U.S. patent number 3,561,543 [Application Number 04/797,537] was granted by the patent office on 1971-02-09 for rotary impact wrench mechanism.
This patent grant is currently assigned to Ingersoll-Rand Company. Invention is credited to Otmar M. Ulbing.
United States Patent |
3,561,543 |
Ulbing |
February 9, 1971 |
ROTARY IMPACT WRENCH MECHANISM
Abstract
A rotary impact wrench mechanism including a hammer rotating
around an anvil with both having cooperating cam surfaces for
periodically engaging shoulders on the hammer and anvil to cause
impacts. The hammer is connected to the wrench motor by a joint
that allows the hammer to move transversely following impact to
cause the hammer to automatically disengage itself from the anvil
and to start further rotary movement.
Inventors: |
Ulbing; Otmar M. (Lisle,
NY) |
Assignee: |
Ingersoll-Rand Company (New
York, NY)
|
Family
ID: |
25171118 |
Appl.
No.: |
04/797,537 |
Filed: |
February 7, 1969 |
Current U.S.
Class: |
173/93.5 |
Current CPC
Class: |
B25B
21/02 (20130101) |
Current International
Class: |
B25B
21/02 (20060101); B25b 021/02 () |
Field of
Search: |
;173/93.5 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Purser; Ernest R.
Claims
I claim:
1. A rotary impact wrench mechanism comprising:
a rotary driving member;
a rotary driven member;
an anvil element having an anvil impact surface and connected to
said rotary driven member;
a hammer element mounted to rotate adjacent said anvil and having a
hammer impact surface adapted to engage said anvil impact surface
periodically as said hammer element rotates, said hammer element
being connected to said rotary driving member;
said members being connected to their respective elements by a
means which prevents relative rotary movement therebetween;
cam means operative to relatively position said anvil and hammer
impact surfaces to cause said surfaces to periodically engage;
and
one of said anvil and hammer elements being connected to its member
by a yieldable joint allowing said one element to move transversely
relative to the other element to cause the two impact surfaces to
automatically disengage each other following each impact.
2. The mechanism of claim 1 wherein:
said hammer element includes an axial bore surrounding said anvil
element;
said hammer impact surface being a radially extending shoulder
projecting inwardly from the wall of said bore; and
said anvil impact surface being a radially extending shoulder
projecting outwardly from said anvil element.
3. The mechanism of claim 2 including:
means resiliently holding said hammer and anvil elements in
substantially parallel planes while allowing them to move
transversely relative to each other.
4. The mechanism of claim 3 wherein:
said means resiliently holding said hammer and anvil elements in
substantially parallel planes is a hollow case substantially
surrounding said hammer and anvil and containing a spring disposed
between one of said elements and said case and positioned
substantially coaxially with said elements.
5. A rotary impact wrench comprising:
motor driving a rotary driving member;
a rotary spindle member adapted to drive fasteners;
an anvil element having an anvil impact surface and connected to
said rotary spindle member;
a hammer element connected to said rotary driving member and
mounted to rotate adjacent said anvil, said hammer element having a
hammer impact surface adapted to engage said anvil impact surface
periodically as said hammer rotates;
said members being connected to their respective elements by a
means which prevents relative rotary movement therebetween;
cam means operative to relatively position said anvil and hammer
impact surfaces to cause said surfaces to periodically engage to
deliver an impact to said anvil; and
one of said anvil and hammer elements being connected to its member
by a yieldable joint allowing said one element to move transversely
relative to the other element to cause the two impact surfaces to
automatically cam each other apart under the application of torque
from said motor following each impact.
6. A rotary impact wrench comprising:
a motor;
a rotary driving member connected to said motor;
a rotary driven member adapted to drive a fastener;
an anvil element connected to said rotary driven member and having
an anvil impact surface;
a hammer element mounted to rotate adjacent said anvil connected to
said rotary driving member, said hammer element having a hammer
impact surface adapted to engage said anvil impact surface
periodically as said hammer element rotates;
said members being connected to their respective elements by a
means which prevents relative rotary movement therebetween;
means holding said anvil and hammer elements together to maintain
them in parallel planes while they rotate;
cam means operative to relatively position said anvil and hammer
impact surface to cause said surfaces to periodically engage;
and
one of said anvil and hammer elements being connected to its member
by a joint allowing said one element to move transversely relative
to the other element to cause the two impact surfaces to
automatically disengage each other following each impact.
