Hand-held power tool

Abstract

The invention relates to a hand-held power tool (100) having a housing (102), a drive motor (114), an intermediate shaft (120), wherein the intermediate shaft (120) can be driven by the drive motor (114), having a percussion mechanism (122) and a tool receptacle (150), the percussion mechanism comprising a percussion hammer (300) and a radial spring system (350) which is connected to the percussion hammer (300) in a torque-proof manner, wherein the percussion mechanism (122) can be driven at least partially by the intermediate shaft (120), the tool receptacle serving to receive a plug-in tool (140), wherein the tool receptacle (150) can be driven by means of the percussion mechanism (122), in particular the percussion hammer (300) and / or the intermediate shaft (120). The invention proposes that the intermediate shaft (120) has at least one bearing (200), wherein the radial spring system (350) bears against the bearing (200).

Description

Technical Field

[0001] The present invention relates to a handheld machine tool as described in the preamble of claim 1. Background Technology

[0002] According to CN 212330861 U, an impact screwdriver is known, which has a drive motor for driving a drive shaft, an output shaft that can be coupled to a tool receiving part, and an impact mechanism. Summary of the Invention

[0003] This invention relates to a handheld power tool having a housing, a drive motor, and an intermediate shaft, wherein the intermediate shaft is drivable by the drive motor. The handheld power tool also has an impact mechanism comprising an impactor and a radial spring system anti-torsionally connected to the impactor, wherein the impact mechanism is at least partially drivable by the intermediate shaft. The handheld power tool further has a tool receiving section for receiving insert tools, wherein the tool receiving section is drivable by means of the impact mechanism, particularly the impactor, and / or the intermediate shaft. The invention proposes that the intermediate shaft has at least one bearing, wherein the radial spring system rests against the bearing.

[0004] This invention provides a handheld machine tool including an impact mechanism with a higher mass moment of inertia, wherein the radial spring system is torsionally connected to the impactor, such that the radial spring system is an additional impactor mass. CN 212330861 U lacks a bearing for the intermediate shaft, preventing the impact mechanism springs of CN 212330861 U from rotating relative to the intermediate shaft.

[0005] The handheld machine tool can be configured as an electrically powered handheld machine tool. Here, the electrically powered handheld machine tool can be configured as either grid-connected or battery-powered. For example, the handheld machine tool can be configured as a rotary impact screwdriver.

[0006] The housing of the handheld machine tool is configured to at least partially receive the tool receiving section, the drive motor, the intermediate shaft, and the impact mechanism. The housing may be configured as a shell-type housing with two half-shells.

[0007] The drive motor can be configured as an electronically commutated drive motor, particularly at least one electric motor. The drive motor is configured to be operable via a manual switch. If the manual switch is operated by the user, the drive motor is turned on and the handheld machine tool is put into operation. If the manual switch is no longer operated by the user, the drive motor is turned off. Preferably, the drive motor is electronically controllable and / or adjustable, enabling reverse operation and pre-setting of a desired speed. In reverse operation, the drive motor can switch between right-hand and left-hand rotational directions. To switch the drive motor in reverse operation, the handheld machine tool can have a rotational direction switching element, particularly a rotational direction switching switch.

[0008] The drive motor is configured to drive the intermediate shaft. For this purpose, the drive motor and the intermediate shaft are interconnected. The intermediate shaft is arranged between the drive motor and the tool receiving unit. The intermediate shaft may have a transmission unit. The transmission unit may be configured as at least one planetary gear transmission, wherein the planetary gear transmission may be, for example, switchable. The planetary gear transmission may have at least one planetary gear group. In a switchable transmission, switching between at least two gear levels can be performed by means of at least one gear shifting element, in particular a gear shifting switch. The transmission unit may have a transmission cover. The transmission cover is configured to cover, in particular at least partially close, the transmission unit relative to the drive motor. The transmission cover may be arranged between the planetary gear transmission, in particular the planetary gear group, and the drive motor. The transmission unit, in particular the planetary gear transmission, may have a hollow wheel. Here, the hollow wheel and the transmission cover may, for example, be integral.

