PORTABLE POWER TOOL COMPRISING AN EPICYCLIC REDUCTION GEAR

Abstract

A portable power tool including, within a housing: an electric motor having a drive shaft, an epicyclic reduction gear having planetary gears meshing with a central gear of the drive shaft of the electric motor, the reduction gear being provided with an output shaft that is rigidly connected to a ball screw of a ball screw/nut mechanism and is coaxial to the ball screw, and a support bearing connecting the output shaft to the housing. The tool includes at least one stabilization bearing axially offset relative to the support bearing. The stabilization bearing connects the output shaft of the epicyclic reduction gear to the housing by at least one intermediate part selected from: the drive shaft of the electric motor, planet-carrier axles of the epicyclic reduction gear, and epicyclic reduction gears of the epicyclic reduction gear. The structure is of use in shears, in particular sheet metal shears.

Claims

1. Portable power tool comprising, in a housing: an electric motor with a drive shaft; an epicyclic reduction gear with planet pinions meshed on a central pinion of the drive shaft of the electric motor, the reduction gear being equipped with an output shaft that is rigidly integral with a ball screw of a ball screw-nut mechanism and coaxial to the ball screw; a support bearing connecting the output shaft to the housing characterized by: at least one stabilization bearing, axially offset relative to the support bearing, the stabilization bearing connecting the output shaft of the epicyclic reduction gear to the housing by at least one intermediate part chosen among: the drive shaft of the electric motor; planet carrier axes of the epicyclic reduction gear; and planet pinions of the epicyclic reduction gear, the planet pinions presenting, in this case, each a cylindrical shoulder with a diameter essentially equal to the pitch diameter of the pinion, the shoulder of the planet pinions forming a roller band and being respectively in rolling contact with a smooth-running ring, integral with the housing.

2. Portable power tool according to claim 1, in which the output shaft of the epicyclic reduction gear comprises an axial boring and in which the drive shaft of the electric motor presents one end received in the axial boring of the output shaft through the intermediary of the stabilization bearing.

3. Portable power tool according to claim 1, in which the stabilization bearing is mounted on a portion of the drive shaft of the electric motor located between the electric motor and the central pinion, the stabilization bearing being connected to the output shaft of the reduction gear through the intermediary of the planet carrier axes.

4. Portable power tool according to claim 1 in which the planet carrier axes are each provided respectively with a stabilization bearing of the output shaft, the stabilization bearings being in rolling contact with a smooth runner ring of the housing.

5. Portable power tool according to claim 1, in which the drive shaft of the motor is connected to the housing by at least one motor bearing, distinct from the stabilization bearing.

6. Portable power tool according to claim 1, in which the epicyclic reduction gear includes at least three planet pinions.

7. Portable power tool according to claim 1, in which the support bearing of the output shaft of the reduction gear includes either a needle bushing or a roller bushing.

8. Portable power tool according to claim 1, including at least one needle thrust bearing cooperating with the output shaft of the epicyclic reduction gear to prohibit an axial movement of the output shaft.

9. Portable power tool according to claim 1, in which the ball screw is made of a single piece with the output shaft of the epicyclic reduction gear.

10. Portable power tool according to claim 1, in which the ball screw presents a free distal end.

11. Portable power tool according to claim 1, in which the ball screw-nut mechanism comprises a mobile ball nut in translation relative to an axis of the ball screw, the nut being connected to a cutting element.

12. Portable power tool according to claim 11 in which the cutting element is a blade of a pruning shear, the ball nut being connected to an actuating cam of the blade of a pruning shear.

13. Portable power tool according to claim 11 in which the cutting element is a blade of a sheet metal shear, the ball screw being connected to an actuating cam of the blade of a sheet metal shear.

14. Portable power tool according to claim 1, in which the output shaft of the epicyclic reduction gear constitutes the ball screw.

15. (canceled)

Description

BRIEF DESCRIPTION OF THE FIGURES

[0060] FIG. 1 is a cross-section of an electric pruning shear according to the invention.

[0061] FIG. 2 is a cross-section of part of a motor and of a reduction gear of the pruning shear of FIG. 1 showing, at a larger scale, the layout of the support and stabilization bearings.

[0062] FIG. 3 is a schematic representation of a possible layout of the support and stabilization bearings according to the invention and corresponding to FIG. 1.

[0063] FIG. 4A is a schematic representation of another possible layout of the support and stabilization bearings according to the invention.

[0064] FIG. 4B is a cross-section along A-A of the device shown in FIG. 4A.

