US20050217449A1 - Adjustable tool station - Google Patents
Adjustable tool station Download PDFInfo
- Publication number
- US20050217449A1 US20050217449A1 US11/140,877 US14087705A US2005217449A1 US 20050217449 A1 US20050217449 A1 US 20050217449A1 US 14087705 A US14087705 A US 14087705A US 2005217449 A1 US2005217449 A1 US 2005217449A1
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- United States
- Prior art keywords
- guide rail
- saw
- housing
- section
- tool
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/04—Ball or roller bearings
- F16C29/06—Ball or roller bearings in which the rolling bodies circulate partly without carrying load
- F16C29/068—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with the bearing body fully encircling the guide rail or track
- F16C29/0683—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with the bearing body fully encircling the guide rail or track the bearing body encircles a rail or rod of circular cross-section, i.e. the linear bearing is not suited to transmit torque
- F16C29/0685—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with the bearing body fully encircling the guide rail or track the bearing body encircles a rail or rod of circular cross-section, i.e. the linear bearing is not suited to transmit torque with balls
- F16C29/069—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with the bearing body fully encircling the guide rail or track the bearing body encircles a rail or rod of circular cross-section, i.e. the linear bearing is not suited to transmit torque with balls whereby discrete load bearing elements, e.g. discrete load bearing plates or discrete rods, are provided in a retainer and form the load bearing tracks
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/001—Bearings for parts moving only linearly adjustable for alignment or positioning
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/768—Rotatable disc tool pair or tool and carrier
- Y10T83/7684—With means to support work relative to tool[s]
- Y10T83/7693—Tool moved relative to work-support during cutting
- Y10T83/7697—Tool angularly adjustable relative to work-support
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/768—Rotatable disc tool pair or tool and carrier
- Y10T83/7684—With means to support work relative to tool[s]
- Y10T83/7701—Supporting surface and tool axis angularly related
- Y10T83/7705—Adjustable angular relationship
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/768—Rotatable disc tool pair or tool and carrier
- Y10T83/7684—With means to support work relative to tool[s]
- Y10T83/7722—Support and tool relatively adjustable
- Y10T83/7726—By movement of the tool
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/768—Rotatable disc tool pair or tool and carrier
- Y10T83/7755—Carrier for rotatable tool movable during cutting
- Y10T83/7763—Tool carrier reciprocable rectilinearly
- Y10T83/7768—With means to adjust path of reciprocation
- Y10T83/7772—Angular relative to previous path
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/768—Rotatable disc tool pair or tool and carrier
- Y10T83/7755—Carrier for rotatable tool movable during cutting
- Y10T83/7788—Tool carrier oscillated or rotated
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/869—Means to drive or to guide tool
- Y10T83/8773—Bevel or miter cut
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/869—Means to drive or to guide tool
- Y10T83/8878—Guide
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/929—Tool or tool with support
- Y10T83/9457—Joint or connection
- Y10T83/9488—Adjustable
- Y10T83/949—Rectilinearly
Definitions
- the present invention relates to an adjustable tool station. More particularly, the invention relates to a guide assembly rotatably engaging a tool head in a substantially play-free manner to prevent rotation of the tool head.
- a saw assembly includes a blade and various actuators adapted to displace the blade linearly along a longitudinal axis, rotate the blade about the longitudinal axis in various angled or beveled positions, and/or displace the blade along a pivot axis extending perpendicular to the longitudinal axis.
- Examples of such a saw assembly include compound miter/chop saws allowing the user to selectively move the saw blade into any of a number of positions for square cutting, miter cutting, bevel cutting, or compound miter cutting where a combination miter angle and bevel angle are cut.
- the saw blade, cutter or other working device can move along a horizontal base across the workpiece. Subsequently, if an angular adjustment of these elements is desirable, the bevel adjustment allows the saw blade, cutter or other working device to be positioned at an angle with respect to the horizontal base. At times it may be desired to cut a combination miter angle and bevel angle by simultaneously adjusting the angle of the blade with respect to both the horizontal base and a vertical guard.
- locking mechanisms for the miter and bevel adjustment must be activated in order to prohibit movement of the saw blade, cutter or other working device from the set position with respect to the base and fence while the cutting operation is performed.
- These locking mechanisms need to be easily activated, adjustable and quick acting in order to optimize the efficiency of the cutting apparatus and provide convenience to the operator of the apparatus.
- sliding compound miter saw 10 disclosed in the above-mentioned patents includes a base 12 , a table 14 , a housing 16 , a saw blade 18 , a blade guard 20 , a motor 22 drivingly connected to saw blade 18 , a handle 24 and a guard 26 .
- the table assembly 14 is secured to the base 12 such that it can be rotated in order to provide adjustment for miter cutting.
- the housing 16 is secured to the table 14 such that it can be pivoted to adjust the angle of the saw blade 18 relative to table 14 for bevel cutting.
