Hand-Held Machine Tool

Abstract

There is a hand-held machine tool, in particular a saber saw, with a housing, a drive motor with an output shaft, a spindle for receiving a tool, in particular a saw blade, and a motion converter for converting a rotational motion of the drive shaft into a reciprocating motion of the spindle. The motion converter comprises an eccentric element driven by the output shaft rotationally about an axis of rotation with a driver part arranged eccentrically to the axis of rotation, and a pendulum element which is mounted pivotably about a bearing point and is connected via a coupling point to the spindle. The pendulum element has a guide element for guiding the driver part. In one embodiment, the guide element is arranged between the bearing point and coupling point.

Claims

1. A hand-held machine tool, in particular saber saw, comprising: a housing; a drive motor with an output shaft; a spindle configured to receive and drive a saw blade; and a motion converter configured to convert a rotational motion of the output shaft into a reciprocating motion of the spindle; wherein: the motion converter has an eccentric element driven by the output shaft rotationally about an axis of rotation with a driver part arranged eccentrically to the axis of rotation, and a pendulum element which is mounted pivotably about a bearing point and is connected via a coupling point to the spindle; the pendulum element has a guide element configured to guide the driver part; and the guide element is arranged between the bearing point and the coupling point.

2. The hand-held machine tool as claimed in claim 1, wherein; the bearing point and the coupling point define a first axis of the pendulum element; and the guide element allows a motion component, directed along the first axis of the pendulum element, of the driver part relative to the pendulum element and largely prevents a motion component, directed perpendicular to the first axis of the pendulum element, of the driver part relative to the pendulum element.

3. The hand-held machine tool as claimed in claim 1, wherein: the guide element forms a receiver in the pendulum element into which the driver part engages.

4. The hand-held machine tool as claimed in claim 3, wherein: the receiver is an elongated hole; and the elongated hole is oriented substantially along the first axis of the pendulum element.

5. The hand-held machine tool as claimed in claim 1, wherein a first distance of the guide element to the bearing point and a second distance of the coupling point to the bearing point are matched to one another in such a manner than the reciprocating motion of the pendulum element at the guide element has a first amplitude and at the coupling point a second amplitude; and an amplitude ratio (R) of the second amplitude to the first amplitude has a value which is not equal to 1.

6. The hand-held machine tool as claimed in claim 5, wherein the amplitude ratio (R) has a value R>1.

7. The hand-held machine tool as claimed claim 1, wherein; the bearing point in each position of the spindle has at least a distance Δ perpendicular to a longitudinal axis of the spindle; and the distance Δ has a fixed value greater than zero.

8. The hand-held machine tool as claimed in claim 1, wherein: the axis of rotation lies perpendicular to the output shaft; and the eccentric element is driven via a worm drive by the output shaft.

9. The hand-held machine tool as claimed in claim 1, wherein: the spindle is mounted using a needle bearing on the housing; and the needle bearing prevents a motion component directed transversely to a longitudinal axis of the spindle of the spindle relative to the housing.

10. The hand-held machine tool as claimed in claim 11, wherein: a third distance between the needle bearing and the coupling point along the longitudinal axis of the spindle is selected so that the reciprocating motion of the spindle is superimposed by a tilting motion of the longitudinal axis of the spindle about the needle bearing so that an orbital motion of the tool arises at a tip of the tool.

11. The hand-held machine tool as claimed in claim 1, wherein an eccentric counterweight configured to compensate an imbalance of the eccentric element is arranged on the driver part.

12. A motion converter configured to convert a rotational motion of an output shaft of a drive motor into a reciprocating motion of a spindle of a saber saw, the motion converter comprising: an eccentric element driven by the output shaft rotationally about an axis of rotation with a driver part arranged eccentrically to the axis of rotation; and a pendulum element with a first end mounted pivotably at a bearing point and a coupling point connected to the spindle, wherein: the pendulum element has a guide element configured to guide the driver part; and the guide element is arranged between the bearing point and the coupling point.

13. The motion converter as claimed in claim 12, wherein: the bearing point and the coupling point define a first axis of the pendulum element; and the guide element allows a motion component, directed along the first axis of the pendulum element, of the driver part relative to the pendulum element and largely prevents a motion component, directed perpendicular to the first axis of the pendulum element, of the driver part relative to the pendulum element.

