, a controlling firing mechanism,
a set of main recovery springs(38), a set off modular
multifunctional supports, a buffer mechanism, a Modular Cocking
Handle mechanism, a direct drive gas system. The alternate
transversal displacement of the Articulated Bolt Train, and the
intrinsic delay designs, conveys to the firearm a unique dynamic
behavior resulting in smooth recoil. Many variable Parameters in
the Operational System of the Articulated Bolt Train constitute a
formidable opportunity for engineers to trim the design for each
specific case of application.
[0062] My co-pending U.S. patent application Ser. No. 13/385,262
generally relates to a firearm having a collection of mechanisms
and arrays, conceived to manage recoil by changing the dynamic
behavior of the weapon when firing, in a manner that redirects
forces, creates delays, decelerates motion, and lowers
significantly the center of gravity, resulting in an improvement of
the handling of the gun. Specially in one embodiment, this
Operating System pertains to a firearm having an Articulated Bolt
Train 90 FIG. 9 and FIG. 9A, FIG. 12 TO FIG. 12C and a by design
Receiver 66 FIG. 10B, FIG. 11B, FIG. 12B, FIG. 12C that operates in
conjunction. In order to function properly, the Bolt Train 90 has
to be placed inside a Receiver (66) that controls and governs its
path, and holds all the sub-assemblies in the convenient location
allowing the synchronic movements of all the components to take
place. The Receiver (66) FIG. 10 A, FIG. 20 can have different
shapes, dimensions, and proportions to be used in several
applications as shown in FIG. 18.
[0063] The Articulated Bolt Train 90 consists of a Front Bolt of
either Types 20, 20A or 20B, as shown in FIG. 2B, initially moving
along the bore axis, articulately linked at the rear to a Mechanism
Carriage Housing 40 types 40 or 40B as shown in FIG. 4, FIG. 4A,
FIG. 4B, containing The Active Firing Mechanisms. The Mechanism
Carriage Housing 40 displaces transversally, articulately linked at
the rear to another optional carriage displacing transversally also
comprising a Recoil Damper Sub Assembly 64 FIG. 4B. The Articulated
Train Bolt 90 is track mounted on slot Channel guides 80 FIG. 10A
embedded or supported laterally inside the receiver 66, directing a
transversal path. In this invention the conventional firing
mechanisms assembly is separated physically in two different
groups. The Active Firing Mechanisms subassembly 39 FIG. 5B
comprise the hammer, the hammer spring, the sear, sear lever; all
of them placed inside a moveable mechanisms carriage housing 40 and
are an integral part of the Bolt Train 90. The controlling firing
mechanisms subassembly 74 FIG. 5B, FIG. 5C comprise the trigger 75,
the lever 76, the safe 77, the column spring fire actuator, and
disengager 78 which are housed in a stationary compact small frame
79 in a convenient fixed location. The Fire Actuator and Disengager
or disconnector 78A can be of a solid piece sustained by a
convenient spring mounted support, enabling its deflection, after
being pushed aside by the sear protrusion portion on the forward
displacement after firing. Part 78, or alternatively part 78A, have
al dual function: pushing the sear out of the engaging surface with
the Mechanism Carriage Housing 40, and serving as disconnector for
the semiautomatic firing mode.
[0064] The Active Firing Mechanisms subassembly 39 compact
mechanism array integrates its mass and its volume to the Bolt
Train 90 and significantly reduces the number of parts, volume,
weight, and lowers the center of gravity, resulting in an effective
recoil management absorbing system for automatic or semiautomatic
firearms.
Name of the Components and Reference Numerals
DRAWING REFERENCE NUMBER
Part Number Part Name
[0065] 20 BOLT [0066] 21 HORIZONTAL PROTRUDING GUIDE (2) [0067] 22
REAR RECTANGULAR PROTRUSION [0068] 22A EDGE LINE [0069] 22B
PROTRUDING DELAY OPENING CAM [0070] 23 CYLINDRICAL CAVITY FOR THE
FIRING PIN [0071] 24 TOP HINGE [0072] 25 HOLE FOR PIN [0073] 26
RECTANGULAR SLOT FOR EXTRACTOR [0074] 27 FRONTAL FACE [0075] 28
CYLINDRICAL DEPRESION FOR CARTRIDGE REAR FACE [0076] 29 FRONTAL
HOLE FOR FIRING PIN [0077] 30 HAMMER [0078] 31 CYLINDRICAL CAVITY
FOR SPRING [0079] 32 PUSH ROD FOR FIRING PIN [0080] 33 HAMMER
SPRING [0081] 34 FRONT FACE OF HAMMER [0082] 35 DELAY OPENING
SLOPED FACE [0083] 36 SEAR ANGULAR FACE [0084] 37 SEAR FLAT SPRING
[0085] 38 SET OF DUAL REOVERY SPRINGS/38A SPRING INTERLOCK TO BOLT
[0086] 39 FIRING MECHANISM SUBASSEMBLY [0087] 40 MECHANISMS CARRIER
HOUSING [0088] 40A RECTANGULAR CAVITY/40 B SPACE/40C CAM [0089] 41
ROD GUIDE (2) [0090] 42 CYLINDRICAL HOLE FOR SEAR SPRING [0091] 43
HINGES FOR SEAR LEVER [0092] 44 HOLES FOR PIN [0093] 45 SQUARE HOLE
FOR SEAR TIP [0094] 46 PIN FOR SEAR LEVER [0095] 47 PIN FOR
BOLT/MECHANISMS CARRIER HOUSING HINGE [0096] 48 MECHANISMS CARRIER
HOUSING HINGE [0097] 49 HOLE FOR MECHANISMS CARRIER HOUSING PIN
[0098] 50 SEAR LEVER [0099] 51 SEAR LEVER HINGE [0100] 52 HOLE FOR
SEAR LEVER HINGE PIN [0101] 53 SEAR LEVER SPRING [0102] 54 ANGULAR
FACE TIP [0103] 55 TOGGLE INTERNAL SEAR SPRING [0104] 56 TOGGLE
INTERNAL SEAR [0105] 57 SEAR CAVITY [0106] 58 EXTRUDED SEAR [0107]
59 WINDOW HOLE [0108] 60 EXTRACTOR [0109] 61 EXTRACTOR PIN [0110]
62 EXTRACTOR SPRING [0111] 63 EXTRACTOR HOLE [0112] 64 RECOIL
DAMPER SUBASSEMBLY [0113] 65 RECOIL DAMPER MECHANISM CARRIAGE/65A
TWO SIDE HINGES [0114] 66 RECEIVER 66A AXIS OF JAWS PIVOTING 66U
UPPER 66L LOWER [0115] 67 MOBILE COMPENSATOR [0116] 68 FRONT
ANGULAR FACE OF MOVABLE COMPENSATOR [0117] 69 CAVITY FOR
COMPENSATOR 69A COMPENSATOR SPRING [0118] 70 FIRING PIN [0119] 71
FIRING PIN REAR [0120] 72 FIRING PIN SPRING [0121] 73 FRONT END OF
FIRING PIN [0122] 74 CONTROLING FIRING MECHANISM SUBASSEMBLY [0123]
75 TRIGGER [0124] 76 LEVER [0125] 77 SAFETY CAM [0126] 78/78A
COLUMN SPRING OR PUSHING BAR/78 A LATERAL PUSHING BAR [0127] 79
FIRING MECHANISM FRAME [0128] 80 SLOT CHANNEL GUIDE/81 CURVED
PORTION OF CHANNEL GUIDE [0129] 90 BOLT TRAIN [0130] 100 BARREL
[0131] 101 CONTROLING FIRING MECHANISM SUBASSEMBLY HOUSING [0132]
102 BARREL HOUSING [0133] 103 GAS PISTON SYSTEM
BRIEF DESCRIPTION OF THE DRAWINGS
[0134] The drawings presented herein are intended to provide
descriptions of the possible embodiments of the inventive firearm
and accessories thereof. No scope limitations are intended nor
should be construed in relation to such representations. Most of
the drawings are self-explanatory; however for a better
understanding of the advantages, capabilities and innovation of
this invention, some of the drawings are explained in more detail.