- the housing 16 has two support arms 34 coupled with the saw for synchronous sliding movement. The sliding movement of support arms 34 drives the housing 16 and the saw blade 18 so that the saw blade can be pulled through the workpiece when the size of the workpiece exceeds the cutting width of the saw blade 18 .
- a fairly complicated combination of movements can be inconvenient for the user operating the miter saw 10 .
- displacement of support arms 34 attached to the saw head for synchronous linear displacement therewith to an initial position, in which the saw blade 18 is located next to the guard 26 increases the overall size of the saw.
- a portable tool design like the miter/chop saw discussed here, requires that such a tool be compact.
- the saw assembly having a structure with minimized play between a saw head, which includes the saw blade, its housing and other parts fixed to the blade for synchronous angular displacement therewith, and a support and guide system is also desirable.
- An improved structure of a portable power tool such as a miter/chop saw, having a reduced overall size and reliable engagement between angularly displaceable parts is attained in accordance with the present invention.
- a saw housing receiving a saw blade- is linearly guided along a guide rail, which is not linearly displaceable along with the say housing. As a consequence, the overall size of the power tool is reduced.
- Another aspect of the present invention is directed at minimization of undesirable play between a guide rail and a saw housing during angular displacement of the entire system.
- the guide rail is shaped to mesh with a linear motion bearing segment which is fixed to the saw blade housing.
- the linear motion bearing segment has a plurality of self-contained roller or ball retainer segments arranged so that the bearing segment and the guide rail engage one another in a substantially play-free manner during pivotal displacement of the miter saw between beveled or angled positions of a saw blade.
- the inventive single guide rail eliminates one shaft or arm of the support system along with a respective plain bushing disclosed by the above-discussed prior art. Furthermore, as a result of the bearing segment and a shape of the guide rail preventing undesired torsional motion of structural components relative to one another, the inventive system is characterized by reduced drag.
- FIG. 1 is a front perspective view of a sliding compound miter/chop saw in accordance with the prior art
- FIG. 2 is a perspective view of the sliding compound miter/chop saw in accordance with the invention and illustrated an initial position of the meter sass;
- FIG. 3A is a transverse cross-sectional view of the sliding compound miter/chop saw taken along lines III-III of FIG. 2 ;
- FIG. 3B is an exploded perspective view of a half bearing segment of a linear motion bearing segment and a guide rail;
- FIG. 3C is a perspective view of the assembled linear motion bearing segment supporting the guide rail in accordance with the present invention.
- FIG. 4 is a diagrammatic cross-sectional view of an alternate embodiment of the guide rail in accordance with the invention.
- FIG. 5 is a perspective view of the sliding compound miter/chop saw shown in FIG. 2 and illustrated in ane extended position of the miter saw;
- FIG. 6 is a perspective view of the sliding compound miter/chop saw shown in FIG. 2 and illustrated in an angled position of the saw blade;
- FIG. 7 is a front elevational view of the compound miter/chop saw shows in FIG. 2 .
- FIGS. 2 and 5 - 7 illustrate a compound miter/chop saw 10 incorporating a support and guide assembly 30 in accordance with the present invention.
- the compound miter/chop saw 10 includes a single guide rail 40 , which is mounted on the table 14 so that the guide rail 40 does not move linearly along an axis A-A, and a saw housing 38 slidable along the guide rail 40 . Linear displacement of the saw housing 38 into a position shown in FIG. 5 along the axis A-A is necessary when a workpiece to be sawed has a substantial size exceeding the diameter of the saw blade 18 .
- the compound miter/chop saw 10 further includes a rotatable join 48 mounted rotatably about an axis A-A on the table 14 and a guide rail housing 68 rigidly coupled to the rotatable joint 48 by means of an arm 66 ( FIG. 6 ) for synchronous pivotal motion around the axis A-A.
- the guide rail housing 68 receives an end 42 (FIG. BB) of the guide rail 40 and engages it so that the guide rail housing 68 and guide rail 40 are rotationally and linearly fixed relative to one another.
- the guide rail 40 as shown in FIGS. 7-7 , has an annular shape provided with a spline 58 ( FIGS.
- guide rail 40 engages a recess or nest 108 ( FIG. 5 ) which has an inner surface formed complementary to the spline 58 .
- the nest 108 of the guide rail housing 68 and the spline 58 engage one another so that there is no rotational or linear displacement between the guide rail housing 68 and the guide rail 40 .
- any arrangement rotationally and linearly fixing the guide rail housing 68 to the guide rail 40 can be used depending on a shape of the guide rail 40 , which, for example, can be cross-like, I-beam, regular or irregular polygonal or annular.
- Linear displacement of the saw housing 38 along the guide rail 40 is provided by means of a linear motion bail bearing assembly 44 ( FIGS. 3A-3C ), which is disclosed in a co-pending application Ser. No. 60/242,850 and fully incorporated herein by reference.
- the ball bearing assembly 44 is fabricated from a plurality of individual arcuate interengageable self-contained rolling element retainer segment.