14. The hand-held machine tool as claimed in claim 6, wherein: the amplitude ratio (R) has a value R>1.5.

15. The hand-held machine tool as claimed in claim 14, wherein: the amplitude ratio (R) has a value R>2.

Description

DRAWINGS

[0034] The invention will be explained in greater detail below on the basis of exemplary embodiments represented in the drawings. In the drawings:

[0035] FIG. 1 shows a schematic side view of a hand-held machine tool according to the invention with a motion converter according to the invention;

[0036] FIG. 2 shows a schematic side view of the motion converter from FIG. 1 in portion A;

[0037] FIG. 3 shows a first schematically perspective side view of the motion converter according to the invention from FIG. 1 in portion A;

[0038] FIG. 4 shows a second schematically perspective side view of the a motion converter according to the invention from FIG. 1 in portion A; and

[0039] FIG. 5 shows a schematic partial cut-out of the a motion converter according to the invention from FIG. 1;

[0040] FIG. 6 shows a schematic representation of the kinematics of a motion converter according to the invention in a hand- held machine tool;

[0041] FIG. 7 shows a trajectory of a tip of a tool in conjunction with the kinematics represented in FIG. 6; and

[0042] FIG. 8 shows a schematic representation of a speed profile of a tip of a tool mounted on a hand-held machine tool according to the invention.

[0043] FIG. 1 represents a side view of a battery-operated hand- held machine tool 100 according to the invention which is formed by way of example as saber saw 100. FIG. 2 shows some of the components arranged inside a housing 110 of the hand-held machine tool.

[0044] These components include, among other things, an electric drive motor 200 with output shaft 210 as well as a spindle 112 mounted at least partially in housing 110 for receiving a tool 114. Spindle 112 projects in the embodiment shown in the region of a workpiece stop 116 out of housing 112.

[0045] Moreover, a motion converter 500 for converting a rotational motion of output shaft 210 into a reciprocating motion of spindle 112 relative to housing 110 is arranged inside hand- held machine tool 100. Spindle 112 is thus fastened movably to housing 110 and in terms of drive is coupled to electric drive motor 200. Tool 114, which is formed, for example, as represented as a saw blade, is attached to a first end of spindle 112. Second end of spindle 112 is located in the embodiment shown in each position inside housing 110 and is connected to a pendulum element 400 described in greater detail in conjunction with FIGS. 2 to 5.

[0046] Housing 110 has a first handle 117 which has the form of a closed bracket and forms an opening 115 so that a user can better enclose handle 117 with his/her fingers. Housing 110 furthermore has a battery pack 600 and in the upper region of handle 117 an operating element 119 to control the drive motor.

[0047] As represented in detail in FIGS. 2 to 5, a motion converter 500 according to the invention has an eccentric element 300 driven by output shaft 210 rotationally about an axis of rotation 220 with a driver part 310 arranged eccentrically to axis of rotation 220.

[0048] Motion converter 500 furthermore has a pendulum element 400 with first end 410 and a second end 420. First end 410 is mounted pivotably at a bearing point P inside housing 110 and second end 420 is connected to spindle 112. In this manner, pendulum element 400 can execute a pendulum or swing motion about bearing point P. Spindle 112 is mounted by means of a needle bearing 118 at a point D shown in figure on housing 110 so that a motion component, directed transversely to a longitudinal axis of spindle 112, of spindle 112 relative to housing 110 is prevented at this point D. The bearing point P in each position of spindle 112 at least a distance Δ>0 perpendicular to a longitudinal axis of spindle 112.

[0049] As is apparent in FIGS. 3 and 4, axis of rotation 220 lies in the embodiment shown perpendicular to output shaft 210. Eccentric element 300 is therefore driven in this embodiment via a worm drive by output shaft 210, wherein, in the embodiment shown, a worm gear 211 sits on the output shaft, as is shown in FIG. 5.

[0050] First end 410 and second end 420 of the pendulum element define a longitudinal axis L of pendulum element 400, wherein pendulum element 400 has a guide element 430 between first end 410 and second end 420.

[0051] Guide element 430 has, in the represented embodiment, an elliptical receiver which is in engagement with a driver part 310, arranged eccentrically to axis of rotation 220, of eccentric element 300.

[0052] Eccentric element 300 is, in the embodiment shown, an eccentric disk which bears driver part 310 formed as a cylinder. In order to reduce the friction between driver part 310 and guide element 430, a ring bearing 314 is arranged between the two components.