All drawings are shown in one of the preferred embodiments.
[0135] FIG. 1 Shows an isometric exploded view of the GENERAL
ASSEMBLY of a Pivotally Articulated Bolt Train in a Particular
embodiment.
[0136] FIG. 1A Shows an isometric exploded view of the GENERAL
ASSEMBLY WITH DELAY OPENING of a Pivotally Articulated Bolt Train
in a Particular embodiment. Notice the interaction of the
PROTRUDING DELAY OPENING CAM (22B) with the DELAY OPENING SLOPED
FACE (35), where the omega Angle (xx) determines the level of
restriction for the Bolt Train to displace rearwards to create the
delay in the breech opening.
[0137] FIG. 2 Shows a front, top, side, isometric, and a lateral
cut view of a FRONT BOLT (20). Notice the HORIZONTAL lateral
PROTRUDING GUIDE (21) or lateral projections, as well as the EDGE
LINE 22A in a Particular embodiment.
[0138] FIG. 2A Shows a front, top, side, isometric, and a lateral
cut view of a FRONT BOLT WITH DELAY OPENING CAM (20). Notice the
PROTRUDING DELAY OPENING CAM (22B) in a Particular embodiment.
[0139] FIG. 2B Shows isometric views of SEVERAL FRONT BOLT
CONFIGURATIONS where the HORIZONTAL lateral PROTRUDING GUIDE (21)
has different possible configurations.
[0140] FIG. 3 Shows a lateral cut view, a front view and an
isometric view of the Striker HAMMER (30) in a Particular
embodiment. Notice the surface (35), which conforms, with the
vertical plane the "ANGLE OMEGA" which determines parametric
variable when interacting with the DELAY OPENING SLOPED FACE
(35).
[0141] FIG. 3A Shows a lateral cut view, a front view and an
isometric view of the Striker HAMMER WITH DELAY OPENING SLOPED FACE
(35) determining the Angle Omega in a Particular embodiment. Notice
the surface (35), which conforms, with the vertical plane, the
"ANGLE OMEGA" which determines parametric variable when interacting
with the DELAY OPENING SLOPED FACE (35).
[0142] FIG. 3B Shows a lateral cut view, a front view and an
isometric view of the Striker HAMMER WITH SEAR AND SPRING (36),
(37) being integral to the hammer (30) in a Particular Alternative
embodiment.
[0143] FIG. 3C Shows several possible embodiments of a HAMMER WITH
ROTARY INTERNAL SEAR (56) AND SPRING (55) being housed internally
in a sear cavity (57) of the hammer Lateral side cut views of the
operational assembly with the Front Bolt (20) are provided.
[0144] FIG. 3D Shows the ROTARY INTERNAL SEAR (56) LOCKING DETAIL,
in a locked, and un locked positions, in a particular
embodiment.
[0145] FIG. 4 Shows an isometric view of the MECHANISMS CARRIER
HOUSING (30) in a Particular embodiment.
[0146] FIG. 4A Shows an isometric view of the MECHANISMS CARRIER
HOUSING FOR HAMMER WITH SQUARE HOLE FOR SEAR TIP (45B) in a
Particular embodiment.
[0147] FIG. 4B Shows an isometric exploded view of the RECOIL
DAMPER SUB ASSEMBLY AND FIRING MECHANISMS CARRIER HOUSING
interaction of part (40C) CAM with (65B) FRONT ANGULAR FACE OF
MOVABLE COMPENSATOR, and the ANGLE BETA FORMED IN SAID FRONT
FACE.
[0148] FIG. 4C Shows schematic CUT VIEW OF BOLT TRAIN WITH A THIRD
MEMBER DELAY DAMPER, when the Train is in the most forward
position, and when the Train is in the most rearward position.
Notice that in the most forward position, the Front Bolt and the
Firing MECHANISMS CARRIER subassembly are aligned horizontally.
Also notice that the Front Bolt (20) displaces linearly
horizontally, in a Particular embodiment.
[0149] FIG. 4D Shows a schematic CUT VIEW RECOIL DAMPER SUB
ASSEMBLY (64), AND FIRING MECHANISMS SUBASSEMBLY (39) in a
Particular embodiment. Notice the cut lined showing contact points
(68) and (35) and (22), wherein both contacts present a parametric
level of difficulty when the complete Articulated Bolt Train
Articulates form a most forward position, to a most rearwards
position.
[0150] FIG. 5 Shows an EXTERNAL SEAR (50) and spring in a
Particular embodiment.
[0151] FIG. 5A Shows an isometric assembly detail of a CYLINDRICAL
ROD INTERNAL SEAR (58) and a sear cavity (57) internal to the
striker HAMMER (30) in a Particular embodiment.
[0152] FIG. 5B Shows an isometric exploded assembly detail of the
FIRING MECHANISM SUBASSEMBLY AND CARRIER (39), and the CONTROLING
FIRING MECHANISM SUBASSEMBLY (74) and their relative position with
respect to the other, in a Particular embodiment.
[0153] FIG. 5C Shows an isometric exploded assembly detail of the
CONTROLLING FIRING MECHANISM SUBASSEMBLY (74) in a Particular
embodiment.
[0154] FIG. 5D Shows an isometric exploded assembly detail of the
CONRTOLLING FIRING MECHANISM SUBASSEMBLY (74) in another different
configuration, in which the LATERAL PUSHING BAR (78A) is used to
disengage the SEAR (58) in a Particular embodiment.
[0155] FIG. 6 Shows an isometric, a front, a lateral, and a top
view of a cartridge EXTRACTOR in a Particular embodiment.
[0156] FIG. 7 Shows an isometric and a cut view of FIRING PIN (70)
in a Particular embodiment.
[0157] FIG. 8 Shows, how for example, the change of the value of
the parameters of "Horizontal Track Length", "Radius of Curvature",
"Arc Length", "Transversal Track Length", and "Center of Circle
Center" produce abundant different shapes, which accommodate the
ergonomy and functionality of the design, and how the rate of
change of the punctual motion Direction over time, in the curve,
induces a different reaction on the receiver.
[0158] FIG. 8A Shows SEPARATED CHANNEL GUIDES (with TRACK SEGMENTS
ZONE A-ZONE B) in a Particular embodiment wherein the Zone B of the
track is located inside a tunnel located inside the of the receiver
(66) handle. Notice that the DUAL set of Channel Guides may have
extended horizontal lengths to allow a long horizontal displacement
of the Articulated Bolt Train (90) when design requirements demand
such condition, in a particular embodiment.
[0159] FIG. 8B Shows a schematic view of POSIBLE LOCATION OF CHANEL
GUIDES (TRACKS) ON A RECEIVER (66) in a Particular embodiment.