- a cross sectional view seen in FIG. 3A and taken along lines III-III of FIG. 2 illustrates a combination of the rolling element bearing segment assembly 44 mounted within a bore provided in an end 73 ( FIGS. 3C and 5 ) of a Z-shaped lever 70 of the saw housing 38 and interengaged witch the guide rail 40 .
- a longitudinal groove 102 ( FIG. 3C ) is formed along an inner surface of the bored end 73 of the saw housing 38 for engaging the half arcuate retainer segment 54 .
- the quarter arcuate retainer segments 52 and the half arcuate retainer segment 54 are adapted and configured to move linearly smoothly on the guide rail 40 , along with the saw housing 38 . Note that a number of segments can vary.
- the half arcuate ball retainer segment 54 includes a base portion 63 ( FIG. 3B ) having an inner surface configured and adapted to be in substantial clearance of the spline 58 formed along a longitudinal length of the guide rail 40 .
- the base portion 63 includes a pair of independent ball bearing tracks 80 formed therein for retaining a plurality of rolling elements, which includes balls or rollers 56 .
- Each rolling element bearing track 80 is made up of a load bearing portion 57 ( FIG. 3A ) and a return portion 59 interconnected by turnarounds 84 ( FIG. 3B ) for recirculating the balls or rollers 56 therealong during linear displacement of the saw housing 38 alone the guide rail 40 .
- the respective load bearing portions 57 are located adjacent to one another and are spaced from one another along the base portion 63 ( FIG. 3B ).
- the half arcuate rolling element retainer segment 54 further includes a single load bearing plate 86 having an inner surface, which is configured and adapted to be disposed over both load bearing portions 57 b of each ball bearing track 80 , and an outer surface defining a pair of longitudinally extending convergent flat portions 58 .
- Each convergent flat portion 88 is configured and adapted to engage a respective biasing member 90 , which can be any resilient element, such as a spring.
- the half arcuate ball retainer segment 54 includes a pair of lids 92 and 94 serving to close the half arcuate ball retainer segment 54 .
- Each lid is provided with a window 96 aligned with one of the convergent segment 88 and through which windows 88 the biasing members 90 extend to contact the inner surface of the end 73 of the saw housing 38 , as shown in FIG. 3C .
- the arm 66 , the guide rail housing 68 , the guide rail 40 and the saw housing 38 pivot about the axis A-A as the rotatable joint 48 rotates about this axis ( FIG. 2 ).
- Interengagement between the guide rail 40 , the linear motion bearing segment assembly 44 and the end 73 of the Z-shaped ever 70 of the saw housing 38 prevents undesired angular displacement between the saw housing 38 and the guide rail 40 .
- the inner surface of the end 73 of the saw housing 38 has radial ribs 104 extending into clearances 106 which are formed between the quarter arcuate and half arcuate retainer segments 52 and 54 .
- Such engagement provides fixed rotational contact between the saw housing 38 and the linear motion bearing segment assembly 44 .
- the half arcuate retainer segment 54 is provided with a longitudinal recess 61 ( FIG. 3B ) having an inner surface extending complementary to opposite sides 100 and 98 of the spline 58 .
- the opposite sides 98 and 100 of the spline 58 are pressed upon by the balls or rollers 56 which are pre-loaded due to a force applied by the biasing members 90 through the converging flats 88 of the load bearing plate 86 .
- the pre-load being applied against opposite sides 98 and 100 of the spline 58 at an angle “ ⁇ ” ( FIG. 3A ) selected so that the spline 58 and the balls or rollers 56 preserve sliding contact therebetween.
- the balls or rollers 56 abut the opposite sides 98 and 100 of the spline 58 such that the guide rail 40 and the balls 56 cannot be angularly displaced independently from one another.
- the converging flats 88 of the load bearing plate 86 , the ball bearing tracks 80 of the base portion 54 and the opposite sides 98 and 100 of the spline 58 are shaped to angularly support the balls or rollers 56 , which circulate along the parallel load bearing portions 57 , as shown in FIG. 3A .
- the balls or rollers 56 are this prevented from moving out of contact with the opposite sides 98 and 100 of the spline 58 during angular displacement of the saw housing 38 and the guide rail 40 .
- any relative angular motion between the balls or rollers 56 and the rail guide 40 is substantially eliminated.
- a retaining member 65 above the load bearing plate 86 is placed in the recess 61 to provide additional lateral support for the balls 56 running along both load bearing portions 57 .
- FIG. 4 illustrates the guide rail 40 provided with a plurality of cutouts 64 which are spaced circumferentially-apart and form respective ball loading bearing tracks receiving the rollers or balls 56 of the linear motion beating assembly 44 .
- the geometry of the guide rail 40 of FIG. 4 has a cross-like shape, this embodiment operates in a mauler similar to the one described immediately above.