7. A rotary impact wrench mechanism comprising:
a hammer element connected to a rotary driving member;
an anvil element connected to a rotary driven member;
said members being connected to their respective elements by a
means which prevents relative rotary movement therebetween;
one of said elements having a bore that receives and rotates around
the other element;
said one element including a pair of radially extending steps or
shoulders located within said bore, spaced substantially
diametrically from each other and facing in opposite rotary
directions; and
said other element including a pair of radially extending steps or
shoulders spaced substantially diametrically from each other and
facing in opposite rotary directions.
8. The mechanism of claim 7 wherein:
said pair of shoulders on said one element are interconnected by a
cam lobe surface projecting radially inwardly into the bore;
and
said pair of shoulders on said other element are interconnected by
a cam lobe surface projecting radially outward from said other
element;
said cam lobe surfaces being adapted to interengage to move said
elements periodically into impact position as said hammer element
rotates relative to said anvil element.
9. The mechanism of claim 8 wherein:
said cam lobe surfaces are arcuate surfaces.
10. The mechanism of claim 9 wherein:
one of said members is connected to its element by a joint allowing
that element to move transversely relative to the opposite
element.
11. The mechanism of claim 8 including:
means resiliently holding said elements in substantially parallel
planes and holding their axes parallel to each other while allowing
them to move transversely relative to each other.
Description
BACKGROUND OF INVENTION
This invention relates to a power-operated rotary impact wrench for
applying rotary or angular impacts to fasteners such as threaded
nuts, bolts, etc. In particular, this invention relates to a rotary
impact wrench mechanism for changing the rotating torque of a
rotary motor, such as an air-driven motor, to a series of rapid
rotary impacts which can be applied to a threaded nut for either
driving it tight or for removing it.
Most rotary impact mechanisms in use today contain an anvil adapted
to be connected to a wrench socket and a hammer rotated by a motor.
The hammer is alternately engaged and disengaged from the anvil,
being engaged to impact the anvil, thereafter being disengaged from
the anvil to gather rotary speed again, prior to striking another
impact to the anvil. Various means are used for accomplishing this
alternate engagement and disengagement between the anvil and
hammer.
One well known rotary impact wrench mechanism used to day is known
as the "swinging weight" mechanism and is disclosed in the U.S.
Pat. No. 2,285,638 to Amtsberg. This mechanism uses a pair of
diametrically opposed tilting hammer dogs which rotate around a
lobed anvil and are cammed into an impact position with the lobes
or jaws on the anvil by engagement with the anvil. The hammer dogs
are released by the cams on the anvil immediately before impact and
means is provided for applying a drive torque to the dogs to cause
them to rotate to a disengaging position following an impact.
Conventional "swinging weight" mechanisms require a separate cam
system utilizing motor torque to declutch the impact jaws following
impact. This requirement complicates these mechanisms and increases
their manufacturing costs. The prior art has attempted to eliminate
the cam system for declutching by using springs but springs wear
out quickly and are limited to low speeds for satisfactory
operation, thereby making it necessary to reduce the speed of the
tool motor by using gearing.
Another disadvantage of the conventional "swinging weight"
mechanism is that it often rebounds after impact and strikes a blow
on its reverse stroke, which is very undesirable because not only
is it inefficient, but it is acting in the reverse direction.
SUMMARY OF INVENTION
The principal object of this invention is to provide a rotary
impact wrench mechanism which eliminates the need for a separate
cam system or springs for declutching the impact jaws following
impact.
Other important objects are: to provide an extremely simple rotary
impact wrench mechanism which comprises very few elements thereby
rendering it relatively economical to manufacture and increasing
its reliability; to provide a simple impact mechanism which has a
substantially reduced amount of rebound following impact; to
provide a rotary impact wrench mechanism which eliminates the
impacting of blows in the reverse direction on rebound; and to
provide a rotary impact wrench mechanism which does not contain a
separate cam system or springs for declutching and which can be
rotated at conventional motor speeds.