Notice that a transversal portion of the Chanel guide (80) runs
inside a Handle Tunnel, as described in the Operating System of
this Patent Application.
[0160] FIG. 9 is a schematic isometric view showing the alignment
of the articulated Bolt Train (90) with the axis of the barrel when
it is in the Horizontal Zone. This also shows an ARTICULATED BOLT
TRAIN WITH ASSEMBLED BOLT (90), AND MECHANISMS CARRIER'S PROTRUDING
GUIDES (21) and lateral ROD GUIDE (41) projected to fit inside a
continuous type of Chanel Guide, in a particular embodiment.
[0161] FIG. 9A Is an isometric view showing an ARTICULATED BOLT
TRAIN WITH TWO OR THREE SUB ASSEMBLIES element in a Particular
embodiment.
[0162] FIG. 10 Shows the schematic PLACEMENT OF BOLT-MECHANISMS ON
A CONTINUOUS CHANNEL TRACK IN A PLANE IN WHICH ALL THE TRAIN MOTION
TAKES PLACE, in a Particular embodiment.
[0163] FIG. 10A Shows the schematic PLACEMENT OF BOLT-MECHANISMS ON
A DUAL SEPARATED CHANNEL TRACKS IN A PLANE IN WHICH ALL THE TRAIN
MOTION TAKES PLACE, in a Particular embodiment.
[0164] FIG. 10B Shows the isometric cut view of the PLACEMENT OF
SEPARATE CHANNEL GUIDES ON A RECEIVER (66) in a Particular
embodiment, wherein the Zone B of the track is located inside a
tunnel located inside the of the receiver (66) handle, as described
in the Operating System of this Application.
[0165] FIG. 11 Shows the schematic placement of the lateral
HORIZONTAL PROTRUDING GUIDE (21) and lateral ROD GUIDE (41) PATH OF
THE CONTINUOUS GUIDES ON THE CHANNEL TRACK when the most forward
position and in the most rearwards position in a Particular
embodiment.
[0166] FIG. 11A Shows the schematic placement of the lateral
HORIZONTAL PROTRUDING GUIDE (21) and lateral ROD GUIDE (41) PATH OF
THE SEPARATE CHANNEL TRACK when the most forward position and in
the most rearwards position in a Particular embodiment.
[0167] FIG. 11B In a schematic showing the placement of THE
DUALSEPARATE CHANNEL TRACK ON An unclosed RECEIVER (66), having an
Upper receiver (66U) with an extended portion of a Track Guide
(80), and a constraining surface placed at the partition edge,
which perfectly mates with the partition edge of a lower receiver
(66L) to totally constrain the Track Guides in the lower receiver
(66L). In this particular embodiment the Upper receiver (66U) and
the Lower receiver (66L) are coupled by a pivotal joint n which
enables the very convenient opening, closing, and mating of the
Upper and Lower receivers, to drop in the Articulated Bolt Train to
move sandwiched along a totally constrain path. Notice how a
portion of the Track guides delineates the down and transversally
path along a tunnel portion inside the Handle of the receiver after
being mated and closed. The receivers pivoting opening and closing
define a JAWS CLOSING AND MATING SYSTEM.
[0168] FIG. 12 Is an schematic isometric showing the PLACEMENT of
the BOLT TRAIN IN FOREWARD PLACEMENT ON CONTINUOUS CHANNEL TRACKS
wherein the Horizontal track is extended to satisfy design
requirements, in a Particular embodiment. Notice that in front of
the Front Bolt (90) there is still a horizontal track segment in
which it can travel, in a particular embodiment.
[0169] FIG. 12A Shows the schematic placement BOLT TRAIN WITH THREE
MEMBERS IN FOREWARD PLACEMENT ON SEPARATE CHANNEL TRACKS in a
Particular embodiment.
[0170] FIG. 12B Shows the isometric placement of the BOLT TRAIN IN
FOREWARD PLACEMENT INSIDE AN ARTICULATED OPEN RECEIVER (66) showing
the Upper (66U) and the lower (66L) receivers in an opened
condition in a Particular embodiment.
[0171] FIG. 12C Shows the isometric placement of the BOLT TRAIN IN
FOREWARD PLACEMENT INSIDE A CLOSED RECEIVER (66) in a Particular
embodiment, wherein the Zone B of the track is located inside a
tunnel located inside the of the receiver (66) handle.
[0172] FIG. 12D Shows the top isometric placement of the BOLT TRAIN
IN FOREWARD PLACEMENT RELATIVE TO UPPER RECEIVER (66U) in a
Particular embodiment, wherein the Zone B of the track is located
inside a tunnel located inside the of the receiver (66) handle, as
described in the Operating System of this application.
[0173] FIG. 12E Shows the side view of the BOLT TRAIN IN FOREWARD
PLACEMENT RELATIVE TO UPPER RECEIVER in a Particular embodiment.
Notice the engagement of the SPRING INTERLOCK TO BOLT (38A) with
the upper plane slot of the head bolt (20), condition which occurs
when the receiver is completely closed to totally constrain the
Articulated Bolt Train Mechanism.
[0174] FIG. 12F Shows the isometric placement of the BOLT TRAIN IN
FOREWARD PLACEMENT RELATIVE TO lower UPPER RECEIVER (661) in a
Particular embodiment, wherein the Zone B of the track is located
inside a tunnel located inside the of the receiver (66) handle as
described in the Operating System of this application.
[0175] FIG. 13 Shows the side cut view of the BOLT TRAIN IN FIRING
POSITION when placed in a continuous track in a Particular
embodiment.
[0176] FIG. 13A Shows a cut view of the interaction of parts
PROTRUDING DELAY OPENING CAM (22B) and DELAY OPENING SLOPED FACE
(35) providing a DETAIL OF DELAY MECHANISM SCHEMATIC in a
Particular embodiment.
[0177] FIG. 13B Shows the schematic cut view of bolt train with a
third member delay damper relative to the controlling firing
mechanism subassembly (74), when the Train is in the most forward
position, in a preferred embodiment.
[0178] FIG. 14 Shows the relative to the CONTROLLING FIRING
MECHANISM SUBASSEMBLY (74) schematic CUT OF A THREE MEMBER BOLT
TRAIN WITH RECOIL DAMPER IN FORWARD POSITION and the engagement of
the set of main recovery springs (38) with the Front Bolt (21).
[0179] FIG. 14A Shows the schematic CUT OF A THREE MEMBER BOLT
TRAIN WITH RECOIL DAMPER IN REARWARDS POSITION relative to the
CONTROLING FIRING MECHANISM SUBASSEMBLY (74) in a Particular
embodiment.
[0180] FIG. 14B Is a schematic view showing the Cocking Action of
the slider hammer (30) relative to the pivoting pin (47) when
rotating as forced when entering the curved zone of the track
guides. Notice the action of the cam (22 B) against the front face
of the striking hammer, and the level of difficulty that the plane
(35) of the Angle Omega may present to complete the motion. This is
the essence of the delay mechanism to the opening of the breech.
Also Notice how the sear (56) internal to the hammer (30) is
engaged against the MECHANISMS CARRIER HOUSING (40), and the firing
mechanism is cocked when it returns to the horizontal position to
close the breech, as described in the Operating System of this
application.