[0009] The impact mechanism is configured to operate during impact operation. During impact operation, the impact mechanism generates a high torque peak to loosen or fasten fixed connecting devices. The impact mechanism has an impactor and a radial spring system to which the impactor is torsionally connected. The impact mechanism can be connected to the drive motor via a transmission unit of the intermediate shaft. The impact mechanism can be configured, for example, as a rotary impact mechanism or a V-groove impact mechanism. The impact mechanism can be driven by the intermediate shaft. The impact mechanism can be arranged between the drive motor and the tool receiving unit. The impact mechanism has an impact mechanism housing in which the impactor and the radial spring system are arranged. Furthermore, the impact mechanism has an impact mechanism cover. The impact mechanism cover can close the impact mechanism in the direction toward the drive motor. The impact mechanism cover can be arranged between the drive motor and the tool receiving unit, particularly the intermediate shaft, and especially the transmission unit. Alternatively, the impact mechanism cover and the transmission cover can be integral, such that the impact mechanism cover forms the hollow wheel.

[0010] The impactor and the radial spring system can be arranged circumferentially about the intermediate shaft. The impactor can be supported on the intermediate shaft by means of an impact mechanism ball. Furthermore, the impact mechanism ball is configured to allow the impactor to move at least partially, particularly axially, toward the drive motor. The impactor can be arranged in a position facing the tool receiver or in a position facing the drive motor. In the position facing the tool receiver, the impactor can abut against the rear end of the tool receiver by means of at least one impact protrusion. For example, two impact protrusions are provided, although more than two are also possible. In the position facing the drive motor, the impactor can be arranged spaced apart from the tool receiver. The impact mechanism ball is configured to tension the impact mechanism by moving the impactor against the spring force of the radial spring system, particularly translating it, from the position facing the tool receiver to the position facing the drive motor, starting from a trigger torque that can act on the tool receiver. The spring force caused by the radial spring system is stored in the radial spring system as tensioning work. Once the impactor reaches the position facing the drive motor, it can be guided back to the position facing the tool receiver by means of the radial spring system. Here, the tension work done by the radial spring system is released, thereby guiding the impactor to the position facing the tool receiver. Here, the impactor can perform rotational and axial movements.

[0011] The drive motor has a drive shaft. The drive shaft is supported in the housing by means of at least one drive shaft bearing. The drive motor can drive the intermediate shaft, the transmission unit, the impact mechanism, and / or the tool receiving unit by means of the drive shaft. The drive shaft bearing can be exemplarily constructed as a ball bearing, rolling bearing, or sliding bearing. The drive shaft bearing is arranged on the end of the drive motor facing the tool receiving unit. The drive shaft can extend into the intermediate shaft through the transmission unit. The drive shaft bearing can be arranged in the intermediate shaft such that the drive shaft is supported in the intermediate shaft by means of the drive shaft bearing. The drive shaft can have another drive shaft bearing arranged on the end opposite to the drive motor. Thus, the drive shaft can then be rotatably supported in the housing by means of the drive shaft bearing and the other drive shaft bearing. Alternatively, the drive shaft can extend into and / or engage with the transmission cover. The handheld machine tool can have a tool axis. Here, the axis of rotation of the drive shaft can constitute the tool axis. In particular, "axial" should be understood as substantially parallel to the tool axis. "Radial" should be understood as being substantially perpendicular to the tool axis.

[0012] The radial spring system is a spring system having spring elements arranged radially offset from the tool axis and / or in the circumferential direction about the tool axis. The radial spring system includes multiple spring elements. Exemplarily, there may be two, three, four, or more than four, for example, eight spring elements. The multiple spring elements may be arranged in the circumferential direction about the tool axis. The impactor has at least one receiving portion for the radial spring system. The number of receiving portions for the radial spring system may correspond to the number of spring elements. The receiving portion for the radial spring system may be canister-shaped, shell-shaped, or cylindrical. It is conceivable that the receiving portion for the radial spring system may be pin-shaped, needle-shaped, or strip-shaped, wherein other shapes are also conceivable. Combinations of receiving portions for the radial spring system are also possible, such as canister-shaped receiving portions with pins, so that at least one of the spring elements can be guided in the circumferential direction of the spring element and substantially within the spring element. A tab may be formed between each pair of adjacent spring elements, which increases the impactor mass to increase the impactor's moment of inertia. The spring element may be configured as, for example, a helical spring, a barrel spring, a conical spring, a conical helical spring, an irregularly shaped spring, or a combination thereof.