In general, the foregoing objects are attained in a rotary impact
mechanism including a driving member driving a hammer element, a
driven member driven by an anvil element, cam means to relatively
position the hammer and anvil impact surfaces or shoulders to cause
said surfaces or shoulders to periodically engage and means
interconnecting one of the hammer and anvil elements to its member
by a yieldable joint allowing the one element to move transversely
relative to the other element to cause the two impact shoulders to
automatically disengage following each impact.
BRIEF DESCRIPTION OF DRAWINGS
The invention is described in connection with the accompanying
drawings wherein:
FIG. 1 is an axial section of an impact wrench containing an impact
mechanism embodiment of this invention;
FIGS. 2 to 5 are sequential sections taken on the line 2-2 in FIG.
1 and showing the impact mechanism in various positions at and
following the striking of an impact blow;
FIG. 6 is a fragmentary axial section showing a second embodiment;
and
FIG. 7 is a section taken on line 7-7 in FIG. 6.
DESCRIPTION OF PREFERRED EMBODIMENT
The rotary impact wrench 1 shown in FIG. 1 conventionally includes
a casing 2 including a nose portion 3, a motor portion 4 and a
handle portion 5. The nose portion 3 carries a spindle 6 projecting
from its front end, the motor portion 4 houses an air motor having
a drive shaft 7 and the handle portion 5 carries an operating
trigger 8 and an inlet passage 9 for feeding air to the motor. The
spindle 6 carries flats 10 adapting it to be attached to a
conventional wrench socket (not shown). All of the foregoing
structure is conventional in the rotary impact wrench art.
The motor shaft 7 is connected to the wrench spindle by a novel
rotary impact clutch 12 which is the subject of this invention. In
general, the clutch 12 includes a hammer 14 rotating around an
anvil 15. The hammer 14 is driven by the motor shaft 7 and the
anvil 15 is integrally fixed to the spindle 6.
The anvil 15 includes a semicircular enlargement or cam lobe 16
forming a pair of diametrically located and extending anvil impact
surfaces or shoulders 17 and 18. The hammer has a bore 20 that has
a cross section similar to that of the anvil 15, except that it is
somewhat larger. The bore 20 includes an internal cam lobe 21 of
reduced radius which is joined to the remainder of the bore 20 by a
pair of diametrically located and radially extending hammer impact
surfaces or shoulders 22 and 23. The bore 20 and internal cam lobe
21 are sized sufficiently larger than the anvil 15 so that when one
set of anvil and hammer impact shoulders 17 and 22 approach each
other, the other set of impact shoulders 18 and 23 can rotate past
each other with a slight clearance.
The foregoing structure is self-camming. That is, it cams the
impact shoulders into impact position once during each rotation of
the hammer 14 about the anvil 15. This can be seen in FIG. 2
wherein the hammer 14 is rotating in a clockwise direction and the
internal cam lobe 21 of the hammer bore 20 has just completed
riding on the external cam lobe 16 on the anvil 15. The engagement
between the cam lobes 16 and 21 forces the hammer impact shoulder
22 into a position to impact the anvil impact shoulder 17.
The anvil 15 and hammer 14 are surrounded by a cup-shaped case 28
that normally rotates with the hammer 15. The case 28 includes a
rear annular flange 29 that projects inwardly in back of the hammer
14 and a annular flange 30 that projects inwardly in front of the
hammer. A belleville spring 31 is disposed between the hammer 14
and the rear flange 29 and a large washer 32 is positioned between
the anvil 15, hammer 14 and the front flange 30. The case 28 is
deformed to form the flanges 29 and 30 while the surrounded
elements, 14, 15, 31 and 32 are located within the case 28. The
case 28 locks the hammer 14 and anvil 15 in parallel positions at
all times (the axes of the hammer 14 and anvil 15 remain parallel)
while allowing the hammer 14 to slide or move transversely relative
to the anvil 15.
The hammer 14 is driven by the motor shaft 7 through a yieldable
connection 35 that allows the hammer 14 to move transversely in any
radial direction relative to the anvil 15. In FIG. 1, this
yieldable connection 35 takes the form of a drive bar 36 loosely
located in the hollow drive shaft 7 and having a universal joint
connection at both ends, one universal joint 37 being at the rear
end of the hammer 14 and the other universal joint 38 being at the
rear end of the drive shaft 7. Each universal joint 36 and 37
includes a ball 39 fixed on the end of the drive bar 36 and a
diametrical located pin 40 projecting from both sides of the ball
39 and seating in notches provided respectively in the drive shaft
7 and the hammer 14.