[0181] FIG. 15 This side cut view shows the schematic OF THE BOLT
TRAIN (20) INTRUSION INTO THE MECHANISMS CARRIER HOUSING (40)
DISPLACING THE STRIKING HAMMER (30) rearwards when relocating
rearwards and causing a rotation relative to the pivoting pin (47),
in a Particular embodiment.
[0182] FIG. 15A This side cut view shows the schematic OF A THREE
MEMBER BOLT TRAIN IN FORWARD POSITION WITH INTERNAL SEAR ENGAGED
relative to the CONTROLING FIRING MECHANISM SUBASSEMBLY(74)
predetermined position, in a READY TO FIRE CONDITION, in a
Particular embodiment.
[0183] FIG. 16 This side cut view shows the schematic OF BOLT AND
MECHANISMS READY TO FIRE WITH BULLET in a Particular
embodiment.
[0184] FIG. 17 This side cut view shows the schematic FIRING
MECHANISMS PLACEMENT ON AN EXTERNAL SEAR in a predetermined
position, in a Particular embodiment.
[0185] FIG. 17A This side cut view shows the ANGLE OF ARTICULATION
SCHMATIC when the Front Bolt (90) moves horizontally rearwards, and
the FIRING MECHANISM SUBASSEMBLY (39) diverts its path
transversally downwards, in a Particular embodiment.
[0186] FIG. 17B This side cut view shows the SCHEMATIC FIRING
MECHANISMS PLACEMENT relative to an articulated bolt train having
AN INTERNAL SEAR in a Particular embodiment.
[0187] FIG. 18 This schematic view shows several POSSIBLE USES OF
THE PIVOTALLY ARTICULATED BOLT TRAIN--in different types of
firearms, in Particular embodiments.
[0188] FIG. 19 This schematic view shows the LOCATION OF THE OFFSET
DISPLACED HINGES when disengaged, in a Particular embodiment.
[0189] FIG. 20 This schematic view shows the SCHEMATIC PLACEMENT OF
COMPONENTS IN A RIFLE in a Particular embodiment. Notice that the
track guides become completely constrictive when the upper and
lower receiver members are placed together converting the
Articulated Bolt Train mechanism into a completely constrained
motion train moving sandwiched between the upper receiver and the
lower receiver. The Bolt train is dropped into the yet
unconstrained tracks, and becomes totally constrained when The
upper portion of the tracks in the upper receiver mate together
after pivoting about the pivoting axis (66A), with the lower
receiver as made possible with the JAW OPENING AND CLOSING
SYSTEM
[0190] FIG. 21 This schematic view shows the PLACEMENT OF
COMPONENTS IN A PISTOL in a Particular embodiment. Notice that the
track guides become completely constrictive when the upper and
lower receiver members are placed together converting the
Articulated Bolt Train mechanism to a completely constrained
motion. The upper portion of the tracks in the upper receiver mate
together after pivoting about the pivoting axis (66A), with the
lower receiver as made possible with the JAW OPENING AND CLOSING
SYSTEM.
[0191] FIG. 22 This schematic view shows the PLACEMENT OF
COMPONENTS IN AN ASSAULT RIFLE in a Particular embodiment. Notice
that the track guides become completely constrictive when the upper
and lower receiver members are placed together converting the
Articulated Bolt Train mechanism to a completely constrained
motion.
DETAILED DESCRIPTION OF THE DRAWINGS AND DIFFERENT EMBODIMENTS
[0192] This invention uses a Bolt Train 90 consisting of two or
more track mounted members, pivotally articulately, and connected
between the adjacent members. The first member of the Bolt Train 90
is a Front Bolt 20, or alternatively a Bolt Carrier 20B containing
a Rotary Bolt 20C, which initially travels axially only, The Second
member is an Mechanism Carriage Housing 40 or alternatively 40B
containing, and including, the Active Firing Mechanisms and
progressively diverts its path to a downwards or transverse motion
as the front bolt 20 displaces rearwards. When needed, a third
optional member is incorporated to the Bolt Train 90. It is a
Recoil Damper Subassembly 64, that travels linearly or
transversally, comprised of a Recoil damper mechanism carrier 65
containing a movable compensator 67 and a spring 69A. The Bolt
Train 90 is track guided slidably mounted by means of protruding
guides 21 or by roller guides 41 or 41A that slide in lateral slot
Channel guides 80 embedded or attached to the receiver 66
frame.
[0193] The slot Channel guides 80 have a planar path that uniquely
directs the displacement of the Bolt Train 90. Because the Firing
Mechanism Sub Assembly 39 FIG. 4B, FIG. 5B is articulately linked
to the front bolt 20, it always places the firing mechanisms in the
closest proximity of the firing pin 70, located inside the front
bolt 20. This train array reduces the total weight and the volume,
by eliminating the need of having a fixed separate mechanisms
subassembly, in other location. The necessary mass to absorb the
recoil is present in this transversally recoiling array, but at the
same time, is the same mass used in the active firing mechanisms.
The mass and volume of the conventional active firing mechanism and
its frame are converted into recoiling mass having a very compact
volume.
[0194] The Articulated Bolt Train 90 is also a kinetic energy multi
absorption device. It accomplishes it in several independent ways:
[0195] 1. By compressing the main recoil spring. [0196] 2. By
diverting the path of the Mechanism Carriage Housing 40 and parts
contained within. The reaction force of the change of direction is
perceived in the receiver as a vertical and rearwards movement.
[0197] 3. By amplifying the force required to compress the Hammer
spring 33 via the principle of mechanism explained in the fourth
purpose. [0198] 4. By compressing the Hammer spring 33 while
cocking as explained in the third purpose. [0199] 5. By compressing
the Spring 69A, and pushing the Movable Compensator 67 of the
optional Recoil Damper Mechanism [0200] 6. By utilizing the mass of
all the above mentioned mechanisms as working mass to compensate
the recoil, saving mass and volume that otherwise would be required
to perform the same results in independent mechanisms.
Purposes
[0201] This invention has at least twelve different purposes. The
order in which the Purposes are presented does not represent a
major importance of one relative to the others. These include:
1: To provide a Bolt Train mechanism to partially redirect the
initial bore axial recoil force into a transversally directed
recoil force and to perform several other functions; 2: To provide
a firing mechanism subassembly incorporated to the Bolt Train that
would displace altogether as part of the recoiling mass; 3: To
provide a Firing Mechanism Subassembly incorporated to the Bolt
Train 90, that cocks in response to the recoil displacement, and to
the angular rotation of the components of the bolt train while
displacing rearwards following a transverse path; 4: To provide a
manageable cam delay blowback mechanism to retard the opening of
the breech operating only on rearward motion; 5: To significantly
reduce the total weight, and volume of the firearm utilizing the
Bolt Train mechanism; 6: To lower the center of gravity of the
firearm utilizing the Bolt Train mechanism; 7: To provide an
independent Recoil Damper Mechanism attachable to the Bolt Train
sub assembly 8: to provide a quick Jaws opening and closing system
of the Upper and Lower receivers pivoting about a hinge joint, like
jaws, to facilitate the access to internal components of bolt train
mechanisms for assemble and disassemble components; 9: To Generate
an Angular Moment, which reduces the Barrel Torque rotation effect:
10: To minimize the moment effect of recoil about the hands and
wrist of the firer. 11: To identify and engineer the different
parameters involved in the functioning of the Articulated Bolt
Train Operational System, and to set the desired values for the
preferred objective embodiment for a certain task. 12: To perform
the following independent mechanical actions, occurring in
mechanisms housed within separated train members: 1) To cock the
firing mechanisms, 2) To create a delay in the breech opening, and
3) To actuate an optional recoil damper mechanism.