[0065] FIG. 5A is a schematic representation of another possible layout of the support and stabilization bearings according to the invention.

[0066] FIG. 5B is a cross-section along B-B of the device shown in FIG. 5A.

[0067] FIG. 6 is a schematic representation of another possible layout of the support and stabilization bearings according to the invention.

DETAILED DESCRIPTION OF IMPLEMENTATIONS OF THE INVENTION

[0068] In the following description all identical or similar portions of the various figures are identified by the same reference signs. It is thus possible to refer from one figure to another. The figures are shown in free scale.

[0069] FIG. 1 represents in cross-section an electric pruning shear 1. The electric pruning shear 1 comprises a main housing 2 accommodating an electric motor 10, an epicyclic reduction gear 20 mounted on a drive shaft 12 of the motor, and a ball nut-screw mechanism 30.

[0070] The shaft 12 of the electric motor 10 is kept in the housing by two motor bearings PM1 and PM2 located on either side of the motor 10. The bearings PM1 and PM2 preferably consist of ball bearings.

[0071] In the example shown, the motor 10 includes a stator 13 and a rotor 14. The presence of an intermediate housing 4 receiving the motor 10 and the epicyclic reduction gear 20 can also be noted. The intermediate housing 4 is received in the main housing 2 of the electric pruning shear.

[0072] The epicyclic reduction gear 20, better visible on FIG. 2, comprises an output ring 22 that is rigidly integral with an output shaft 32. The output ring serves as support of the planet carrier axes 24 which carry the planet pinions 25. These are pinions engaged on a central pinion 26 integral with the drive shaft 12 of the motor 10, and running in a toothed running ring 27. The planet pinions 25 are simply called planet gears in the rest of the text.

[0073] The function of the epicyclic reduction gear is to confer to its output shaft 32 a reduced rotary speed relative to the rotary speed of the drive shaft 12 of the motor. The reduced rotary speed is accompanied by an increase in the rotary torque.

[0074] The output shaft 32 of the reduction gear is also part of the ball screw-nut mechanism 30 to the extent that a portion of this shaft, visible in FIG. 1, forms the ball screw 34. In effect, the free end of the output shaft is provided with a helical groove for the circulation of the balls. The ball screw 34 of the output shaft cooperates with a nut 36 through the intermediary of balls (not shown) which circulate in a ball race formed by the conjunction of the helical groove of the ball screw and a corresponding helical groove of the ball nut 36. The nut 36 is not shown in cross-section.

[0075] Rotation of the output shaft 32 thus activates a displacement of the ball nut 36. The nut moves in a direction which either brings it closer to or farther away from the motor depending on the sense of rotation of the output shaft.

[0076] The ball nut 36 of the ball screw-nut mechanism 30 is connected to a cutting element 40. This is, in the case of FIG. 1, a mobile blade 42 of the pruning shear, pivoting around a blade pivot 43. More precisely, the nut 36 is connected to a cam 44 of the mobile blade through the intermediary of a cam pivot 45 and two rods 46, only one of which is visible. Displacement of the nut 36 thus provokes the mobile blade 42 to pivot in a direction which either brings it closer to or farther away from a counter-blade 48 called a hook. In the example of FIG. 1 the mobile blade pivots while moving away from the hook when the ball nut 36 moves in the direction of the distal end of the ball screw 34. This movement corresponds to the opening of the pruning shear. Inversely, the mobile blade 42 pivots to close on the hook when the ball nut moves in the direction of the motor 10. This movement is a cutting motion.

[0077] The movements of opening and cutting of the cutting element generate, primarily on the ball screw 34 and the output shaft 32 of the reduction gear 30, axial loads which is to say parallel to the axis of the output shaft 32. They also generate radial loads, which is to say perpendicular to the axis of the output shaft 32. The radial loads are due, for example, to a transitory tilt of the rods relative to the axis of the output shaft 32 or of the ball screw 34. This is the case especially when the rods are connected to a pivoting cam 44 by a cam pivot 45 which cannot be maintained constantly in the axis of the ball screw, considering its circular trajectory centered on the blade pivot 43.

[0078] The output shaft 32 of the epicyclic reduction gear 20 is maintained in the main housing 2 by a support bearing PS1.

[0079] The function of the support bearing PS1 visible at a larger scale on FIG. 2 is to maintain the output shaft and to transfer toward the housing axial and radial loads applied to the output shaft 32 by the work of the cutting element. The loads are transmitted to the main housing 2 through the intermediary of a ring 52 of the support bearing PS1.