- a mechanical link is created between the saw housing 38 , the linear motion bearing assembly 44 , the guide rail 40 , the guide rail housing 68 , the arm 66 and the rotatable joint 48 , which pivot synchronously about the axis A-A axis in a substantially play-free manner.
- the housing 38 can be displaced into a desired angled or beveled position of the blade 18 in a manner preventing the saw housing 38 from undesired torsional motion relative to the guide rail 40 .
- the inventive structure avoids drag even when the saw housing 38 , the guide rail 40 , and the guide rail housing 68 are displaced into a 45° angled position of the blade 18 .
- the Z-shaped lever 70 of the saw housing 38 ( FIGS. 2, 5 and 6 ) positions the rail guide 40 so that the latter is laterally offset from a vertical axis B-B of the table assembly 14 when it is in a normal, vertical position, as shown in FIG. 7 .
- clearance for the guard plates 26 is always provided regardless of whether the saw housing 38 rotates clockwise or counterclockwise.
- a combination of the guide rail 40 and the bearing segment assembly 44 can be successfully utilized in any portable power tool provided with rotatably meshing par-s.
- a portable tool can included, but limited to, routers, plate joiners, and different types of drill presses, coping and dic saws.
Abstract
A miter saw includes a tool adjustment unit having a joint pivotable about an axis, a guide rail spaced from and coupled to the joint so as to pivot about the axis, a saw housing mounted on the guide rail and a linear motion bearing assembly, which is positioned between the guide rail and the saw housing. The guide rail and the linear motion bearing are so shaped and dimensioned that the saw housing and the guide rail rotationally engage one another in a substantially play free manner to displace a saw blade between a plurality of angled positions.
Description
- The present application is a continuation-in-part of International Application No. PCT/US01/50897, filed Oct. 24, 2001, which claims the benefit of U.S. Provisional Application 60/242,850, filed on Oct. 24, 2000.
- The present invention relates to an adjustable tool station. More particularly, the invention relates to a guide assembly rotatably engaging a tool head in a substantially play-free manner to prevent rotation of the tool head.
- Numerous power hand tools assisting a user in accomplishing a variety of tasks are known. Generally, such tools include a base and a tool head for performing a certain task, for example, cutting and/or sawing a workpiece composed of wood, plastic, metal or other various materials. Typically, a saw assembly includes a blade and various actuators adapted to displace the blade linearly along a longitudinal axis, rotate the blade about the longitudinal axis in various angled or beveled positions, and/or displace the blade along a pivot axis extending perpendicular to the longitudinal axis.
- Examples of such a saw assembly include compound miter/chop saws allowing the user to selectively move the saw blade into any of a number of positions for square cutting, miter cutting, bevel cutting, or compound miter cutting where a combination miter angle and bevel angle are cut. In addition, it is essential that the saw blade move linearly to accommodate different lengths of the workpiece. In order to allow for the adjustment of the miter and the bevel angle, the saw blade, cutter or other working device can move along a horizontal base across the workpiece. Subsequently, if an angular adjustment of these elements is desirable, the bevel adjustment allows the saw blade, cutter or other working device to be positioned at an angle with respect to the horizontal base. At times it may be desired to cut a combination miter angle and bevel angle by simultaneously adjusting the angle of the blade with respect to both the horizontal base and a vertical guard.
- Once the saw blade, cutter or other working device has been adjusted to the desired position with respect to the horizontal base and the vertical fence, locking mechanisms for the miter and bevel adjustment must be activated in order to prohibit movement of the saw blade, cutter or other working device from the set position with respect to the base and fence while the cutting operation is performed. These locking mechanisms need to be easily activated, adjustable and quick acting in order to optimize the efficiency of the cutting apparatus and provide convenience to the operator of the apparatus.
- A typical saw assembly of the type, as discussed above, is disclosed in U.S. Pat. Nos. 6,035,754; 5,907,987, 5,870,938; and 5,870,838. As shown in
FIG. 1 , sliding compound miter saw 10 disclosed in the above-mentioned patents includes abase 12, a table 14, ahousing 16, asaw blade 18, ablade guard 20, amotor 22 drivingly connected to sawblade 18, ahandle 24 and aguard 26. Thetable assembly 14 is secured to thebase 12 such that it can be rotated in order to provide adjustment for miter cutting. Thehousing 16 is secured to the table 14 such that it can be pivoted to adjust the angle of thesaw blade 18 relative to table 14 for bevel cutting. To provide linear movement of a saw head consisting of thesaw blade 18, themotor 22, thehandle 24 and theblade guard 20 relative the table 14, thehousing 16 has twosupport arms 34 coupled with the saw for synchronous sliding movement. The sliding movement ofsupport arms 34 drives thehousing 16 and thesaw blade 18 so that the saw blade can be pulled through the workpiece when the size of the workpiece exceeds the cutting width of thesaw blade 18. - A fairly complicated combination of movements can be inconvenient for the user operating the miter saw 10. First, displacement of
support arms 34 attached to the saw head for synchronous linear displacement therewith to an initial position, in which thesaw blade 18 is located next to theguard 26, increases the overall size of the saw. A portable tool design, like the miter/chop saw discussed here, requires that such a tool be compact. - Still another disadvantage oa the above-disclosed miter saw may be observed during angular displacement of the saw blade between numerous angular positions which may be accompanied by undesired rotation of the saw head relative to the support arms. To minimize undesired rotation, mans prior-art references including those discussed above disclose a two-aim support and guide system.