Operation
[0202] In relation to the first purpose, above, to provide a Bolt
Train mechanism to partially reroute the initial bore axial recoil
force into a transversally directed recoil force and perform
several other functions. In one embodiment the Bolt Train 90 can
have a plurality of members interconnected by hinges, or any other
proper interlinking means, one after the other that move guided
along slot channel guides 80, internal to the receiver, inducing a
planar motion of the bolt train along a planar path to which the
barrel belongs. None of the members is a dead mass. Each has a
specific function and a mechanism inside the corresponding carrier
housing. In order to function properly, the Bolt Train 90 has to be
placed inside a by design Receiver 66 that controls and urges its
path, and holds all the sub assemblies in the convenient location,
allowing the synchronic movements of all the components to take
place in time and space. The Receiver 66 is conceived in a manner
that it has an Upper receiver and a Lower receiver, so that when
both are put together, it will completely define and constrain a
plurality of cavities and tracks to enable the unique travel of the
Bolt Train 90, and the housing of the modular subassemblies and
components of the firearm.
[0203] When a firearm is discharged there is a reaction force in
the opposite direction of the projectile. That causes the Bolt to
displace rearwards over a straight path. In the case of this
invention, the Bolt Train is comprised by several articulately
linked members that form a Bolt Train 90. The bolt train 90
consists of two or more different bodies. See FIG. 9A, FIG. 10,
FIG. 10A. The front bolt 20, and mechanisms carrier housing 40, are
connected by a pin 47 that holds together the top displaced hinge
24 of the front bolt 20 and mechanisms carrier housing displaced
hinge 48. Hinges 24 and 48 can be displaced outside of the bodies
to which they are attached and the center of the hinges holes host
pin 47, FIG. 19. The total mass of the bolt train 90 is the sum of
the mass of front bolt 20 with all the elements that get attached
to it, plus the mass of the mechanisms carrier housing 40 with all
the elements that get attached to it and hold inside it (the firing
mechanisms).plus the mass of the optional recoil damper mechanism
carrier 64 and all the elements that get attached to it. See FIG.
9A. The Bolt Train 90 is track mounted on slot Channel guide tracks
80 embedded inside the internal sides of the receiver 66 and direct
the course (path) in a horizontal, curved, and transverse direction
in a continuous, and smooth reciprocating motion. The Channel guide
80 are internally attached, embedded, or held on the firearm frame.
At the moment of firing the cartridge transmits the total recoil
force to the bolt train 90. The protruding guides 21 (one at the
right other at the left) slide inside the slot Channel guide 80
located on both sides of the cavity where the bolt train 90 moves.
Slot Channel guides 80 can be continuous or separated as shown in
FIG. 8 and FIG. 8A. The Roller guides 41, which are round, also
slide inside the slot Channel guides 80. The slot Channel guides 80
are built to the proper length or may have travel stops to limit
the rearwards displacement of the Bolt Train 90. The forward
displacement of the front bolt 20 is limited by proper means
depending on the design application. The slot Channel guides 80 can
be of continuous path as shown on FIG. 8, FIG. 10, FIG. 12 or
separate discontinuous paths as shown on FIG. 8A, FIG. 8B, FIG.
10B, FIG. 11, FIG. 12A, FIG. 12 C. Due to its design the horizontal
protruding guides 21 of front bolt 20, can displace linearly inside
the slot Channel guide 80 within the zone A FIG. 8. Due to the
integral design of the bolt train 90, the protruding rod guides 41
or the rollers 41A can move within the zone B, FIG. 8, or FIG. 8A.
When the bolt train 90 moves to the back from the forward position,
the front bolt 20 displaces linearly, urging the displacement of
the mechanisms carrier housing 40 with all contained within (the
firing mechanisms) by means of bolt top hinge 24, the mechanisms
housing carrier hinge 48, and the connecting pin 47. The latter
named parts (24, 48, and 47) interlock the first two bodies (20 and
40) of the Bolt Train, and all the contained components, in an
articulated manner that enables the rotation about the connecting
pin 47. The mechanisms carrier housing 40 with all the elements
contained inside (the firing mechanisms), moves transversally only
through the zone B. A conventional main recovery spring needs to be
permanently acting on the front bolt 20 either by pushing or by
pulling, depending on the design needs, in order to urge the return
of the bolt train 90 to the full forward position after it has
displaced back and down by the action of the recoil force. The
transverse displacement of the recoiling bolt train 90 changes the
direction, and the dynamics of the recoil with respect to
traditional bore axis lineal recoiling bolts.
[0204] In relation to the second purpose, above, to provide a
firing mechanism subassembly incorporated to the Bolt Train 90 that
displaces altogether as part of the recoiling mass. In one
embodiment the firing mechanisms have two different separate types
of sub assemblies: The controlling firing mechanisms subassembly
74, FIG. 5C, which has a permanent location, and the Active Firing
Mechanism Subassembly 39 FIG. 5B, which moves as a part of the Bolt
Train 90. The lever 76, and the spring column fire actuator, and
disconnector 78 all mounted on the frame 79, and the active firing
mechanism subassembly 39, FIG. 5B which comprises the hammer, the
hammer spring, the sear, sear lever. In conventional designs all of
the components of the firing mechanisms are placed together in one
subassembly kept in place by a strong frame. The Active Firing
Mechanism Subassembly 39, FIG. 5B is located in the closest
proximity to the Front Bolt 20, 20a, 20b FIG. 2B, and linked by
means of a hinges 48 and 24 in a manner that they become moveable
and integrally coupled to the Articulated Bolt Train 90 and fit
into a one and only predetermined placement in a synchronized
movement at the moment of firing. The mechanism works in the
following way. See FIG. 1. The hammer 30 has the form of a
rectangular prism at the rear end it has cylindrical cavity for the
spring 31. This hammer has an optional frontal protruding push rod
for the firing pin 32. All of it is a single body with no moving
parts. The above mentioned parts move freely inside a rectangular
cavity 40A of the mechanisms carrier housing 40.
[0205] Alternatively, an angular sear lever 50 is attached at the
top side of the mechanisms carrier housing 40 by means of a pin for
sear lever which passes through holes for pin 44 and the hole for
sear lever pin 52 of the hinges for sear pin 43 and hole for sear
lever hinge pin 52 respectively. The angular sear lever 50 has a
small angular face tip 54 that passes through a rectangular hole
for the sear tip 45.
[0206] A sear lever spring 53 accommodates into the cylindrical
hole for sear spring 42 and pushes the angular sear lever 50 so
that the angular sear lever 50 is permanently pushed into the
rectangular hole for the sear tip 45. The angular face tip 54 is
long enough to cause a temporary interference with the frontal face
of the hammer 30 retaining it in a cocked loaded position when the
hammer 30 is moved enough to the rear inside the rectangular cavity
40A of the mechanisms carrier housing 40 causing the compression of
the hammer spring 33.
