WO2013030381A1

WO2013030381A1 - Handle device

Info

Publication number: WO2013030381A1
Application number: PCT/EP2012/067035
Authority: WO
Inventors: Patrick Heinen; Carsten Diem; Axel Kuhnle; Willy Braun
Original assignee: Robert Bosch Gmbh
Priority date: 2011-09-02
Filing date: 2012-08-31
Publication date: 2013-03-07
Also published as: EP2750835B1; EP2750837A1; WO2013030380A1; EP2750836B1; CN103796800B; CN103781597A; EP2750837B1; CN103764350B; EP2750834B1; EP2750836A1; EP2750835A1; CN103764350A; WO2013030382A1; CN103796800A; WO2013030377A1; EP2750834A1; DE102011082093A1

Abstract

The invention relates to a handle device for a hand-held power tool, which hand-held power tool has an operating-mode switching device and a driving device for driving an insert tool in different operating modes, the handle device comprising at least one spring element (18) and a handle unit (22) attached in at least limitedly movable manner to a power tool housing (20). The handle element is at least partially vibrationally decoupled from the power tool housing (20) by means of the at least one spring element (18) and has a switch actuator (24) for starting up the driving device (14), wherein the switch actuator (24) can be switched between two switching positions in both a monostable manner and a bistable manner. According to the invention, the handle device has an intermediate plate (26), which is provided in the power tool housing (20) and which at least accommodates the spring element (18) at one end, and a control element (28), by means of which the switch actuator (24) interacts with the operating-mode switching device (12) in such a way that bistable switching is not possible in certain operating modes of the switch actuator (24).

Description

description

Handle device prior art

The invention relates to a handle device for a hand tool according to the preamble of the independent claims.

The entry into force of legal requirements, which limit the vibration behavior of hand-held power tools, has given rise to this in the industry

Topic an ever-increasing importance. Especially with heavy drilling and impact hammers due to the high single impact strength vibration is very pronounced. The standard or law now stipulates how long the user may work with it, depending on the vibration level of the machine. If the load from the vibration exceeds specified limits, the permissible service life per day is correspondingly reduced.

As a result, product development is increasingly working on vibration reduction measures. The primary goal is to further increase the ease of use and to maintain a practicable measure of the associated service life per day. In order to reduce vibrations in hammers, part of the machine movement is usually decoupled directly by means of handles for an operator. With regard to the type of decoupling, the market uses fundamentally different concepts. In addition to a double-shell housing, the most widely used method is a handle with an elastic connection to the hammer, in order to decouple the occurring vibrations from the operator via suspension and damping.

Antivibration handles with an elastic connection to the hammer also cause relative movements between the hammer and the handle itself due to the required rigidity as a side effect. From this, requirements for the interface between a hammer and an anti-vibration handle can be derived:

□ In spite of its elastic connection for decoupling, the anti-vibration handle must continue to allow precise guidance of the power tool.

□ Connecting and guiding the anti-vibration handle should not affect the hammer's ergonomic size / length.

□ When designing the internal parts in the anti-vibration handle, the additional movement from the decoupling of the hand-held power tool must be taken into account.

□ Dust protection must be ensured.

□ The switchover from the hammer switch as a function of an operating mode of the hammer, in particular the switching of the switch function and the lockability of the hammer switch, should continue to be maintained.

Disclosure of the invention

The invention relates to a handle device for a hand tool having an operating mode switching device and a drive device for driving an insert tool in different modes, with at least one spring element and with a machine housing at least limited movably mounted handle unit, which over the at least one spring element relative to the Machine housing is at least partially vibration decoupled and comprises a switch actuator to a commissioning of the drive device, wherein the switch actuator can be switched both mono-stable and bi-stable between two switching positions.