[0080] In the implementation shown the portions of the motor or of the reduction gear maintained in the main housing 2 of the pruning shear are maintained there through the intermediary of the intermediate housing 4 already mentioned. However, maintaining them directly in the main housing is conceivable.

[0081] The support bearing PS1 includes a first needle bushing forming a first needle roller bearing 54 rolling on the surface of the output shaft 32 of the reduction gear. The needles of the needle bearing 54 make it possible to transmit to the housing a portion of the radial loads sustained by the output shaft 32 through the intermediary of the ring 52. The support bearing PS1 includes a second needle cage which forms a needle thrust bearing 56. The needle thrust bearing 56 rolls against the output ring 22 of the reduction gear, and more precisely against a flange 57 resting on the ring. The needle thrust bearing 56 allows transferring toward the housing, via the ring 52, the axial loads of the output shaft 32 of the roller bearing during the cutting movement.

[0082] Finally, the support bearing PS1 includes a third needle cage forming another needle thrust bearing 58 resting against a second flange 59 maintained on the output shaft 32 by a plastic ring 60. The needle thrust bearing 58 allows transferring towards the housing axial loads sustained by the output shaft 32 of the reduction gear during an opening movement of the cutting element.

[0083] As shown in FIGS. 1 and 2, the end of the drive shaft 12 of the motor turned towards the epicyclic reduction gear is provided with a stabilization bearing PS2. The stabilization bearing is mounted in an axial boring 33 of the output shaft 32 of the epicyclic reduction gear. In the example shown, it is a ball bearing. The drive shaft 12 of the motor, the boring 33, the stabilization bearing PS2 and the output shaft 32 of the epicyclic reduction gear are coaxial.

[0084] As shown particularly in FIG. 2, the stabilization bearing PS2 is axially offset relative to the support bearing PS1 in the direction of the motor. The offset confers to these two bearings a good range to support the radial loads and stresses sustained by the ball screw 34 and hence the output shaft 32 of the epicyclic reduction gear. Use of the stabilization bearing PS2 greatly relieves the support bearing PS1 of the radial stresses and consequently affords improved maintenance of the ball screw and a more modest dimensioning of the support bearing PS1. It also avoids direct support of the radial loads by the planet gears of the reduction gear, thereby avoiding premature wear of the teeth of the various gears of the reduction gear (planet gears, running ring).

[0085] It should be noted in this regard that the ball screw 34 is without a bearing at its free end, as shown in FIG. 1. The absence of a bearing at the end of the ball screw allows, as mentioned earlier, a greater displacement of the travel of the ball nut and a more compact design of the tool.

[0086] FIG. 3 is a schematic cross-section showing the layout of the major components involved in the stabilization of the output shaft in a design comparable to FIGS. 1 and 2. Here can be seen, centered on the same axis 3, the motor 10, the motor bearings PM1, PM2 supporting the drive shaft 12 of the motor, the central drive pinion 26 mounted on the drive shaft 12 of the motor 10, the stabilization bearing PS2 integrated in an axial boring 33 of the output shaft 32, the support ring 22 of the planet carrier axes 24, the support bearing PS1 and the output shaft 32 of the epicyclic reduction gear 30.

[0087] In FIG. 3 as well as in the following figures, the housing receiving the mechanical stresses and loads of the motor and the reduction gear is shown in a symbolic manner. It may be either the main housing 2 or the intermediate housing 4 received rigidly in the main housing. A double reference 2, 4 is therefore shown in the figures.

[0088] A planet gear 25 is mounted on a planet carrier axis 24 of the ring 22. It is driven in rotation by the central pinion 26 of the drive shaft 12 of the motor 10. The planet gear 25 is meshed on a toothed peripheral running ring 27 in which it can roll. The toothed running ring 27 is maintained fixed by the central housing 2 or by the intermediate housing 4. The running of the planet gear 25 in the toothed running ring 27 drives the planet gear in a circular movement around the axis 3 of the drive shaft. The movement of the planet gear 25 drives the output ring 22 which serves as support for the planet carrier axes, and the output ring 22 drives the output shaft 32 of the reduction gear of which it is an integral part.

[0089] FIG. 3 shows only a single planet gear 25 situated in the cut plane. Two more planet gears are situated outside of the cut plane and are not shown.

[0090] In general the reduction gear 30 comprises preferably a number of planet gears of three or more.