[0207] The rear of the mechanisms carrier housing 40 has two
laterally protruding rod guides 41 or Roller guides 41 A on to the
right, another to the left. They slide along the zone B see FIG. 11
of the Slot Channel guide 80; see FIG. 8. The zone B has a straight
part and a curved part adjacent to the zone A. The mechanisms
carrier housing 40 connected to the Front Bolt 20 by means of the
hinges mechanisms housing carrier hinge 48 and bolt top hinge 24 as
previously explained. The mechanisms carrier housing 40 pivots
about the connecting pin 47 and connects it (40) with the front
bolt 20, constituting on the whole the bolt train 90. The
horizontal protruding guides 21 can move linearly inside the slot
Channel guide 80 within the zone A FIG. 8. The front bolt 20 and
the mechanisms carrier housing 40 are perfectly aligned when the
protruding rod guides 41 and the horizontal protruding guides 21
are both in the zone A, This can happen in two situations: when The
Bolt Train 90 is in cocked position as described in FIG. 15, and
when bolt and firing mechanisms are in forward discharged position
as described in FIG. 13. Every time those protruding rod guides 41
are in the zone B, the mechanisms carrier housing 40 and the front
bolt 20 are at an angular position pivoting about the connecting
pin 47 as shown in FIG. 14. Notice that FIG. 14 is at the extreme
position since the horizontal protruding guides 21 is located at
the end of zone A. The grouping of the active firing mechanism FIG.
5A inside mechanisms carrier housing 40, is defined as the Active
Firing Mechanism Subassembly 39 FIG. 5B. When incorporated to the
Bolt Train 90, makes the entire mass to displace when recoiling,
fulfilling the purpose.
[0208] In relation to the third purpose, above, to provide a firing
mechanism subassembly incorporated to the Bolt Train that cocks in
response to the recoil displacement, and to the angular dislocation
or misalignment of components of the bolt train while displacing
rearwards following a transverse path. In one embodiment the
increasing displacement of the Articulated Bolt Train 90 in the
rearward motion causes an increasingly divergent rotation of the
Mechanism Carrier Housing 40 about pin 47, increasing the Angle of
Articulation FIG. 17A.
[0209] The non parallel paths of zone A and zone B of the slot
Channel guides 80 FIG. 10 and FIG. 10 A, forces the two members of
the train to move in different directions crating an angle of
articulation center at the top hinge 24, (PIN 47) that
progressively increases as the parts displace more along the
different paths. The angle of articulation is defined as shown in
FIG. 17A. Relative motions are described. The cocking action of the
firing mechanisms takes place in the following way. As the
mechanisms carrier housing 40 starts to move through the zone B,
FIG. 8, and FIG. 8A, it starts to rotate about the connecting pin
47, in a manner that the edge line 22A of the thin rear rectangular
protrusion 22 describes a circular path about the connecting pin
47, and penetrates inside the rectangular cavity 40 A, occupied at
this moment by the spring loaded hammer 30, and pushes the hammer
30 towards the back of the rectangular cavity 40A by sliding over
the frontal face of the hammer 30. After the hammer 30 passes
beyond the sear engagement point, rectangular hole for sear tip 45,
the angular face tip 54 of the angular sear lever 50 moves inside
the rectangular cavity 40A pushed by the force of the sear lever
spring 53 blocking the path of the Hammer 30 and retaining the
hammer 30 spring 33. When the bolt train 90 returns forward from
the extreme rearward position, the angle of articulation FIG. 17A
diminishes, the rear rectangular protrusion 22 moves back reducing
the penetration inside the rectangular cavity 40A allowing the
hammer 30 to move forward pushed by the force of the compressed
spring only to the point that the front face of hammer 34
interferes and contacts the angular face tip 54 locking the firing
mechanism in a cocked position. As the Bolt train 90 moves to the
aligned position, the protruding rod guides 41 reach the zone A. At
this point the hammer 30 is aligned with the front bolt 20 and the
firing pin 70 located inside the cylindrical cavity for the firing
pin 23. The firing action takes place when the angular sear lever
50 is depressed causing it to pivot about the pin for sear lever 46
raising the angular face tip 54 out of the way of the hammer 30
which moves forward impacting with the push rod of firing pin 32
the rear end of the firing pin 72, which causes the front end of
firing pin 73 to strike the primer of the cartridge firing the
projectile. On the front bolt 20 there is a rectangular slot 26 to
host the placement of a cartridge case extractor 60 which pivots
about the extractor pin 61.
[0210] It is clear that the recoil force causes the displacement of
bolt train 90 rearwards inducing an angular displacement of
mechanisms carrier housing 40 and the front bolt 20 about the
center of the top hinge 24, which produces the cocking of the
active parts of the movable firing mechanism.
[0211] In relation to the fourth purpose, above, to provide a cam
delay blowback opening mechanism to retard the opening of the
breech. In one embodiment, this Invention achieves the purpose of
creating a delay in the opening of the breech on the rearward
motion by generating a restriction to the rearwards motion only, As
the recoil force starts to build up it urges the bolt train 90 to
move backwards as explained previously. The force opposing to that
displacement is that of the main recovery spring of the firearm. An
additional force opposing the displacement of the bolt train 90 is
crated in the following manner: As the protruding rod guide (2) 41
slidably moves to zone B it starts to rotate about pin 47, as well
as the mechanisms carrier housing 40 and the firing mechanisms
contained within, causing the protruding delay opening cam 22B of
FIG. 1A, 2A to describe a circular path about the center of the top
hinge 24, moving inside the rectangular cavity 40A, contacting the
delay opening sloped face 35 of front face of hammer 34 of FIG. 1A,
3A as shown in FIG. 13A. The hammer 30 is pushing foreword by the
action of the hammer spring 33 of FIG. 1A with a force Fs. To
overcome that force, the protruding delay opening cam 22B must
exceed a value of force of the equation form F=Fs/cosine of Omega
being Omega angle FIG. 3B the one formed by the plane of the front
face of hammer 34 and delay opening sloped plane of face 35 as
shown more explicitly in FIG. 13A. That is the value of the
additional force created by this mechanism and depending on the
spring force Fs and the value of the Omega angle FIG. 3B. Once the
bolt train 90 progresses into the zone B, the value of that force
diminishes as the angle of contact between the protruding delay
opening cam 22B and the delay opening sloped face 35 becomes more
favorable. The value of the axial force exerted by the front bolt
20 to exceed Fs/cosine of omega depends also of the distance of the
protruding rod guide (2) 41 to the pin 47 and other matters. That
significant force value is added to the force of the main recovery
spring of the firearm, meaning that it will take more time to
buildup in the explosion process inside the cartridge, translating
into a delay in the opening of the bolt in the recoil. In order to
ease the motion and to reduce friction, a roller cam may be used at
the protruding delay opening cam 22B. Also rollers can be placed on
the side of the hammer 30 in order to smooth the displacement and
minimize wear.
[0212] In relation to the fifth purpose, above, to significantly
reduce the total weight, and volume of the firearm utilizing the
Bolt Train mechanism. In one embodiment, this Invention achieves
the purpose by substituting the conventional fixed placed firing
mechanisms by movable firing mechanisms, and placing them and its
frame inside the Mechanisms Carrier Housing 40, behind the Front
bolt 20 converting then into a part of the Bolt train 90. The
Articulated front Bolt 20 and mechanism carrier housing 40 with
firing mechanism incorporated within substitutes the fixed
conventional firing mechanisms eliminating the volume and weight
that is normally dedicated to it, thus reducing substantially the
volume and weight. The controlling firing mechanisms sub assembly
74 FIG. 5B, FIG. 5C, which comprises trigger, safe, automatic and
semi automatic selector, require a small and light structural frame
with small volume. It is placed in a convenient predetermined
location with the only requirement that, a in order to fire, a
pushing element belonging to the firing mechanism can exert a
pushing action, to disengage, on the sear 50 or 58, at a unique
fixed predetermined location that aligns with the traveler angular
sear lever 50 every time that the bolt train 90 is in the full
forward position. See FIG. 17. If an internal extruded sear 58 FIG.