Arms 34 can be positioned relative to one another either in a vertical or a horizontal plane. - The vertical arrangement of the arms, as disclosed in the cited patents, minimizes undesired rotation of a saw head until the saw head reaches a 40-45° angular position. In this position, the upper arm supports some of the load of the saw head and rubs against a plain bushing supporting this arm, which, in turn, causes drag. In the horizontal arrangement, both arms always support the load of the saw head and; thus, the drag problem manifests itself at an angle smaller than a 45° angle.
- It is, therefore, desirable to provide a compact, light and simple structure saw assembly of the type described above. Also, the saw assembly having a structure with minimized play between a saw head, which includes the saw blade, its housing and other parts fixed to the blade for synchronous angular displacement therewith, and a support and guide system is also desirable.
- An improved structure of a portable power tool, such as a miter/chop saw, having a reduced overall size and reliable engagement between angularly displaceable parts is attained in accordance with the present invention.
- In accordance with one aspect of the invention, a saw housing receiving a saw blade-is linearly guided along a guide rail, which is not linearly displaceable along with the say housing. As a consequence, the overall size of the power tool is reduced.
- Another aspect of the present invention is directed at minimization of undesirable play between a guide rail and a saw housing during angular displacement of the entire system. To attain this, the guide rail is shaped to mesh with a linear motion bearing segment which is fixed to the saw blade housing. The linear motion bearing segment has a plurality of self-contained roller or ball retainer segments arranged so that the bearing segment and the guide rail engage one another in a substantially play-free manner during pivotal displacement of the miter saw between beveled or angled positions of a saw blade.
- As a consequence, the inventive single guide rail eliminates one shaft or arm of the support system along with a respective plain bushing disclosed by the above-discussed prior art. Furthermore, as a result of the bearing segment and a shape of the guide rail preventing undesired torsional motion of structural components relative to one another, the inventive system is characterized by reduced drag.
- The above and other objects, features and advantages will become more readily apparent from a specific description of the preferred embodiments accompanied by the following drawings, in which:
-
FIG. 1 is a front perspective view of a sliding compound miter/chop saw in accordance with the prior art; -
FIG. 2 is a perspective view of the sliding compound miter/chop saw in accordance with the invention and illustrated an initial position of the meter sass; -
FIG. 3A is a transverse cross-sectional view of the sliding compound miter/chop saw taken along lines III-III ofFIG. 2 ; -
FIG. 3B is an exploded perspective view of a half bearing segment of a linear motion bearing segment and a guide rail; -
FIG. 3C is a perspective view of the assembled linear motion bearing segment supporting the guide rail in accordance with the present invention; -
FIG. 4 is a diagrammatic cross-sectional view of an alternate embodiment of the guide rail in accordance with the invention. -
FIG. 5 is a perspective view of the sliding compound miter/chop saw shown inFIG. 2 and illustrated in ane extended position of the miter saw; -
FIG. 6 is a perspective view of the sliding compound miter/chop saw shown inFIG. 2 and illustrated in an angled position of the saw blade; and -
FIG. 7 is a front elevational view of the compound miter/chop saw shows inFIG. 2 . - Referring now to the drawings, in which like reference numerals designate corresponding parts throughout the several views,
FIGS. 2 and 5 -7 illustrate a compound miter/chop saw 10 incorporating a support andguide assembly 30 in accordance with the present invention. - The compound miter/
chop saw 10 includes asingle guide rail 40, which is mounted on the table 14 so that theguide rail 40 does not move linearly along an axis A-A, and asaw housing 38 slidable along theguide rail 40. Linear displacement of thesaw housing 38 into a position shown inFIG. 5 along the axis A-A is necessary when a workpiece to be sawed has a substantial size exceeding the diameter of thesaw blade 18. - The compound miter/
chop saw 10 further includes arotatable join 48 mounted rotatably about an axis A-A on the table 14 and aguide rail housing 68 rigidly coupled to therotatable joint 48 by means of an arm 66 (FIG. 6 ) for synchronous pivotal motion around the axis A-A. Theguide rail housing 68 receives an end 42 (FIG. BB) of theguide rail 40 and engages it so that theguide rail housing 68 andguide rail 40 are rotationally and linearly fixed relative to one another. Theguide rail 40, as shown inFIGS. 7-7 , has an annular shape provided with a spline 58 (FIGS. 2,3 and 5-7), andguide rail 40 engages a recess or nest 108 (FIG. 5 ) which has an inner surface formed complementary to thespline 58. Thenest 108 of theguide rail housing 68 and thespline 58 engage one another so that there is no rotational or linear displacement between theguide rail housing 68 and theguide rail 40. Note that any arrangement rotationally and linearly fixing theguide rail housing 68 to theguide rail 40 can be used depending on a shape of theguide rail 40, which, for example, can be cross-like, I-beam, regular or irregular polygonal or annular. - Linear displacement of the
