Patent Document

CROSS-REFERENCE TO RELATED APPLICATION 
   This application claims the priority, under 35 U.S.C. §119, of Chinese Patent Application 2005 10 094 719.7, filed Sep. 30, 2005; the prior application is herewith incorporated by reference in its entirety. 
   BACKGROUND OF THE INVENTION 
   Field of the Invention 
   The present invention relates to a power tool, in particular to a wobble plate reciprocating saw. The power tool includes a housing, a rotary motor disposed in the housing, a jackshaft coupled to the rotary motor, a spindle mounted in the housing for carrying a tool, a first wobble plate assembly mounted on or coupled to the jackshaft so as to drive the spindle to reciprocate at least approximately linearly in a linear path along a predetermined axis, a counterweight mounted in the housing for performing a reciprocating motion relative to the housing, and a second wobble plate assembly mounted on or coupled to the jackshaft so as to drive the counterweight. 
   Known wobble plate reciprocating saws have a guide sleeve, a spindle sleeved in the guide sleeve, a first wobble plate assembly driving the spindle, a counterweight sleeved on the guide sleeve, and a second wobble plate assembly driving the counterweight. U.S. Pat. No. 5,025,562 discloses such a wobble plate reciprocating saw in which the counterweight is disposed on the guide sleeve and the spindle is disposed in the guide sleeve. The movement path of the counterweight is parallel to or coincident with the movement path of the spindle. In that conventional saw, there are a large number of fitting surfaces and frictional areas. The fitting surfaces need precision work so that there is a need to assemble the parts accurately, which results in heavy manufacturing costs. Large frictional areas also lead to the development of heat. 
   SUMMARY OF THE INVENTION 
   It is accordingly an object of the invention to provide a power tool, which overcomes the hereinafore-mentioned disadvantages of the heretofore-known devices of this general type, which is effective, but which has less frictional areas. 
   With the foregoing and other objects in view there is provided, in accordance with the invention, a power tool, comprising a housing, a rotary motor disposed in the housing, a jackshaft coupled to the rotary motor, and a spindle mounted in the housing for carrying a tool. A first wobble plate assembly is mounted on or coupled to the jackshaft for driving the spindle to reciprocate at least approximately linearly in a linear path along a predetermined axis. A counterweight is mounted in the housing for performing a reciprocating motion relative to the housing. The counterweight is pivotable relative to the housing about a pivot axis, to perform the reciprocating motion as a rotative reciprocating motion. The pivot axis is disposed in a plane perpendicular to the predetermined axis and fixed relative to the housing. A second wobble plate assembly is mounted on or coupled to the jackshaft for driving the counterweight. 
   The present invention advantageously exploits a counterweight pivotally connected to the housing in such a way that there is basically no friction with a large stroke and large area. If a guide sleeve should be applied to guide the spindle, the counterweight does not impede the guide sleeve during its motion towards and away from the front end of the tool. Nevertheless, due to the counterweight, the tool is basically vibration-free. This improves the stability of the tool, and assembling the counterweight and the guide sleeve is a straightforward, low cost procedure. 
   According to an embodiment of the invention, there is provided a power tool including a housing, a rotary motor, a jackshaft coupled to the motor, a spindle and a counterweight. A biangular driving member may be mounted radially on the jackshaft and may cooperate with a first wobble plate assembly to reciprocatingly linearly drive the spindle, and a second wobble plate assembly to reciprocatingly drive the counterweight. The counterweight is pivotally connected to the housing. The second wobble plate assembly drives the counterweight to swing back and forth relative to the housing about the pivot so that the swing path of the counterweight may intersect with the linear path of the spindle or may swing in a plane parallel to or containing the longitudinal axis of the spindle. 
