Hand-held power tool having planetary gear

Abstract

The invention relates to a hand-held power tool (100) having a tool receptacle and a housing in which a planetary gear (120) having at least one first planetary stage (202) and one second planetary stage (203) for driving the tool receptacle and a drive motor (180) having a drive shaft (215) are arranged, the invention relates to a planetary gear (120) for a motor vehicle, comprising a first planetary stage (202) for driving the planetary gear (120), the first planetary stage (202) having at least three planet gears (233, 234) which are connected to one another by means of a carrier ring (263), the carrier ring (263) being arranged in a ring gear (251) of the planetary gear (120).

Description

Technical Field

[0001] The present invention relates to a handheld power tool, which has a tool receiving part and a housing, in which a planetary transmission and a drive motor are arranged, the planetary transmission having at least a first planetary stage and a second planetary stage for driving the tool receiving part; the drive motor has a drive shaft for driving the planetary transmission. Background Art

[0002] Such a handheld power tool having a tool holder and a housing is known from the prior art, in which a planetary gear is arranged, the planetary gear having a first and a second planetary stage for driving the tool holder. In addition, a drive motor having a drive shaft for driving the planetary gear is provided. Summary of the invention

[0003] The present invention relates to a handheld power tool, which has a tool receiving part and a housing, in which a planetary transmission and a drive motor are arranged, the planetary transmission having at least a first planetary stage and a second planetary stage for driving the tool receiving part; the drive motor has a drive shaft for driving the planetary transmission. The first planetary stage has at least three planetary gears, which are connected to each other via a carrier ring, wherein the carrier ring is arranged in a hollow gear of the planetary transmission.

[0004] The present invention thus makes it possible to provide a robust and compact handheld power tool.

[0005] Preferably, at least three planetary gears are connected to one another via a further carrier ring which is arranged rotatably in a gear housing associated with the first planetary stage, in particular in a receptacle of the gear housing.

[0006] Thus, a safe and robust arrangement of the planetary gear can be achieved.

[0007] Preferably, at least the first planetary stage is arranged in the transmission housing.

[0008] Therefore, the first planet stage can be arranged simply and uncomplicatedly.

[0009] According to one embodiment, the transmission housing has a receptacle for receiving a bearing element, wherein the bearing element is designed for supporting a drive shaft having a rotation axis, and wherein the bearing element is arranged perpendicularly to the rotation axis in the first and / or second support ring.

[0010] Therefore, the drive shaft can be supported safely and robustly.

[0011] Preferably, the bearing element is arranged along the axis of rotation in the transmission housing.

[0012] Thus, a compact arrangement can be achieved in a simple manner.

[0013] According to one specific embodiment, the ring gear associated with the first planetary stage and the sun gear provided for driving the second planetary stage are designed integrally.

[0014] The installation space required for constructing the planetary gear can thus be reduced in a simple and uncomplicated manner.

[0015] Preferably, the ring gear and the sun gear have a common axis of rotation and are connected to one another via webs oriented perpendicularly to the axis of rotation.

[0016] Thus, a robust and stable connection of the ring gear to the sun gear can be achieved.

[0017] The internal gear preferably has an internal gear part and is arranged in a rotatable manner in the housing.

[0018] This makes it possible to achieve a simple and uncomplicated arrangement of the ring gear in the housing.

[0019] Preferably, a ring gear arranged in a rotationally fixed manner in the housing is associated with the first planetary stage, wherein the at least three planetary gears each have a first gear section operatively connected to the rotationally fixed ring gear and each have a second gear section operatively connected to the ring gear.

[0020] A rotational transmission from the drive motor to the planetary gear can thus be achieved in a simple manner.

[0021] Preferably, the first gear section and the second gear section have different diameters.

[0022] Thus, a simple, uncomplicated, compact planetary gear with a reduced longitudinal dimension can be provided.

[0023] According to one specific embodiment, in an operating mode of the hand-held power tool, in particular a hammering mode or a percussion drilling mode, an output shaft drivable by the planetary gear can be arranged in sections within the planetary gear.

[0024] This makes it possible to further compact the handheld power tool.

[0025] Preferably, the output shaft can be arranged in sections in an inner receptacle of a sun gear or an internal gear of the planetary gear arranged facing the output shaft.

[0026] A safe and reliable arrangement of the output shaft in the planetary gear can thus be achieved. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] The invention is explained in more detail in the following description based on the exemplary embodiments shown in the accompanying drawings. The accompanying drawings show:

[0028] Figure 1 : Schematic diagram of a handheld power tool with a drive motor and a planetary gear,

[0029] Figure 2 : Figure 1 Longitudinal section of the drive motor and planetary transmission,

[0030] Figure 3 :Assigned to Figure 2 Exploded perspective view of the planetary stage of a planetary transmission.

[0031] Figure 4 :Assigned to Figure 2 and Figure 3 A three-dimensional view of the planetary transmission components,

[0032] Figure 5 : Figures 2 to 4 A longitudinal section of the first planetary class,

[0033] Figure 6 : In the first position of the output shaft Figure 1 A longitudinal section of an alternative planetary stage of a planetary transmission, and

[0034] Figure 7 : In another position of the output shaft Figure 6 Longitudinal section of an alternative planetary stage.

[0035] In the figures, elements having the same or similar functions are provided with the same reference symbols and are described in detail only once. DETAILED DESCRIPTION

[0036] Figure 1 An exemplary handheld power tool 100 is shown with a housing 105, in which a drive unit is preferably arranged for rotationally driving a tool receptacle 140. As shown, the handheld power tool 100 can be mechanically and electrically connected to a battery pack 190 for mains-independent power supply, but can also be operated in a mains-dependent manner as an alternative or in addition thereto.

[0037] The tool receiving portion 140 is designed as shown for receiving an inserted tool 198 and rotating it during operation about an associated rotation axis 199. The tool receiving portion 140 is designed as a drill chuck 145. However, as an alternative to this, the tool receiving portion 140 can also be designed as a tool accessory, which can be detachably arranged on the handheld power tool 100. The handheld power tool 100 is designed as a drill driver, for example, but can also be designed as a percussion drill with a percussion mechanism or as a hammer drill.

[0038] In the exemplary embodiment shown, the drive unit has at least one drive motor 180 and a transmission 120. Preferably, the drive motor 180 is designed as an electronically commutated motor. Preferably, the drive motor 180 can be switched on and off via a manual switch 195, wherein the manual switch 195 is illustrated as being arranged on the handle 115 of the housing 105.

[0039] The transmission 120 is configured as a planetary transmission, preferably as a switchable planetary transmission. Preferably, the planetary transmission 120 is arranged in the transmission housing ( Figure 2 220).

[0040] Furthermore, the handheld power tool 100 optionally comprises a torque adjustment device having a torque adjustment sleeve 197. Such torque adjustment devices are sufficiently known from the prior art, so that a detailed description of the optional torque adjustment device is omitted here for the sake of brevity of the description.

[0041] Figure 2 A drive motor 180 with a drive shaft 215 is shown for driving the planetary gear 120 , and an optional fan 210 is arranged on the side of the drive motor 180 facing away from the planetary gear 120 or on the left side of the drive motor 180 in the illustration.

[0042] The planetary gear 120 is arranged, for example, in a gear housing 220. The gear housing 220 has three housing sections 221, 222, 223 as shown. Here, the housing section 221 is arranged facing the drive motor 180, and the housing section 223 faces the gear housing 221. Figure 1 The output shaft 240 of the tool receiving portion 140 is arranged. The housing section 222 is arranged along Figure 1 An axis of rotation 199 of the drive motor 180 , which also forms the axis of rotation of the planetary gear 120 , for example, is arranged between the two housing sections 221 , 223 .

[0043] The planetary gear 120 preferably has at least one first and one second planetary stage 202, 203 for driving the tool holder 140. Three planetary stages 202, 203, 204 are shown schematically.

[0044] Preferably, the planetary stages each have at least three planetary gears, wherein Figure 2 At most two planetary gears can be seen in the diagram, so they are described further below. As shown, the first planetary stage 202 has planetary gears 233, 234.

[0045] According to one embodiment, the planetary gears 233, 234 are connected to one another via a support ring 263. The support ring 263 is preferably arranged in the hollow gear 251 of the planetary gear 120, in particular the first planetary stage 202. For this purpose, the hollow gear 251 has a receptacle 268 in which the support ring 263 can be arranged. The hollow gear 251 preferably has an internal toothing 253. Furthermore, the hollow gear 251 is arranged rotatably in the housing 105, in particular the transmission housing 220 or the first housing section 221. At least the first planetary stage 202 is arranged in the housing section 221 of the transmission housing 220. Each planetary gear 233, 234 is assigned a shaft 262, 261, and the planetary gears 233, 234 are arranged on the support ring 263 via the shafts 262, 261.

[0046] According to another embodiment, the planetary gears 233, 234 are connected to one another via a further support ring 263. The support ring 263 is preferably arranged rotatably in the transmission housing 220 or the first housing section 221 associated with the first planetary stage 202. For this purpose, the housing section 221 has a receptacle 269.

[0047] Furthermore, the first planetary stage 202 is assigned a ring gear 265 which is arranged in a rotationally fixed manner in the housing 105, in particular in the transmission housing 220 or in the first housing section 221. It should be pointed out that the rotationally fixed ring gear 265 can alternatively also be constructed integrally with the first housing section 221. The planetary gears 233, 234 are also arranged in the ring gear 265 and can roll therein.

[0048] Each planetary gear 233, 234 has a first gear section 281 and a second gear section 282. The first gear section 281 is preferably operatively connected to the rotationally fixed internal gear 265, while the second gear section 282 is operatively connected to the internal gear 251. According to one embodiment, the first gear section 281 and the second gear section 282 have different diameters 298, 299. Preferably, the first diameter 298 associated with the first gear section 281 is smaller than the second diameter 299 associated with the second gear section 282.

[0049] The planetary gears 233, 234, in particular the respective second gear sections 282 of the planetary gears, are driven by the sun gear 229 arranged on the drive shaft 215. The second gear section 282 in turn drives the ring gear 251 via its internal gearing 253. In addition, the planetary gears 233, 234 move together with their first gear sections 281 along the internal gearing 266 of the fixed ring gear 265.

[0050] According to one embodiment, the hollow gear 251 assigned to the first planetary stage 202 and the sun gear 252 provided for driving the second planetary stage 203 are integrally constructed. Here, the hollow gear 251 and the sun gear 252 form a gear component 250. Preferably, the hollow gear 251 and the sun gear 252 have a common axis of rotation 199. In addition, the hollow gear 251 and the sun gear 252 are preferably connected by a web ( Figure 3 342) are connected to each other.

[0051] At least three planetary gears of the second planetary stage 203 are preferably arranged on the outer toothing 254 of the sun gear 252, wherein only the planetary gears 235, 236 can be seen here. As shown in the figure, the planetary gears 235, 236 are assigned a hollow gear 276 with a switching wire bow 278. The second planetary stage 203 is arranged in the second housing 222. Here, the shafts 206, 207 are assigned to the planetary gears 235, 236. A support ring 205 is arranged between the hollow gear 251 and the planetary gears 235, 236 along the axis of rotation 199. The support ring 205 supports the shafts 206, 207 of the planetary gears 235, 236. The support ring 272 is preferably arranged on the side of the planetary gears 235, 236 facing the output shaft 240. The support ring 272 also supports the shafts 206, 207.

[0052] Furthermore, the sun gear 271 of the third planetary stage 204 is shown as being assigned to a carrier ring 272. According to one embodiment, the carrier ring 272 and the sun gear 271 are constructed in one piece. The planetary gears 237, 238 are in turn assigned to the sun gear 271. The planetary gears 237, 238 are in turn operatively connected to a switching hollow gear 275 having a switching wire bow 277, for example. Furthermore, a driver 273 is preferably provided, which transmits the rotational movement of the third planetary stage 204 to the output shaft 240.

[0053] The sun gears 252, 271 preferably have inner receptacles 255, 274, each having a larger diameter than the output shaft 240. The output shaft 240 is supported in the third housing section 223, for example, via the inner receptacle 212 of the driver 273 and via the bearing element 232. For this purpose, the third housing section 223 preferably has a bearing receptacle 225.

[0054] According to one embodiment, in an operating mode of the handheld power tool 100, in particular a hammering mode or a percussion drilling mode, the output shaft 240 driven by the planetary gear 120 can be arranged in sections along the rotation axis 199 of the drive motor 180 in the planetary gear 120. Here, the end side 283 of the output shaft 240 is arranged spaced apart from the end side 211 of the driver 273 in the direction of the drive motor 180. Here, the output shaft 240 can preferably be arranged on the sun gear 271 or the internal gear ( Figure 6 In the inner receiving portion 274 of 630).

[0055] As shown, a bearing element 231 is arranged on the end of the transmission housing 220 facing the drive motor 180. The bearing element 231 is arranged, for example, in a receptacle 224 of the first housing section 221. Here, the bearing element 231 is designed to support the drive shaft 215. Preferably, the receptacle 224 of the bearing element 231 is arranged perpendicularly to the rotation axis 199 on the first and / or second support ring 263 ( Figure 3 In addition, the bearing element 231 is preferably arranged along the rotation axis 199 in the transmission housing 220 or the first housing section 221.

[0056] Figure 3 Show Figure 2 An exemplary first planet stage 202. Here, Figure 3 The torsionally fixed arrangement Figure 2 The internal gear 265 in the transmission housing 220 has an anti-rotation element 311 on its outer circumference. The anti-rotation element 311 is preferably designed as a peripheral widening and can be arranged, for example, at Figure 2 The gear housing 220 is provided in an associated receiving portion. Four rotation-proof elements 311 are shown in the diagram, wherein a gap 312 is formed between two adjacent rotation-proof elements 311 in the circumferential direction.

[0057] also, Figure 3 Intuitively show Figure 2 The planetary gears 233, 234 have first and second gear sections 281, 282 and shafts 261, 262 for being supported on the carrier ring 263 or the carrier ring 320. As shown, the carrier ring 320 is arranged facing the hollow gear 265, while the carrier ring 263 faces the hollow gear 265. Figure 2 The transmission component 250 is arranged.

[0058] also, Figure 3 The transmission component 250 is shown schematically with an internal gear 251 and a sun gear 252. The internal gear 251 and the sun gear 252 are preferably connected perpendicularly to the rotation axis 199 (see Figure 1 and Figure 2 ) or the webs 342 oriented in the radial direction 301 are connected to each other.

[0059] As shown, the transmission component 250 has four webs 342 . It should be noted that the transmission component 250 can also have fewer or more than four webs 342 .

[0060] Figure 4 The sun gear 252 is shown. Figure 2 and Figure 3 The transmission component 250. Here, Figure 4 The tab 342 and the Figure 2 and Figure 3 The receiving portion 268 of the carrying ring 263.

[0061] Figure 5 Shown with Figures 2 to 4 The transmission component 250 Figure 2 and Figure 3 202 of the exemplary first planetary stage. In this case, the support ring 263 is arranged in the receiving portion 268 of the transmission component 250. The support ring 320 is arranged on the left side of the internal gear 265 in this diagram. In addition, Figure 5 A first diameter 298 associated with first gear section 281 is shown schematically and is smaller than a second diameter 299 associated with second gear section 282 .

[0062] Figure 6 An alternative planetary stage 602 is shown with ring gears 640 , 630 and planet gears 637 , 638 , which are each arranged on a carrier ring 650 via a shaft 661 , 662 . The planet gears 637 , 638 are driven by a central sun gear 660 .

[0063] The planetary gears 637, 638 illustratively include a first tooth segment 681 having a first diameter 699 and a second tooth segment 682 having a second diameter 698. The first diameter 699 is preferably greater than the second diameter 698. Figures 2 to 5 Compared to the embodiment of FIG. 2 , the first tooth section 681 having the first diameter 699 is arranged facing away from the output shaft 240 , while the second tooth section 682 having the second diameter 698 is arranged facing the output shaft 240 .

[0064] Furthermore, the internal gear 640, which meshes with its inner teeth 641 with the first tooth section 681, is arranged facing away from the output shaft 240. The internal gear 630 meshes with its inner teeth 631 with the second tooth section 682 and is arranged facing the output shaft 240. Preferably, the internal gear 630 is formed integrally with the driver 273.

[0065] and Figures 2 to 5 Similar to the embodiment of FIG. 2 , the output shaft 240 is supported by the bearing element 232 and the driver 273. Figure 6 In the arrangement shown, the end face 283 of the output shaft 240 and the end face 211 of the driver 273 are located schematically on a common cross-sectional line 601. The internal gear 630 has an inner receptacle 674, in which the output shaft 240 can preferably be arranged in sections. Figure 6 , the output shaft 240 is not arranged in the inner receiving portion 674 .

[0066] Figure 7 Shows the hammer mode or impact drill mode Figure 6 The planetary stage 602, wherein the output shaft 240 can be arranged in sections Figure 1 and Figure 2 In the planetary gear 120 or planetary stage 602. In particular, the output shaft 240 is arranged in sections in the inner receiving portion 674 of the internal gear 630. Here, the end side 283 of the output shaft 240 is arranged in the diagram shifted distance 703 from the end side 211 of the driver 273 toward the internal gear 640.

[0067] Furthermore, end face 283 of output shaft 240 is arranged in internal gear 630 , for example in longitudinal direction 701 of planetary stage 602 . End face 283 of output shaft 240 is also preferably arranged coaxially with planetary gears 637 , 638 , in particular toothed section 682 .

Claims

1. A handheld power tool (100) comprising a tool receiving portion (140) and a housing (105), wherein a planetary transmission (120) and a drive motor (180) are arranged in the housing, the planetary transmission having at least a first planetary stage (202) and a second planetary stage (203) for driving the tool receiving portion (140), the drive motor having a drive shaft (215) for driving the planetary transmission (120), characterized in that: The first planetary stage (202) has at least three planetary gears (233, 234) which are connected to one another via a carrier ring (263), wherein the carrier ring (263) is arranged in a hollow gear (251) of the planetary gear (120).

2. The handheld power tool according to claim 1, characterized in that The at least three planetary gears (233, 234) are connected to one another via a further support ring (263), which is rotatably arranged in a transmission housing (221) associated with the first planetary stage (202), in particular in a receptacle (269) of the transmission housing (221).

3. The handheld power tool according to claim 1 or 2, characterized in that: At least the first planet stage (202) is arranged in the transmission housing (221).

4. The handheld power tool according to claim 2 or 3, characterized in that: The transmission housing (221) has a receiving portion (224) for receiving a bearing element (231), wherein the bearing element (231) is designed to support the drive shaft (215), the drive shaft having a rotation axis (199), and wherein the bearing element (231) is arranged perpendicular to the rotation axis (199) in the first and / or second support ring (263; 320).

5. The handheld power tool according to claim 4, characterized in that The bearing element (231) is arranged along the rotation axis (199) in the transmission housing (221).

6. The hand-held power tool according to claim 1, characterized in that A ring gear (251) associated with the first planetary stage (202) and a sun gear (252) provided for driving the second planetary stage (203) are integrally formed.

7. The handheld power tool according to claim 6, characterized in that The ring gear (251) and the sun gear (252) have a common axis of rotation (199) and are connected to one another via webs (342) oriented perpendicularly to the axis of rotation (199).

8. The handheld power tool according to claim 6 or 7, characterized in that: The internal gear (251) has an internal toothing (253) and is arranged in the housing (105) so as to be rotatable.

9. The hand-held power tool according to claim 1, characterized in that The first planetary stage (202) is assigned a ring gear (265) which is arranged in a rotationally fixed manner in the housing (105), wherein the at least three planetary gears (233, 234) each have a first gear section (281) which is operatively connected to the rotationally fixed ring gear (265) and each have a second gear section (282) which is operatively connected to the ring gear (251).

10. The handheld power tool according to claim 9, characterized in that The first gear section (281; 681) and the second gear section (282; 682) have different diameters (298, 299; 698, 699).

11. The hand-held power tool according to claim 1, characterized in that In an operating mode of the handheld power tool (100), in particular a hammering mode or a percussion drilling mode, an output shaft (240) drivable by the planetary gear (120) can be arranged in sections within the planetary gear (120).

12. The handheld power tool according to claim 11, characterized in that The output shaft (240) can be arranged in sections in an inner receptacle (274; 674) of a sun gear (271) or an internal gear (630) of the planetary gear (120) which is arranged facing the output shaft (240).

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