Handheld power tool

Abstract

A handheld power tool includes an output shaft, a drive unit, a securing ring, and a securing element. The output shaft is configured to be releasably connected to an insert tool of the handheld power tool. The drive unit is configured to transmit a movement to the output shaft. The securing element is configured to secure the securing ring. The securing element has a recess which is provided to surround the securing ring in the radial direction in at least one operating state.

Claims

1. A handheld power tool, comprising: an output shaft configured to be releasably connected to an insert tool, the output shaft defining a securing groove that encircles the output shaft, the output shaft having a flange that extends radially outwardly; a drive unit configured to transmit a movement to the output shaft; a securing element defining a recess that is aligned with the securing groove, the securing element being a transmission gear element or a brake element that is configured to brake the transmission gear element; a securing ring having an inner portion received in the securing groove and an outer portion received in and radially surrounded by the recess so as to secure the securing ring; and a bearing element having a first end that abuts the flange of the output shaft and a second opposite end that is secured by the securing ring.

2. The handheld power tool according to claim 1, wherein the recess delimits the securing element at least partially in at least one of the radial direction and an axial direction of an output axis.

3. The handheld power tool according to claim 1, wherein the securing groove has a bent contour.

4. The handheld power tool according to claim 1, wherein: the securing element and the securing groove form a securing apparatus, and the securing apparatus is configured to secure the securing ring against independently coming loose in at least one operating state.

5. The handheld power tool according to claim 1, wherein the securing element has a supporting region that contacts the bearing element in an axial direction, the supporting region being radially spaced apart from the output shaft.

6. The handheld power tool according to claim 5, wherein (i) the transmission gear element or the brake element, and/or (ii) the bearing element is connected to the output shaft by an interference fit.

7. The handheld power tool according to claim 1, wherein: the output shaft has a first contact region forming a first active surface for the bearing element of the drive shaft, the output shaft has a second contact region forming a second active surface for the securing element, and the securing groove separates the first contact region from the second contact region and is adjacent to both the first and second contact regions.

8. The handheld power tool according to claim 1, wherein the bearing element and the one of the transmission gear element and or the brake element are surrounded by a machine housing.

9. The handheld power tool, according to the claim 1, wherein the securing ring is a circlip.

10. The handheld power tool according to claim 1, wherein the handheld power tool is an angle grinder.

11. The handheld power tool according to claim 3, wherein the securing groove has a concave contour.

12. The handheld power tool according to claim 5, wherein the bearing element is a roller bearing element.

13. The handheld power tool according to claim 8, wherein the machine housing is a transmission housing.

14. The handheld power tool according to claim 1, wherein the securing element is the transmission gear element, and the recess is defined in the transmission gear element.

15. The handheld power tool according to claim 1, wherein the securing element is the brake element, and the recess is defined in the brake element.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Further advantages can be gathered from the following description of the drawing. The drawing illustrates exemplary embodiments of the disclosure. The drawings, the description and the claims contain numerous features in combination. A person skilled in the art will expediently also look at the features individually and combine them to form useful further combinations. In the drawing:

(2) FIG. 1 shows a view of an exemplary handheld power tool 13,

(3) FIG. 2 shows a section through a transmission housing of the handheld power tool 13,

(4) FIGS. 3a to 3b show two perspective views of an output shaft,

(5) FIGS. 4a to 4b show two sections through a transmission element and a brake element,

(6) FIG. 5 shows a section through the output shaft from FIG. 3,

(7) FIG. 6 shows an enlarged view of the output shaft, and

(8) FIG. 7a to e show several embodiments of securing rings.

DETAILED DESCRIPTION

(9) Identical components are provided with the same reference symbols in the following figures.

(10) FIG. 1 shows a handheld power tool 13 13, which is designed as an angle grinder 13, comprising a housing 15, comprising an additional handle 17 which is arranged on the housing 15, comprising a cutting disk 19 and comprising a protective hood 21 which surrounds the cutting disk 19 at least in sections.

(11) The cutting disk 19 is designed to cut and/or grind workpieces. The cutting disk 19 can be used universally and is suitable, in particular, for processing workpieces which are composed of cellulose, such as grass, scrub or roots, wood, plastic or a composite for example. However, as an alternative, the cutting disk 19 may also be suitable for processing metal, stone or a composite for example.

(12) The protective hood 21 is intended to be releasably held on rotationally driven commercially available angle grinders 13. The protective hood 21 can be held in a holding apparatus 23, which is already known to a person skilled in the art and is designed to hold the protective hood 21, of a power tool, preferably a handheld power tool 13, with a rotational and/or translatory movement towards a workpiece which is to be processed.