[0013] The radial spring system is torsionally connected to the impactor, causing the radial spring system to rotate together with the impactor. The radial spring system can be form-locked, force-locked, and / or material-locked connected to the impactor. Here, the spring element can be received via a receiving portion for the spring element of the radial spring system and, for example, inserted, pressed, press-fitted, or glued. If the receiving portion is canister-shaped, the corresponding spring element can be inserted. If the receiving portion is pin-shaped, the corresponding spring element can be inserted. Both possibilities increase the impactor's moment of inertia because the impactor's mass is higher than that of a single helical spring.

[0014] The tool receiver can be configured as an internal tool receiver, such as a bit receiver, and / or as an external tool receiver, such as a socket receiver. Alternatively, the tool receiver can be configured as a drill chuck. The tool receiver can receive insert tools, such as screwdriver bits or socket wrenches, allowing the user to establish a threaded connection between the fastening element and the fastening carrier.

[0015] Furthermore, the handheld power tool includes a power supply, wherein the power supply is configured for battery operation by means of a battery, particularly a handheld power tool battery pack, and / or for grid operation. In a preferred embodiment, the power supply is configured for battery operation. Within the framework of this invention, "handheld power tool battery pack" should be understood as a combination of at least one battery cell and a battery pack housing. The handheld power tool battery pack is advantageously configured to power commercially available handheld power tools that operate on batteries. The at least one battery cell can, for example, be configured as a lithium-ion battery cell with a nominal voltage of 3.6V. Exemplarily, the handheld power tool battery pack may include up to ten battery cells, wherein other numbers of battery cells may also be considered. The implementation of handheld power tools as battery-operated and as grid-operated handheld power tools are well known to those skilled in the art, and therefore the details of the power supply are not discussed here.

[0016] The handheld power tool may have at least one control unit for controlling the drive motor. The control unit may be located in the housing, for example, in the handle of the handheld power tool or in the area of ​​the power interface.

[0017] The bearing of the intermediate shaft enables the radial spring system to be rotatably arranged relative to the intermediate shaft within the impact mechanism housing. The radial spring system is torsionalally connected to the impactor and simultaneously rotatable relative to the intermediate shaft. The bearing of the intermediate shaft can be exemplarily constructed as a needle roller bearing, roller bearing, rolling bearing, sliding bearing, or ball bearing. The radial spring system rests against the bearing. "Rests" here should be understood as being in direct and immediate contact. Therefore, the bearing of the intermediate shaft has direct and immediate contact with the bearing, and in particular with at least one element of the bearing. The radial spring system rests against the bearing of the intermediate shaft such that when the radial spring system rotates, the bearing of the intermediate shaft also rotates at least partially. Thus, the impact mechanism spring can be rotated relative to the intermediate shaft by means of the bearing.

[0018] In one embodiment of the handheld machine tool, the intermediate shaft has at least one planetary carrier, wherein the bearing is arranged between the radial spring system and the planetary carrier. The intermediate shaft is part of the planetary gear transmission. The planetary gear transmission has planetary gears and at least one planetary carrier. The at least one planetary carrier rotatably supports the planetary gears relative to the intermediate shaft. The bearing is axially arranged between the at least one planetary carrier and the radial spring system.

[0019] In one embodiment of a handheld machine tool, the radial spring system rests against a bearing washer of the bearing. The radial spring system rests directly and immediately against the bearing washer. The bearing washer is arranged toward the tool receiving portion. The bearing washer is configured to allow a rotational speed different from that of the intermediate shaft for the element resting against it. The bearing washer can be configured as a gasket or a ring. The bearing has rolling elements, which can be configured as balls, needle rollers, or cylindrical rollers, for example. The bearing washer is axially arranged between the rolling elements and the radial spring system. The bearing washer can be configured substantially disc-shaped or annular. Furthermore, the bearing washer can be substantially flat, depending on the rolling elements. If the rolling elements are configured as balls, the bearing washer can have a shell-like receiving portion for the balls. If the rolling elements are configured as cylindrical rollers or needle rollers, the bearing washer can be configured flat, respectively.

[0020] Alternatively, the radial spring system can be partially abutted against the bearing washer. Here, a first number of spring elements may abut against the bearing washer, while a second number of spring elements are spaced apart from the bearing washer. The second number of spring elements abut from a definable tension point during impactor tensioning. Thus, two radial spring systems can be implemented.

[0021] In one embodiment of the handheld machine tool, the planetary carrier is at least partially configured as a bearing cover. The planetary carrier and the bearing cover may be integral. The bearing cover is arranged toward the drive motor. The bearing cover may be arranged opposite to the bearing washer. The bearing cover is at least configured to support the rolling elements. The bearing cover may have a receiving portion depending on the rolling element, for example, a shell-like receiving portion in the case of a ball, and a flat receiving portion in the case of a roller or needle roller. The bearing washer and the bearing cover together with the rolling elements constitute the bearing.