It is proposed that the handle device has an intermediate plate, which is provided in the machine housing and which accommodates at least the spring element on one side, and a control means, via which the switch actuator with the Betriebsarten tenschaltschaltvorrichtung cooperates such that in certain modes of the switch actuator is not bi-stable can be switched. By "mono-stable" is to be understood in this context, in particular, that the switch actuator only has a stable switching position, in which the switch actuator can be switched or in which the switch actuator preferably falls back automatically, while the switch operator in at least one other switching position of a operator must be kept in particular. In this context, the term "bi-stable" should be understood in particular to mean that the switch actuator has two stable switching positions into which the switch actuator can be switched

Switch actuator is preferably formed as an on-off switch of the power tool.

The handle device according to the invention with the features of the main claim solves the task in a simple to assemble and cost-effective manner. It fulfills all requirements placed on it.

The measures listed in the dependent claims and in the following description of the embodiments, advantageous refinements and improvements of the main claim features.

Thus, it is further proposed that the control means is designed as a drawstring. The drawstring may preferably be made of a plastic or other material that appears appropriate to a person skilled in the art. The tension band preferably has an at least substantially rectangular cross section with an at least substantially circular-like, in particular circular middle fiber. It is also conceivable for the middle formers to have an at least essentially four- or hexagonal or another cross-section which appears expedient to a person skilled in the art. The middle fiber is preferably provided to serve at least partially as a filling channel, in particular during an injection process, and / or to form an advantageously narrow contact line with the leaf spring. The drawstring may preferably be made of a plastic. As a result, an advantageous cost-effective design can be achieved.

In addition, it is proposed that the at least one spring element is formed by a leaf spring. As a result, in particular a preferably cost-effective implementation and an advantageously simple assembly of the handle device can be achieved.

Furthermore, it is proposed that the handle device has at least one secondary spring element, which is formed by an elastomeric spring element. As a result, the spring element formed by the leaf spring can be advantageously supported in a spring action, and use of the handle device, in particular in larger and more powerful hand tool machines, can be achieved. It is also proposed that the secondary spring element is acted upon only after a certain compression travel. It is proposed that the spring stiffness of the spring element formed by the leaf spring is adjusted so that with a compression travel between 2 mm and 10 mm, preferably between 3 mm and 7 mm, more preferably between 4 mm and 5 mm minimum operating pressure points for most important Use cases can be achieved. From this Andruckschwelle the secondary spring element begins to act. The more volume of the

Eiastomerfederelements is deformed during compression, the stiffer is a characteristic of the secondary spring element.

It is therefore further proposed that a volume compression of the

Eiastomerfederelements is designed such that at an additional compression of 2 mm to 5 mm, in particular from 3 mm to 4 mm over a minimum operating pressure point beyond the elastomeric spring element is compressed to 70% of its original volume. In a further compression of 1 mm to 2 mm, virtually the entire volume of the Eiastomerfederelements is acted upon, so that the spring stiffness increases relatively quickly. This has the advantage that in a case on the Antivibrati- onshandgriff very much energy can be absorbed, so that the impact-like components are less loaded.

drawing

Further advantages emerge from the following description of the drawing. In the drawing, several embodiments of the invention are shown. The drawing, the description and the claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations.

Show it:

1 a shows a handheld power tool with a handle device according to the invention in a schematic side view,

Fig. 1 b shows a detail of the handle device according to the invention in a

Sectional view 2 shows an assembly of the handle device according to the invention in a perspective view,

3a shows a detail of the handle device according to the invention in one

Sectional view

3b, the assembly of the handle device according to the invention in a

Sectional view

4a shows a detail of the handle device according to the invention in a

Sectional view

4b an alternatively configured section of the handle device according to the invention in a sectional view,

Fig. 4c shows a detail of the handle device according to the invention in one

Sectional view

Fig. 5 shows a detail of the handle device according to the invention in a

Sectional view

6a shows a part of the assembly of the handle device according to the invention in a perspective view,

6b shows a part of the assembly of the handle device according to the invention in a side view,

6c shows a part of the assembly of the handle device according to the invention in a side view,

7a shows a control means of the handle device according to the invention in a schematic representation,

Fig. 7b, the control means of the handle device according to the invention in a

Sectional view

Fig. 7c, the control means of the handle device according to the invention in a

Sectional view

8a shows a detail of the handle device according to the invention in one

Sectional view

8b shows a detail of the handle device according to the invention in one

Sectional view

8c shows a detail of the handle device according to the invention during assembly in a sectional view,