5A is utilized, the pushing action of the controlling firing
mechanism bar 78 is exerted through a Window Hole 59 of the
Mechanism Carrier Housing 40 close to the engaging location of the
cylindrical rod sear 58. When the bolt train 90 moves full forward
closing the breech, the Window Hole 59 moves to a predetermined
position aligning with the pushing bar 78 FIG. 17B of the
stationary and compact controlling firing mechanism subassembly 74.
This substitution of masses eliminates the volume and mass of the
conventional firing mechanisms. The design purpose is possible by
identifying masses that can perform dual functions and convert it
into a mechanism that serves both functions. The mass present in
the hammer, the sear, the mechanisms frame, the hammer spring is
used by arranging it into a mechanism that is coupled to the bolt
train 90 giving it the necessary mass that needs to be present in
the bolt to absorb the recoil.
[0213] In relation to the sixth purpose, above, to lower the center
of gravity of the firearm utilizing the Bolt Train 90 assembly. In
one embodiment, the very dense nature and slim profile of the Bolt
Train 90 containing the Firing Mechanism enables the substitution
and elimination of the conventional voluminous firing mechanisms as
explained above and placing it in a predetermined location where it
will align to interact with the miniature compact controlling
firing mechanism subassembly 74, FIG. 5C placed in the closest
proximity of the Window Hole 59. FIG. 17 B. The compact size of the
subassembly 73 lowers the center of gravity.
[0214] In relation to the seventh purpose, above, to provide an
independent Recoil Damper mechanism linkedly attachable to the Bolt
Train sub assembly to additionally restrain the rearwards motion
increasing the total delay. In one embodiment, when an optional
third member, the Recoil Damper sub assembly 64 FIG. 4C is attached
to the Bolt Train 90, it will be positioned at the rear behind of
the mechanism carrier housing with rear cam 40B, and linked to it
by means of roller with pin 41B passing through the centre hole of
the two side hinges 65A and the rear center hole of the mechanism
carrier housing with rear cam 40B. The mechanisms carriage housing
40B has a protruding cam 40C that penetrates through the front of
the cavity for 69 where the compensator 67 slides freely pushed by
the spring 69A. As the Bolt Train 90 moves rearwards, the mechanism
carrier housing with rear cam 40B and the Recoil Damper sub
assembly 64, initially at an angle, move into a straighter path to
align with the transverse axis of the ZONE B FIG. 11A, FIG. 13B and
FIG. 14A by pivoting about the Roller with pin 41B. This relative
rotation causes the tip of the Protruding cam 40C to describe a
circular path inside the cavity for compensator 66 and to slide
against the front Angular Face 68 of the Movable Compensator 67,
displacing it to the interior of the Recoil damper mechanism
carrier 65 and compressing the spring 69A. The action of
compressing the spring 69A and pushing the Movable Compensator 67
back at an angle requires a force that opposes to the rearward
displacement of the Bolt Train 90 and necessarily delays the
opening of the breech, creating an additional retard. It is a
kinetic energy storing and absorption device.
[0215] In relation to the eighth purpose, above, to provide an
quick Jaws Opening and Closing System of the upper (66U) and lower
(66U) receivers, pivoting about a hinge Axis (66A), like jaws, to
facilitate the access to internal components of Bolt Train
mechanisms and sub-assemblies, for assemble and disassemble
operation. The array of train elements, paths in the internal array
of guide tracks, the mechanisms subassemblies receptacles, the
means of fixation, the means of coupling of independent interacting
components, the Articulated Bolt Train within the receiver, become
totally unconstrained when the upper and lower receivers are
rotated, in a plane, one relative to the other like jaws to allow
the fast opening, the quick access and removal of All internal
subassemblies of the floating articulated Bolt Train Operating
System.
[0216] In relation to the ninth purpose, above, to Generate an
Angular Moment, which reduces the Barrel Torque rotation effect,
the angular motion of the Articulated Bolt Train 90 in the curved
path, while shifting from the horizontal path to the transverse
path, generates a Gyroscopic effect and a Gyroscopic Moment or
Angular Moment which induces a force vector perpendicular to the
plane of motion of the articulated Bolt Train. As a result, the
Articulated Bolt Train is capable of compensating to an extent, the
barrel rotation reaction, commonly known as Barrel Torque, which
occurs as a reaction, when rotation is impaired to the projectile
whilst being propelled through the rifled barrel. Such temporary
Gyroscopic Effect is transient and occurs again, in the
reciprocating motion of the Train, while returning forward to close
the breech. The magnitude of the Moment is a function of The Mass
of the parts subject to angular motion; to the Radius of rotation;
the Angle of Articulation, Which determines the Arc Length and to
the Velocity of rotation. All the latter mentioned are measurable
parameters and subject of being calculated for design
efficiency.
[0217] In relation to the tenth purpose, above, to minimize the
moment effect value of recoil about the support hand and wrist of
the firer. By definition, the magnitude of a Moment is the product
of a force, multiplied by the distance (arm) to the line or point
of application. Therefore by locating a portion of the path of some
elements of the Articulated Bolt Train directly through the hand,
and by locating the curved portion of the path in the closest
ergonomical proximity to the hand or wrist, the Distance factor of
the Moment value is minimized. Such perspective is of important
when determining the path of the firearm.
[0218] In relation to the eleventh purpose, above, to identify the
different Parameters involved in the operation of the Articulated
Bolt Train Operational System, and to engineer the desired values
to the parameters to obtain a preferred dynamic behavior embodiment
for a certain operation. Parameters herein are numerical or other
measurable factors, forming one of a set that defines a system or
sets the conditions of its operation. Thus the identification of
the parameters, and the determination of the best possible values,
and the interaction of the internal mechanisms is a very noble
instrument in the process of improving recoil management in guns
design. The identified parameters in the functioning of the
Articulated Bolt Train Operation al System are at least:
[0219] a) in terms associated with the firearm, including i) the
total mass of the firearm when ready to
fire, and ii) the location of the center of gravity of the
firearm;
[0220] b) in terms associated with the path of the articulated Bolt
Train, including i) the length of the horizontal zone parallel to
the axis of the Barrel, ii) the shape of the curved zone
(semicircular, elliptical, combined, with inflexion point, singular
or multiple, Radius of the circle, coordinates of center point,
Axis of ellipse, Length of arc of circle or ellipse, angle of
articulation, as examples), and iii) the length, shape and
direction of the of the downwards transversal zone (as above,
including, again, the angle of articulation, as examples);
[0221] c) in terms associated with the articulated bolt train,
including i) bolt mass, ii) firing mechanism subassembly (39) Mass,
iii) Recoil Damper Sub-assembly mass, and iv) Spring force of the
main springs (basically the mechanism design and physical
interaction of mechanisms therein the bolt train);
[0222] d) in terms associated with the conditions of operation,
including i) cartridge energy utilized in the firearm, and ii)
Initial Bolt Train velocity (measurable);
[0223] e) in terms associated with the bolt train motion
restriction;
[0224] f) in terms associated with the cam delay blowback opening,
including i) the Cam (22B) shape, ii) the Angle Omega of the Front
face of the striker hammer, iii) the Force of the spring for the
Striker Hammer, and iv) the mass of the Striker Hammer;
[0225] g) in terms associated with the recoil damper mechanism,
including i) shape of the cam (40C), ii) the shape and Angle Beta
of the recoil compensator (67), iii) the Force of the spring for
the recoil compensator, and iv) the mass of the recoil compensator;
and [0226] h) in terms associated with the firearm, including i)
the Weight of the receiver, ii) the height of the receiver, iii)
the weight of the Barrel, iv) the length of the barrel, v) the
Center of mass of the complete firearm, vi) the total weight of the
firearm, among others.