   The power tool may include a guide sleeve sleeved on the spindle, in such a way that the spindle is slideable in the sleeve. The counterweight may swing past such a guide sleeve. The spindle may include a front component on which a blade is mounted, and a rear component connected to the front component. A first slot may be formed in and extend longitudinally along the guide sleeve. An opposing projecting portion may be defined on the rear component. The projecting portion may slide in the first slot along the longitudinal axis of the spindle. A second slot may be formed in and extend longitudinally along the guide sleeve. A socket and a cavity may be formed in the rear component. The first wobble plate assembly may include a first wobble arm passing through the second slot and the cavity to be received in the socket. 
   Preferably, the counterweight may include a U-shaped body. The U-shaped body may have two mass bodies of the same weight and the same configuration. The guide sleeve may be received in the U-shaped body. 
   The side arms of the U-shaped body may swivel at a very short distance from the sleeve. Thus, the rotative movement of the counterweight is not impeded by the guide sleeve. The counterweight may include a stirrup which surrounds or receives the second wobble plate assembly. The counterweight may be provided with a pin rotatably connected to the housing. The counterweight may pivotally rotate relative to the housing with the driving of the second wobble plate assembly. The angle between the first wobble plate assembly and the second wobble plate assembly may be zero. 
   The first wobble plate assembly may include a first bearing directly or indirectly mounted radially on the jackshaft. The first bearing may extend radially outwardly into a first wobble arm. The first wobble arm may operatively engage the spindle. The first wobble arm may terminate in a spherical tip. 
   The second wobble plate assembly may include a second bearing directly or indirectly mounted on the jackshaft. The second bearing may extend radially outwardly into a second wobble arm. The second wobble arm may terminate in a spherical tip. The first wobble arm and the second wobble arm may be in a common axial plane, i.e. at substantially the same angle when viewed along the axis of the spindle. 
   A biangular driving member may be mounted radially on the jackshaft and may cooperate with the first wobble plate assembly to linearly drive the spindle reciprocatingly and with the second wobble plate assembly to linearly drive the counterweight reciprocatingly. The biangular sleeve is typically stepped. The biangular sleeve may have a first angular part and a second angular part. The first angular part and the second angular part may respectively engage the first bearing and the second bearing and may be adapted to cause the first wobble arm and the second wobble arm to be driven reciprocatingly (particularly preferably to be driven reciprocatingly 180° out-of-phase and to reverse at the same instant). 
   Preferably, the counterweight includes a U-shaped body in which the guide sleeve is received axially. The U-shaped body may include a first arm, a second arm and a transverse connecting base connecting the first and second arms in a spaced apart relationship. The first arm and the second arm may be parallel. The first arm and the second arm may be upright. A receiving bore or cavity in the connecting base may receive the tip of the second wobble arm. 
   Preferably, the counterweight includes a stirrup (e.g. a substantially square-shaped stirrup) which surrounds the second wobble plate assembly. The stirrup may extend from the transverse connecting base. The base of the stirrup may be concave. 
   Preferably, the counterweight is pivotally mounted on a first transverse pin and on a second transverse pin in such a way that the second wobble arm drives the counterweight to pivotally rotate relative to the housing. The first transverse pin and the second transverse pin may be provided on the housing or on the counterweight (preferably on the stirrup). In this embodiment, there is an opposing element respectively disposed on the counterweight or on the housing to respectively engage the first and the second transverse pin. Preferably, the first transverse pin and the second transverse pin are provided on a peripheral face of the stirrup near a lower edge. 
   The center of mass of the counterweight is preferably positioned away from the point of engagement of the second wobble arm with the counterweight (e.g. the receiving bore in the transverse connecting base). 
   Preferably, the angle between the first wobble plate assembly and the second wobble plate assembly is zero, as mentioned above. 
   According to a preferred embodiment of all of the aspects of the invention, the power tool of the invention is a reciprocating saw, such as a saber saw. Of course, the invention may also be used in a plurality of other tools for making them largely free of vibrations during operation. 
   Other features which are considered as characteristic for the invention are set forth in the appended claims. 
   Although the invention is illustrated and described herein as embodied in a power tool, it is nevertheless not intended to be limited to the details shown, since various modifications and structural changes may be made therein without departing from the spirit of the invention and within the scope and range of equivalents of the claims. 