9 is a detail of the handle device according to the invention in a schematic representation,

Fig. 10 shows a detail of the handle device according to the invention in a

Sectional view Fig. 1 1 a detail of the handle device according to the invention in a

Sectional view along the section line Xl-Xl,

12a shows a detail of the handle device according to the invention in one

Sectional view

Fig. 12b shows a detail of the handle device according to the invention in one

Sectional view

Fig. 13 shows a detail of the handle device according to the invention in one

Exploded

14a shows a detail of the handle device according to the invention in one

Sectional view

Fig. 14b shows a detail of the handle device according to the invention in one

Sectional view along the section line XIVb-XIVb and

Fig. 15 shows a detail of the handle device according to the invention in a

Sectional view.

Description of the embodiments

1 shows a schematic view of a drill and / or chisel hammer as an example of a hand tool 10 with a machine housing 20, a tool holder 54 movably mounted on the machine housing 20 for exchangeable reception of an insert tool 16 and with a housing 20 accommodated in the machine housing, a drive unit and a gear unit having drive device 14 for driving the insert tool 16 in different modes. The tool holder 54 is preferably rotatably arranged on an end face of the machine housing 20. On one of the front side of the machine housing 20 opposite side of the machine housing 20, a handle device is further provided in the example of Figure 1 further. The handle device comprises in the present example a switch actuator 24 for commissioning the drill and / or chisel hammer. The switch actuator 24 can be switched both monostable and bi-stable between two switching positions. Furthermore, an additional handle device 56 is arranged on the machine housing 20 of the drill and / or chisel hammer, in particular arranged adjustable. The hand tool 10 has an operating mode switching device 12. In addition, a Bedienhebei for a mode switch is arranged on the machine housing 20, with which an operator can choose between different drive types for the insert tool 16 used in the tool holder 54.

The handle device for the power tool 10 comprises a spring element 18 and a at least limited movably mounted on the machine housing 20 handle unit 22 which is vibration-decoupled via the spring member 18 relative to the machine housing 20 and the switch actuator 24 includes a commissioning of the drive device 14. The handgrip unit 22 comprises an anti-vibration handle 58. The handheld power tool device further comprises a control means 28, via which the switch actuator 24 cooperates with the mode changeover device 12 in such a way that in certain operating modes

Switch actuator 24 can not be bi-stable switched. The control means 28 is designed as a drawstring 30. The u.a. shown assembly consists of the following functional units: an intermediate plate 26, the spring element 18 and a slide valve assembly. The intermediate plate 26 is the central

Component of this module. Their structure allows a number of possibilities for the simple implementation of existing functions in the hand tool 10 formed by the hammer when using the anti-vibration handle 58 and a mechanical switch operation with switching.

One of the central tasks of the intermediate plate 26 is the receiving and guiding of the spring element 18, as shown in Figures 3a and 3b. The spring element 18 is clamped by the intermediate plate 26 in the anti-vibration handle 58 and fixed at the clamping point over a contour. The contour is preferably realized in a contact surface on the intermediate plate 26, on which the spring element 18 can be supported. The curve of this contour determines stiffness, bending line and paths of the spring element 18. The spring element 18 is designed as a leaf spring 32.

Furthermore, the intermediate plate 26 serves as a stop for or as a stop for one or more secondary spring elements 34, 34 ', 34 ", which can serve as damping elements. FIGS. 4a to 4c show conceivable variants and embodiments of the secondary spring elements 34, 34', 34 "presented. According to FIGS. 4 a to 4 c, pockets with supporting ribs 60 and a frame 62 additionally provide for the introduction of damping elements into the intermediate plate 26. The secondary spring elements 34, 34 ', 34 "can preferably be made of foam, a cellular rubber

Sponge rubber, another synthetic or natural foam, elastomer, TPE, rubber, be formed gel or a similar elastic material. The degree of damping or suspension can also be adjusted via the volume of individual chambers. The frame 62 prevents jamming with other surrounding components.

