US20110252686A1

US20110252686A1 - High Reliability Extractor Depressor for Use in Handguns

Info

Publication number: US20110252686A1
Application number: US12/760,686
Authority: US
Inventors: William J. Coleman
Original assignee: Individual
Current assignee: Individual
Priority date: 2010-04-15
Filing date: 2010-04-15
Publication date: 2011-10-20

Abstract

A high reliability extractor depressor assembly for use in handguns which significantly reduces the effect of recoil on the extractor depressor plunger assembly. These positive effects are accomplished by the following: (a) designing a new longer piece (standoff bar) of greater mass, (b) redistributing the mass from the rear of the assembly to the front, (c) designing a new shorter piece (extractor depressor plunger), (d) reversing the location of the longer piece (standoff bar) and the shorter piece (extractor depressor plunger) in the assembly, (e) increasing total mass of the assembly, and (f) changing the balance of the assembly by shifting mass to the rear of the spring.

Description

CROSS REFERENCE TO RELATED APPLICATIONS

None.

FEDERAL RESEARCH STATEMENT

None

BACKGROUND OF THE INVENTION

The present invention relates to an improved extractor depressor plunger assembly for use in handguns. More particularly, the present invention is a high reliability extractor depressor assembly that is designed to significantly increase reliability in harsh or extreme environments and/or in heavy usage.
While the claimed high reliability extractor depressor assembly can be used effectively in many different types of handguns, for the purposes of explaining the attributes of the invention, a Glock 17 will be used as the demonstration platform.

DESCRIPTION OF THE PRIOR ART

Handguns are well known and disclosed in the prior art. In most handguns, the extractor depressor assembly is well known and mature technology. The primary feature of this design is having the majority of the mass forward of the extractor depressor plunger spring (i.e. towards the muzzle). While this has served the various Glock models well in the past, it has occasionally led to performance problems in severe environments on in heavy use.
The prior art teaches several distinct types of handguns and in particular several types of Glocks.
U.S. Pat. No. 4,539,889 to Gaston Glock teaches a standard Glock pistol with a conventional extractor depressor mechanism.
Similarly, U.S. Pat. No. 4,825,744 also to Gaston Glock discloses a Glock pistol with a conventional extractor depressor mechanism.
The above cited examples of the prior art comprise a standard extractor depressor assembly as is shown in FIG. 6. While these extractor depressor assemblies have served the handgun well, they have led to a deterioration of performance in extreme environments, heavy use, or when weight (such as a tactical flashlight or extra capacity magazines) is added to the frame. The instant invention resolves this deteriorated performance in extreme and heavy use environments as is described herein.

SUMMARY OF THE INVENTION

The present invention is directed toward a high reliability extractor depressor assembly that is designed to significantly increase reliability in harsh or extreme environments and/or in heavy usage. This is accomplished by redesigning the extractor depressor assembly to include higher mass, an optimized redistributed balance that results in greater and, most importantly, more consistent extractor tension, nominally less recoil, and somewhat improved friction wear.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1A shows a close up view of the high reliability extractor depressor assembly. The three components of the high reliability extractor depressor assembly are the standoff bar 20, extractor depressor plunger spring 30, and extractor depressor plunger 40.

FIG. 1B shows an exploded view of the high reliability extractor depressor assembly including the standoff bar 20, extractor depressor plunger spring 30, and extractor depressor plunger 40.

FIG. 2 shows a side view of the extractor depressor assembly 10 in close proximity to the rear of a Glock 17 slide 50.

FIG. 3 is a rear view of the Glock 17 slide which shows the extractor depressor assembly 10 as it would be inserted into the extractor depressor plunger raceway 65 in the slide 50.

FIG. 4A shows a closeup view of the extractor depressor plunger 40.

FIG. 4B shows a closeup view of the standoff bar 20. The standoff bar incorporates the following changes to the stock component: more than ten times greater overall mass, beveled rear edge to reduce wear on the slide cover plate, beveled nose to ensure the coils of the spring pass smoothly, and is made of stainless steel or some other corrosion resistant material.

FIG. 5 shows a rear view of the High Reliability Extractor Depressor (also known as the HRED) 10 inserted into the extractor depressor plunger raceway 65 in the slide 50. Also shown is the slide cover plate 53 which holds the HRED in place in the raceway during operation of the handgun.