   The construction and method of operation of the invention, however, together with additional objects and advantages thereof will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  is a diagrammatic, partly broken-away, side-elevational view of an embodiment of a reciprocating saw according to the invention, in which a first wobble plate assembly is in its first position and a second wobble plate assembly is in its first position; 
       FIG. 2  is an enlarged, partly broken-away, side-elevational view of the embodiment of the reciprocating saw according to  FIG. 1 , in which the first wobble plate assembly is in its second position and the second wobble plate assembly is in its second position; 
       FIG. 2A  is a further enlarged, sectional view taken along a line IIA-IIA of  FIG. 2 , in the direction of the arrows; 
       FIG. 3  is a further enlarged, sectional view of the first and second wobble plate assemblies taken approximately along a line III-III of  FIG. 1 , in the direction of the arrows, perpendicular to an axis of a spindle; 
       FIG. 4  is a perspective view of a spindle and a counterweight of the embodiment of the invention shown in  FIGS. 1-3 ; 
       FIG. 5  is a perspective view of the counterweight of the embodiment of the invention shown in  FIGS. 1-4 ; 
       FIG. 6  is a highly-diagrammatic, side-elevational view of the spindle in its first position and the counterweight in its first position; 
       FIG. 6A  is a fragmentary, sectional view taken along a line VIA-VIA of  FIG. 6 , in the direction of the arrows; 
       FIG. 7  is a highly-diagrammatic, side-elevational view of the spindle in a position between its first position and its second position and the counterweight in a position between its first position and its second position; and 
       FIG. 8  is a highly-diagrammatic, side-elevational view of the spindle in its second position and the counterweight in its second position. 
   

   DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   Referring now to the figures of the drawings in detail and first, particularly, to  FIGS. 1 and 2  thereof, there is seen an embodiment of a reciprocating saw incorporating the invention. The saw is basically vibration-free. The saw generally includes a housing  1  and (within the housing  1 ) a rotary motor  2  having an output shaft  2   a  which is provided with a pinion  2   p . The pinion  2   p  engages a larger gear or wheel  2   q , which is coupled to a jackshaft  4  having a shaft axis Z. The jackshaft  4  is supported in the housing  1  by bearings  4   a  and  4   b.    
   An eccentric cam  4   f  and a biangular wobble drive member  10  are radially mounted between the bearings  4   a ,  4   b . The cam  4   f  rotates along with the gear  2   q  and the jackshaft  4  when the motor  2  is in operation. The cam  4   f  is basically an eccentric tube. A protrusion (not denoted by a reference symbol) is provided on the right side of the eccentric cam  4   f . The protrusion meshes with a slot in the left end face of the wobble drive member  10 . 
   The wobble drive member  10  cooperates with a first wobble plate assembly  5  to reciprocatingly drive a spindle  8  and with a second wobble plate assembly  6  to reciprocatingly drive a counterweight  7  about a pivotal axis Y (which can be seen in  FIGS. 3-5 ). 
   A guide sleeve  9  is also accommodated in the housing  1 . The spindle  8  is slideably mounted in the guide sleeve  9 . A bearing  95  disposed internally at the front end of the guide sleeve  9  supports the spindle  8 . The longitudinal direction of the spindle  8  and of the guide sleeve  9  is denoted by reference symbol X. 
   The spindle  8  includes a tubular rear portion or component  81  and a tubular front portion or component  82 . In the illustrated embodiment, the front component  82  has a slightly smaller diameter than the rear component  81 . The front component  82  has a back end fastened inside the rear component  81  through the use of a pin  84 . The entire spindle  8  is movable in the direction X relative to the housing  1 . This can be seen by comparing  FIG. 1  with  FIG. 2 . A clamping system  3   a  which is attached on the front end of the spindle  8  holds a longitudinal saw blade  3  as a tool. Thus, the direction X may be considered as a working axis. A pin  86  and a ring  87  are used for attachment. 