[0022] In one embodiment, the bearing, particularly the bearing washer, has at least one retaining element configured to retain the rolling elements of the bearing. The retaining element is configured to radially retain the rolling elements. The configuration of the retaining element depends on the construction of the bearing, particularly the bearing washer, the rolling elements, and the bearing cover. The retaining element can be arranged, particularly radially, between the tool axis and the rolling elements. Here, the retaining element prevents the rolling elements from falling radially toward the tool axis. The retaining element can be constructed as a step, edge, protrusion, tab, flange, or shoulder. Alternatively, the bearing, particularly the bearing washer, can form the retaining element. Thus, the bearing washer and the retaining element are integral.

[0023] The impactor may have a contact element on its inner periphery. The contact element can be received by the journal of the intermediate shaft. The contact element can slide on the journal of the intermediate shaft.

[0024] In one embodiment, the abutment element of the impactor extends into the inner circumference of the retaining element of the bearing, particularly the bearing washer, during impact operation. At the end stop of the impactor, the abutment element is radially arranged between the intermediate shaft, particularly the journal of the intermediate shaft, and the retaining element.

[0025] In one embodiment of the handheld machine tool, an air spring can be formed between the guide element and the journal of the intermediate shaft, at least during impact operation. In a first embodiment, an air spring can be formed when the impactor moves axially during impact operation. The air spring can form an air chamber or air cushion. The air spring can be formed radially between the journal of the intermediate shaft and the outer diameter of the impactor. The air spring then applies another spring force.

[0026] In one embodiment of a handheld machine tool, the radial spring system has a plurality of first spring elements and a plurality of second spring elements. The plurality of first spring elements may be spring elements with a first spring stiffness, such as coarse springs. The plurality of second spring elements may be spring elements with a second spring stiffness, such as thin springs. The plurality of first spring elements and the plurality of second spring elements may have different spring stiffnesses, diameters, shapes, and / or spring characteristic curves. The plurality of first spring elements and the plurality of second spring elements may also be different spring types, such as a combination of helical springs and barrel springs. The number of the plurality of first spring elements and the plurality of second spring elements may each be even, for example, four first spring elements and four second spring elements, two first spring elements and six second spring elements, wherein other suitable combinations may also be considered. Alternatively, the plurality of first spring elements and the plurality of second spring elements may each be odd. The plurality of first spring elements and the plurality of second spring elements may be arranged circumferentially around the tool axis.

[0027] Alternatively, the plurality of first spring elements and the plurality of second spring elements may be constructed using the same spring elements. Here, different spring forces can then be created by steps in the impactor or the bearing washer, such that corresponding spring stiffnesses are achieved using pre-tensioned springs.

[0028] In one embodiment of the handheld machine tool, the plurality of first spring elements and the plurality of second spring elements are arranged alternately. Here, in the circumferential direction, one of the plurality of first spring elements may be followed by one of the plurality of second spring elements, or vice versa.

[0029] In one embodiment of a handheld machine tool, at least two similar spring elements are arranged adjacent to each other. Here, the two similar spring elements can be two spring elements from a plurality of first spring elements or two spring elements from a plurality of second spring elements. The two similar spring elements can be adjacent in the circumferential direction relative to the tool axis. If the spring receiving portion is constructed as an annular groove, the annular groove can be arranged in the circumferential direction relative to the tool axis such that the groove is concentric with the tool axis. The connecting element of the spring element can be constructed complementary to the spring receiving portion, enabling a connection between the spring element and the spring receiving portion.

[0030] In one embodiment of the handheld machine tool, the spring elements are arranged opposite each other. The spring elements may be arranged radially opposite each other relative to the tool axis. Attached Figure Description

[0031] The present invention will now be described with reference to preferred embodiments. The accompanying drawings are shown below: Figure 1 : A schematic view of a handheld machine tool according to the present invention; Figure 2a A partial longitudinal section of the impact mechanism of a handheld machine tool in its first working state; Figure 2b : A partial longitudinal section of the impact mechanism in the second working state; Figure 3a : A three-dimensional view of the impactor; Figure 3b The first cross-section of the impactor in the impact mechanism; Figure 3c The second cross-section of the impactor. Detailed Implementation