(13) A suitable power tool is a non-stationary handheld power tool 13, such as, for example, an angle grinder 13 or a handheld circular saw according to the application DE 3740200 A1 or such as, for example, a backpack-type brush cutter according to the application DE 19616764 A1.

(14) The housing 15 is designed as a machine housing 25 and comprises a transmission housing 27, which at least partially surrounds a transmission (not shown), in particular an angular transmission, and at least one handle housing 29, which accommodates a drive unit (not shown) at least in sections or at least surrounds said drive unit. The protective hood 21 is expediently intended to cover at least or up to 180° of the cutting disk 19 in order to protect the operator of the angle grinder 13 against flying sparks.

(15) The handheld power tool 13 has a drive unit, not shown, for transmitting a rotational movement U to an output shaft 31 which can be releasably connected to an insert tool 19. The rotational movement U is transmitted from the drive unit to the output shaft 31 by means of a transmission 33 which is designed as an angular transmission 33.

(16) The drive unit has an electric motor. The electric motor can be designed as an electrically commutated motor.

(17) The handheld power tool 13 further has a securing ring 35 which is provided to secure components, such as a transmission gear element 37 and/or a bearing element 39 for example, against axial movement along an output axis a of the output shaft 31. In the present case, the securing ring 35 is intended to minimize and/or delimit the bearing element 39 and a brake element 41 (FIG. 3a) or the transmission gear element 37 (FIG. 3b) an axial movement along the output axis a.

(18) The bearing element 39 is designed as a roller bearing element 39 which is configured in the form of a conventional ball bearing. The ball bearing 39 has an inner bearing ring 41a and an outer bearing ring 41b which surrounds the inner bearing ring 41a. The outer bearing ring 41b is mounted on the inner bearing ring 41a by means of balls 41c (FIG. 3). In an alternative embodiment, any other roller bearing arrangement which appears to be expedient to a person skilled in the art or a sliding bearing arrangement or the like can also be used.

(19) The angular transmission 33 has a crown gear element 37 which forms an interference fit in relation to the output shaft 31 and is pressed onto the output shaft 31. The crown gear element 37 has a helical gearing, so that the crown gear element 37 meshes with a bevel gear element 43 which extends along a longitudinal extent L of the handheld power tool 13 and is directly or indirectly coupled to the drive shaft 45 (FIG. 2). In an alternative embodiment, other angular transmissions 33, such as worm gear transmissions or spur gear transmissions for example, also come into consideration.

(20) The drive shaft 45 is preferably integrally formed with a drive shaft 45 of the drive unit.

(21) The handheld power tool 13 further has a securing element 47 with a recess 49 for securing the securing ring 35. The recess 49 is provided to surround the securing ring 35 in the radial direction in at least one operating state.

(22) The output shaft 31 is be directly connected to the insert tool 19. The output shaft 31 protrudes out of the transmission housing 27 and has a receiving end 51 with a receiving thread 53. The receiving end 51 of the output shaft 31 is provided to detachably receive an insert tool 19 and to be releasably connected to the output shaft 31 by means of a nut (not shown) and the receiving thread 53. As a result, the insert tool 19 can be releasably connected to the handheld power tool 13.

(23) The securing ring 35 is provided to be fitted onto the output shaft 31 in order to limit an axial movement of components, such as a transmission gear element 37 and/or a bearing element 39 for example, in an interlocking and force-fitting manner. The securing ring 35 is formed from a spring steel. The securing ring 35 is phosphatized. The securing ring 35 is lubricated. The securing ring 35 is designed as a circlip 35. The circlip 35 has a circular cross section Q (bottom of FIG. 7a). In an alternative embodiment, the circlip 35 can have an angular cross section Q, such as a square (bottom of FIG. 7b) or a rectangular (bottom of FIG. 7c) cross section Q for example, or a round cross section Q, such as an oval (bottom of FIG. 7d) or a teardrop-shaped (bottom of FIG. 7e) cross section Q for example.

(24) The circlip 35 is formed from a round wire. The circlip 35 has an inside diameter of exactly 10.8 mm, approximately except for a manufacturing tolerance. The circlip 35 is designed in accordance with DIN 7993. The circlip 35 is of c-shaped design. The circlip 35 is designed as a segment of a ring.