   As mentioned above, the spindle  8  is slideably disposed in the tubular guide sleeve  9 . An end face of the guide sleeve  9  is attached to an internal wall  1   i  of the housing  1 . Therefore, the guide sleeve  9  cannot move in the direction X. However, a pin  55  seen in  FIG. 6A  is inserted into a hole  54  in the guide sleeve  9 . Thus, the guide sleeve  9  can swivel very slightly about the axis of the pin  55 . In other words, the guide sleeve  9  in this case is pivotally attached to the housing  1 . The small up-and-down pivoting movement of the guide sleeve  9  is indicated by a double arrow D in  FIG. 1 . 
   Referring to  FIGS. 1 and 2 , it is seen that the front component  82  extends into the rear component  81 . A first slot  91  and a second slot  92  extend longitudinally along the guide sleeve  9 . The slots  91 ,  92  are disposed on opposite sides of the guide sleeve  9 . As can be seen in  FIG. 2 , a substantially rectangular projection  811  projects radially from the surface of the rear component  81  and is slideably engaged in the first slot  91  along the axis of the spindle  8 . The longitudinal length of the projection  811  is smaller than the longitudinal length of the first slot  91 . A tubular extension or socket  812  and a cavity  813  are defined in the interior of the rear component  81  of the spindle  8 . The socket  812  and the cavity  813  have a common axis which is perpendicular to the axis of the spindle  8 . The diameter of the socket  812  is smaller than that of the cavity  813 . 
   As a result of this construction, the spindle  8  can be moved longitudinally between the two ends of the first slot  91 . 
   The first wobble plate assembly  5  includes a first bearing  52  mounted radially on the biangular wobble drive member  10 . The first wobble plate assembly  5  additionally includes a first wobble arm  51  mounted on the first bearing  52 . The first wobble arm  51  terminates in a spherical tip  511 . The tip  511  of the first wobble arm  51  passes through the second slot  92  and through the cavity  813  and is received in the socket  812 . The length of the second slot  92  is chosen correspondingly to allow a sufficient movement of the first wobble arm  51 . 
   The second wobble plate assembly  6  includes a second bearing  62  mounted radially on the biangular wobble drive member  10 . The second bearing  62  supports a second wobble arm  61 , which is similar to the first arm  51 . The second wobble arm  61  terminates in a spherical tip  611 . It may be seen that the second wobble arm  61  is shorter than the first wobble arm  51 . The tip  611  of the second wobble arm  61  is received in a cavity  75  of the counterweight  7 , as is best seen in  FIG. 3 . The first wobble arm  51  and the second wobble arm  61  are in a common axial plane, i.e. they are at the same angle when viewed along the axis X of the spindle  8 , as is also seen in  FIG. 3 . The spindle  8  and the counterweight  7  thereby reverse at the same point in time. Of course, the reversal is in opposite directions. 
   The eccentric cam  4   f , which was already mentioned above, transmits the torque of the jackshaft  4  (i.e. the rotation of the gear  2   q ) to the wobble drive member  10 . The eccentric cam  4   f  is connected to a driving plate  96  which is mounted on the guide sleeve  9 . When the eccentric cam  4   f  rotates to drive the driving plate  96  into an up and down movement, the guide sleeve  9  moves and thus causes the spindle  8  and the blade  3  to move up and down slightly, as is indicated by the double arrow D. This improves the speed and quality of the sawing process. 
   The rotary motor  2  drives the jackshaft  4  to rotate, thereby causing the biangular wobble drive member  10  to rotate. The biangular wobble drive member  10  has a first angular part and a second angular part which respectively engage the first bearing  52  and the second bearing  62  and which are adapted to cause the first wobble arm  51  and the second wobble arm  61  to be driven reciprocatingly 180° out-of-phase and to reverse at the same instant (see  FIGS. 6 ,  7  and  8 ). When the first wobble arm  51  and the spindle  8  move to their first position illustrated in  FIG. 1 , the second wobble arm  61  and the counterweight  7  move oppositely to their first position. When the first wobble arm  51  and the spindle  8  move from their first position illustrated in  FIG. 1  to their second position within a U-shaped body  71  illustrated in  FIGS. 3-5 , the second wobble arm  61  and the counterweight  7  move oppositely to their second position. 
     FIGS. 3-5  illustrate that the counterweight  7  driven by the second wobble plate assembly  6  may be considered as a swing mechanism, as opposed to a mechanism carrying out linear reciprocating movements. The swing or pivot axis Y is defined on the counterweight  7 . 
   Referring to  FIGS. 3-5 , it is seen that the counterweight  7  includes a U-shaped body  71  and a frame-like receiving member or stirrup  72  which extends from the U-shaped body  71 . The U-shaped body  71  includes a first mass body  76 A, a second mass body  76 B and a transverse connecting base  77  which interconnects the first and second mass bodies  74 A,  76 B in a spaced apart relationship. The guide sleeve  9  extends axially through the space between the mass bodies  76 A,  76 B. A receiving bore or burrow hole  75  for receiving the tip  611  of the second wobble arm  61  is formed in the connecting member  77 . The tip  611  can be rotated in the hole  75 . 
   The stirrup  72 , which has a substantially square configuration, extends from the bottom of the U-shaped mass body  71 . This stirrup  72  receives or surrounds the second wobble plate assembly  6 . The stirrup  72  includes the connecting base  77 , a first side arm or side post  72   a , a second side arm or side post  72   b , which is parallel to and spaced apart from the first side arm  71   a , and a connecting member  72   c.    
   A first transverse pin  73  and a second transverse pin  74  are formed on the peripheral face of the stirrup  72  near the lower edges of the side arms  72   a ,  72   b . The pins  73 ,  74  are mounted coaxially and rotatably with the housing  1  to define the pivot axis Y substantially perpendicular to the longitudinal axis X of the spindle  8 . Thus, they form a pivot about which the counterweight  7  swings during operation. Alternately, the first pin  73  and the second pin  74  can be provided on the housing  1 , and corresponding holes may be disposed in the counterweight  7 , so that in this case the counterweight  7  is also pivotally connected to the housing  1 . 
   It must be stressed that the pivotal axis Y is fixed (i.e. not movable) with respect to the housing  1 . 
   As was already mentioned, the pivot axis Y of the counterweight  7  is substantially perpendicular to the longitudinal axis X of the spindle  8 . That is: the pivot axis Y is located in a plane perpendicular to the longitudinal axis X and is offset with regard to a non-illustrated axis which extends directly and perpendicularly through the longitudinal axis X. During operation, the second wobble arm  61  drives the counterweight  7  to swing back and forth relative to the housing  1  about the pivot axis Y. This reciprocating motion occurs in such a way that the swing path of the counterweight  7  intersects the linear path of the spindle  8 . The counterweight  7  pivots in (or alternately parallel to) a plane containing the longitudinal axis X of the spindle  8 . 
   The first pin  73  is disposed in a bearing seat  73 B, which is provided with a bearing, such as a powder bearing that is not illustrated in  FIG. 4  for the sake of clarity. The bearing seat  73 B is attached to the housing  1 . A lower attachment hole  73   u  and an upper attachment hole  73   o  are provided for this purpose. Similarly, the second pin  74  is disposed in a bearing seat  74 A, which is provided with a bearing that may again be a powder bearing. Correspondingly, there are provided holes  74   u  and  74   o  for fixing the bearing seat  74 A on the housing  1 . 
     FIG. 4  shows a side hole  85  for the pin  86  in the front component  82  of the spindle  8 , as well as the side hole  54  for the pin  55 . The pin  55  is illustrated in  FIG. 6A , as mentioned above. 
   According to  FIG. 6A , the guide sleeve  9  is provided with pinholes  54  on both sides. A pin  55  having a pinhead  55 H is inserted into each pinhole  54 . The pinheads  55 H each have an outside thread. Each pinhead  55 H can thereby be screwed into a channel  56  in each of two respective walls  1   a ,  1   b  of the housing  1 . The pins  55  prevent a movement of the sleeve  9  in the direction X. Yet, the sleeve  9  can slightly pivot about the longitudinal axis of the pins  55  (see the double arrow D in  FIG. 1 ). 
   During operation, the motor  2  drives the jackshaft  4  into rotation, and the jackshaft  4  drives the driving member  10  mounted on the jackshaft  4  into rotation. As a consequence, the driving member  10  drives the first wobble plate assembly  5  and the second wobble plate assembly  6  into movement. While the first wobble arm  51  along with the spindle  8  move to the position illustrated in  FIG. 1 , the second wobble arm  61  and the counterweight  7  move in the opposite direction. Finally, the first wobble plate assembly  5  and the spindle  8  driven by it are in their first position, and the second wobble plate assembly  6  and the counterweight  7  driven by it are in their first position. When the first wobble arm  51  and the spindle  8  subsequently move from the first position illustrated in  FIG. 1  towards the second position illustrated in  FIG. 2 , the second wobble arm  61  and the counterweight  7  move in the opposite direction. Finally, the first wobble plate assembly  5  and the spindle  8  driven by it are in their second position, and the second wobble plate assembly  6  and the counterweight  7  driven by it are in their second position. It must be stressed again that the reciprocating movement of the counterweight  7  is a rotational motion. 
   The swiveling angle of the counterweight  7  going from the first position to the second position, and vice versa, is about 10°. 
   It will be seen that the second wobble arm  61  is shorter than a conventional wobble arm and also shorter than the first wobble arm  51 . Referring to  FIG. 2  it will also be seen that the first wobble arm  51  cannot strike the second wobble arm  61  in the second position. Therefore, with reference to  FIG. 3 , the angle between the first wobble arm  51  and the second wobble arm  61  can be zero, as is seen along the longitudinal axis X of the spindle  8 . 
   Referring to the movement sequences shown in  FIG. 6 ,  FIG. 7  and  FIG. 8 , the following will be clear: When the jackshaft  4  driven by the motor  2  rotates half of a revolution, the first wobble plate assembly  5  and the spindle  8  driven by it move from their first position to their second position, and the second wobble plate assembly  6  and the counterweight  7  driven by it move from their first position to their second position. The opposite occurs when the jackshaft  4  rotates in the next half of a revolution. 
   In order to reduce vibrations when the reciprocating saw operates, a stroke s 2  and a weight w 2  of the system including the second wobble arm  61  and the counterweight  7  should be proportionate to a stroke s 1  and a weight w 1  of the entire system including the first wobble arm  51 , the spindle  8 , the blade  3 , and the clamping system  3   a . Preferably, the product (s 2 ×w 2 ) should be approximately equal to the product (s 1 ×w 1 ). For instance, if the weight w 1  of the entire system  51 ,  8 ,  3  and  3   a  is w 1 =200 g and the stroke is s 1 =32 mm, the product is (w 1 ×s 1 )=0.2 kg×32 mm=6.4 kg mm. Then, in order to balance or compensate for vibrations, the parameters of the counterweight system  7  may be selected in such a way that it has a weight w 2 =0.4 kg and a stroke s 2  of the center of the mass s 2 =16 mm, so that the product will be w 2 ×s 2 =0.4 kg×16 mm=6.4 kg mm. 
   It was already mentioned that the counterweight  7  is pivotally connected with the housing  1  (rotation about pins  73 ,  74 ), and that the guide sleeve  9  is received in the U-shaped mass body  71  of the counterweight  7 . This permits the counterweight  7  to reciprocate relative to the guide sleeve  9  which represents a simple movement. There is no friction with a large stoke and a large area, and the counterweight  7  does not impede the guide sleeve  9 . Therefore, the movement of the counterweight  7  and the spindle  8  improve the system&#39;s stability. The generation of heat is also relatively small, since linear sliding of the counterweight on a sleeve, which is used in the prior art, is avoided.

Technology Category: 7