JPH10136784A - Hand working device provided with driving motor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a hand working device provided with a driving motor by which structure is simplified as much as possible and wear is reduced in a transmission device such as a shearing blade tool, etc. SOLUTION: The transmission device 9 for converting the rotary movement of the driving motor into the progressive movement of the tool 10 is provided with a gear connected to a structure material 13 which eccentrically slides on a gear end surface. The structure material 13 which slides on the base part of the gear and/or the gear end surface is provided with recessions 16 and 17 (at least one) being opened as against a sliding plane and being useful for the reception of a lubricant. Thus, wear loss and the wear of the material 13 are clearly reduced so that an effective and sure lubrication is normally executed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hand-held power tool, and more particularly to a hand-held power tool provided with a driving motor according to the preamble of claim 1, and more particularly to a shearing blade or a scissor tool (pruning or shearing tool). . That is, more specifically, the present invention relates to a hand-held working device such as a shearing blade tool including a drive motor and a transmission device between the drive motor and the tool (10, 11, 36). A working device comprising at least one gear and a structural member slidable along an end face of a base of the gear.

[0002]

2. Description of the Related Art German Patent Publication No. 38 16 362 describes an electric shearing tool (or pruning scissors) which includes two blades driven via a transmission provided between a drive motor and a shearing blade. I have. The transmission includes, in particular, a gear that is supported by a shaft bolt and is connected to an eccentric wheel. The eccentric wheel comprises a base provided with eccentric projections on each end face, and both eccentrics are diametrically opposed. The eccentric engages an opening in a connecting rod that is also articulated to the shearing blade.

[0003]

The connecting rod is configured such that only a small surface is in contact with the end surface of the eccentric wheel.
Thus, a large surface pressure occurs. However, wear is thus increased. This is because wear of the end face of the eccentric wheel is inevitable.

[0004] The object of the present invention is thus to create a hand-held working device whose construction is as simple as possible and which suffers substantially less wear, in particular of the kind disclosed at the outset (introductory part of claim 1). It is in.

[0005]

This object is achieved by a hand-held working device having the features of the characterizing part of claim 1. That is, the present invention provides that the base of the gear is provided with at least two recesses or notches serving to receive lubricant, and the recess or notch in the base of the gear is opened at both end faces, Is characterized in that a sliding surface is formed on the end face of the.

An essential advantage of the present invention is that the lubrication that is maintained on the high load surface over an extended operating period is ensured without additional structural components. As the lubricant, grease whose viscosity changes according to a temperature change but does not fluidize is used. Depressions or notches (represented by "recesses" hereinafter) serve as grease reservoirs, which are open to the sliding surface, and thus, the sliding of structural members that slide along the end face of the gear. Grease existing on the end face is constantly applied to the surface. On both ends of the base,
A sliding surface is formed and the recess in the base of the gear is open at both end faces. Thus, the grease reservoir in each recess simultaneously serves to lubricate both sliding surfaces.

[0007]

DETAILED DESCRIPTION OF THE INVENTION The present invention, in a further aspect,
The respective features are set forth in the dependent claims, but advantageous embodiments of the invention are outlined below. It should be noted that reference numerals in the drawings appended to each claim in the claims are for the purpose of facilitating the understanding only, and are not intended to limit the present invention to the illustrated embodiments.

It is expedient if the gear has at least two recesses diametrically arranged. Thus, a uniform application is achieved on the sliding surface, in which case the excess amount of lubricant removed from the dent is respectively transferred to the next dent. If the recess is a slot extending in the circumferential direction, a particularly preferred configuration of the recess is obtained. In this case, it is advantageous to provide six recesses symmetrically arranged with respect to the axis of symmetry in the radial direction, distributed over the circumference of the base.

[0009] In a special embodiment, the structural member cooperating with the gear is a device for converting a rotational movement into a translational movement.
For this reason, the structural member is eccentrically supported by the gear, and the structural member is provided with an opening in which the eccentric projection on the base end face engages (fits). In the case of a device based on the crank principle, the structural member is a connecting rod which is connected to a shearing blade. In order to reduce the structural components required for the transfer of forces, a ring can be formed at the rear end of the blade of the structural member, which is preferably a shear blade, with an opening acting as a coupling mechanism for the eccentric.

To avoid solidification of the lubricant due to deterioration, it is advantageous to exert an effect on the grease volume such that a slight sliding of the lubricant takes place parallel to the axis of rotation of the gear. Thus, the lubricant is always supplied to the sliding plane or the sliding surface of the structural member and is driven by the structural member.
The base has two recesses in the area of the sliding surface for the structural member, so that the excess grease volume removed from the lubricant reservoir is not pushed out and is fed appropriately to the next recess. It is advantageous to provide at least one groove extending between them and interconnecting said recesses. In this case, a ring-shaped groove, in which a plurality, preferably four, depressions touch, is considered a preferred embodiment. It is particularly advantageous if the grooves extend along the peripheral contour of the legs of the eccentric, so that the peripheral surface of the eccentric or the connecting mechanism (connecting link) also has the effect of lubricating.

[0011]

Embodiments of the present invention will be described below in detail with reference to the drawings.

FIG. 1 shows a drawing of the lower part of a shearing blade tool having a blade 10 slidably supported in a longitudinal direction on a housing 2. The housing 2 includes a transmission housing 3 provided with a transmission 9 connected to a blade 10. Transmission 9
Is essentially a gear 20 driven by the pinion 8
And an eccentric 15 provided on the end face of the gear 20 and engaging with an opening 18 formed in a ring 13 at the rear end 12 of the blade 10
Consists of The opening 18 has an inner dimension corresponding to the diameter of the eccentric 15 in the longitudinal direction of the blade 10.
Is configured wider than the eccentric in the direction perpendicular to the longitudinal direction of the blade, so that the inner peripheral surface of the ring 13 forms a coupling mechanism 14 for the peripheral surface of the eccentric 15. Gear 20
Are provided with recesses or notches (hereinafter, referred to as “recesses”) 16, 17 extending in an arc shape at a radial distance from the outer peripheral surface of the gear 20.

FIG. 2 shows an axial sectional view of the pinion 8 connected to the transmission 9 and the driving motor or motor (Antriebsmotor). Housing 2
Includes the transmission housing and the clutch housing 4 as an integral structure. In the clutch housing 4, there is provided a clutch drum 6 in which a pinion 8 is rigidly connected to a bottom surface 6 'with torque. The pinion 8 is provided with the shaft 5 received by the ball bearing 6 adjacent to the bottom surface 6 ′ of the clutch drum 6. The pinion 8 meshes with a tooth ring 20 ′ of a gear 20 including a base (main body or hub) 23 and eccentrics 15 and 19 protruding from the base end faces 21 and 21 ′.
The gear 20 is provided at its center with a shaft 25 which is received in a bearing 24 formed in the transmission housing 3.
As is evident from FIG. 2, the shearing blade tool 1 also has, however, a mirror-symmetrical arrangement of the end faces 21, 21 'of the gear 20.
And two relatively moved blades 10, 11 received on the first and second blades. In this case, an opening is provided in the rear end 12 which has a large diameter and is formed in a long ring shape, and the eccentrics 15 and 19
Project into this opening, thus each ring 13
It surrounds the peripheral surfaces of the eccentrics 15,19. Thus, ring 1
3, 13 'are in contact with the end surfaces 21, 21' of the base 23, and sliding surfaces 22, 22 'are formed between the base 23 and the rings 13, 13'.

FIG. 3 shows a gear 2 as a single (integral) member.
0 is shown from the axial direction. The gear 20 has a tooth ring 20 'on the outer peripheral surface, and has a bore 26 at the center for receiving the shaft shown in FIG. The base 23 has a tooth ring 20
A total of six recesses 16, 17, 27, 16 ', 17 extending in an arc and having the shape of a slot, at a radial distance from'
'And 27' are provided. In this case, the recesses 27, 27 '
Are configured to be wider in the radial direction than the recesses 16, 17, 16 ', 17'. With respect to an axis A extending at right angles to the rotation axis of the gear 20, recesses 16, 17, 27 and 16 ', 17
'And 27' are arranged symmetrically. From FIG. 3, it is further evident that the mass centers of gravity of the eccentrics 15, 19 are also on the axis A and each have the same radial distance to the axis of rotation, so that the gear 20 is effectively unbalanced Is not shown. Along the peripheral surface of the eccentric 15, a concave 1
An annular groove 28 intersects the radially inner area of 6, 17, 27, 27 ', i.e. the annular groove 28 contacts four out of a total of six recesses of the base 23.

FIG. 4 is a sectional view taken along line IV-IV in FIG. As is apparent from FIG.
Each of the eccentrics 15 and 19 has the same radial distance with respect to the axis of rotation. Along the circumference of the eccentric 15, the legs of the eccentric and the end face 21
Has an annular groove 28 extending to the crossing portion. A corresponding annular groove 28 'is provided at the intersection of the eccentric 19 and the end face 21'.

FIG. 5 is an enlarged view of a portion V of FIG.
The base 23 extends exactly along the peripheral surface of the eccentric 15,
An annular groove 28 having an outer edge formed by the end face 21 of the base 23 is provided.

FIGS. 6a to 6d show plan views of the gear 20 shown in FIG. In the figure, on one side (left side), the blade 10
With the relevant end 12 excluded, while the other (right side)
The associated end 12 is shown. FIG.
FIG. 6 shows the position of the gear 20 at an angle of 360 ° or 360 °.
6B shows the position at a rotation angle of 90 °, FIG. 6C shows the position at a rotation angle of 180 °, and FIG. 6D shows the position at 270 °. The reference symbols of the same parts are the same as those of FIG.

As shown in FIG. 6 a, the eccentric 15 is in the uppermost position, that is, in a range where the connecting mechanism 14 as the opening 18 shows the arc shape of the ring 13. In this case, the curvature of the arc corresponds to the peripheral surface of the eccentric 15. The gear 20
From this position, it is rotated about the axis of rotation D in the direction of arrow P, and thus the eccentric 15 of the gear 20 reaches the position of FIG. 6b. In this case, the peripheral surface of the eccentric 15 is
Along 4 (ring inner surface), the coupling mechanism 14 is moved to the straight part, thus the ring 13 is moved to the left in the drawing, so that the blade 10 is also pulled to the left.
In this case, the ring 13 slides on the surface 21 of the gear 20 and receives lubricant application by movement along recesses 16, 17, 27 which serve as a lubricant reservoir.

The gear 2 moves in the direction of arrow P around the rotation axis D.
With a further rotation of 0, the eccentric 15 reaches the position of FIG. 6c and assumes the lowest position. Based on this movement of the eccentric 15, the ring 13 and thus the blade 10 are also moved to the right again, and the further rotation of the gear 20, the further movement of the blade 10 in the longitudinal direction, thus the eccentric 15 The straight section of the coupling mechanism 14 is reached. On the basis of such a movement, the ring 13 is provided with recesses 16, 17, filled with lubricating grease.
It slides along the end face 21 over 27, 16 ', 17', 27 ', i.e. the ring is always coated with a sufficient amount of lubricant. The excess amount of lubricant is supplied to the next recess or pushed into the annular groove 28 by the movement of the ring 13, so that the lubricant passes through the annular groove into one of the openings where the annular groove 28 contacts. Can be supplied.

The entrainment of the lubricant by the movement of the ring 13 and the pushing of a portion of the lubricant into the next recess produces a pumping effect to move the stored lubricant. In this case, ring 1
Predetermined amount (volume) of lubricant introduced into the recess by 3
Pushes the lubricant in the recess, so that the lubricant gradually reaches the other end face of the base in the axial direction and is then entrained by the ring sliding along said end face. That is, the circulation of the lubricant that suppresses the solidification or the resinification occurs. The viscosity of the lubricant also changes based on the heating (temperature rise) of the transmission, but fluidization is avoided.

FIG. 7 shows a gear 30 having a central opening 26 for receiving a rotating shaft or shaft. A tooth ring 30 'is provided on the outer peripheral surface. Radially opposed recesses 32, 32 'are provided radially relative to the central opening 26 and the annulus 30' to assist in receiving lubricant. In addition, other recesses 34 serving as lubricant reservoirs can be provided with a uniform distribution.

FIG. 8 is a sectional view taken along line VIII-VIII in FIG. In this case, the end face 31 of the base 32 of the gear 30,
31 ′ is configured flat, ie, no eccentric is formed on the end face. FIG. 9 shows the movement of the gear 40 by the transmission 29 in the form of a crank drive,
6 shows a device for transmission. In this case, the base 43 of the gear 40 is provided with an eccentric 42 on the front surface 41,
An eccentric 42 'is provided on the back, and both eccentrics are arranged diametrically next to one another. Gear 40
Is provided with a center bore 26, and a tooth ring 40 'is formed on the outer peripheral surface. The eccentrics 42, 42 'are provided with concave curved portions 45, 45' in the range of the outer peripheral surface farthest from the center bore 26. The base is correspondingly provided with two recesses 44, 44 ', in which case the recess 44 in the front face 41 is almost completely covered by the eccentric 42, and the recess 44' in the back face is likewise The eccentric 42 is likewise well covered.

The eccentric 41 has a connecting rod (link rod).
A ring 39 is formed at one end of 38 and surrounds the peripheral surface of the eccentric 41, and a radial play (clearance) is formed between the ring 39 and the eccentric 41.
The connecting rod 38 is pivotally linked at the other end to the neck 37 of the shearing blade 36, so that the circular movement performed by the eccentric 41 is converted into a longitudinal movement of the blade 36. An opening is formed between the inner peripheral surface of the ring 39 and the concave curved portion 45 of the eccentric 41 to connect the recess 44 to the outer surface. Due to the sliding movement of the ring 39 along the circular path, the ring is recessed 44 as already described with respect to the other embodiments.
The lubricant is received at the time of application of ′, thus lubricating the sliding surface. The temperature rise that occurs during operation of the work implement causes the viscosity of the grease to decrease, thus allowing the grease—with the aid of centrifugal force—to easily exit the recess 44 and flow into the lubrication gap. The wear particles that collect in the dents are also washed out by the grease and can flow out without consolidation due to the radial gap between the ring 39 and the eccentric 41. When the lubricant needs to be replenished, grease may be applied to the end face 41 of the gear 40 near the tooth ring 40 ′. Next, connecting rod 3
8 applies grease to the depressions 44.

[0024]

According to the basic structure of the present invention (claim 1),
With a structure which is as simple as possible, a transmission with essentially reduced wear is achieved. That is, an eccentric transmission having a simple mechanism in which the lubricant is constantly supplied to the eccentric sliding surface at the end face of the base portion of the gear is provided.

Further developments based on the above-mentioned basic structure of the present invention are as shown in the dependent claims 2 and so on, and a special additional effect is achieved in each case. For more information on its effects,
This is as described in the means for solving the problem, the embodiment, and the example, and the re-statement is omitted.

[Brief description of the drawings]

FIG. 1 is a bottom view of a housing including a transmission coupled with a shearing blade.

FIG. 2 is a sectional view along the axis of the transmission received in the housing.

FIG. 3 is a drawing of a gear seen from an axial direction.

FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3;

FIG. 5 is an enlarged view of a portion V in FIG. 4;

FIG. 6 shows the angular movement of the gear in four different angular positions and the resulting movement of the shearing blade.

FIG. 7 is a drawing showing one embodiment of a gear.

FIG. 8 is a sectional view taken along line VIII-VIII in FIG. 7;

FIG. 9 is a drawing showing a crank drive for a shearing blade.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Shear blade tool 2 Housing 9,29 Transmission device 10,11,36 Tool 13,13 ', 39 Structural member 14 Connection part 15 Eccentric 16,16', 17,17 ', 27,27', 32,32 ' , 44,44 'recess (or notch) 20,30,40 gear 21,21', 31,31 'end face (of gear) 23,33 base (of gear)

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Karl-Heinz Lange Germany, 73630 Remsharden, Wilhelm Enslestrasse 77 (72) Inventor Stefan Ostendorf, Germany, 71384 Weinstadt, Burgunderstrasse 16

Claims (13)

[Claims] And a transmission (9, 2) provided with a drive motor.
9) between a drive motor and a tool (10,11,36), the transmission comprising at least one gear (20,30,40) and a gear (20,3).
0,40) at the end face (21,33) of the base (23,33,43).
21 ', 31, 31') and a base member (23, 33, 43) of a gear (20, 30, 40) comprising a structural member (13, 13 ', 39) slidable along the gear (20, 30, 40).
Have at least two recesses or notches (16, 16 ', 17, 17', 27, 27) which serve to receive lubricant.
', 32, 32', 44, 44 ') and recesses or notches (16, 16', 17, 17 ', 27, 27') in the base (23, 33) of the gear (20, 30). , 3
, 32 ′) are both end faces (21, 21 ′, 31, 3)
1 ′), and both end faces (21,
21 ′, 31, 31 ′) is provided with a sliding surface. 2. A recess or notch (44, 44 ') on one side of the base (42) essentially comprises an eccentric (42, 4).
The working device according to claim 1, wherein the working device is covered by one of 2 ′). 3. The gears (20, 30, 40) have recesses or notches (16, 16 ', 17, 17', 27, 27 ',
32, 32 ', 44, 44') are diametrically arranged on the gear wheel. 4. The dent or notch (16, 16 ', 1)
7, 17 ') is configured as an elongated hole extending in the circumferential direction. 5. The dent or notch comprises six dents or notches (16, 16 ', distributed over the circumference).
17. The working device according to claim 4, wherein the first, second, third, fourth, third, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fourth, fifth and seventh are symmetrically arranged. 6. A gear (2), wherein said structural member (13, 38) is
2. The working device according to claim 1, wherein the working device is eccentrically supported at (0, 40). 7. The base member (2, 3), wherein said structural member (13, 38) is
The opening (1) with which the eccentric projection (15, 19, 42, 42 ') of the end face (21, 21', 41) of the third surface (43, 43) engages.
7. The working device according to claim 6, comprising: (8). 8. The working device according to claim 7, wherein the structural member is a connecting rod (38) pivotally connected to the shearing blade (36). 9. A concave or notch (44, 44 ') is provided on the peripheral surface of the eccentric (42, 42').
The working device according to claim 8, further comprising a concave curved portion (45, 45 ') connected to an outer surface of the working device. 10. The working device according to claim 7, wherein the structural member is a ring formed at the rear end of the shearing blade and having a connecting mechanism. 11. The base (23) extends between two recesses or notches (16, 17, 27) for the structural member (13) in the area of the sliding surface (22). 11. Working device according to one of claims 2 to 10, characterized in that at least one groove (28, 28 ') interconnecting the two recesses or notches is provided. 12. A plurality of recesses or notches (16, 17,
12. Working device according to claim 11, characterized in that there is provided an annular groove (28, 28 ') in contact with the working device (27, 27'). 13. The eccentric (1) is provided with a groove (28, 28 ').
13. The working device according to claim 12, wherein the working device extends along the peripheral contour of (5, 19).