[0053] In order to reduce vibrations during operation, an eccentric counterweight 312 for compensation of the imbalance of eccentric element 300 is arranged on driver part 310.

[0054] FIG. 6 shows a schematic representation of the kinematics of motion converter 500. Pendulum element 400 is represented by its longitudinal axis L in the various positions L′, L″ and L″′. As a result of the mounting of first end 410 at bearing point P, representations L′, L″ and L″′ of longitudinal axis L intersect at point P. Second end 420 of pendulum element 400 is connected to spindle 112 which in turn at point D is mounted via needle bearing 114 in the transverse direction on the housing.

[0055] The path of a center point of driver part 310 is represented in FIG. 6 by circle A. Since, in the embodiment shown, the center point of driver part 310 always lies on longitudinal axis L of pendulum element 400, a position of the center point of driver part 310 in the case of A1 corresponds to a location of the longitudinal axis in the case of L′. In FIG. 6, this is the position at which spindle 112 is maximally retracted in the housing. A position of the center point of driver part 310 in the case of A2 correspondingly corresponds to a location of the longitudinal axis in the case of L″′. This is in turn the position in which spindle 112 projects maximally out of the housing. A1 and A2 correspond to the turning points of spindle 112 in their lifting motion along their longitudinal axis.

[0056] In the case of a rotation of the center point of driver part 310 along circular path A in a clockwise direction, represented by arrow R, an increase in this center point to bearing point P increases and reduces cyclically. This distance has at point A3 maximum value d3 and at point A4 minimum value d4. In the case of a constant speed of rotation of drive motor 200, this means that the pendulum motion of pendulum element 400 from location L″′ to L′ occurs more quickly than that from location L′ to L″′. This can be referred to as an asymmetrical cutting motion. The lifting motion of spindle 112 in the direction into housing 112 is correspondingly faster than the opposite direction out of housing 112. In the case of arrangement of the teeth on saw blade 114 such that they cut under tension, i.e. in the case of the motion of the spindle in the direction into the housing, this means that the cutting motion is executed with greater energy than the lifting movement out of the housing. High efficiency of the cutting process is achieved as a result.

[0057] It is furthermore apparent from FIG. 6 that the kinematics according to the invention result in a tilting of the longitudinal axis of spindle 112 about needle-mounted point D which superimposes the lifting movement of spindle 112. This leads to a point E at the end of spindle 112 remote from pendulum element 400 executing a movement along path 600 which is represented in an enlarged form in FIG. 7. This type of motion which is transmitted to saw blade 114 can be referred to as an orbital motion and brings about a fast and highly efficient sawing process with high cutting power.

[0058] The circumstances explained on the basis of FIG. 6 are once again illustrated in FIG. 8. FIG. 8 shows a diagram which reproduces the magnitude of the path speed at point E represented in FIG. 6 over the angle covered by pendulum element 400 (as a magnitude-based sum) in the form of a curve v.

[0059] As a result of the reciprocating motion of spindle 112, curve v has a cyclical profile. Since the path speed of point E ultimately goes back to the circular motion of driver part 310 which is transmitted by a variable lever arm to pendulum element 400 and as a result to spindle 112, curve v has in portions a profile which can be referred to as approximately sinusoidal.

[0060] Points A1, A2, A3, and A4 on curve v marked in FIG. 8 correspond to the positions, represented in FIG. 6, of driver part 310 along circle A. According to the kinematics described in the context of FIG. 6, the path speed of the the point E which is transmitted, for example, to a saw blade, at point A4, i.e. in the case of the maximum movement of spindle 400 directed toward the housing, is at its maximum, while it is at its minimum at points A1 and A2, i.e. the turning points of spindle 112, corresponding to positions L′ and L″′ of pendulum element 400. At point A3, corresponding to the maximum speed of spindle 112 directed out of the housing, curve v reaches a value which, in the present embodiment of the invention, lies 42% below the value reached at point A4.

[0061] It is fundamentally pointed out that the present invention is not restricted to a saber saw, rather in principle can also be used in different hand-held machine tools with a motion converter, in the case of which a cabled or a wireless with a battery-operated electric drive motor 200 or a drive motor 200 is arranged in a housing 110.

[0062] In addition to the described and depicted embodiments, further embodiments are conceivable which can encompass further modifications as well as combinations of features.