saw housing 38 along theguide rail 40 is provided by means of a linear motion bail bearing assembly 44 (FIGS. 3A-3C ), which is disclosed in a co-pending application Ser. No. 60/242,850 and fully incorporated herein by reference. In particular, theball bearing assembly 44 is fabricated from a plurality of individual arcuate interengageable self-contained rolling element retainer segment. A cross sectional view seen inFIG. 3A and taken along lines III-III ofFIG. 2 , illustrates a combination of the rolling element bearingsegment assembly 44 mounted within a bore provided in an end 73 (FIGS. 3C and 5 ) of a Z-shapedlever 70 of thesaw housing 38 and interengaged witch theguide rail 40. Two individual quarter arcuate self-contained rollingelement retainer segment 52 and a single half arcuate self-containedball retainer segment 54, which constitute the bearingsegment assembly 44, are supported in interengageable association with theend 73 of the Z-shapedlever 70 of thesaw housing 38. A longitudinal groove 102 (FIG. 3C ) is formed along an inner surface of thebored end 73 of thesaw housing 38 for engaging the halfarcuate retainer segment 54. When fully assembled, the quarterarcuate retainer segments 52 and the halfarcuate retainer segment 54 are adapted and configured to move linearly smoothly on theguide rail 40, along with thesaw housing 38. Note that a number of segments can vary. - The half arcuate
ball retainer segment 54 includes a base portion 63 (FIG. 3B ) having an inner surface configured and adapted to be in substantial clearance of thespline 58 formed along a longitudinal length of theguide rail 40. Thebase portion 63 includes a pair of independent ball bearing tracks 80 formed therein for retaining a plurality of rolling elements, which includes balls orrollers 56. Each rollingelement bearing track 80 is made up of a load bearing portion 57 (FIG. 3A ) and areturn portion 59 interconnected by turnarounds 84 (FIG. 3B ) for recirculating the balls orrollers 56 therealong during linear displacement of thesaw housing 38 alone theguide rail 40. The respectiveload bearing portions 57 are located adjacent to one another and are spaced from one another along the base portion 63 (FIG. 3B ). - The half arcuate rolling
element retainer segment 54 further includes a singleload bearing plate 86 having an inner surface, which is configured and adapted to be disposed over both load bearing portions 57 b of eachball bearing track 80, and an outer surface defining a pair of longitudinally extending convergentflat portions 58. Each convergentflat portion 88 is configured and adapted to engage a respective biasingmember 90, which can be any resilient element, such as a spring. In addition, the half arcuateball retainer segment 54 includes a pair oflids ball retainer segment 54. Each lid is provided with awindow 96 aligned with one of theconvergent segment 88 and through whichwindows 88 the biasingmembers 90 extend to contact the inner surface of theend 73 of thesaw housing 38, as shown inFIG. 3C . - To displace the
saw blade 18 between a plurality of beveled or angled positions, as shown inFIG. 6 , thearm 66, theguide rail housing 68, theguide rail 40 and thesaw housing 38 pivot about the axis A-A as the rotatable joint 48 rotates about this axis (FIG. 2 ). Interengagement between theguide rail 40, the linear motion bearingsegment assembly 44 and theend 73 of the Z-shaped ever 70 of thesaw housing 38 prevents undesired angular displacement between thesaw housing 38 and theguide rail 40. - In particular, as shown in
FIGS. 3A-3C , the inner surface of theend 73 of thesaw housing 38 hasradial ribs 104 extending intoclearances 106 which are formed between the quarter arcuate and halfarcuate retainer segments saw housing 38 and the linear motion bearingsegment assembly 44. The halfarcuate retainer segment 54 is provided with a longitudinal recess 61 (FIG. 3B ) having an inner surface extending complementary toopposite sides spline 58. Furthermore, theopposite sides spline 58 are pressed upon by the balls orrollers 56 which are pre-loaded due to a force applied by the biasingmembers 90 through the convergingflats 88 of theload bearing plate 86. The pre-load being applied againstopposite sides spline 58 at an angle “θ” (FIG. 3A ) selected so that thespline 58 and the balls orrollers 56 preserve sliding contact therebetween. - To prevent angular displacement of the linear motion bearing
segment assembly 44 and thesaw housing 38 relative to theguide rail 40, the balls orrollers 56 abut theopposite sides spline 58 such that theguide rail 40 and theballs 56 cannot be angularly displaced independently from one another. Particularly, the convergingflats 88 of theload bearing plate 86, the ball bearing tracks 80 of thebase portion 54 and theopposite sides spline 58 are shaped to angularly support the balls orrollers 56, which circulate along the parallelload bearing portions 57, as shown inFIG. 3A . The balls orrollers 56 are this prevented from moving out of contact with theopposite sides spline 58 during angular displacement of thesaw housing 38 and theguide rail 40. Thus, any relative angular motion between the balls orrollers 56 and therail guide 40 is substantially eliminated. As shown inFIG. 3A , a retainingmember 65 above theload bearing plate 86 is placed in therecess 61 to provide additional lateral support for theballs 56 running along bothload bearing portions 57. - Note that the number of the rolling element retainer segment and their cross-section, as well as the number of the splines can vary depending on a load and a shape of the guide rail 400. It is essential, however, that the