[0091] In a simplified implementation of the invention the second motor bearing PM2 may be omitted. In this case, the motor shaft is only supported by the first motor bearing PM1 located opposite the epicyclic reduction gear 30, and by the stabilization bearing PS2. The stabilization bearing PS2 is in effect maintained on the axis 3 by the output ring 22 integral with the output shaft 32, and by the support bearing PS1 connected to the main housing 2 or to the intermediate housing 4.

[0092] FIG. 4A is a schematic cross-section corresponding to another possible implementation of the invention in which a stabilization bearing PS2 connects the output shaft of the reduction gear to the housing through the intermediary of the planet carrier axes 24. The planet carrier axes are integral with the output shaft 32 through the intermediary of the output ring 22. Now, as shown in FIG. 4A, the axes are also received in a stabilization disk 70 mounted on the drive shaft 12 of the motor 10 through the intermediary of the stabilization bearing PS2. The stabilization disk 70 is rigidly integral with the planet carrier axes 24 and forms a seat for the stabilization bearing PS2.

[0093] The drive shaft 12 of the motor is itself connected to the housing through the intermediary of the motor bearings PM1 and PM2 already mentioned in reference to the preceding figures.

[0094] FIG. 4B is a view along a plane A-A of FIG. 4A. It shows in cross-section the stabilization disk 70 and the planet carrier axes 24 of three planet gears 25 of which only the pitch circles are indicated in broken lines. The planet gears 25 present a regular angular distribution at 120 around the axis 3 of the drive shaft 12. The stabilization bearing PS2 is indicated schematically. It connects the drive shaft 12 to the stabilization disk 70.

[0095] FIGS. 5A and 5B show a variant of the implementation of the invention in which several stabilization bearings are used. The stabilization bearings PS2a, PS2b, PS2c are always integral with the output shaft 32 of the epicyclic reduction gear 30 through the intermediary of the output ring 22 and the planet carrier axes 24 rigidly integral with the output ring 22. The stabilization bearings PS2a, PS2b, PS2c are mounted on the planet carrier axes, behind the planet gears, and run on a smooth runner ring 29. The term smooth does not prejudge the condition of the surface of the so-called smooth runner ring, but simply distinguishes it from the toothed runner ring 27. The smooth runner ring 29 is in effect without teeth and presents a peripheral and cylindrical running band for the bearings. The smooth runner ring 29 may be formed by a shoulder of the toothed runner ring 27. As stated before, the planet gears 25 are meshed on the toothed runner ring 27.

[0096] The bearings PS2a, PS2b, PS2c are, for example, ball or needle bearings. Bearings without rollers can also be used.

[0097] FIG. 5B shows the bearings PS2a, PS2b, PS2c along the cut B-B of FIG. 5A. The pitch circles of the planet gears 25, as well as of the central pinion 26 are shown in broken lines.

[0098] FIG. 6 shows still another possibility of implementation in which the planet gears 25 directly form the stabilization bearings.

[0099] The planet bearings 25 of which only one is seen in cross-section on FIG. 6, present a toothing 25a extending only over a portion of their width. The toothing of the planet gear is meshed in a portion 26a of the equally toothed central pinion 26, and with a toothed roller ring 27. This mechanism is similar to the one described in reference to the preceding figures. The planet gears furthermore form, over a portion of their width, a roller with a shoulder forming a roller band 25b.

[0100] The roller band 25b of the planet gears is set to roll on a smooth roller ring 29 and on a corresponding roller band 26b of the central pinion 26. The smooth roller ring 29 is comparable to the one described in reference to FIGS. 5A and 5B. The smooth roller ring 29, the roller band 26b of the central pinion 26, just like the roller band 25b of the planet gear are without toothing.

[0101] The radial stresses sustained by the output shaft 32 of the epicyclic reduction gear are thus transmitted to the housing 2, 4 through the intermediary of the output ring 22, the planet carrier axes 24, the planet gears 25 forming the rollers, and the smooth roller ring 29. The stresses are also transmitted to the housing through the intermediary of the roller band 26b of the central pinion 26, the drive shaft 12 and the motor bearings PM1, PM2.

[0102] In this implementation, the planet pinions 25 also constitute stabilization bearings. It must be clearly stated that the diameter of the roller band 25b of the planet gears and the diameter of the roller band 26b of the central pinion 26 correspond to the pitch diameter of the portions 25a, 26a featuring toothing so as to avoid friction during the rolling. The same is true for the smooth roller ring 29 the diameter of which is matched to the roller pitch circle of the toothed roller ring 27.

[0103] In a simplified version the roller band 25b of the planet gears may be designed to roll only on the smooth roller ring 29 or only on the roller band 26b of the central pinion 26.