[0032] Figure 1 A handheld power tool 100 according to the present invention is shown, wherein the handheld power tool is configured herein as an exemplary battery-powered rotary impact screwdriver. The handheld power tool 100 includes an output shaft 124, a tool receiving portion 150, and an impact mechanism 122, such as a rotating or rotary impact mechanism. The handheld power tool 100 includes a housing 110 having a handle 126. The handheld power tool 100 is configured as a battery-powered handheld power tool 100 so that it can be connected to a power source and ground for battery operation without relying on mains power. Here, the handheld power tool battery pack 130 serves as the power source. However, the present invention is not limited to battery-powered handheld power tools, but can also be applied to grid-dependent, i.e., grid-operated handheld power tools.

[0033] The housing 110 includes a drive unit 111 and an impact mechanism 122, both arranged within the housing 110. The drive unit 111 includes an electronically commutated drive motor 114 powered by a handheld power tool battery pack 130 and a transmission unit 118. The transmission unit 118 is configured as at least one planetary gear transmission 166, also see FIG. 2. The drive motor 114 is designed to be actuated, for example, by a manual switch 128, allowing the drive motor 114 to be turned on and off. Advantageously, the drive motor 114 is electronically controllable and / or adjustable, enabling reverse operation and desired speeds. For reverse operation, the handheld power tool 100 has a rotation direction switching element 121, configured as a rotation direction switching switch. The rotation direction switching element 121 is configured to switch the drive motor 114 between right-hand and left-hand rotation directions. The structure and operation of suitable drive motors are well known to those skilled in the art and will not be described further here.

[0034] The transmission unit 118 is connected to the drive motor 114 via a drive shaft 116. The drive shaft 116 is supported in the housing 110 by means of a motor-side bearing (not shown in detail). The transmission unit 118 is configured to convert rotation of the drive shaft 116 into rotation between the transmission unit 118 and the impact mechanism 122 via an intermediate shaft 120. This conversion is preferably performed such that the intermediate shaft 120 rotates relative to the drive shaft 116 with an increased torque but a decreased speed, see also FIG. 2. The intermediate shaft 120 at least partially drives the impact mechanism 122. The transmission unit 118 has a transmission housing 119 arranged in the housing 110. The handheld machine tool 100 includes a tool axis 102, wherein the axis of rotation of the drive shaft 116 forms the tool axis 102.

[0035] Impact mechanism 122 is connected to intermediate shaft 120 and includes impactor 300 and at least one radial spring system 350 torsionally connected to impactor 300, wherein impact mechanism 122 generates high-intensity impact-type rotary pulses during impact operation, see also FIG2. Intermediate shaft 120 includes bearing 200, see also FIG2. Radial spring system 350 rotatably rests against bearing 200. These impact-type rotary pulses are transmitted to output shaft 124, such as a work spindle, via impactor 300. Impact mechanism 122 includes impact mechanism housing 123, wherein impact mechanism 122 may also be arranged in other suitable housings, such as transmission housing 119. Impact mechanism 122 is configured to drive output shaft 124. Tool receiver 150 is provided on output shaft 124. Preferably, tool receiver 150 is formed and / or constructed on output shaft 124. Preferably, tool receiver 150 is arranged in an axial direction 132 away from drive unit 111. The tool receiver 150 is configured as an internal hexagonal receiver, according to the type of bit holder, and is configured to receive the insert tool 140. The insert tool is configured as a screwdriver bit, having a polygonal external coupling 142. The type of screwdriver bit, such as the HEX type, is well known to those skilled in the art. However, the invention is not limited to the use of HEX screwdriver bits, but other tool receivers that are deemed meaningful by those skilled in the art can also be used, such as HEX drill bits, SDS-Quick insert tools, or round shank drill chucks. Furthermore, the structure and operation of suitable bit holders are well known to those skilled in the art.

[0036] The handheld power tool 100 has a control unit 170 for controlling the drive unit 111, particularly the drive motor 114. The housing 110 at least partially receives the control unit 170. The control unit 170 has a microprocessor (not shown in detail). Furthermore, the housing 110 includes a power retention device 160. The power retention device 160 receives the handheld power tool battery pack 130 and forms a standing foot 162 thereon with a standing surface. The handheld power tool battery pack 130 can be removed from the power retention device 160 without tools. Additionally, the housing 110 has a handle 126 and the power retention device 160. The handle 126 can be gripped by a user. In one embodiment, the power retention device 160 is arranged on the handle 126. The handheld power tool 100 can be placed using the standing foot 162.