Suspension and damping are consequently adjusted to one another centrally via the reception of the spring element 18 and the secondary spring elements 34, 34 ', 34 "in the intermediate plate 26. The result is the compact assembly which is intended for pre-assembly and which comprises all essential components for the operative connection of the The principle facilitates the tuning of the components for decoupling and also makes it possible to derive a rigid handle of the handle unit 22 without switching from it by omitting the assembly without great effort

Guiding the power tool 10 and in particular an improved transmission of operating forces on the anti-vibration handle 58 on the machine housing 20 of the power tool 10. According to Figure 5 are in the upper region of a handle housing 64 and at the connection to the motor assembly comprising drive device 14 support points and recordings of Intermediate plate 26 designed so that along the power flow from the anti-vibration handle 58 operating forces unfiltered or unsprung can be transferred to the power tool 10. This results in a good control of the manual power tool 10. The intermediate plate 26 is provided in the machine housing 20 and receives the spring element 18 on one side. Finally, in the intermediate plate 26, the slide valve assembly is added The slide valve assembly consists of 6a to 6c of a slide 66, the drawstring 30 and a compensation spring 68. In addition to the intermediate plate 26 forms another important unit especially in the transmission of switching or Switching paths to the switch actuator

24. The trained as a drawstring 30 control means 28 is made of plastic.

As a result, it is possible to regulate dimensional dependencies, which affect the mode of operation of the switch actuator 24, in only one component. It takes little space. The assembly is easy. The widened headrest at the

Slide valve 66 paired with jumps / steps in the guide prevents one Dust enclosure between sliding surfaces. As a result, a malfunction can be avoided by clamping on the slide valve 66 in principle.

The z-shaped, cranked slide switch 66 can be pushed into the intermediate plate 26 with a simple sliding movement and locked in place by means of a snap hook connection, not shown, in the intended installation position. It is also conceivable that the z-shaped, cranked slide switch 66 can rotate into the intermediate plate 26 with a simple pivoting movement. The aspect ratio of the guide surfaces ensures sufficient pre-centering during the entire pre-assembly. A wrong assembly is thereby excluded.

For a mode-dependent switching from the hammer switch according to the publication DE 197 20 947 A1, the disclosure of which is explicitly made at this point, the path and the force must be transmitted from a control lever trouble-free mechanically to a switch from the switch operator in the handle. In

Combination with an anti-vibration handle opens up approaches similar to the document DE 10 2010 038 753 A1, in which a tension band is arranged in the neutral fiber of the handle movement. Frictional losses, deformation of the spring element 18 and aspects of the manufacturing process, however, make it difficult to implement this concept in practice.

For this reason, especially the material and geometry are crucial for the execution of the drawstring 30. As a material, plastic offers a great variety of variations in order to combine low friction values with good emergency running properties and low dust susceptibility. Therefore, a plastic is fundamentally a very suitable material for this application. In order to achieve sufficient rigidity for the transmission of tensile forces, while at the same time lose flexibility for a driving on the spring element 18, cross-sectional conditions are determining.

A band cross section of the tension band 30 must be very flat in height and long in the width. In the present construction, a rectangular cross-section with an aspect ratio of 1:10 was combined with a substantially circle-like - lo chen, in particular circular, medium fiber chosen (see Figures 7a to 7c), but it can also cross sections with rounded corners and / or different aspect ratios, in particular in the range between 1: 2 to 1: 20, particularly preferably from 1: 5 to 1: 15 be beneficial.

Area shares are variably adjustable over the entire length of the drawstring 30, but must remain balanced in total. As a result, in spite of eyelets and deflection in use, an always constant tension in the tension band 30 is maintained. It is possible to ensure uniform loading of the material.

Between stiffness and flexibility also helps the variation of the area proportions. The substantially circle-like, in particular circular portion serves to fill the mold in the manufacturing process and at the same time advantageously increases the strength.

Due to manufacturing tolerance, thermal-elastic length changes, shrinkage / recrystallization and the pronounced flow behavior of plastic under load of the tension band 30, add up in the transmission of tensile forces and paths on the drawstring 30, which is made of plastic, differences that a secure re and satisfactory function of the switch actuator 24 by mechanical means only partially ensure.