[0227] In relation to the twelfth purpose, above, to perform the
following independent mechanical actions, occurring in mechanisms
housed within separated train members: 1) To cock the firing
mechanisms, 2) To create a delay in the breech opening, and 3) To
actuate an optional recoil damper mechanism. The cocking action of
the firing mechanism occurs when the edge line 22A of the bolt 20
contacts and pushes back sufficiently the Front face 34 of the
hammer as a consequence of the pivotal rotation about pin 47 of the
Bolt head 20 and Firing Mechanism Subassembly 39. The delay action
in the breech opening occurs when the protruding delay opening cam
22B of the bolt 20 contacts and pushes back sufficiently the Delay
opening sloped face 35 of the hammer 30 at the Omega Angle, as a
consequence of the pivotal rotation about pin 47 of the Bolt head
20 and Firing Mechanism Subassembly 39. The action of actuating an
optional Recoil Damper Mechanism 64 occurs when the protruding
delay opening cam 40C of the 40 contacts and pushes back
sufficiently the Front angular Face of compensator 68 of recoil
Damper Subassembly 64 at the Beta Angle, as a consequence of the
pivotal rotation about pin 41A of mechanisms carrier housing 40 and
Recoil Damper Mechanism Carriage 65.
ALTERNATIVE EMBODIMENTS
[0228] a. This invention presents a linearly displacing hammer.
Similar results in terms of recoil absorption can be obtained by
placing a compact array of firing mechanisms with conventional
rotary parts behind the front bolt as a part of another type of
traveling mechanisms carriage, however it would require more
volume, which defeats the purpose of accommodating the traveling
mechanisms in a tight space such as the inside of the handgrip.
[0229] b. Additional recoil absorption can be achieved by placing
conventional shock absorbers, hydraulic or pneumatic, rubber pads
at the end of the cavity that receives the mechanisms carrier
housing 40. Elastomeric shock absorber can be placed to
additionally abate the recoil by allowing the recoiling mechanisms
carrier housing 40 stop against them. [0230] c. Neither the
mechanisms carrier cavity 40A, the hammer 30, nor the mechanism
carriers housing 30 are necessarily rectangular. They are of the
convenient shape to accommodate a convenient shaped hammer. [0231]
d. FIG. 3B Shows a simpler design of the hammer that incorporates
the sear and the sear spring as an integral part of the hammer 30.
This locking action takes place internally when the sear angular
face 36 moves into the rectangular hole 45B of FIG. 4A at the force
of the sear flat spring 37, enabling the elimination of parts
numbers 42, 43, 44, 46 50,51, 52,53, 54. Such simpler design of the
hammer also makes possible to use a mechanisms carrier housing 40
as shown in FIG. 4B. [0232] e. Slot channel guides 80 are used in
this description of the operation; however, other different methods
to guide and control the path of the mechanisms may be used without
affecting the novelty of this patent. [0233] f. To enhance
compactness, the Slot Channel Guides 80 have been shown to be
located inside the handle or grip, however, its placement in any
other convenient location and with a suitable direction can be used
to attain the desired result of recoil management or trimming.
[0234] g. FIG. 3C shows a compact design of the hammer that
incorporates an internal articulated toggle internal sear 56 and in
a similar way to the latter explained mechanism, has the same
benefits, with the advantage of being able to tune the trigger pull
sensitivity by using different strength of the toggle internal sear
spring 55. [0235] h. A similar active firing mechanism to the one
described in this application can be developed to be placed in the
Front Bolt location, and operating under the same principles of
dislocation of the two main components of the Bolt Train. In this
way, the Front Bolt becomes a "Front Bolt and active Firing
Mechanisms Carriage Housing", with active firing mechanisms inside,
and the mechanisms carrier housing 40, becomes just a mass with the
convenient shape and size. The hammer can integrate with the firing
pin, in one sole part. [0236] i. Similar results cad be obtained by
substituting the transverse slot Channel tracks that urge the
displacement, by articulated bar plates of proper length or plates
in which one end of the bar is hinged about a fixed position on the
receiver, and at the other end is articulated to a hinge placed at
the back of Firing Mechanisms Carriage Housing 40, See FIG. 20.
Forcing a semi-circular motion of the rear end of the Firing
Mechanisms Carriage Housing 40. [0237] j. The channel slotted
guides can have a convenient form and direction as long as they
force the articulation of the Bolt Train Assembly when displacing,
can be embedded, stamped, machined slotted in the receiver or
separately manufactured and properly attached to the receiver.
[0238] k. The receiver 66 can be manufactured by several different
processes; machined, stamped, injected, metal injection molding; in
clam shells, upper and lower receivers, with the condition that
when assembled, it will define some cavities and track slots, to
accept the necessary parts and subassemblies for its proper
functioning [0239] l. The cocking handle can be placed acting
directly on the front bolt or as a part of a bar actuated bi a
direct drive gas piston system. [0240] m. A direct drive gas piston
system can be used to push back the articulated bolt train upon
firing the firearm. [0241] n. When the articulated bolt train is
used with large sized projectiles the gun can be fitted with an
electric device to assist the drive. [0242] o. The sear can engage
in many ways, as long as it locks against the firing mechanisms
carriage housing 40, holding the hammer back inside the carriage
spring loaded. [0243] p. It is possible to trim, both, the trigger
pull, and the trigger travel by placing threaded holes inside the
Hammer 30, at the upper side, and the lower side of the cavity that
hosts the sear. By placing a spring against the upper part of the
seat, exerting trim able force controlled by the displacement of a
trimming screw at the opposite side of the threaded hole. The
trigger travel is controllable by placing a trim able screw acting
over the lower side of the sear, limiting the sear travel to
engage, and consequently
[0244] It is evident that firearms described in one out of the
several possible embodiments, represent improvements in numerous
ways in terms of ergonomy, comfort, recoil control, ease of
manufacture, ease to serve, size of the weapon, weight of the
weapon, stability, appearance, cost, concealability, and safety due
to the simplified technology herein described. But most importantly
the Operating System herein described represent an outstanding tool
for the process of gun design for the ability to engineer the value
of the parameters involved the management of the recoil control
within a range of attainable results. Today's technology enables
the use of simulation software to thoroughly obtain data to predict
the recoil changes in three dimensions and three axis
rotations.
[0245] The utilization of composite polymers, carbon fibers and
modern manufacturing processes is compatible with the weapons using
the present invention.
[0246] The potential use of this invention is abundant in nearly
all categories of semi and full automatic guns for civilian and
military purposes crating a noble class of weapons. Implications in
defense are immediate due to the advantages exposed. Most
importantly, the ability to identify the Operating System
Parameters and to engineer its values in order to attain improved
recoil effects represents an extraordinary tool in firearms
design.
* * * * *