U.S. patent number 3,847,229 [Application Number 05/363,711] was granted by the patent office on 1974-11-12 for portable impact wrench.
This patent grant is currently assigned to Robert Bosch GmbH. Invention is credited to Jorg Falchle, Hubertus Karl, Wolfgang Schmid, Karl Wanner.
United States Patent |
3,847,229 |
Wanner , et al. |
November 12, 1974 |
PORTABLE IMPACT WRENCH
Abstract
A portable impact wrench wherein a crank assembly reciprocates a
cylinder which propels an impeller against the rear end of a tool
holder in response to each of its forward strokes. The tool holder
is rotatable stepwise in a single direction by a group of three
sleeves the first of which is rotatable on but moves lengthwise
with the cylinder and is normally held against rotation by a claw
clutch one element of which is fixed to the housing. An
intermediate sleeve has inclined teeth or threads meshing with
complementary threads or teeth of the first sleeve so that the
intermediate sleeve rotates back and forth in response to rearward
and forward movements of the first sleeve. A third sleeve is
rotatable in the housing and is connected with the intermediate
sleeve by a one-way clutch. The tool holder is movable axially in
but shares all angular movements of the third sleeve. Another
element of the claw clutch is biased against the fixed element by a
helical spring and has axially parallel teeth mating with
complementary teeth of the first sleeve so that the latter can move
axially but is normally held against rotation. The bias of the
spring may be changed, terminated and/or assisted by a projection
which can be manipulated by hand so that the user can apply his
muscle power in order to increase the resistance of the other
clutch element to disengagement from the fixed clutch element when
the tool holder resists rotation with the third sleeve. When the
claw clutch is disengaged and the cylinder continues to move
forwardly and rearwardly, the intermediate sleeve rotates the first
sleeve.
Inventors: |
Wanner; Karl (Echterdingen,
DT), Schmid; Wolfgang (Plattenhardt, DT),
Karl; Hubertus (Bernhausen, DT), Falchle; Jorg
(Bempflingen, DT) |
Assignee: |
Robert Bosch GmbH (Stuttgart,
DT)
|
Family
ID: |
5847927 |
Appl.
No.: |
05/363,711 |
Filed: |
May 24, 1973 |
Foreign Application Priority Data
|
|
|
|
|
Jun 16, 1972 [DT] |
|
|
2229388 |
|
Current U.S.
Class: |
173/48; 173/118;
173/110; 173/122 |
Current CPC
Class: |
B25D
16/00 (20130101); B25D 2211/003 (20130101); B25D
2211/068 (20130101) |
Current International
Class: |
B25D
16/00 (20060101); E21B 6/00 (20060101); E21B
6/06 (20060101); B25d 011/04 () |
Field of
Search: |
;173/47,48,110,111,109 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Purser; Ernest R.
Assistant Examiner: Pate, III; William F.
Attorney, Agent or Firm: Striker; Michael S.
Claims
What is claimed as new and desired to be protected by Letters
Patent is set forth in the appended claims:
1. In a portable power tool, particularly in an impact wrench or
drill, a combination comprising a housing; drive means provided in
said housing and including an output member movable forwardly and
rearwardly; a tool holder rotatably and reciprocably mounted in
said housing in front of said output member; impeller means
provided in said housing and operative to strike against said tool
holder in response to forward movements of said output member; and
means for normally rotating said tool holder in response to forward
movements of said output member, including an input element
rotatably surrounding and movable with said output member, blocking
means provided in said housing for normally holding said input
element against rotation, an intermediate element rotatably mounted
in said housing, said elements having tubular portions telescoped
into each other and provided with mating inclined teeth or threads
so that the forward and rearward movements of said input element
result in rotation of said intermediate element in opposite
directions, an output element rotatably mounted in said housing,
said tool holder being movable axially relative to and being
rotatable with said output element, and one-way clutch means
provided between said intermediate element and said output element
to rotate said tool holder by way of said output element in
response to forward movements of said input element.
2. A combination as defined in claim 1, wherein said drive means
further comprises an electric motor having a rotor and a crank
assembly connected between said rotor and said output member for
converting the rotary movements of said rotor into reciprocatory
movements of said output member.
3. A combination as defined in claim 1, wherein said blocking means
comprises a clutch having a first clutch element rigid with said
housing, a second clutch element rotatably and axially movably
mounted in said housing, said clutch elements having complementary
male and female portions, and means for biasing said second clutch
element against said first clutch element, said second clutch
element having first axially parallel teeth and said input element
having second axially parallel teeth mating with said first teeth
so that said input element is rotatable with said first clutch
element relative to said output member only when said second clutch
element is disengaged from said first clutch element.
4. A combination as defined in claim 3, wherein said means for
biasing comprises resilient means.
5. A combination as defined in claim 3, wherein said means for
biasing comprises a manually operable biasing device.
6. A combination as defined in claim 5, wherein said means for
biasing further comprises prestressed resilient means and said
biasing device comprises means for changing the stressing of said
resilient means and for disengaging said resilient means from said
second clutch element.
7. A combination as defined in claim 3, wherein said male portions
of said clutch elements comprise conical claws.
8. A combination as defined in claim 7, wherein each of said clutch
elements is an annulus and said annuli having adjacent end faces
provided with said claws.
9. A combination as defined in claim 8, wherein said means for
biasing comprises a prestressed spring provided in said housing and
arranged to normally bear against said second clutch element so as
to urge the claws thereof into engagement with the claws of said
first clutch element, and a biasing device having a projection
movable relative to said housing to thereby change the stressing of
said spring or to disengage said spring from said second clutch
element.
10. A combination as defined in claim 9, wherein said biasing means
further comprises a handle which is accessible from without said
housing and is operable by hand to thereby move said projection
relative to said housing.
11. A combination as defined in claim 9, wherein said projection is
movable by hand to at least one position in which the force
furnished by the hand maintains the claws of said second clutch
element in engagement with the claws of said first clutch
element.
12. A combination as defined in claim 11, wherein said biasing
device further comprises a handle rotatably mounted in said housing
and being operable by hand to thereby move said projection relative
to said housing and to maintain said projection in said one
position.
13. A combination as defined in claim 12, wherein said biasing
device further comprises at least one stop provided in said housing
and cooperating with locking means provided on said handle to
maintain said handle in a selected angular position, said handle
being movable radially of said clutch elements to thereby disengage
said locking means from said stop and further comprising resilient
means yieldably opposing the movement of said handle radially of
said clutch elements in a direction to disengage said locking means
from said stop.
Description
BACKGROUND OF THE INVENTION
The present invention relates to portable power tools in general,
and more particularly to improvements in portable impact wrenches,
especially electrically powered impact wrenches wherein the tool
holder is movable axially and is also rotatable during penetration
into a workpiece or during the application or removal of a nut,
screw, bolt or the like.
It is already known to provide a portable impact wrench with a
drive wherein an electric motor operates a crank assembly which
reciprocates an output member. The latter transmits motion to an
axially movable impeller which strikes against the tool holder
during or in response to each forward stroke of the output member.
The means for rotating the tool holder includes a first sleeve
which rotatably surrounds the output member, a one-way clutch which
transmits torque from the first sleeve to the tool holder while the
first sleeve rotates in a given direction, and a device which
rotates the first sleeve in response to reciprocation of the output
member. This device has a second sleeve which is provided with
inclined teeth or threads mating with complementary teeth or
threads on the first sleeve. The second sleeve is rigid with or
forms part of the output member and tends to rotate the output
member whenever the first sleeve rotates whereby the parts of the
crank assembly must stand very high torsional stresses resulting in
pronounced wear and relatively short useful life of the drive. In
other words, the drive must take up and stand all such stresses
which develop when the tool in the tool holder is rotated against
the resistance of a material in which the tool rotates or against
resistance of a nut, bolt or screw which must be driven home or
removed. The torsional stresses to which the drive is subjected
increase very substantially when the tool jams in or on a workpiece
while the output member continues to move back and forth and to
cause the impeller to strike against the tool holder. Furthermore,
the just described impact wrenches are likely to injure the
operator, especially a weak person who is incapable of holding the
housing with a requisite force while the tool offers a very high
resistance to rotation with its holder.
It was already proposed to connect the second sleeve with the
reciprocable output member of the drive by means of a safety clutch
which becomes disengaged in response to a preselected maximum
resistance which the tool holder offers to rotation during forward
movement of the output member. When the safety clutch is
disengaged, the impact wrench operates simply as a hammer wherein
the tool moves axially in but does not rotate relative to the
housing as long as the safety clutch remains disengaged. As a rule,
the safety clutch is designed or adjusted to become disengaged in
response to a relatively low torque to thus insure that the impact
wrench can be properly manipulated by a relatively weak person,
e.g., an adolescent or a tinker using the power tool once an a
while in his basement workshop or garage. The lower the torque
which is needed to disengage the safety clutch, the more frequent
is the disengagement of this clutch so that its parts undergo
excessive wear. Moreover, the drive is still called upon to take up
the torsional stresses because the safety clutch is provided
between the reciprocable output member and the second sleeve.
SUMMARY OF THE INVENTION
An object of the invention is to provide a portable impact wrench,
especially an impact wrench which can be used as a drill,
screwdriver and/or for analogous purposes, and whose drive
comprises an electric motor serving to transmit motion to a
reciprocable output member of the drive by way of a crank assembly,
wherein the torque which develops when the tool and its holder
rotate or resist rotation need not be taken up by the drive so that
the latter is subjected to less pronounced wear than in heretofore
known power tools.
Another object of the invention is to provide a portable impact
wrench whose operation is safer than that of conventional impact
wrenches and which is more versatile than the aforediscussed
conventional wrenches.
A further object of the invention is to provide in a portable
impact wrench novel and improved means for rotating the tool in
stepwise fashion and novel and improved means for preventing damage
to the impact wrench when its tool jams or is held against angular
movement for other reasons.
An additional object of the invention is to provide a portable
impact wrench with novel and improved means for selecting the
resistance which the tool holder must offer to rotation in order to
deactivate the torque transmitting means for the tool holder.
Still another object of the invention is to provide a portable
impact wrench with a device which enables the operator to
determine, at his will and with his own muscle power, the exact
magnitude of resistance which the tool holder must offer to
rotation in order to terminate its angular movement while the
output member of the drive continues to actuate the impeller which
propels the tool forwardly.
A further object of the invention is to provide a portable impact
wrench wherein the torque transmitting connection between the drive
and the tool holder can be established, adjusted and/or terminated
at the will of the operator and while the impact wrench is in
actual use.
The invention is embodied in a portable impact wrench, drill,
screwdriver or the like which comprises a housing, drive means
provided in the housing and including a driving member or output
member which is movable forwardly and rearwardly (preferably in
response to rotation of the rotor of an electric motor which moves
the output member by way of a crank assembly), a tool holder which
is rotatably and reciprocably mounted in the housing in front of
the output member, impeller means provided in the housing and being
operative to strike against an anvil at the rear end of the tool
holder in response to forward movements of the output member, and
torque transmitting means for normally rotating the tool holder in
response to forward movements of the output member.
The torque transmitting means comprises an input element which
rotatably surrounds and is movable with the output member forwardly
and rearwardly, blocking means provided in the housing for normally
holding the input element against rotation (the blocking means
preferably comprises a claw clutch a first element of which is
fixedly mounted in the housing and a second element of which is
provided with axially parallel teeth in mesh with complementary
teeth of the input element so that the latter can move axially of
the second clutch element, and biasing means including one or more
springs and/or a manually held part for holding the second clutch
element in engagement with the first clutch element), an
intermediate element which is rotatably mounted in the housing and
has an annulus of inclined teeth or threads mating with
complementary inclined teeth or threads of the input element so
that the intermediate element rotates in opposite directions in
response to forward and rearward movements of the output member as
long as the blocking means holds the input element against
rotation, an output element which is rotatably mounted in the
housing in such a way that the tool holder can move axially of but
cannot rotate relative to the output element, and one-way clutch
means provided between the intermediate element and the output
element. The blocking means allows the intermediate element to
rotate the input element relative to the output member of the drive
means when the tool holder offers such resistance to rotation that
the blocking means permits the input element to rotate on the
output member.
Since the blocking means normally establishes a connection between
the housing and the input element, the drive means is not required
to take up any torsional stresses irrespective of whether the tool
holder rotates or is held against rotation, for example, due to
jamming of the tool in or on a workpiece.
The impact wrench preferably further comprises a device for
changing the bias of the aforementioned spring or springs; such
device may constitute or include the aforementioned manually held
part so that the operator can apply his muscle power in order to
assist the spring or springs in preventing disengagement of the
safety clutch until the resistance which the tool holder offers to
rotation reaches a value which might render further operation of
the impact wrench dangerous.
The novel features which are considered as characteristic of the
invention are set forth in particular in the appended claims. The
improved impact wrench itself, however, both as to its construction
and its mode of operation, together with additional features and
advantages thereof, will be best understood upon perusal of the
following detailed description of certain specific embodiments with
reference to the accompanying drawing.
BRIEF DESCRIPTION OF THE DRAWING
FIG. 1 is a fragmentary partly elevational and partly longitudinal
vertical sectional view of a portable impact wrench which embodies
the invention; and
FIG. 2 is a sectional view as seen in the direction of arrows from
the line II--II of FIG. 1.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
The impact wrench of FIG. 1 comprises a housing or support 1
including a handle 1a and a cylindrical barrel 1b. The rear portion
of the housing 1 contains a motor M (e.g., an electric motor)
forming part of a drive which further includes a reciprocable
tubular output member or cylinder 6 movable forwardly and
rearwardly in the barrel 1b. The rotor R of the motor M
reciprocates the cylinder 6 by way of a crank assembly including a
rotary crank arm 5 having a crank pin 5a and a connecting rod 10
which is mounted on the crank pin 5a at one end and the other end
of which is coupled to the rear end of the cylinder 6 by means of a
vertical shaft 9. The shaft 9 is mounted in a rear end wall 11 of
the cylinder 6. The reference character 8 denotes a cylindrical
bore provided in the barrel 1b for the cylinder 6. The latter
comprises a larger-diameter rear portion 7, a smaller-diameter
front portion 15, an a rearwardly and outwardly flaring
intermediate portion 28 between the portions 7 and 15. The cylinder
6 surrounds an impeller 12 having at its rear end a piston 13 which
is reciprocable in the portion 7. The front portion or shank 14 of
the impeller 12 is reciprocable in the smaller-diameter portion 15
of the cylinder 6. The shank 14 can strike against an anvil 60 at
the rear end of a turnable and reciprocable tool holder 19 having a
socket 62 for reception of a suitable tool 20 (e.g., a boring tool,
a screw driver or the like). The piston 13 can move into and out of
register with apertures 16 which are provided in the
larger-diameter portion 7 of the cylinder 6. The chamber 107 in the
portion 7 is then sealed from the atmosphere and its volume
decreases while the cylinder 6 moves forwardly under the action of
the connecting rod 10. The cushion of air which is entrapped in the
chamber 107 urges the impeller 12 forwardly so that the shank 14
bears against the anvil 60 and moves the tool holder 19 and the
tool 20 forwardly with the result that the tip of the tool
penetrates into or moves with a workpiece. For example, the tool
may penetrate into a wall which is to be provided with a hole.
The torque-transmitting means for rotating the tool holder 19 while
the latter moves forwardly (i.e., away from the connecting rod 10)
comprises a sleeve-like output element 22 which allows the tool
holder to move axially but prevents the tool holder from rotating
relative thereto. The output element 22 is rotatable in the barrel
1b and is coupled to an intermediate sleeve-like element 24 by a
one-way clutch 52. The element 24 is rotatable but cannot move
axially in the housing 1. The tool holder 19 moves forwardly when
its anvil 60 is struck by the shank 14 of the impeller 12. The
rearward movement of the tool holder 19 takes place in response to
rebounding of the tool 20 on the adjacent material of the
workpiece.
A sleeve-like input element 26 of the torque transmitting means
surrounds the smaller-diameter portion 15 of the cylinder 6 with a
relatively small clearance. The front end portion of the input
element 26 is coupled to the portion 15 by a ring 27 and the rear
portion of the input element 26 forms a collar which abuts against
the intermediate portion 28 of the cylinder 6. In this way, the
input element 26 invariably shares all forward and rearward
movements of the cylinder 6. The just mentioned flange at the rear
end of the input element 26 has an annulus of axially parallel
external teeth 26a whose root diameter is at least equal to but
preferably at least slightly greater than the outer diameter of the
portion 7. The front end portion of the input element 26 has an
annulus of inclined external teeth or threads 26b which mate with
similarly inclined internal threads or teeth 24b of the
intermediate element 24 which is coupled to the output element 22
by means of the aforementioned one-way clutch 52.
The axially parallel teeth 26a at the rear end of the input element
26 mate with internal teeth 29a of a sleeve-like clutch element 29
which surrounds the portion 7 of the cylinder 6 and whose front end
portion is provided with one or more claws 30 engaging
complementary claws at the rear end of a ring-shaped clutch element
31 fixedly mounted in the housing 1. The claws 30 are normally held
in engagement with the claws of the clutch element 31 by a strong
helical spring 34 which surrounds the portion 7 and reacts against
a split ring 35 in the barrel 1b. The foremost convolution of the
spring 34 bears against an annular retainer 33 which abuts against
the rear end face of the clutch element 29. The reference character
38 denotes a distancing ring which is inserted in front of the
split ring 35 to increase the bias of the spring 34. The distancing
ring 38 can be removed, replaced with a distancing ring of greater
or smaller axial length, or used together with one or more
additional distancing rings 38 of identical or different axial
length. The distancing ring or rings can be installed between the
split ring 35 and the rearmost convolution of the spring 34 and/or
between the foremost convolution of this spring and the retainer
33. The latter resembles a cylindrical sleeve which surrounds the
rear end portion of the clutch element 29. The front end portion of
the clutch element 29 has a collar 36 which is immediately adjacent
to the claws 30 and defines with the front end portion of the
retainer 33 an annular compartment or space 37 for the eccentric
projection or pin 39 of a stud 40 which can be rotated to thereby
change the bias of the spring 34 and hence the force which is
needed to disengage the claws 30 of the clutch element 29 from the
complementary claws of the fixedly mounted clutch element 31. The
stud 40 extends radially of and into the housing 1 and is
surrounded by a cylindrical sleeve 41 the upper end portion of
which meshes with the barrel 1b. The stud 40 can rotate within but
cannot move axially of the sleeve 41 which can be said to
constitute a component part of the housing 1. In order to change
the angular position of the stud 40 and to thereby change the bias
of the spring 34 by way of the projection 39, the user of the
impact tool must manipulate a handle 42 which surrounds the sleeve
41 and is movable angularly with the stud 40. The handle 42 can be
pulled downwardly, as viewed in FIG. 1 (i.e., away from the barrel
1b) by stressing a helical spring 44 which bears against a washer
45 surrounding a threaded stem 40a of the stud and abutting against
a nut 46. When the user exerts a pull in the direction indicated by
arrow A. The spring 44 is compressed and the handle 42 moves
relative to the sleeve 41 and stud 40. At the same time, a locking
bolt 48 of the handle 42 is moved to a level below a fixed stop 49
of the barrel 1b so that the handle 42 is free to turn with the
stud 40 and to thereby change the angular position of the
projection 39 in the annular compartment 37. When the handle 42 is
rotated in a direction to move the projection 39 toward and into
engagement with the collar 36, the sleeve-like clutch element 29 is
held by hand (muscle power) against movement away from the tool
holder 19 and its claws 30 remain in engagement with the claws of
the fixed clutch element 31, i.e., the operator's hand assists the
bias of the spring 34. This insures that each and every forward
stroke of the cylinder 6 normally results in an axial as well as in
an angular displacement of the tool 20. In other words, the user
can hold the handle 42 by hand in such angular position that the
clutch element 29 is held against disengagement from the fixed
clutch element 31 by the spring 34 as well as by that force which
the user applies to hold the projection 39 in engagement with the
collar 36.
If the user decides to rotate the handle 42 in a different
direction, the projection 39 moves toward the retainer 33 and
shifts the latter against the opposition of the spring 34 so that
the claws 30 of the clutch element 29 can become disengaged from
the claws of the fixed clutch element 31. In such angular position
of the handle 42, each forward stroke of the cylinder 6 results in
a mere axial movement of the holder 19 and tool 20. The barrel 1b
is preferably provided with a second stop (not shown) which may be
similar to the stop 49 and against which the locking bolt 48 abuts
when the pin 39 of the stud 40 stresses the spring 34 and allows
the clutch element 29 to become disengaged from the clutch element
31. It is preferred to locate the second stop for the locking bolt
48 in such position that the bolt 48 bears against the second stop
under the action of the stressed spring 34 and cannot automatically
return into engagement with the stop 49. The intermediate element
24 can rotate the tool holder 19 through the one-way clutch 52 and
output element 22 only while the claws 30 of the clutch element 29
engage the claws of the clutch element 31. The apparatus is then
operated as a simple impact hammer without any rotation of the tool
20.
When the clutch element 29 engages the clutch element 31, each
forward and rearward movement of the cylinder 6 results in a rotary
movement of the intermediate element 24 because the inclined teeth
24b mate with the inclined teeth 26b of the input element 26 which
latter moves back and forth with the cylinder 6 and is held against
rotation by the teeth 26a, 29b as long as the claws 30 engage the
claws of the fixed clutch element 31. The extent of angular
movement of the intermediate element 24 is determined by the
inclination of the teeth 26b, 24b. The aforementioned one-way
clutch 52 causes the output element 22 (and hence the tool holder
19 and tool 20) to rotate while the intermediate element 24 rotates
in a first direction (in response to a forward movement of the
cylinder 6). The clutch 52 is ineffective when the intermediate
element 24 rotates in the opposite direction (in response to a
rearward movement of the cylinder 6) so that the material into
which the tool 20 is caused to penetrate then prevents the holder
19 and input element 22 from rotating with the element 24.
The construction of the one-way clutch 52 is shown in FIG. 2. This
clutch is installed in a flange 53 at the rear end of the output
element 22. The flange 53 is provided with tangential bores 54 for
clutch pins 55 which are biased outwardly by helical springs 56 so
that they extend into suitably configurated internal notches 57 of
the intermediate element 24. Each notch 57 is bounded by a surface
57a against which the respective pin 55 bears while the
intermediate element 24 rotates in a first direction
(counterclockwise, as viewed in FIG. 2) whereby the intermediate
element 24 rotates the output element 22 and tool holder 19. Each
notch 57 is further bounded by a suitably inclined surface 57b
along which the respective pin 55 slides while the intermediate
element 24 rotates in a second direction (clockwise, as viewed in
FIG. 2). The springs 56 insure that the pins 55 invariably bear
against the adjacent internal surface of the intermediate element
24. When the intermediate element 24 rotates clockwise, as viewed
in FIG. 2, each pin 55 can move from a preceding notch 57 into the
next-following or further notch. As mentioned above, the housing 1
allows the intermediate element 24 to rotate back and forth but
holds this element against appreciable axial movement.
The hollow front portion or socket 62 of the tool holder 19 which
receives the shank of the tool 20 is reciprocable and rotatable in
an axial bore 61 of the barrel 1b. The rear portion of the tool
holder 19 is movable axially in but cannot rotate relative to the
output element 22. An external annular groove 63 of the tool holder
19 immediately behind the socket 62 receives a portion of an
elastic cushion 64 which is installed in the barrel 1b. The axial
length of the groove 63 determines the extent of axial displacement
of the tool holder 19.
An important advantage of the improved impact wrench is that, when
the tool 20 jams in the material of the workpiece, the torque is
transmitted to the housing 1 by way of the input element 26, clutch
element 29, claws 30, the corresponding claws of the clutch element
31 and clutch element 31. Thus, the cylinder 6 need not take up any
torsional stresses and this also holds true for all other parts of
the drive means for the impeller 12. Such construction protects the
crank assembly between the electric motor M and the cylinder 6
against torsional stresses. Consequently, the wear upon the parts
of the crank assembly is minimal and its useful life is much longer
than in heretofore known impact wrenches.
When the torque exceeds the value which is selected by the bias of
the spring 34 and/or projection 39, the claws 30 of the clutch
element 29 become disengaged from the claws of the fixed clutch
element 31 with the result that the tool 20 ceases to turn as long
as the claws 30 remain disengaged from the complementary claws. The
minimum torque which is needed to disengage the clutch 29, 31 is
determined by the bias of the spring 34. As mentioned before, the
bias of the spring 34 can be assisted by the operator if the handle
42 is manipulated in the aforedescribed manner so that the
projection 39 bears against the collar 36 and thus participates in
retention of claws 30 in engagement with the claws of the fixed
clutch element 31. Also, the user can decide to intentionally
disengage the clutch element 29 from the fixed clutch element 31 by
moving the locking bolt 48 against the aforementioned second stop
on the barrel 1b so that the clutch element 29 has sufficient
freedom of axial movement to disengage its claws 30 from the claws
of the clutch element 31. The device then merely acts as a hammer
by causing the impeller 12 to strike against the anvil 60 in
response to each forward stroke of the cylinder 6. The clutch 29,
31 constitutes a safety device or blocking means which insures that
the operator cannot be injured when the resistance which the tool
20 offers to rotation exceeds a permissible value. The parts 39-48
also constitute a safety device because it enables the operator to
select that torque which can be handled by the operator without
risking an injury. The minimum resistance which the tool 20 must
offer to disengage the clutch 29, 31 is preferably low so that the
impact wrench can be properly and safely manipulated by a
relatively weak person. On the other hand, the projection 39
enables the operator to select a relatively high torque, i.e., the
tool 20 must offer a very high resistance to rotation before the
clutch element 29 becomes disengaged from the clutch element 31.
The aforementioned positioning of the second stop for the locking
bolt 48 prevents an accidental or unintentional change in the bias
of the spring 34 so that the minimum torque which is needed to
disengage the clutch element 29 from the clutch element 31 remains
unchanged until the operator decides to move the projection 39 away
from the collar 36. In other words, the operator must decide to
move the handle 42 axially and to change the angular position of
the stud 40; otherwise the magnitude of selected torque remains
unchanged. If desired, the impact wrench can be provided with means
for adjusting the position of one or both stops so that the user
can select an optimum torque for a particular operation.
The claws 30 and the complementary claws of the clutch element 31
are preferably conical. This is desirable because such claws can
transmit substantial torque while taking up a small amount of
space.
The provision of a single projection 39 which can change the bias
of the spring 34, disengage the spring 34 from the clutch element
29 or serve to transmit muscle power for retention of the clutch
element 29 in engagement with the clutch element 31 contributes to
simplicity, compactness, convenience of manipulation and lower cost
of the impact wrench. The spring 44 cooperates with the locking
bolt 48 to insure that the angular position of the handle 42 cannot
be changed accidentally, i.e., the operator knows that he must
exercise great care whenever the handle 42 is moved against the
opposition of the spring 44 because the projection 39 is then
likely to change its angular position under the bias of the spring
34 or in response to disengagement of the clutch element 29 from
the clutch element 31.
It is also within the purview of the invention to omit the input
element 26 and to provide the teeth 26a, 26b directly on the output
member 6. The clutch element 29 then meshes with axially parallel
teeth on the output member 6 and the inclined teeth or threads of
the output member 6 then mesh with the teeth or threads 24b of the
intermediate element 24. Such modified torque transmitting means
operates satisfactorily if the threads or teeth on the parts 29, 6,
24 are machined with a high degree of precision; otherwise, the
crank assembly of the drive means would be subjected to substantial
torsional stresses.
The structure which is shown in the drawing is preferred at this
time because the crank assembly is not subjected to any torsional
stresses, even if the input element 26 has substantial freedom of
radial movement with respect to the output member 6 and even if the
teeth 26a, 29a and/or 24b, 26b are not machined with a high degree
of precision. Moreover, a damaged or worn element 26 and/or 24 can
be replaced by a fresh one with minimal losses in time and at a
cost which is a small fraction of the cost of the output member
6.
All such parts which are subject to extensive wear are readily
accessible to allow for replacement with minimal losses in time.
Moreover, the adjustment of the assembled impact wrench is either
unnecessary or minimal so that the initial cost of the impact
wrench is reasonable in spite of its versatility and ability to
transmit substantial torque.
Without further analysis, the foregoing will so fully reveal the
gist of the present invention that others can, by applying current
knowledge, readily adapt it for various applications without
omitting features which fairly constitute essential characteristics
of the generic and specific aspects of our contribution to the art
and, therefore, such adaptations should and are intended to be
comprehended within the meaning and range of equivalence of the
claims.
* * * * *