With the help of the compensation spring 68 (see Figure 6a), these difficulties can be solved easily.

In the bias of the compensation spring 68, a buffer is created by the installation situation in the slide valve 66, which can compensate for any blurring of manufacture and mechanical behavior of the tension band 30, which is made of plastic.

The drawstring 30 must have a body for receiving the compensation spring 68 and safely taken up with the help of two rotational recordings in the slide valve 66 / performed. The slide valve 66 supports the compensation spring 68 on the opposite side and determines the measure of the compensation over the installation length. Upon actuation of the switching, the path from the slide valve 66 is now transmitted force-dependent on the drawstring 30 and the switch actuator 24 (see Figures 8a and 8b). The coupling is no longer rigid but linear-elastic. The paths between the slide valve 66 and switching lever on the switch actuator 24, which forms a hammer switch, are designed so that in the compensation spring 68 is always a

Reserved reserve. This reserve from the length of the compensation spring 68 in operation can be used for tolerance compensation and compensation of thermal, elastic as well as plastic changes in length on the drawstring 30, which is made of plastic. An overload protection is ensured and tensile forces are now applied to the tension band 30 via the compensation spring 68.

For ease of assembly, an opening in the guide has been left on the slide switch at the front and the pull strap 30 has been snap-fitted, i. provided (see Figure 8c). The drawstring 30 is tuned in width to the inclusion in the switching slide 66. As a result, the tension band 30 together with the compensating spring 68 can simply be threaded through the receptacle in the slide switch 66. The components are then automatically pulled into their installed position via the force in the intended direction of pull and remain secured therein. For effective dust protection is on the intermediate plate 26 further a labyrinth

70 is provided, which for covering a percussion gear housing and a housing cover comprising a machine housing 20, the engine assembly comprising a drive device 14 and the anti-vibration handle 58 inwardly reached (see Figure 9). The labyrinth 70 engages the transitions into the surrounding parts and, especially during the switchover of the switch actuator 24 formed by the hammer switch, effectively ensures dust protection and safe operation. Additional sealing elements are not required.

Another aspect of the invention relates to the fact that for larger and more powerful hand tool machines 10, such as e.g. in heavy drilling and

Chisel hammers, the above-described fixation of the leaf spring 32 between the anti-vibration handle 58 and the machine housing 20 is no longer sufficient. For example, here, the leaf spring 32 is no longer sufficient as the sole spring element. Additional secondary spring elements 34 have to be introduced between the machine housing 20 and the leaf spring 32 in order to prevent the too soft leaf spring 32 in its ih- to support spring action. The secondary spring elements 34 are each formed by an elastomeric spring element 36.

According to the document DE 10 2006 029 630 A1, the leaf spring can be acted upon by a clamping piece and the screw plate only on the back side functionally or with forces. On the side of the leaf spring facing the device side, no holding or fixing functions or forces can be introduced. The invention thus represents an extension of the known from the document DE 10 2006 029 630 A1 solution to implement the presented there anti-vibration handle concept even with larger and more powerful hand tool machines can.

The operator-held anti-vibration handle 58 includes the switch actuator 24 formed as an on-off switch, and is closed by screwing a handle of the anti-vibration handle 58 backward.

At the top, the leaf spring 32 is clamped between the anti-vibration handle 58 and two screw plates 48. The two screw plates 48 are pushed in the transverse direction on both sides of the leaf spring 32. The screw plates 48 thus enclose an upper clamping region 50 of the leaf spring 32 up to the contact zone to the anti-vibration handle 58 in all spatial directions. This ensures a durable and stable enclosure of the leaf spring 32. In the screw 48 are screw dome 52, which serve for screwing the screw 48 and thus one of the leaf spring 32 with the anti-vibration handle 58. The screw 48, the leaf spring 32, the anti-vibration handle 58 and a strained bellows 72 form a fastening system, which is held together advantageously on form and frictional connection. The positive connection is formed by mutually supporting and penetrating retaining domes and ribs, so that the adhesion has only a fixing function and the essential forces are absorbed by the positive connection of the components.

A significant advantage of the screw plates 48 pushed on both sides is the provision of additional functional surfaces in front of a region and laterally of a region of the screw plates 48 of the leaf spring 32.

In the front region, the screw plates 48 are formed so that they can accommodate the additional secondary spring elements 34. In addition to spring shots have the screw 48 even more features. In order to prevent tearing out of the anti-vibration handle 58 and thus also overloading of the leaf spring 32, the screw plates 48 have lateral abutment surfaces which are supported on the back on two rear plates 38 designed as housing rear plates. As a result, the anti-vibration handle 58 has a stable and defined back stop. Another function of the screw 48 is the lateral guiding and covering the control means 28 formed by the tension band 30 relative to that of a

Elastomer formed secondary spring element 34. With the drawstring 30 of the switch actuator 24 formed by the on-off switch is blocked during a Meißeins, so that the operator does not press the switch actuator 24 constantly. The

Tieback 30 must be able to slide smoothly on the leaf spring 32 and must not be jammed or pinched.

During the pushing together of the two screw plates 48 on the leaf spring 32, the tension band 30 is chambered in a slot of the screw 48. Also the

Bellows 72 is chambered by the screw plates 48 in the anti-vibration handle 58. Furthermore, the screw 48 also form the end stop in the longitudinal and vertical direction of the anti-vibration handle 58. The lower Blattfederklemmung is in the screw system of the back plates

38 has been advantageously integrated into the machine housing 20 (see FIGS. 14a and 14b). The previously one-piece backplate was split into two mirror-symmetrical backplates 38 in order to fulfill all required functions, favorable mountability and mold endformability.

As with the document DE 10 2006 029 630 A1, the bellows 72 already mounted on the anti-vibration handle 20 and the rocker arms (not shown) are chambered during assembly by pushing the two back plates 38 together. Due to the required bias of the leaf spring 32, the leaf spring 32 is then a bit of the back plates designed as housing rear plates 38 from. In order to simply press the leaf spring 32 in its operating position during assembly, a spring plate 40 is inserted above with its two retaining ribs 42 in two corresponding retaining grooves 44 formed as housing rear plates back plates 38 and then folded against a leaf spring tension in the direction of the back plates 38 to the rear , In order to hold this position, two are in the back plates 38

Snap hook 46 integrates, which engage in the spring plate 40 and these in the Keep assembly position. The thus pre-assembled complete, designed as a handle assembly handle device can then be applied in an assembly line on the core device.

For clamping the leaf spring 32 both positive and positive elements are used. As a positive connection, the leaf spring 32 has at its lower end two openings and a Abfalzung 74. The leaf spring 32, the spring plate 40 and the machine housing 20 are threaded onto two domes of the respective side of the back plates formed by the housing rear plates 38. Furthermore, the spring plate 40 engages around the two screw domes of the machine housing 20. The Abfalzung 74 of the leaf spring 32 is clamped between the back plates 38 and the spring plate 40. By screwing the rear plates 38 formed by the housing rear plates with the machine housing 20, all parts are clamped together. The advantageous nesting of the components into one another produces a permanent connection which withstands the high vibration load in the hand-held power tool 10 formed by a striking power tool.

Even in the case of a loss of preload in the screw connection due to settling or dissolution processes, the connection is maintained due to the positive connection. The spring plate 40 is designed in its contour height so that the leaf spring 32 is firmly clamped down to about 25% of its length. The remaining length can cantilever freely during compression.

Another aspect of the invention is the combination of the leaf spring 32 as the primary spring element and the at least one further secondary spring element 34, which is acted upon only after a certain compression travel.

FIG. 15 shows a cross-section through the upper region of the anti-vibration handle 58 with the leaf spring 32 and the secondary spring element 34. The screw plates 48, which surround the leaf spring 32, are designed to receive the one or the additional secondary spring elements 34 can. In the embodiment shown, for example, a foamed elastomer molded part between the screw plate 48 or the leaf spring 32 and the spring plate 40 is introduced. The elastomeric molded part is formed as the elastomeric spring element 36 and forms the secondary spring element 34. Foamed elastomer moldings have the advantage of cost-effective production by a continuous extrusion molding process with subsequent cutting to the required length. Furthermore, they act in virtually all directions, ie they have no preferred direction such as a helical compression spring.

The advantageous, formed as Elastomerfederelement 36 secondary spring element 34 supports the leaf spring 32 at loads that are above an optimal Betriebsandruckpunkts. The optimum operating pressure point is the minimum pressure that the operator just has to provide in order for the hand tool 10 formed by the hammer to perform a regular and clean impact operation. This operating pressure is dependent on the power class of the power tool 10 and the particular application.

That by providing a certain play of the elastomeric spring element 36 between see the contact surfaces, an at least two-stage spring characteristic is generated. Until the operating pressure point, only the leaf spring 32 acts, so that a very good decoupling of the anti-vibration handle 58 with a low vibration level can be achieved. A good decoupling is achieved in this area, especially because the leaf spring 32 has a very low damping constant. In an overpressure or in a case of the power tool 10 on the anti-vibration handle 58 then takes the elastomeric spring element 36 to the significant proportion of loads.

It is proposed that the spring stiffness of the leaf spring 32 is adjusted so that with a compression travel between 2 mm and 10 mm, preferably between

3 mm and 7 mm, more preferably between 4 mm and 5 mm, the minimum operating pressure points are achieved for most important applications. From this Andruckschwelle the secondary spring element 34 starts to act. The more the volume of the elastomeric spring element 36 is deformed during spring deflection, the higher is the characteristic of the secondary spring element 34. It is therefore further proposed that a volume compression of the elastomeric spring element 36 be designed such that with an additional compression of 2 mm to 5 mm, in particular from 3 mm to 4 mm beyond the minimum operating pressure point beyond the

Elastomer spring element 36 is compressed to 70% of its original volume. With further compression of 1 mm to 2 mm, almost the entire volume of

Elastomer spring member 36 is applied, so that the spring stiffness relatively quickly increases. This has the advantage that in a case on the anti-vibration handle 58 a lot of energy can be absorbed, so that the impact-like components are less loaded. A described compression characteristic can also be effected or supported by a targeted shaping of the elastomer spring element 36. It is thus also possible to install tubular or other contours that can be produced in an extrusion process. The elastomer spring element 36 is preferably made of foamed elastomer (sponge rubber), which is produced in a continuous extrusion molding process with subsequent cutting to length.

Claims

A handle apparatus for a hand tool machine (10) having a mode changeover device (12) and a drive device (14) for driving an insert tool (16) in different modes, comprising at least one spring element (18) and one on a machine housing (20). at least a limited movably mounted handle unit (22), which is at least partially vibration decoupling via the at least one spring element (18) relative to the machine housing (20) and a switch actuator (24) for commissioning the drive device (14), wherein the switch actuator (24) both mono-stable and bi-stable can be switched between two switching positions, characterized by an intermediate plate (26) which is provided in the machine housing (20) and which accommodates at least the spring element (18) on one side, and a control means (28), via the switch actuator (24) with the operating mode switching device (12) de cooperates, that in certain modes of the switch actuator (24) can not be switched bi-stable.

Handle device according to claim 1, characterized in that the control means (28) is designed as a drawstring (30).

Handle device according to claim 1 or 2, characterized in that the at least one spring element (18) by a leaf spring (32) is formed.

Handle device according to one of the preceding claims, characterized by at least one secondary spring element (34), which of a

Elastomer spring element (36) is formed.

5. Handle device according to claim 4, characterized in that the secondary spring element (34) is acted upon only after a certain compression travel.

6. Hand tool (10), in particular drill and / or chisel, with a handle device according to one of the preceding claims.

7. drawstring (30) of a handle device at least according to claim 2, which is made of plastic.

8. drawstring (30) according to claim 7, characterized by a substantially rectangular cross section with a substantially circular middle fiber.