OPERATION
In describing the operation of the impact wrench 1, it is assumed
that the operator has placed a socket on the spindle 6 and has
positioned the socket on a fastener to be driven. When the motor is
first started, the fastener is continuously rotated during its
rundown, without impacting due to the frictional engagement between
the hammer 14 and anvil 15 caused by the belleville spring 31. As
soon as the fastener begins tightening, the torque load on the
spindle 6 will rise and cause the wrench to begin impacting.
Impacting begins as soon as the hammer 14 begins rotating relative
to the anvil 15.
Looking at FIG. 2, the hammer 14 is rotating in a clockwise
direction and the hammer impact shoulder 22 has impacted the anvil
impact shoulder 17. The hammer 14 was forced to move transversely
into the impact position by the internal hammer cam lobe 21 riding
on the anvil cam lobe 16. The two cam lobes 16 and 21 drop off each
other at substantially the instant of impact.
Looking at FIG. 3, following impact, the torque applied to the
hammer 14 causes the hammer impact shoulder 22 to pivot on the
anvil impact shoulder 17, swinging the hammer transversely
generally downward as shown in FIG. 3. This swinging of the hammer
14 about the anvil will result in two actions both of which act to
disengage the hammer from the anvil. In one case, as the hammer 14
moves transversely downward, relative to the anvil 15, the hammer
impact shoulder 22 is tilted or inclined relative to the anvil
impact shoulder 17, causing the hammer shoulder 22 to act as a cam
and to force the hammer 14 transversely to the left as shown in
FIG. 3 whereby the hammer 14 tends to slide off of the anvil impact
shoulder 17. In addition, the engagement point between the hammer
bore surface 20 and the anvil surface 16 will travel clockwise,
looking at FIGS. 2 to 4, providing a leverage force tending to lift
the hammer shoulder 22 to the left off of the anvil impact shoulder
17. The result of these two actions is to disengage the hammer from
the anvil whereby it begins rotating again until striking another
impact.
FIGS. 4 and 5 show further positions of the hammer 14 as it
accelerates. The internal hammer cam lobe 21 is riding on the anvil
cam lobe 16 and begins to progressively move the hammer 14
transversely into the impact position shown in FIG. 2. This
mechanism impacts once each full revolution.
It can be seen that the yieldable connection 35 between the motor
drive shaft 7 and the hammer 14 allows the hammer 14 to move
transversely in any direction that it may be urged by the
self-camming impact clutch mechanism 12.
When the motor is reversed and the hammer 14 rotates in the
counterclockwise direction, looking at FIGS. 2 to 5, the impact
shoulders 18 and 23 will periodically engage to deliver impacts to
the anvil. Otherwise, the impact clutch mechanism 12 will operate
in the same manner as above-described.
The fact that the impact clutch 12 automatically cams the clutch
into disengagement following impact reduces the amount of rebound
of the hammer 14, reducing the possibility of a reverse impact
occurring on rebound.
FIGS. 2 to 5 illustrate the hammer 14 as having a cam lobe 21 that
is concentric with the hammer bore 20. This is not always true as
applicant has found that the lobe 21 can be nonconcentric to the
bore 20. In addition, the anvil lobe 16 can be nonconcentric with
the remainder of the anvil surface.
SECOND EMBODIMENT - FIGS. 6 AND 7
The second embodiment differs from the first embodiment by having a
different type of yieldable joint 45 between the hammer 14 and
motor drive shaft 7. The yieldable joint includes an intermediate
coupling disc 46 having diametrically extending keys 47 on its
opposite faces extending at right angles to each other and fitting
in corresponding notches or kerfs 48 provided in the hammer 14 and
the front end of the drive shaft 7. This joint 45 allows the hammer
to move in any transverse direction relative to the hammer 14.
Although plural embodiments of the invention are illustrated and
described, it should be understood that the invention is not
limited thereto and that various changes may be made in the design
and arrangement of the parts without departing from the spirit and
scope of the invention as set forth in the claims.
* * * * *