DETAILED DESCRIPTION OF THE INVENTION

The instant invention refers to a redesigned and improved high reliability extractor depressor assembly for a handgun. For ease in understanding the instant invention will be described in the context of a Glock 17.
In order to understand and appreciate the significant benefits of the instant invention, it is instructive to review the function of current extractor depressor plunger assemblies in relation to other parts of a Glock. In a standard or stock Glock, once the gun has been “fired”, and the bullet and propellant gases have exited the barrel, the slide begins to decelerate. This deceleration causes free mass components in the slide (for example, the extractor assembly, firing pin, etc.) to exert rearward pressure on the slide. Said another way, as the slide decelerates, free masses in the slide will press against the rear of the slide just as a person riding in a vehicle presses against his or her seatbelt during sudden braking.
In the standard Glock, the deceleration of the slide causes de-loading of the extractor. Essentially, the deloading occurs as the weight/mass of the extractor depressor plunger exerts force to the rear as the slide decelerates. The resulting force is in opposition to the spring and results in less pressure on the extractor. The deceleration in a recoiling firearm is not generally smooth and tends to sharpen at several key points prior to extraction:

- First, when the recoiling barrel makes contact with the locking block.
- Second, when the barrel first starts to unlock and the extractor shifts on the cartridge.
- Third, when the barrel binds in the locking block and the extractor attempts to dislodge the cartridge.

