WO2012049016A1

WO2012049016A1 - Pneumatically driven hand tool having a modular turbine

Info

Publication number: WO2012049016A1
Application number: PCT/EP2011/066732
Authority: WO
Inventors: Jan Sitzler; Dieter Kaiser
Original assignee: Schmid & Wezel Gmbh & Co.
Priority date: 2010-09-27
Filing date: 2011-09-27
Publication date: 2012-04-19
Also published as: DE202010013940U1; SI2622180T1; PL2622180T3; ES2614087T3; EP2622180A1; EP2622180B1

Abstract

The invention relates to a hand tool (10) having a housing (12) and a tool holder (14) rotationally connected to a rotor (32) that is rotatably mounted in the housing (12) and that comprises at least two separate individual turbines (46, 48, 50, 52) which are disposed one behind the other on the rotor (32), are connected to the rotor (32) in a rotationally fixed manner and are set up to be pneumatically driven. The manual tool is characterized in that the manual tool (10) comprises the at least two individual turbines (46, 48, 50, 52), which are connected to each other in a rotationally fixed manner by first coupling means (176) in a prescribed angle of rotation position and which are elastically clamped against each other in the direction of the rotational axis thereof to form a compact turbine packet.

Description

Pneumatically powered hand tool with a modular turbine

The present invention relates to a hand tool according to the preamble of claim 1.

Such a hand tool is known from US 2005/0064803 A1 and has a housing and a tool holder, which is rotatably connected to a rotatably mounted in the housing drive shaft. US 2005/0064803 A1 starts from a hand tool with a single turbine and mentions an enlargement of the turbine diameter as a way of increasing the torque of the hand tool. However, this could greatly increase the weight, size and volume of the housing and thereby reduce the benefits of a hand-held and lightweight hand tool.

In the description of US 2005/0064803 A1, the possibility is mentioned in this context to use two stacked turbines ("two stacked turbine rotors"). However, this would have disadvantages in terms of weight, noise and the development of vibrations, air consumption and the number of moving parts that could wear out. As an alternative to using stacked turbines, US 2005/0064803 A1 proposes the use of a two-piece, one-piece turbine.

The present invention therefore has at least two individual turbines, which are rotationally fixedly interconnected by first coupling means in a predetermined rotational angular position and elastic in the direction of their rotational axis relative to one another to form a compact turbine package are tense.

By these features, a turbine package formed from individual modules is provided, the individual modules are braced relative to each other in a defined position with each other

and since it therefore behaves like a one-piece multi-chamber turbine in operation, the hand tool according to the invention in particular has the advantage over the stacked turbine known from US 2005/0064803 A1 that no more vibrations than in the case of a single turbine are to be expected.

It is also advantageous that the individual parts of the turbine package can not move relative to each other due to their mutual mutual tension during operation of the hand tool. Therefore, an increased wear of these parts, as it is called a disadvantage in US 2005/0064803 A1, avoided.

Compared to the single-turbine comprising several chambers from US 2005/0064803 A1, the present invention has the particular advantage of a modular construction which allows a combination of turbine packages with two, three, four or in principle any number of turbines. The modular construction is particularly advantageous for offering various hand tools of a series with different values of their respective maximum torque, since the maximum torque increases as the number of turbines increases. In addition, the multi-chamber turbine of US 2005/0064803 A1 is limited for manufacturing reasons to designs with two chambers. Such a limitation is not present in the hand tool according to the invention.

Compared to a hand tool with a single turbine, the invention has the particular advantage that a turbine package having at least two individual turbines can provide a predetermined maximum torque with a much smaller turbine radius than is the case with a single turbine. The invention thus has the advantages of the multi-chamber turbine from US 2005/0064803 A1 and has the additional advantages resulting from the modular design.

In a preferred embodiment, each turbine consists of a first half wheel and a second wheel half, each wheel half has a disc-shaped base body and from the disk-shaped body protruding and mutually identical guide structures, which are separated by mutually equal gaps from each other, and in one of the number Lead structures correspondingly-count rotational symmetry are distributed over each wheel half, wherein the lead structures and spaces complementary to each other are designed so that the lead structures of the first half wheel when joining the two wheel halves so in the interstices of the second wheel half and the lead structures of the second half wheel when assembling the two wheel halves fit into the interstices of the first half wheel so that between walls walls of adjacent conductive structures of the first half wheel and the second wheel half billow flow channels the.

These features provide individual turbines, which in turn are constructed from modules, namely from the wheel halves.

Due to the separation of the individual turbines in the above-mentioned wheel halves, each wheel half is easily accessible for production engineering measures, with which in particular the internal flow channels can be designed with assembled wheel halves.

The symmetrical design avoids imbalances, which contributes to a high speed stability and a desired low vibration during operation.

The fact that the flow channels are generated by joining complementary Radhälften, very narrow flow channels with exact geometry manufacturing technology can be easily produced. The narrow flow channels provide high flow rates, which is helpful for high maximum speed, for example, over 100 000 min ^-1 at small air losses.

The individual wheel halves can be made of compact solid material with very stable and thus very speed-resistant structures.

It is also preferred that the wheel halves arranged coaxially to its axis of rotation and in one of the number of holes corresponding-counted rotational symmetry distributed over the wheel half holes, which are adapted to receive a rod which is arranged as a first coupling means, aligned bores penetrate the wheel halves of all turbines of the turbine package and thus rotatably couple the individual turbines of the turbine package with each other.

Together with the rod, the holes each allow a coupling of both wheel halves of a turbine, in which these wheel halves are fixed relative to each other in predetermined angular positions. This ensures that neighboring guide structures of the wheel halves do not abut each other and that the desired narrow flow channels form between the mentioned guide structures.

Due to the fact that the rod penetrates the wheel halves of all turbines of a turbine package, the individual wheel halves can in a sense be threaded onto the turbine package during manufacture, which simplifies the manufacture and handling of the turbine package during the production of the inventive hand tool.

Further advantages will be apparent from the dependent claims, the description and the attached figures.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

drawings

Embodiments of the invention are illustrated in the drawings and are explained in more detail in the following description. Show, in schematic form:

Figure 1 shows an embodiment of a hand tool according to the invention;

Figure 2 is a plan view of a pressure-connection part of the hand tool of Figure 1;

3 shows a longitudinal section through the hand tool 10;

FIG. 4 shows a first half wheel of a single turbine of the hand tool;

Figure 5 is a complementary second wheel half;

FIG. 6 shows a single turbine with a speed control function;

Figure 7 is a perspective view of a control sleeve;

Figure 8 is a plan view of the front end of the control sleeve;

9 shows a longitudinal section through the control sleeve;

FIG. 10 shows a cross section through the control sleeve;

Figure 11 shows an embodiment of a brake;

Figure 12 is another view of the article of Figure 11; and FIG. 13 adjustment-rotational angle characteristics of the control sleeve.

1 shows an embodiment of a hand tool 10 according to the invention. The hand tool 10 has a housing 12 designed as a handle part, from the front end of which a tool holder 14 protrudes. The tool holder 14 is rotatably connected to a rotor which is rotatably mounted in the housing 12 and is driven by a pressurized fluid. Compressed air is in particular compressed air in question. The compressed air is supplied to the hand tool 10 via a connecting part 16, which has a valve for controlling the compressed air supply. The actuation of the valve via a rotatable control sleeve 18, which is arranged at a rear end 20 of the housing 12 between the housing 12 and the connecting part 16. The control sleeve 18 has a front end 22 and a rear end 24.

FIG. 2 shows a plan view of the connection part 16 from FIG. 1. The connection part 16 has a central supply air opening 26 and a plurality of peripherally arranged exhaust air openings 27.

In the following, an embodiment of an internal structure of the hand tool 10 will be explained with reference to FIG. 3, which allows the slim housing form presented here.

FIG. 3 shows a longitudinal section through the hand tool 10. In the illustrated embodiment, the housing 12 has an inner sleeve 28 and an outer sleeve 30, which are fitted into one another with an exact fit and fixedly connected to one another. The inner sleeve 28 is preferably made of metal, in particular a light metal such as aluminum and gives the housing 12 the required strength. The outer sleeve 30 is preferably made of a compared to the metal of the inner sleeve 28 poor heat conductive plastic.

This has the advantage that the cooling occurring during the relaxation of the compressed air in the hand tool 10 during manual handling does not lead to an annoying cooling of the gripping surface of the outer sleeve 30. This is perceived as an advantage during handling.

The execution of the inner sleeve made of light metal keeps the weight of the hand tool 10 low, which also contributes to a good handling and fatigue-free work, especially in fine work and is therefore also felt in handling as an advantage.

In the inner sleeve 28, a rotor 32 is rotatably mounted in bearings 34, 36. The rotor 32 is at its end, which protrudes from the front end 15 of the housing 12, rotatably connected to a tool holder 14. The tool holder is in one embodiment, a collet 38, which is connected via a pliers spindle 40 with the rotor 32. The other end of the rotor 32 is configured as a hollow spindle 42 whose central cavity 44 is pneumatically connected to the compressed air supply when the compressed air valve 45 is open and the compressed air supply connected to the connection part 16.

On an outer surface of the spindle 42 are preferably n mutually equal radial turbine modules 46, 48, 50, 52 are arranged, where n may be equal to two or in principle any number greater than 1. In a preferred embodiment, n is less than or eight. Particularly preferred is an embodiment with n = 4 radial turbines. By the successive arrangement of n radial turbines, which have a comparatively small diameter, the same torque can be generated, as by a single radial turbine, which has a comparatively large diameter. A hand tool with a single radial turbine with a comparatively large diameter is known from the aforementioned DE 201 03 600 U1.

The preferred sequential arrangement makes it possible to make the housing 12 substantially slimmer than is the case with the subject matter of DE 201 03 600 U1.

The series connection thus improves in particular the ease of handling and, in particular, together with the features of claim 1 relating to the housing 12, develops a combinatorial effect with respect to the desired improvement in handling.

Further improvements in the handling result from a special embodiment of the control sleeve 18. Before an explanation of the control sleeve 18, further elements of the drive of the hand tool are first described.

The radial turbines 46, 48, 50, 52 are flowed over in the axial direction along the spindle 42 offset openings 54, 56, 58, 60 from the cavity 44 of the spindle 42 from the inside with compressed air. In this case, three openings are preferably provided for each module of the radial turbine, which are distributed uniformly over the circumference of the portion of the spindle 42 which is within the respective radial turbine module. After flowing through the radial turbines, the expanded air escapes radially outward, from where it flows out of the hand tool 10 via a silencer 62 having exhaust air duct 64. The radial turbines 46, 48, 50, 52 are rotatably coupled to the spindle 42 of the rotor 32 and therefore drive the rotor 32 at. In the illustrated embodiment, the rotationally fixed coupling takes place by axial clamping of the radial turbines 46, 48, 50, 52 with the spindle 42 by a clamping nut 66. In a housing adapted to accommodate n radial turbines less than n radial turbines can be used by one or several of the turbines are replaced by a collet.

Before discussing further features of the hand tool 10 illustrated in FIG. 3, a preferred embodiment of a modular turbine will first be explained with reference to FIGS. 4-6.

The individual turbines each have a first wheel half, a second wheel half and means for coupling the two wheel halves. FIG. 4 shows a first wheel half 120, while FIG. 5 shows a second wheel half 122 complementary thereto. The first wheel half 120 has a disk-shaped basic body 124 and n conductive structures 126, 128, 130, 132, 134 and 136 which project from the disk-shaped basic body 124 and are identical to one another. on. These conductive patterns 126, 128, 130, 132, 134, and 136 are separated by n equal spacing 138, 140, 142, 144, 146, and 148 from each other. In the illustrated embodiment, n = 6. Depending on the embodiment, n may also have other even-numbered or odd-numbered values. The conductive patterns 126, 128, 130, 132, 134 and 136 and the gaps 138, 140, 142, 144, 146 and 148 are distributed in an n-fold rotational symmetry over the first wheel half 120, so that the shape of the first wheel half at a turn by 360 ° / n is converted back into itself.

The first wheel half 120 has distributed over its surface holes 150, 152, 154, which are arranged by their arrangement and their dimensions to receive first coupling means. The first coupling means are preferably rods which are passed into the bore and through the holes, so that a plurality of wheel halves are threaded. The bores 150, 152, 154 are preferably distributed rotationally symmetrically over the surface of the first wheel half 120 in order to generate as much as possible no imbalance during operation.

FIG. 5 shows a second wheel half 122 designed to be complementary to the first wheel half 120 from FIG. 4. The second wheel half 122 likewise has a disc-shaped main body and n = six guide structures projecting from the disc-shaped basic body and identical to one another, which are separated from each other by n mutually equal spaces are. Again, the lead structures and spaces are distributed over the second wheel half 122 in an n-fold rotational symmetry. In addition, the second wheel half distributed over its surface holes 156, 158, 160, which are adapted by their dimensions and arrangement to receive the aforementioned pin-shaped or rod-shaped first coupling means.

In contrast to the first wheel half 120, in which the bores 150, 152, 154 lie in the intermediate spaces, the bores 156, 158, 160 are arranged in the second wheel half in the projecting guide structures. When joining the wheel halves 120, 122 using the first coupling means, each projecting guide structure of the one wheel half is then placed at a predetermined position within a space of the other wheel half. In each case, the guide structures of one wheel half do not completely fill the intermediate spaces of the other wheel half.

The guide structures and the interstices of the two wheel halves are rather complementary to each other designed so that the lead structures of the first half fit into the intermediate spaces of the second half of the wheel when joining the two wheel halves and the guide structures of the second wheel half when joining the two wheel halves so in the interstices fit in the first half of the wheel, that flow channels form between walls of adjacent guide structures of the first half wheel and the second wheel half. A pair formed in this way from a first and a second wheel half forms a module in the form of a single turbine.

The illustration of the wheel halves 120, 122 in FIGS. 4 and 5 shows that, when the wheel halves 120, 122 are assembled, an annular space is created, which is defined by a wall 162 in the second wheel half 122 and by the wall sections arranged concentrically with the central opening 166 164 of the conductive structures of the two wheel halves is limited.

In a preferred embodiment, which is shown schematically in FIG. 6, at least one elastic ring, for example a rubber ring, is inserted in this space during assembly of the wheel halves. This rubber ring will expand during operation of the turbine at high speeds and the radially inwardly facing openings of the flow channels 172, 174 increasingly close with increasing speed. This results in a speed-regulating and limiting function.

By attaching further modules to the correspondingly long-sized pin or rod-shaped first coupling means 176, a turbine package with a desired number of individual turbines is formed. The formation takes place, for example, such that the individual wheel halves are pushed onto the hollow spindle 42 of the rotor 32 and coupled to one another by the first coupling means 176. Subsequently, the turbine package thus formed with the help of the clamping nut 66 axially braced with each other and with the spindle 42, so that the entire turbine package behaves ultimately in view of its noise and wear behavior as a compact single turbine. The clamping nut represents insofar as an embodiment of a second coupling means.

The flow channels are then flowed radially through the openings in the spindle 42, wherein the flow in the preferred, a speed-regulating and / or limiting function having configuration by the at least one elastic ring 168, 170 element is limited.

In operation, the turbine speeds can reach min ^-1 in an order of 100 000th When switching off the compressed air supply, it then continues to run for, for example, about 30 seconds. This results in a safety and injury risk during handling. In order to reduce these risks, the hand tool 10 has a brake which is partially visible in FIG. 3 as a pairing of a friction plate 68 and a pressure plate 70 and which will be explained in more detail below.

First, reference is again made to FIG. The compressed air valve 45 in the illustrated embodiment is a ball valve having a ball 72 which is urged by a resilient member 74, for example a spring, onto a circular supply port of a compressed air channel 76 to close that opening. The compressed air channel 76 is preferably a central channel in a valve body 77. To open the valve 45, a valve pin 78 is provided. The valve pin 78 has a first end 80 facing the ball 72 and a second end 82 which is guided in a recess in the inner surface of the control sleeve 18 that is shaped as a valve guide track 84.

The valve pin 78 itself is guided substantially radially in a guide within the valve body 77. With respect to a longitudinal axis 86 of the hand tool 10, the distance of that control surface of the valve guide track 84, which faces the second end 82 of the valve pin 78, of the longitudinal axis 86 of the hand tool from the rotation angle of the control sleeve 18 is dependent. This means that the inward and outward movement of the valve pin 78 is controllable by a rotation of the control sleeve 18.

Figure 3 shows a closed position of the valve 45. To open the valve 45, the control sleeve 18 is rotated about the axis 86 around. Due to the design of the guide track 84, the valve pin 78 is initially pressed radially inwardly against the ball 72. Upon further rotation of the control sleeve 18 of the valve pin 78 then pushes the ball 72 laterally (ie in the figure 3 upward) out of the closed position, so that compressed air can flow over the central air inlet opening 26 on the ball 72 in the compressed air passage 78.

Figure 7 shows a perspective view of a control sleeve 18. The control sleeve 18 has distributed over its outer circumference recesses 88, which facilitate the adhesion in a manual operation and thus also contribute to improved handling.

The axially extending recess 90 opens the valve guide track 84 to the front end 22 of the control sleeve 18 and thus allows an axial relative movement between the valve pin 78 and the control sleeve eighteenth., In the control sleeve 18, the above-mentioned, realized as a recess valve guide track 84 for the valve pin 78th During assembly and / or disassembly of the hand tool 10. In addition, the control sleeve 18 has two open towards its front end 22 brake pin guide tracks 92, 94, which are also realized as depressions in the inner surface of the control sleeve 18.

Figure 8 shows a plan view of the front end 22 of the control sleeve 18 and serves primarily to illustrate the position of the longitudinal section, which is shown in the figure 9. FIG. 9 illustrates, in particular, the position of the cross section, which is shown in FIG. Figures 8 and 10 are mirror images of each other. In the drawing plane of FIG. 10, the valve guide track 84 lies in particular. A comparison of these FIGS. 8 and 10 shows, in particular, that the actuation of the brake and the actuation of the compressed-air valve 45 take place in parallel, wherein the control and Absteuerung the compressed air supply over a further rotation angle range away takes place as a releasing and / or braking operation of the brake.

FIG. 11 shows, in a schematic form, an embodiment of a brake, as it is actuated by the control sleeve 18 in connection with the hand tool 10 according to the invention. The brake has for each brake pin guide track 92, 94 of the control sleeve 18 on a brake pin 96 which is guided in the valve body 77 substantially perpendicular to the longitudinal axis 86 of the hand tool 10 movable. For this purpose, the valve body 77 guides 98, in which the brake pins are guided translationally displaceable.

The brake pin 96 has an end facing the control sleeve 18 and a control sleeve 18 facing away from the end 102. At this end 102, the brake pin 96 has an inclined plane 104. A brake axle 105 lying substantially coaxially to the longitudinal axis 86 of the hand tool 10 has a recess with an inclined plane 106. The inclined planes 104 of the brake pin 96 and the brake axle 105 have the same inclination and are arranged and arranged to slide on each other. During the opening rotation of the control sleeve 18, the brake pin 96 is pressed down in FIG. 11 and thereby presses the brake axis 105 to the right via the inclined planes 104 and 106. As a result, a pressure plate 108 is lifted by the action of brake springs 110 from a friction plate 112, which is rotatably coupled to the rotor 32. This releases the brake.

Conversely, the brake is activated when the control sleeve 18 is rotated in a direction abscursing the compressed air supply and thus closing direction. In this case, the brake pin 96 slides upward in FIG. 11 and allows the brake springs 110 to press the pressure plate 108 against the friction lining 112. The brake is thus realized as a spring brake in which the braking force is applied by springs and is released against the force of the springs. This has the advantage that the closing rotation of the control sleeve 18 is automatically braked, even if no manual force is applied when the control sleeve 18 is closed.

A manual hold the brake is therefore not required. This also improves the handling and the reliability. On the other hand, the brake springs but also do not cause automatic adjustment of the control sleeve 18, since the reaction forces of the springs 110 are not sufficient to overcome the self-locking frictional forces in the operation of the control sleeve 18.

FIG. 12 shows the object of FIG. 11 in a representation rotated through 90 ° about the longitudinal axis 86.

Due to the two offset by 180 ° brake axes tilting when operating the brake is effectively prevented. In addition, the offset of the brake axes by 180 ° has the advantage that the brake axes can be distributed around the circumference, so that the central compressed air supply to the rotor can be maintained. The bolts 92 and 94 are preferably mounted so that they move against each other in an anti-parallel operation: The bolt 96 is perpendicular to the plane of the drawing, while the bolt 100 is suspended vertically below the plane of the drawing.

FIG. 13 shows, for a preferred embodiment of a control sleeve 18, the path 114 of a brake axle 105 in millimeters, plotted against the angle of rotation of the control sleeve 18 in degrees. The curve 116 shows the path of the valve pin 78 of the compressed air valve 45 also in dependence on the angle of rotation of the control sleeve 18 in degrees. FIG. 10 thus shows, in particular, that the rotatable control sleeve 18 is configured to control the brake and the pressurized fluid supply in such a way that the compressed-air valve 45 is opened in parallel to release of the brake, and wherein a brake displacement-rotational angle characteristic 114 the control sleeve 18 in a first rotation angle range, which extends in the figure 10 approximately to the angle 32 °, is steeper than in a second, further away from the closed position rotation angle range.

The closed position corresponds to the object of the figure 13, the rotation angle 0 of the control sleeve 18. The second rotation angle range is the range between about 32 and about 110 °, in which the characteristic 114 is not only less steep, but in the illustrated case even without inclination. The course of the characteristic curve 116 shows how the entire angle of rotation range of 0 ° to 110 ° of the control sleeve 18 is used to regulate the supply of compressed air. This results in the already mentioned improved meterability.

The realization of the actuating element as a rotary sleeve has the advantage that a rotational movement for the adjustment of the hand tool mentioned above is subjectively perceived as ergonomic. The interaction of adjusting torque and the torque of the hand tool causes in the rotatable control sleeve with respect to the sliding sleeve better and more sensitive haptic feedback, as superimposed on the manually applied adjusting torque with a resulting torque change of the hand tool. The better haptic feedback in particular improves the controllability of small changes in the drive power, which improves handling by improving the metering.

The control of the compressed air supply, which takes place in parallel with releasing the brake, permits an expansion of the adjustment path of the actuating element during the metering of the compressed air supply, which likewise leads to an improvement in the meterability and thus also in the handling.

Characterized in that a brake-displacement-rotational angle characteristic of the control sleeve in a first rotation angle range in the vicinity of the closed position of the control sleeve is steeper than in a second, further away from the closed position rotation angle range, is a fast separation of the brake when opening and a late Successful closing the brake when Absteuern the compressed air supply ensured. Due to the steeper course, the opening of the brake when opening the compressed air supply takes place early and quickly, that is, over only a small rotational angle range of the sleeve. Similarly, the closing of the brake is late and fast. Overall, despite the parallel operation of the valve and the brake taking place under the influence of a compressed air drive rubbing the friction surfaces of the brake largely avoided, so that improved metering of compressed air supply is not at the expense of the life of the brake.

A preferred embodiment is characterized in that the control sleeve is adapted to allow a control and Absteuerung the compressed air supply over a larger rotation angle range done as a release and actuation of the brake. The Aufsteuerung takes place in particular via a further take place rotation of the control sleeve beyond a rotation angle at which the brake is already completely dissolved. This avoids, on the one hand, that large torques become effective when the brake is not yet fully released, which could lead to premature wear of the brake. On the other hand, there is the advantage that a large angle of rotation for an up and down control of the compressed air supply is available, which improves the one aspect of the handling formability dosing.

Both

characteristic curves

114, 116 have different angular ranges for the angle of rotation of the control sleeve, in which the respective characteristic has a non-zero slope. Each of the two angular ranges can be mentally divided into a first half and a second half, wherein the first half contains the closed position and the second half of the open position of the air valve, or the brake.

The characteristic curve 114 is preferably distinguished by the fact that in the first half or at least in a partial area of its first half it becomes progressively steeper, preferably a continuously steeper course and overall monotonically increasing course. In addition, the characteristic 114 is characterized in that it has a course with decreasing slope, preferably with continuously decreasing slope, at least in a partial area of its second half. The characteristic curve 114 is therefore distinguished in a preferred embodiment by a continuously increasing profile with a change of curvature. The characteristic curve 116 is preferably characterized in that in its first half or at least in a partial area of its first half it has a steeper course, preferably a continuously steeper course and an overall monotonically increasing course. The slope of the characteristic 116 is on average between its closed position and its open position smaller than the slope of the characteristic 114 between the closed position and the open position.

Claims

Hand tool (10) having a housing (12) and a tool holder (14) rotatably connected to a rotatably mounted in the housing (12) rotor (32) which at least two successively on the rotor (32) arranged and rotatably with the rotor (32) coupled separate single turbines (46, 48, 50, 52) which are adapted to be pneumatically driven, characterized in that the at least two individual turbines (46, 48, 50, 52) by first coupling means ( 176) rotatably connected to each other in a predetermined rotational angular position and elastically clamped in the direction of its axis of rotation against each other to form a compact turbine package.
Hand tool (10) according to Claim 1, characterized in that each individual turbine (46, 48, 50, 52) has a first wheel half (120) and a second wheel half (122), each wheel half having a disc-shaped base body (124) and out of Disc-shaped base body (124) protruding and mutually identical guide structures (126, 128, 130, 132, 134, 136), which are separated by mutually equal gaps (138, 140, 142, 144, 146, 148) and in a the number of conductive patterns (126, 128, 130, 132, 134, 136) are distributed over each wheel half (120, 124) according to countless rotational symmetry, the conductive patterns (126, 128, 130, 132, 134, 136) and Interspaces (138, 140, 142, 144, 146, 148) complementary to each other are configured so that the lead structures of the first half wheel (120) when joining the two wheel halves so in the interstices of the second wheel half (122) and the guide structures of the second Wheel half (122) fit into the intermediate spaces of the first wheel half (120) when joining the two wheel halves so that flow channels form between walls of adjacent guide structures of the first wheel half (120) and the second wheel half (122).
Hand tool (10) according to claim 2, characterized in that the wheel halves (120, 122) arranged coaxially to its axis of rotation and in one of the number of holes correspondingly countless rotational symmetry distributed over the wheel half holes (150, 152, 154), in addition are adapted to receive a rod which is configured as a first coupling means (176) to penetrate aligned bores of the wheel halves of all turbines of the turbine pack and the individual turbines of the turbine stack so rotatably coupled to each other.
Hand tool (10) according to one of the preceding claims, characterized in that the individual turbines of a turbine package on a spindle (42) of the rotor (32) by a clamping nut (66) elastically to each other and the spindle (42) are clamped.
Hand tool (10) according to one of the preceding claims, characterized in that the individual turbines have at least one elastic ring (168, 170) which is adapted and arranged to reduce an influx of compressed air to flow channels of the individual turbines with increasing speed increasingly.
Hand tool (10) according to one of the preceding claims, characterized in that the housing (12) has an inner sleeve (28) which consists of metal.
Hand tool (10) according to claim 6, characterized in that the housing (12) has an outer sleeve (30) which consists of a compared to the metal of the inner sleeve (28) poor heat conductive plastic.
Hand tool (10) according to any one of the preceding claims, characterized in that the hand tool (10) n successively arranged radial turbines (46, 48, 50, 52), wherein n is a number greater than or equal to two and less than or equal to eight, in particular equal four is.
Hand tool (10) according to one of the preceding claims, characterized by a control sleeve (18) arranged for controlling the supply of compressed air and a brake and rotatable about a longitudinal axis (86) of the hand tool (10).
Hand tool (10) according to one of the preceding claims, characterized in that the hand tool has a spring-loaded brake.