(25) The recess 49 of the securing element 47 runs in the circumferential direction U around the output axis a of the output shaft 31. The securing element 47 can be formed by the brake element 41 (FIG. 3a, FIG. 4b) or the transmission gear element 37 (FIG. 3b, FIG. 4a) which is fitted onto the output shaft 31 in each case. The securing element 47 extends in the axial direction along the output axis a of the output shaft 31 and surrounds the securing ring 35 at least in sections. The securing element 47 surrounds the securing ring 35 in the circumferential direction U around the output axis a through 360°.

(26) The recess 49 has a maximum radial extent in the radial direction of the output axis a, which maximum radial extent is greater than a radial extent of a section of the output shaft 31 which is surrounded by the recess 49 of the securing element 47 in at least one operating state.

(27) The recess 49 delimits the securing element 47 at least partially in the radial and in the axial direction in relation to the output axis a.

(28) The recess 49 has a recess surface 55 which delimits the recess 49 in the radial direction of the output axis a. The recess surface 55 is designed to be substantially concentric in relation to the output shaft 31 about the output axis a. The recess surface 55 can have an axial extent along the output axis a, which axial extent is greater than an axial extent of the securing ring 35.

(29) The output shaft 31 has a securing groove 57 (FIG. 6), which encircles the output shaft 31, for receiving the securing ring 35. The securing groove 57 is designed as a partial tapered portion of the diameter of the output shaft 31. The securing groove 57 is designed as a securing notch which is provided to receive the securing ring 35 and to hold said securing ring in an interlocking manner in the axial direction along the output axis a. The recess 49 is provided to surround the securing groove 57 in the radial direction in relation to the output axis a in at least one operating state. The securing groove 57 has a round or a concave contour 59 (FIG. 6). In this case, the contour 59, as viewed along the output axis a, steadily tapers and steadily rises again, so that there is no jump in the diameter profile. As a result, the notching effect of the output shaft is minimized.

(30) The securing element 47 has a securing apparatus 61 which is provided to secure the securing ring 35 against independently coming loose in at least one operating state. The securing apparatus 61 comprises the recess 49 with a maximum radius which is smaller than a maximum radius of the securing ring 35 in a state fitted on the output shaft 31 which is not situated in the securing groove 57. The recess 49 surrounds the securing ring 35 in at least one operating state in such a way that the securing ring 35 is prevented from independently coming loose in the radial direction. The recess 49 has a maximum radius which is greater than a maximum radius of the securing ring 35 in a state inserted in the securing groove 57. In other words, the maximum radius of the recess 49 in a section of the output shaft 31 adjacent to the securing groove 57 is smaller than a radius of the output shaft 31 and the material thickness t of the securing ring 35, so that the securing ring 35 cannot independently come loose from the securing groove 57 in an operating state surrounded by the recess 49. The recess surface 55 of the recess 49 can form a distance x from the output shaft 31, which distance is smaller than a material thickness t of the securing ring 35. The securing ring 35 has a constant material thickness t.

(31) The roller bearing element 39 is provided to support the output shaft 31 in a rotatable manner. The roller bearing element 39 makes contact with the crown gear element 37 or the brake element 41 in the axial direction. In the process, the crown gear element 37 can particularly advantageously make contact with the roller bearing element 39 by the transmission gear element forming a supporting region, in particular a supporting point, a supporting line and/or a supporting surface, in relation to the bearing element, which supporting region is at a distance from the output shaft in the radial direction. Therefore, the supporting region of a transmission gear element or of a brake element 41 is displaced further radially outward and reduces a bending moment, which acts on the output shaft 31, as a result.

(32) The output shaft 31 has a first contact region 64, which is designed as a first active surface 63 for the roller bearing element 39, and a second contact region 66, which is designed as a second active surface 65 of the crown gear element 37 or of the brake element 41. The first contact region 64 is separated from the second contact region 66 by the securing groove 57. The first active surface 63 serves as the active surface onto which the roller bearing element 39 is fitted. The second active surface 65 serves as the active surface onto which the crown gear element 37 or the brake element 41 is fitted.

(33) The circlip 35 has a constant cross section. The circlip 35 is bent around the output axis a. The circlip 35 can have a tensioned and an untensioned state. In the untensioned state, the circlip 35 is bent in a c shape in such a way that a radius of the circlip 35 is smaller than a radius of the output shaft, and/or that a radius of the securing ring is equal to or smaller than a radius of the securing groove of the output shaft. In the tensioned state, the securing ring has a larger radius than in an untensioned state. For example, in a tensioned state, the circlip 35 can be arranged on the first contact region 54 or the second contact region 66, as a result of which the radius of the circlip 35 widens. For example, in an untensioned state, the circlip 35 can be arranged in the securing groove 57, so that the radius of the circlip 35 reduces in size.