At each of these points, any mass forward of the extractor spring will apply compressive force (rearward force) to the spring and reduce the pressure on the extractor. Variations in extractor pressure increase the likelihood of the extractor jumping over the rim of the cartridge and leaving the cartridge in the chamber—failure to extract. The extractor is basically a hook that grabs onto the rim of the cartridge. Pressure on the extractor maintains the hook in place. If pressure is reduced just as the cartridge is extracted the extractor may not stay in place. In other words, the mass of the extractor depressor is thrown toward the rear of the firearm away from the extractor as the slide decelerates. As there are significant G forces involved, the mass of the extractor depressor is multiplied many times. It is for this reason that it is critical to keep the mass forward of the spring relatively low.
This compressive force on the extractor spring is further exacerbated by anything that increases the frame's resistance to movement as this increases the rate of deceleration in the slide. Put simply, the harder the frame is to move the more quickly the slide will come to a stop. This means the addition of mass such as tactical lights or metal guide-rods all reduce extractor effectiveness. The effect is also more pronounced with very experienced shooters who take a very high, very firm grip on the weapon. The effect is more pronounced for aftermarket metal frames which tend to have different characteristics than stock frames, or with the addition of tactical lights.
In semi-automatic firearms, the extractor serves to latch onto and remove the shell casing from the chamber after firing. In designs such as the Glock the extractor is a claw-like catch that hooks into a depression in the base of the cartridge and pulls the round out of the chamber. Generally, there is a spring (or springs) that provides the tension to keep the extractor claw in the groove of the cartridge. If there is insufficient pressure on the extractor to keep it in the groove of the cartridge the extractor will slip off of the cartridge rather than pulling it free from the chamber. This is what is generally known as a “failure to extract” malfunction or FTE. As extraction takes place during recoil it is important that the violent recoil of the firearm does not inadvertently reduce the pressure on the extractor when it is needed most. Additionally, as extractors are typically spring powered it is important that they are designed to reduce their tendency to ‘bounce’ and loose contact with the cartridge.
The present invention improves the performance of the Glock by significantly reducing the effect of recoil on the extractor depressor plunger assembly. These positive effects are accomplished by the following:
A. designing a new longer piece (standoff bar) of greater mass.
B. redistributing the mass from the front of the assembly to the rear.
C. designing a new shorter piece (extractor depressor plunger).
D. increasing total mass of the assembly.
The attributes of these redesigned components will be discussed in the following sections.
Referring to FIG. 1B, the three components of the high reliability extractor depressor assembly 10 are shown: namely the standoff bar 20, the extractor depressor plunger 40 and the spring 30. One of the major attributes of the high reliability extractor depressor assembly 10 is that the mass of the HRED is significantly greater than that of the stock extractor depressor assembly. This is done in order to increase extractor tension during the rearward acceleration phase of recoil without increasing spring weight. When the slide starts to accelerate to the rear, the weight of this bar pushes against the extractor helping seat it fully just before the actual extraction takes place.
FIG. 1A shows the three components of the HRED as they joined together as they would be installed into a handgun.
At this point, it is instructive to describe the mechanics of the extraction process. When the slide first begins to accelerate toward the rear, the mass of the entire extractor depressor plunger assembly bears forward against the extractor. Ideally, you want an extremely heavy assembly when the slide is accelerating to the rear to maximize seating pressure on the extractor. However, when the slide starts to decelerate while moving to the rear, that same mass works the other way and tries to move away from the extractor. To counter this, the design of the instant invention moves the majority of the mass rearward of the spring.
In order to better understand this concept, it is instructive to think of a person riding in a car attempting to keep pressure against the backrest of the seat on which he or she is sitting during acceleration, normal at speed travel, and heavy braking. In this analogy the backrest represents the extractor where we want pressure applied. When the car accelerates a person's mass helps push them against the backrest. Applying this analogy to a standard Glock there is a spring in front of the person (between them and the dash) helping to keep pressure against the back of the seat. This works fine while accelerating. However, the situation is somewhat different when the brakes are applied heavily (or “slammed”). When the brakes are slammed, the person's weight presses forward and compresses the spring, which takes pressure off of the backrest behind them. Even if the seatbelt stops their forward movement they may have already moved far enough forward that their back is no longer touching the backrest behind them. Similarly, once the gun is fired, the forces inherent to the firing process would tend to relieve pressure on the extractor and cause the mechanism to become unstable and more susceptible to jamming and instability. The present design differs from the standard design in that the spring is located behind the person (between their back and the seat) rather than in front of them. In this case when the car accelerates the weight of the person helps push the spring more firmly into the back of the seat, so during acceleration this works just as well as the typical design. However, when the brakes are slammed with the spring located between the backrest and person's back, the spring will continue to apply pressure to the backrest even if the person leans forward into the seatbelt. In the standard design the mass of the person beneficial during acceleration, but a detriment during deceleration, so a compromise of lighter mass is generally used. With the present design the person's mass remains a benefit during acceleration, but has no negative effect during deceleration. As a result, a higher mass can be used to maximize the benefit during acceleration.
Referring to FIG. 4B, the standoff bar 20 of the instant invention represents a significant departure from that of a standard Glock. The standoff bar incorporates the following attributes: it has a maximum diameter 26 for the entire active length 22 of the piece. This is done to ensure the maximum amount of mass in the rear part of the high reliability extractor depressor assembly 10. In addition, the consistent diameter of the standoff bar shaft allows the standoff bar to be trimmed to various lengths by grinding or other methods in order to customize spring tension.
FIG. 4B also shows the spring retainer 21 of the standoff bar 20 which allows the spring 30 to be firmly seated and held onto the standoff bar. The spring retainer 21 can vary in size between 0.080 and 0.140 inches long and a diameter of between 0.095 and 0.0105 inches.
FIG. 4A shows the redesigned extractor depressor plunger 40 which incorporates the following attributes:
A. the length of the bearing nose 46 was increased slightly to provide greater resistance to canting.
B. The spring retention section 48 of the bearing spring guide was widened. This geometry ensures that the first coil of the spring which is wound around the bearing has a slightly greater diameter than the bearing diameter. As a result the first coil of the spring makes solid contact with the raceway. This effectively lengthens the nose of the bearing (reducing canting) without adding mass. This also shields the sharp edge of the bearing seat from the raceway.
C. the bearing seat 47 was slightly back cut to reduce any gap and improve fit between the spring seat and the spring itself. This is done to reduce the likelihood of binding in the raceway.
D. finally, the geometry of the spring guide 42 was designed to limit canting to approximately 1 degree, so even if other measures fail, the spring itself will hold the bearing in the proper position.
Perhaps the most significant improvement of improved extractor depressor plunger assembly is the mass distribution of the new assembly with respect to the stock assembly. Whereas the stock assembly has the longer (high mass) component forward (towards the muzzle) of the actuating spring and the shorter (low-mass) component to the rear of the spring, the improved extractor depressor plunger assembly has the long component to the rear of the spring and the shorter piece toward the front.
FIG. 2 shows a perspective view of the assembled HRED 10 in relation to the rear of the slide 50.
FIG. 3 shows a rear view of the slide 50 including the extractor depressor plunger raceway 65 into which the assembled HRED 10 is inserted when the Glock is fully assembled.
FIG. 5 shows a further rear view of the slide 50 with the HRED inserted into the extractor depressor plunger raceway 65. Also shown is the slide cover plate 53 which slides into place in the opening in the rear of the slide 50 and holds the FIRED in place in the raceway during operation of the handgun.
The approximate size and geometry of the various components in the present invention are as follows:

- a. The standoff bar 20 is between 1.30 inches and 1.80 inches long with the optimal length being approximately 1.66 inches. The diameter of the bar is between 0.13 inches and 0.16 inches with the optimal diameter being approximately 0.15 inches.
- b. The extractor depressor plunger 40 is between 0.25 inches and 0.75 inches long with the optimal length being approximately 0.48 inches. The maximum diameter of the extractor depressor plunger is between 0.13 inches and 0.16 inches with the optimal diameter being approximately 0.15 inches. The forward end of the plunger is slightly rounded or domed and is approximately the same diameter as the standoff bar. Approximately one third of the way along the length of the plunger, the diameter is reduced by 30 to 40 percent with a 36 percent reduction being optimal in order to form the seat for the forward end of the spring. Approximately half way along the longitudinal axis, the plunger is further beveled to reduce the diameter to about half of its original diameter. This reduced diameter remains until the end of the plunger at which point the end is slightly rounded.
- c. The extractor depressor plunger spring 30 is between 0.60 and 0.80 inches long in the rest position and between 0.41 and 0.45 inches long in the fully compressed position. The diameter of the spring is approximately 0.15 inches.
- d. The standoff bar 20 is rounded at the rear end is structured to accommodate the spring and also provide a mechanical stop for the spring at the front end.

The standoff bar can be made of any strong rigid material with a high density, good heat tolerance and galvanic compatibility with the rest of the firearm. The spring can be made of stainless steel, various carbon steels, titanium, or composite with the preferred material being stainless steel. Finally, the plunger can be made of any strong hard material with good heat and abrasion resistance with a martensitic grade of stainless steel being the preferred material.

Claims

1. A high reliability extractor depressor for use in handguns comprising

a. a standoff bar

b. an extractor depressor plunger spring and

c. an extractor depressor plunger.

2. A high reliability extractor depressor as in claim 1 where the extractor depressor plunger is located toward the front of the extractor depressor raceway in the slide of a handgun.

3. A high reliability extractor depressor as in claim 1 where the standoff bar is located toward the rear of the extractor depressor raceway in slide of a handgun.

4. A high reliability extractor depressor as in claim 1 where the extractor depressor spring separates the standoff bar from the extractor depressor plunger.

5. A standoff bar for use in high reliability extractor depressors for handguns where the length of the bar is between 1.30 inches and 1.80 inches long and the diameter of the bar is between 0.13 inches and 0.16 inches.

6. A standoff bar as in claim 5 which is slightly rounded at rear end and contains a spring retainer at the inner end to accommodate a spring.

7. A standoff bar as in claim 5 where the length is 1.66 inches and the diameter of the bar is 0.15 inches.

8. A standoff bar as in claim 5 which is made of a strong rigid material with a high density, good heat tolerance and galvanic compatibility with the rest of the firearm.

9. A standoff bar as in claim 5 which is made of stainless steel.

10. An extractor depressor plunger for use in high reliability extractor depressors for handguns where the length of the plunger is between 0.25 inches and 0.75 inches long.

11. An extractor depressor plunger as in claim 10 which is slightly rounded at the front end and contains a spring retainer at the inner end to accommodate a spring.

12. An extractor depressor plunger as in claim 10 where the length is 0.48 inches and the diameter of the bar is 0.15 inches.

13. An extractor depressor plunger as in claim 10 where the bearing seat is reduced.

14. An extractor depressor plunger as in claim 10 which is made of stainless steel.

15. An extractor depressor plunger as in claim 10 where the diameter is between 0.15 and 0.155 inches and the length is between 0.15 and 0.20 inches.

16. An extractor depressor plunger as in claim 10 where the spring retention section is between 0.05 and 0.1 inches.

17. An extractor depressor plunger as in claim 10 where the spring retention section is chamfered.