guide rail 40 rotationally engage the linear motion bearingsegment assembly 44 and thesaw housing 38 in such a manner as to minimize a possibility of voluntary angular displacement of the saw housing about therail guide 40. Thus, for example,FIG. 4 illustrates theguide rail 40 provided with a plurality ofcutouts 64 which are spaced circumferentially-apart and form respective ball loading bearing tracks receiving the rollers orballs 56 of the linearmotion beating assembly 44. Although the geometry of theguide rail 40 ofFIG. 4 has a cross-like shape, this embodiment operates in a mauler similar to the one described immediately above. - Thus, in response to an external torque, a mechanical link is created between the
saw housing 38, the linearmotion bearing assembly 44, theguide rail 40, theguide rail housing 68, thearm 66 and the rotatable joint 48, which pivot synchronously about the axis A-A axis in a substantially play-free manner. As a result of the described kinematics, thehousing 38 can be displaced into a desired angled or beveled position of theblade 18 in a manner preventing thesaw housing 38 from undesired torsional motion relative to theguide rail 40. Also, the inventive structure avoids drag even when thesaw housing 38, theguide rail 40, and theguide rail housing 68 are displaced into a 45° angled position of theblade 18. - The Z-shaped
lever 70 of the saw housing 38 (FIGS. 2, 5 and 6) positions therail guide 40 so that the latter is laterally offset from a vertical axis B-B of thetable assembly 14 when it is in a normal, vertical position, as shown inFIG. 7 . As a result of such a shape of thelever 70, clearance for theguard plates 26 is always provided regardless of whether thesaw housing 38 rotates clockwise or counterclockwise. - A combination of the
guide rail 40 and the bearingsegment assembly 44 can be successfully utilized in any portable power tool provided with rotatably meshing par-s. Such a portable tool can included, but limited to, routers, plate joiners, and different types of drill presses, coping and dic saws. Thus, while the invention has been particularly shown and described with reference to the preferred embodiments, it will be understood that various modifications and changes in form and detail may be made therein without departing from the scope and spirit of the invention as defined in the following claims.
Claims (7)
1-17. (canceled)
18. A saw comprising:
a table having an elongated axis;
a rotary joint fixed to the table and rotatable about the elongated axis in response to an external torque;
a longitudinally extending guide rail spaced radially from the elongated axis and fixed to the rotary joint to pivot with respect to the elongated axis during rotation of the rotary joint, the guide rail having an annular cross-section and a shape selected from the group consisting of a cross-shaped cross-section, I-beam cross-section, regular polygonal cross-section and an irregular polygonal cross-section;
a saw housing receiving a saw blade and mounted on the guide rail; and
a linear motion bearing assembly mounted between the guide rail and the saw housing and rotationally fixed to the housing to provide linear displacement of the saw housing along the guide rail, the linear motion bearing assembly and the guide rail being shaped and dimensioned to prevent rotational movement relative to one another during angular displacement of the saw housing between beveled positions of the saw blade.
19. The saw as claimed in claim 18 , further comprising two guard plates mounted on the table and spaced laterally apart to define clearance therebetween which is unblocked during displacement of the saw housing and the guide rail between the beveled positions of the saw blade.
20. A power hand tool comprising:
an elongated guide rail pivotable about an axis;
a tool housing mounted on the guide rail; and
a linear motion bearing assembly mounted between the guide rail and the tool housing to provide smooth linear displacement of the tool housing along a length of the guide rail between a plurality of axial positions of the tool housing,
the guide rail and the linear motion bearing assembly being shaped to engage one another in a fixed rotational relationship during displacement of the tool housing between a plurality of angled positions,
the linear motion bearing assembly having a plurality of individual rolling element retainer segments surrounding the guide rail,
the plurality of individual rolling element retainer segments each including a respective load bearing track portion and a respective return track portion receiving a plurality of rolling elements which circulate along the load bearing and return portions during displacement of the tool housing along a length of the guide rail, and
the guide rail having an annular cross section and a shape selected from the group consisting of a cross-shaped cross section, I-beam cross section, regular polygonal cross-section and irregular polygonal cross section.
