Patent Grant
7743846
The present invention relates to rotary spindles for power tools, and relates particularly, but not exclusively, to rotary spindles for hammer drills. The invention also relates to power tools incorporating such spindles.
Electrically driven hammer drills are known in which a motor causes a driving member in the form of a flying mass to be reciprocally driven in a hollow spindle by means of piston, while at the same time causing the piston to rotate about its longitudinal axis. The spindle supports a working member such as a drill bit, either by direct mounting of the drill bit to the spindle, or by supporting a tool holder which in turn supports the drill bit, such that rotation of the spindle about its axis causes rotation of the drill bit to effect a drilling action, while reciprocating movement of the flying mass within the spindle imparts hammer impacts to the drill bit.
The spindle of a hammer drill of such known types is generally manufactured in a single piece. As a result, the entire spindle generally needs to be constructed as robustly as that part of the spindle subjected to the greatest amount of wear, even though most of the spindle does not need to be constructed to such a level of robustness. This significantly increases the cost and difficulty of manufacturing the hammer drill. Furthermore, when the hammer drill is repaired, the entire spindle generally needs to be replaced, even if only part of the spindle is damaged, which makes repair of the drill costly.
U.S. Pat. No. 5,373,905 discloses a hammer drill in which a spindle in which a striker mass is reciprocally driven is formed from two separate parts, i.e. a guide tube, and a tool socket arranged forwardly of the guide tube, the guide tube and tool socket overlapping each other in a certain region and being connected to each other by means of a press fit. As a result, only the tool socket needs to be formed from a robust, high-grade material, which significantly reduces the cost of manufacture and repair of the drill.
However, this arrangement suffers from the drawbacks that because the guide tube and tool socket are connected to each other by means of a press fit, the cooperating parts of the guide tube and tool socket must be manufactured to accurate dimensions, as a result if which manufacture of the drill is still costly. Also, the hammering action of the striker mass against the tool socket causes the tool socket to tend to detach from the guide sleeve, as a result of which components such as profiled rings securing the guide tube and tool socket together are subjected to significant stresses and can become damaged and must be frequently replaced.
Preferred embodiments of the present invention seek to overcome the above disadvantages of the prior art.
According to an aspect of the present invention, there is provided a rotary spindle for a power tool, the spindle comprising:—
a first spindle member having at least one first abutment portion adjacent a first end thereof;
a second spindle member for supporting a working member of the power tool adjacent a first end thereof for rotation with said second spindle member about said axis, wherein said second spindle member is adapted to extend through an aperture adjacent said first end of said first spindle member and has at least one second abutment portion adjacent a second end thereof for cooperating with at least one said first abutment portion of said first spindle member to prevent removal of said second spindle member from said first end of said first spindle member in a first direction;
locking means for preventing removal of said second spindle member from said first end of said first spindle member in a second direction, opposite to said first direction; and
biasing means for urging said second spindle member in said second direction relative to said first spindle member.
By providing first and second abutment portions for preventing removal of the second spindle member from the first spindle member in a first direction, and biasing means for urging the second spindle member in a second direction, opposite to the first direction, relative to the first spindle member, this provides the advantage of minimising the tendency of impacts on the second spindle member to cause the second spindle member to become detached from the first spindle member. In addition, by providing at least one first abutment portion which cooperates with at least one second abutment portion, this provides the advantage that the first and second spindle members no longer need to fit together by means of a press fit, as a result of which the first and second spindle members do not require cooperating parts manufactured to as high a degree of accuracy as prior art devices having two-part spindles. This in turn reduces the cost of manufacture of the spindle and therefore of apparatus incorporating the spindle.
The first spindle member may be adapted to be rotated by a motor of the power tool. However, the spindle may be arranged such that there is no rotary movement, the power tool only impacting hammer impacts on the drill bit.
At least one said second abutment portion may comprise a rim extending outwardly of said axis.
In the case where the spindle forms part of a power tool having hammer action, for example a hammer drill, this provides the advantage of enabling direct impact of a beat piece flying mass of a hammer mechanism of the tool against the first spindle member to be avoided, which in turn minimises wear and damage to the first spindle member, thus increasing the useful lifetime of the first spindle member.
At least one said second abutment portion may comprise a rim extending towards said axis.
Said biasing means may include at least one resilient member.
At least one said resilient member may comprise an O-ring arranged between a said first abutment portion and a said second abutment portion.
Said damping means may comprise at least one compression spring.
Said locking means may comprise at least one removable member adapted to be mounted to said second spindle member on a side of a said first abutment portion opposite to said biasing means.
This provides the advantage of minimising the extent to which the or each removable member is subjected to wear by hammer impacts on the second spindle member.
At least one said removable member may comprise a metal clip.
Said first and second spindle members may comprise cooperating engaging means for preventing rotation of said second spindle member about said axis relative to said first spindle member.
Said cooperating engaging means may comprise a plurality of splines on one of said first and second spindle members and a plurality of grooves on the other of said first and second spindle members.
According to another aspect of the present invention, there is provided a power tool comprising a housing, a motor having an output shaft for actuation of a working member of the tool, and a spindle as defined above for rotation about said axis by means of said motor.
A preferred embodiment of the present invention will now be described, by way of example only and not in any limitative sense, with reference to the accompanying drawings, in which:—
Referring to
A wobble drive hammering mechanism, of a type which will be familiar to persons skilled in the art, is provided for reciprocatingly driving a piston 24. The piston 24 is slidably located within a hollow cylindrical spindle 4 and an O-ring seal (not shown) is mounted around the piston 24 so as to seal between the periphery of the piston 24 and the internal surface of the spindle 4. A ram 28 is slidably mounted within the spindle 4 and an O-ring seal (not shown) is mounted around the ram 28 so as to seal between the periphery of the ram 28 and the internal surface of the spindle 4. In this way, during normal operation of the hammer, a closed air cushion is formed between the forward face of the piston 24 and the rear face of the ram 28, which causes the ram to be reciprocatingly driven by the piston via the closed air cushion. During normal operation of the hammer, the ram 28 repeatedly impacts a beat piece 32, which is reciprocatingly mounted within the spindle 4. The beat piece 32 transfers impacts from the ram 28 to a tool or bit (not shown) mounted within a forward tool holder portion of the spindle 4 by means of a tool holder arrangement 36, of a type which will be familiar to persons skilled in the art. The tool or bit is releasably locked within the tool holder portion of the spindle 4 so as to be able to reciprocate within the tool holder portion of the spindle by a limited amount.
The spindle 4 is rotatably mounted in the hammer housing 2 by means of bearings 15, 17. Simultaneously with, or as an alternative to, the hammering action generated by the hammering mechanism described above, the spindle 4 can be rotatingly driven by the intermediate shaft 6 as described below. Thus, as well as reciprocating, the tool or bit is rotatingly driven because it is non-rotatably mounted within the spindle 4 by the tool holder arrangement 36.
An overload clutch mechanism includes a spindle drive gear 40 rotatably and axially slidably mounted on a slider sleeve 41, and the slider sleeve 41 is non-rotatably and axially slidably mounted on the spindle 4. The spindle drive gear 40 is formed on its periphery with a set of teeth 43. The intermediate shaft 6 is formed at its forward end with a pinion 38 and the teeth 43 of the spindle drive gear 40 may be brought into engagement with the pinion 38 in order to transmit rotary drive to the slider sleeve 41 and thereby to the spindle 4. The spindle drive gear 40 transmits rotary drive to the slider sleeve 41 via the overload clutch arrangement. The spindle drive gear 40 has a set of rearwardly facing teeth 40a formed on a rearward facing surface thereof, this set of teeth 40a being biased into engagement with a set of teeth formed on a forward facing surface 41a on an annular flange of the slider sleeve 41. The sets of teeth are biased into engagement with each other by a spring 47 mounted on the slider sleeve 41 to extend between a washer 49 axially fixedly mounted at the forward end of the slider sleeve 41, and a forward facing end surface of the spindle drive gear 40.
The slider sleeve 41 is axially biased by means of a spring 56 into a rearward position against an elastomeric O-ring 42 mounted in a recess formed in the external surface of the spindle 4 and having an inclined surface. In the rearward position, the hammer is in a rotary mode and rotation of the intermediate shaft 6 is transmitted to the spindle 4, provided the torque transmitted is below a threshold torque of the overload clutch.
The slider sleeve 41 can also be moved into a forward position against the biasing force of the spring 56 via a mode change mechanism. In the forward position, the spindle drive gear 40 is moved on the slider sleeve 41 forwardly out of engagement with the intermediate shaft pinion 38 and into engagement with a spindle lock arrangement 60, the function of which is not relevant to the present invention and will therefore not be described in further detail. With the slider sleeve 41 and spindle drive gear 40 in a forward position, the hammer is in a non-rotary mode with the spindle 4 fixed against rotation. The mode change arrangement may comprise a mode change knob 55 rotatably mounted on the housing 2 and having an eccentric pin 57 which is engageable with the rearward face of the annular flange 41a of the slider sleeve 41 to move the slider sleeve forwardly.
In the position shown in
Referring now to
The second spindle part 404 is made of more robust material than first spindle part 402 and is held in position relative to the first spindle part 402 by means of resilient metal circlip 414 arranged to grip second spindle part 404 in a groove 416 thereof to maintain rubber O-rings 412 under compression to prevent axial movement of second spindle part 404 relative to first spindle part 402.
In order to assemble the spindle 4, the second spindle part 404 is urged outwardly of the aperture 408 in first spindle part 402 until the rubber O rings 412 are placed under compression between the rims 406, 410. The circlip 414 then secures the second spindle part 404 in position relative to the first spindle part 402.
During operation of the hammer drill, the motor causes the two-part spindle 4 to rotate about its longitudinal axis, while reciprocally driving the ram 28 axially in the hollow spindle 4 to impart impacts to the beat piece 32. The ram 28 only impacts against the second spindle part 404, as a result of which wear and damage to the first spindle part 402 is minimised, and only the second spindle part 404 need be replaced during repair of the hammer drill.
It will be appreciated by persons skilled in the art that the above embodiment has been described by way of example only, and not in any limitative sense, and that various alterations and modifications are possible without departure from the scope of the invention as defined by the appended claims. For example, rubber O-rings 412 may be replaced by a compression spring.
| Number | Date | Country | Kind |
|---|---|---|---|
| 0412594.4 | Jun 2004 | GB | national |
| Number | Name | Date | Kind |
|---|---|---|---|
| 2451234 | Mitchell | Oct 1948 | A |
| 2478195 | Hull | Aug 1949 | A |
| 2736561 | Hansen | Feb 1956 | A |
| 2926020 | Dayton et al. | Feb 1960 | A |
| 3734516 | Smith | May 1973 | A |
| 3743307 | Benjamin et al. | Jul 1973 | A |
| 4107949 | Wanner et al. | Aug 1978 | A |
| 4114699 | Wolf | Sep 1978 | A |
| 4131165 | Wanner et al. | Dec 1978 | A |
| 4429775 | Teramoto | Feb 1984 | A |
| 4434859 | Rumpp et al. | Mar 1984 | A |
| 4477095 | Atkinson, III | Oct 1984 | A |
| 4491444 | Rumpp et al. | Jan 1985 | A |
| 4491445 | Hunger et al. | Jan 1985 | A |
| 4502824 | Dohse et al. | Mar 1985 | A |
| 4547105 | Hofle et al. | Oct 1985 | A |
| 4592560 | Neumaier et al. | Jun 1986 | A |
| 4691929 | Neumaier et al. | Sep 1987 | A |
| 4710079 | Smith et al. | Dec 1987 | A |
| 4775269 | Brix | Oct 1988 | A |
| 4824298 | Lippacher et al. | Apr 1989 | A |
| 4878679 | Plank et al. | Nov 1989 | A |
| 5042848 | Shiozaki | Aug 1991 | A |
| 5199833 | Fehrle et al. | Apr 1993 | A |
| 5201620 | Forrest et al. | Apr 1993 | A |
| 5222956 | Waldron | Jun 1993 | A |
| 5316323 | Jovanovic | May 1994 | A |
| 5373905 | Bleicher et al. | Dec 1994 | A |
| 5379848 | Rauser | Jan 1995 | A |
| 5398946 | Quiring | Mar 1995 | A |
| 5437465 | Vogele et al. | Aug 1995 | A |
| 5474139 | Odendahl et al. | Dec 1995 | A |
| 5558478 | Odendahl et al. | Sep 1996 | A |
| 5588496 | Elger | Dec 1996 | A |
| 5603516 | Neumaier | Feb 1997 | A |
| 5674031 | Bilz et al. | Oct 1997 | A |
| 5678961 | Fleege et al. | Oct 1997 | A |
| 5706903 | Odendahl et al. | Jan 1998 | A |
| 5709391 | Arakawa et al. | Jan 1998 | A |
| 5954347 | Buck et al. | Sep 1999 | A |
| 5971403 | Yahagi et al. | Oct 1999 | A |
| 6089330 | Miescher et al. | Jul 2000 | A |
| 6092814 | Kageler | Jul 2000 | A |
| 6116352 | Frauhammer et al. | Sep 2000 | A |
| 6173792 | Hald | Jan 2001 | B1 |
| 6497418 | Yahagi | Dec 2002 | B2 |
| 6732815 | Hanke et al. | May 2004 | B2 |
| 20010048855 | Lin | Dec 2001 | A1 |
| 20020151902 | Riedel et al. | Oct 2002 | A1 |
| 20050224243 | Baumann et al. | Oct 2005 | A1 |
| Number | Date | Country |
|---|---|---|
| 36 13 526 | Oct 1987 | DE |
| 618546 | Feb 1949 | GB |
| 2 276 578 | Oct 1994 | GB |
| 2 324 482 | Oct 1998 | GB |
| WO 03035321 | May 2003 | WO |
| 2004007149 | Jan 2004 | WO |
| Number | Date | Country | |
|---|---|---|---|
| 20050271489 A1 | Dec 2005 | US |