[0037] Figure 2a The image shows a longitudinal section 400 of the impact mechanism 122 of the handheld power tool 100 in a first operating state 402. In the first operating state 402, the impactor 300 is arranged toward the tool receiving section 150. Figure 2a and Figure 2b The diagram shows an impact mechanism 122, an intermediate shaft 120, a transmission unit 118, and an output shaft 124, wherein the intermediate shaft 120 exemplary partially constitutes the transmission unit 118. The intermediate shaft 120 is arranged between a drive motor 114 and a tool receiver 150, which are not shown here. The transmission unit 118 is configured as a planetary gear transmission 166, exemplarily configured with one planetary gear group. The transmission unit 118 includes a transmission cover 125 in addition to a transmission housing 119. Here, the transmission cover 125 is configured to at least partially close the transmission unit 118 relative to the drive motor 114. Here, the transmission cover 125 is arranged between the planetary gear transmission 166 and the drive motor 114. Furthermore, the planetary gear transmission 166 includes a hollow wheel 129, wherein the hollow wheel 129 and the transmission cover 125 are exemplary integrally constructed. The intermediate shaft 120 has an intermediate shaft bearing 164. The transmission cover 125 includes a receiving portion for an intermediate shaft bearing 164, such that the receiving portion for the intermediate shaft bearing 164 receives the intermediate shaft bearing 164. The intermediate shaft bearing 164 enables the intermediate shaft 120 to rotate relative to the transmission cover 125.

[0038] The drive motor 114 includes a drive shaft 116, which is supported in the housing 110 by means of a drive shaft bearing 117. The drive shaft 116 is not shown in FIG. 2. The drive shaft bearing 117 is exemplarily constructed as a needle roller bearing. Here, the drive shaft bearing 117 is arranged on the end of the drive motor 114 facing the tool receiving portion 150. The drive shaft 116 extends through the planetary gear transmission 166 into the intermediate shaft 120. Here, the drive shaft bearing 117 is arranged in the intermediate shaft 120.

[0039] Impact mechanism 122 is connected to drive motor 114 via planetary gear transmission 166. Impact mechanism 122 is configured as a V-groove impact mechanism. Impact mechanism 122 is arranged between drive motor 114 and tool receiving portion 150. Impactor 300 and radial spring system 350 are arranged in impact mechanism housing 123. Impact mechanism 122 includes impact mechanism cover 127, which closes impact mechanism 122 in the direction toward drive motor 114. Here, impact mechanism cover 127 can be arranged between drive motor 114 and planetary gear transmission 166. Here, impact mechanism cover 127 and transmission cover 125 are exemplary integrally constructed, wherein impact mechanism cover 127 then forms a hollow wheel 129.

[0040] The impactor 300 is supported on the intermediate shaft 120 by means of an impact mechanism ball 310. The impact mechanism ball 310 is configured to move the impactor 300 at least partially toward the drive motor 114. Figure 2a The impactor 300 is shown in the position facing the tool receiving section 150. The impactor 300 can also be arranged in the position facing the drive motor 114, see [reference needed]. Figure 2b In the position facing the tool receiver 150, the impactor 300 abuts against the rear end of the tool receiver 150, i.e., against the output shaft 124, by means of two impact protrusions 312, which are not shown in detail. In the position facing the drive motor 114, the impactor 300 is arranged spaced apart from the tool receiver 150.

[0041] In the radial spring system 350, the spring elements 352 are radially offset from the tool axis 102 and arranged in the circumferential direction around the tool axis 102. The radial spring system 350 has a plurality of spring elements 352, for example, eight spring elements 352 are provided, also see FIG3. The impactor 300 includes a receiving portion 302 for the spring elements 352 of the radial spring system 350. The number of receiving portions 302 for the radial spring system 350 corresponds to the number of the plurality of spring elements 352. Here, the receiving portion 302 for the radial spring system 350 is constructed in a can shape. A tab 305 is formed between each pair of adjacent spring elements 352, see FIG3 for this. The spring element 352 is exemplary constructed as a helical spring. The radial spring system 350 is torsionally connected to the impactor 300, wherein the spring elements 352 and the receiving portions 302 for the spring elements 352 are at least form-locked together. Here, the spring element 352 is inserted into one of the receiving portions 302 of the spring element 352 for the radial spring system 350.

[0042] The bearing 200 of the intermediate shaft 120 rotatably arranges the radial spring system 350 relative to the intermediate shaft 120 within the impact mechanism housing 123. The bearing 200 of the intermediate shaft 120 is exemplarily constructed as a needle roller bearing 202 having needle rollers 222 as rolling elements 220. The radial spring system 350 rests against the bearing 200. The intermediate shaft 120 includes a planet carrier 280 of a planetary gear transmission 166. The bearing 200 is arranged between the radial spring system 350 and the planet carrier 280. The planetary gear transmission 166, in addition to the planet carrier 280, also has planet gears 282, wherein the planet carrier 280 rotatably supports the planet gears 282 relative to the intermediate shaft 120 by means of corresponding bolts 284. The bearing 200 is axially arranged between the planet carrier and the radial spring system 350.

[0043] A radial spring system 350 rests against the bearing washer 210 of the bearing 200. The bearing washer 210 is arranged toward the tool receiving portion 150. Exemplarily, the bearing washer 210 is constructed as a gasket. The bearing washer 210 is axially arranged between the rolling element 220 and the radial spring system 350. Furthermore, one side of the bearing washer 210 is substantially flat, such that the needle roller 222 rests planarly against the bearing washer 210. The planetary carrier 280 is at least partially constructed as the bearing cover 240 of the bearing 200. Exemplarily, the planetary carrier 166 and the bearing cover 240 are integrally constructed. Furthermore, the bearing cover 240 is arranged toward the drive motor 114. Additionally, the bearing cover 240 is arranged opposite to the bearing washer 210. The bearing cover 240 supports the rolling elements 220 and receives these rolling elements flatly. The bearing 200 is composed of the bearing washer 210, the bearing cover 240, and the rolling elements 220. The bearing 200, and particularly the bearing washer 210, includes a retaining element 244. The retaining element 244 is configured to radially retain the rolling elements 220 of the bearing 200. The retaining element 244 is radially arranged between the tool axis 102 and the rolling elements 220 and is constructed as a surrounding shoulder 245. The bearing washer 210 and the retaining element 244 are integrally formed here. Here, the bearing cover 240 has a radial stop 246 designed to retain the rolling elements 220. The radial stop 246 is constructed as a surrounding tab and is integrally formed with the bearing cover 240. The radial stop 246 is radially arranged between the rolling elements 220 and the impact mechanism housing 123.

[0044] The intermediate shaft 120 includes a guide element 250. The impactor 300 includes a guide receiver 330. The guide element 250 is configured to guide the impactor 300 by means of the guide receiver 330, at least during the impact operation of the impact mechanism 122. The intermediate shaft 120, and in particular the planetary carrier 280, has the guide element 250 and the guide element is constructed in the circumferential direction about the tool axis 102. The guide element 250 and the planetary carrier 280 are integral. The guide element 250 is here constructed as a surrounding tab. The guide receiver 330 is integrally constructed with the impactor 300 and is constructed as a surrounding groove. The guide receiver 330 surrounds the receiver 302 for the spring element 352 in the circumferential direction about the tool axis 102. During impact operation, the guide element 250 extends into the guide receiver 330 and here guides the impactor 300 axially relative to the tool axis 102, see also Figure 2b .

[0045] During impact operation, an air spring 360 is formed between the guide element 250 and the spring receiving part 330. When the impactor 300 moves axially during impact operation, the air spring 360 is generated by forming an air chamber. The air spring 360 is formed radially between the intermediate shaft 120 and the outer diameter of the impactor.

[0046] The impactor 300 includes an abutment element 340 on its inner periphery, which is received by the journal 168 of the intermediate shaft 120. The abutment element 340 is configured to slide on the journal 168 of the intermediate shaft 120. During impact operation, the abutment element 340 of the impactor 300 extends into the retaining element 244 of the bearing 200, particularly the inner periphery 201 of the bearing washer 210, see also Figure 2b .

[0047] Figure 2b A partial longitudinal section 400 of the impact mechanism 122 in the second operating state 404 is shown. In the first operating state 404, the impactor 300 is arranged toward the drive motor 114. At the end stop of the impactor 300, the abutment element 340 is arranged radially between the intermediate shaft 120, particularly the journal 168 of the intermediate shaft 120 and the retaining element 244.

[0048] Figure 3 shows three views 410, 412, and 414 of the impactor 300 of the impact mechanism 122. Figure 3a A perspective view 414 of the impactor 300 is shown. A canister-shaped spring receiver 302 is shown, into which spring elements 352 can be inserted, as shown in Figure 2. Figure 3b The first cross-section 410 of the impactor 300 is shown. Eight spring elements 352 are arranged circumferentially along the tool axis 102. Here, the eight spring elements 352 are of the same type. Furthermore, the eight spring elements 352 are arranged opposite to each other. A tab 305 is formed between each pair of spring elements 352 in the impactor 300, which helps to increase the moment of inertia of the impactor 300, see also Figures 2, 3a, and 3c. The abutment element 340 is constructed in a sleeve-like manner. Figure 3cThe second cross-section 412 of the impactor 300 is shown. Here, the radial spring system 350 includes a plurality of first spring elements 354 and a plurality of second spring elements 356. The plurality of first spring elements 354 have a higher first spring stiffness. The plurality of second spring elements 356 have a lower second spring stiffness. The plurality of first spring elements 354 and the plurality of second spring elements 356 are each constructed as helical springs. Here, four first spring elements 354 and four second spring elements 356 are constructed. The first and second spring elements 354, 356 are constructed on the impactor 300 in the circumferential direction relative to the tool axis 102. For this purpose, the impactor 300 has a plurality of first spring receiving portions 304 and a plurality of second spring receiving portions 306. The plurality of first and second spring receiving portions 304, 306 are respectively constructed in a can shape, wherein the number of the plurality of first and second spring receiving portions 304, 306 corresponds to the number of the plurality of first and second spring elements 354, 356. The plurality of first and second spring elements 354, 356 are arranged such that, in the circumferential direction, at least one of the second spring elements 356 is arranged next to the first spring element 354, or vice versa. Furthermore, in the circumferential direction, one of the first spring elements 354 is arranged next to one of the first spring elements 354. In the circumferential direction, one of the second spring elements 356 is arranged next to one of the second spring elements 356. One of the first spring elements 354 is arranged opposite to one of the first spring elements 354. One of the second spring elements 356 is arranged opposite to one of the second spring elements 356.

Claims

1. A handheld machine tool (100), comprising: Shell (102) Drive motor (114). Intermediate shaft (120), where, The intermediate shaft (120) can be driven by the drive motor (114). An impact mechanism (122) having an impactor (300) and a radial spring system (350) torsionally connected to the impactor (300), wherein the impact mechanism (122) is at least partially driveable by the intermediate shaft (120), and A tool receiving section (150) for receiving an insert tool (140), wherein the tool receiving section (150) can be driven by means of the impact mechanism (122), in particular the impactor (300) and / or the intermediate shaft (120). Its features are, The intermediate shaft (120) has at least one bearing (200), wherein the radial spring system (350) rests against the bearing (200).

2. The handheld machine tool (100) according to claim 1, characterized in that, The intermediate shaft (120) has at least one planetary carrier (280), wherein the bearing (200) is arranged between the radial spring system (350) and the planetary carrier (280).

3. The handheld machine tool (100) according to claim 1 or 2, characterized in that, The radial spring system (350) rests against the bearing washer (210) of the bearing (200).

4. The handheld machine tool (100) according to claim 2 or 3, characterized in that, The planetary carrier (280) is at least partially constructed as a bearing cover plate (240).

5. The handheld machine tool (100) according to any one of the preceding claims, characterized in that, The intermediate shaft (120) has a guide element (250), and the impactor (300) has a guide receiver (330), wherein the guide element (250) is configured to guide the impactor (300) by means of the guide receiver (330) at least during the impact operation of the impact mechanism (122).

6. The handheld machine tool (100) according to claim 5, characterized in that, At least during the impact operation, an air spring (360) can be formed between the guide element (250) and the journal (168) of the intermediate shaft (120).

7. The handheld machine tool (100) according to any one of the preceding claims, characterized in that, The radial spring system (350) has a plurality of first spring elements (354) and a plurality of second spring elements (356).

8. The handheld machine tool (100) according to claim 7, characterized in that, The plurality of first spring elements (354) and the plurality of second spring elements (356) are arranged alternately.

9. The handheld machine tool (100) according to claim 7, characterized in that, At least two spring elements of the same type (352, 354, 356) are adjacent to each other.

10. The handheld machine tool (100) according to any one of claims 7 to 9, characterized in that, The spring elements (352, 354, 356) are arranged opposite each other.

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