21. The tool as claimed in claim 20 , wherein the load bearing track portions are spaced apart and juxtaposed with the guide rail so that the rolling elements running along the load bearing tracks engage the guide rail to prevent relative rotation of the saw housing and the guide rail.
22. The tool as claimed in claim 20 , wherein the return track portions are spaced radially outwards from the load bearing track portions.
23. The tool as claimed in claim 20 , further comprising a base, a joint mounted on the base and rotatable about the axis, and a rail guide rail housing rigidly coupled to the joint and to the rails guide, so that the opposite ends of the guide rail are rotationally fixed to the tool housing and to the guide rail housing
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/140,877 US20050217449A1 (en) | 2000-10-24 | 2005-05-31 | Adjustable tool station |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US24285000P | 2000-10-24 | 2000-10-24 | |
PCT/US2001/050897 WO2002055895A1 (en) | 2000-10-24 | 2001-10-24 | Linear motion bearing segment |
US10/146,106 US6918330B2 (en) | 2000-10-24 | 2002-05-15 | Adjustable tool station |
US11/140,877 US20050217449A1 (en) | 2000-10-24 | 2005-05-31 | Adjustable tool station |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US10/146,106 Continuation US6918330B2 (en) | 2000-10-24 | 2002-05-15 | Adjustable tool station |
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US20050217449A1 true US20050217449A1 (en) | 2005-10-06 |
Family
ID=29548278
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
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US10/146,106 Expired - Lifetime US6918330B2 (en) | 2000-10-24 | 2002-05-15 | Adjustable tool station |
US11/140,877 Abandoned US20050217449A1 (en) | 2000-10-24 | 2005-05-31 | Adjustable tool station |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/146,106 Expired - Lifetime US6918330B2 (en) | 2000-10-24 | 2002-05-15 | Adjustable tool station |
Country Status (5)
Country | Link |
---|---|
US (2) | US6918330B2 (en) |
EP (1) | EP1507618A1 (en) |
AU (1) | AU2003241440A1 (en) |
CA (1) | CA2485789A1 (en) |
WO (1) | WO2003097284A1 (en) |
Cited By (1)
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US20110290092A1 (en) * | 2004-09-02 | 2011-12-01 | Shigeharu Ushiwata | Miter saw |
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US20060201299A1 (en) * | 2003-01-21 | 2006-09-14 | Santa Ana Roland C | Combination table-mitter saw & assembly |
US7047856B2 (en) * | 2003-01-24 | 2006-05-23 | Tapco International Corporation | Saw table |
JP4534549B2 (en) * | 2004-03-26 | 2010-09-01 | 日立工機株式会社 | Tabletop cutting machine |
JP2005279933A (en) * | 2004-03-26 | 2005-10-13 | Hitachi Koki Co Ltd | Bench cutter |
WO2005102626A2 (en) * | 2004-04-15 | 2005-11-03 | Milwaukee Electric Tool Corporation | Saw, such as a miter saw |
GB0503102D0 (en) * | 2005-02-15 | 2005-03-23 | Gmca Pty Ltd | Guide for cutting unit |
JP4650296B2 (en) * | 2006-02-22 | 2011-03-16 | 日立工機株式会社 | Tabletop cutting machine |
GB0713817D0 (en) * | 2007-07-17 | 2007-08-29 | Gmca Pty Ltd | Saw with circular blade |
US8359959B2 (en) * | 2008-01-08 | 2013-01-29 | Makita Corporation | Cutting devices |
DE202008011654U1 (en) * | 2008-09-02 | 2010-01-21 | Metabowerke Gmbh | Chop saw with pull function |
DE102008053901A1 (en) * | 2008-10-30 | 2010-05-06 | Schaeffler Kg | Supporting track element for a linear ball bearing and manufacturing method for the supporting track element and linear ball bearings |
US9649703B2 (en) | 2012-03-15 | 2017-05-16 | Rexon Industrial Corp., Ltd. | Circular saw with a moving mechanism |
JP2012176492A (en) * | 2012-05-13 | 2012-09-13 | Hitachi Koki Co Ltd | Table top cutter |
US8898913B1 (en) * | 2014-06-17 | 2014-12-02 | Michael J. Lones | Masonry circular saw stabilizing and supporting shoe |
CN208195813U (en) | 2015-02-25 | 2018-12-07 | 米沃奇电动工具公司 | Mitre saw |
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US8561513B2 (en) * | 2004-09-02 | 2013-10-22 | Hitachi Koki Co., Ltd. | Miter saw |
Also Published As
Publication number | Publication date |
---|---|
US6918330B2 (en) | 2005-07-19 |
CA2485789A1 (en) | 2003-11-27 |
WO2003097284A1 (en) | 2003-11-27 |
AU2003241440A1 (en) | 2003-12-02 |
EP1507618A1 (en) | 2005-02-23 |
US20030056632A1 (en) | 2003-03-27 |
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Legal Events
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |