• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A pneumatic tool having an electromagnetically actuated control member (27) for controlling a pneumatic control circuit to maintain a load independent torque at a constant speed. The tool comprises a main valve (5) which is displaceably arranged in a drive housing (1) by the supplied compressed air against the force of a helical spring (13) and a generator (43) mounted on the shaft (49) of a turbine wheel (51). sitting. With a speed sensor (75), the speed of the shaft (49) is measured and at speed drop due to a load, the inflow of compressed air to the main valve (5) is controlled.
    公开号:CH713925A2
    申请号:CH00758/18
    申请日:2018-06-14
    公开日:2018-12-28
    发明作者:Wiedemeier Stefan；Ineichen Stefan
    申请人:Suhner Otto Ag；
    IPC主号:
    专利说明:

    Description: [0001] The subject matter of the invention is a pneumatic tool according to the preamble of patent claim 1.
    Pneumatically driven tools are mainly used in the metalworking industry and are characterized by a relatively low weight in terms of performance, since no drive motor, such as an electric motor, is disposed within the tool and especially in hand-operated tools for rapid fatigue of the actuator - or the operator leads.
    The speed control in such tools is expensive and has been made by centrifugal governors that throttle the air supply at idle and release again when loaded. The reliability demanded today and the constant speed maintenance with changing work processes and conditions can not be achieved.
    From US 6,908,277 a speed controller for a rotating air motor is further described. In this speed controller, a generator is arranged on the shaft of the tool, which generates a correspondingly variable output voltage as a function of the speed of the shaft. With the respective output voltage, an electromagnetic actuator is supplied to control the intake valve for compressed air on the tool in direct dependence on the output voltage. In this known embodiment, the centrifugal element is replaced by an electromagnetic driven actuator. This means that a voltage is generated for the actuation of the electromagnetic actuator within the tool, so that it can do without an external power source.
    A disadvantage of this speed control is the fact that the regulation of the working speed depends on the variable voltage generated by the motor shaft. This means that the maintenance of the speed of the tool, especially with variable load, is not or only insufficiently possible.
    From EP 2 449 999 a fluid-operated medical, in particular dental, handle is known. The determination of the actual value of the speed takes place via the amplitude of the rectified generator voltage (analog) and the actuator is designed as a proportional valve or as a throttle. For fluid drives in the medical field, where very low torques must be generated, this procedure is sufficient, but not for tools of the metalworking industry.
    From US 2001/0 088 921 a pneumatically operated hand tool is further known in which via an internal battery and a microcomputer, an electromagnetic valve is directly controllable in the supply air duct. The battery is powered by a generator in the exhaust air flow, the generated energy is not sufficient for the operation of an electromagnetic valve. From EP 2 727 552 a further medical handpiece is known in which an electrical energy source such as a constant current source and / or a constant voltage source, i. an external power source is used. A power connection, which should be avoided by the application according to the tool, is essential here.
    An object of the present invention is to provide a compressed air tool in which the set speed is precisely adjustable even under the influence of disturbances such as the load to an adjustable value. Another object of the invention is that in case of power failure due to failure of the internal generator, the speed drops immediately to a harmless value for the tool and the workpiece minimum.
    This object is achieved by a pneumatic tool according to the features of claim 1. Advantageous embodiments of the tool are described in the dependent claims.
    By a voltage regulator, a constant output voltage for feeding a microcontroller can be generated independently of the current and at the same time adapted to the work to be performed variable speed of the shaft. As a result, depending on the measured speed of the engine regardless of the load on the tool, the electromagnetic control member for controlling the air passage at the intake valve and thereby the selected speed can be maintained at a variable load. The internally generated voltage is only used to power the microcontroller and the inlet valve.
    Based on two illustrated embodiments, the invention will be described in more detail. It shows:
    1a is a functional diagram of the operated with compressed air tool,
    1b is a schematic representation of a pneumatic tool, in the example an angle grinder,
    2a shows a vertical section through a first embodiment of the tool immediately after the application of compressed air,
    2b shows the tool according to FIG. 2a during the start-up phase, FIG.
    2c the tool during operation at the highest speed or maximum torque,
    2d an alternative embodiment of the speed detection with unchanged air supply in the tool according to Fig. 2a,
    3a shows a vertical section through a second embodiment of the tool immediately after the application of compressed air,
    3b shows the tool according to FIG. 3a during the start-up phase, FIG.
    3c the tool during operation at the highest speed or maximum torque,
    FIG. 3d an alternative embodiment of the speed detection with unchanged air supply in the tool according to FIG. 3a, FIG.
    4 is a graphical representation of the speed curve on the shaft with and without speed control during startup,
    5 is a graphical representation of the voltage on the generator along the time axis during the starting process,
    6 is a graph showing the on-state of the solenoid with respect to the time axis during start-up;
    7 is a graphical representation of the opening cross-section of the main valve during startup,
    8 is a graphical representation of the torque curve during the starting process,
    9 is a graphical representation of the speed curve on the shaft with and without speed control in the load case,
    10 is a graphical representation of the voltage across the generator along the time axis in the load case,
    11 is a graphical representation of the on state of the electromagnet with respect to the time axis in the load case,
    12 is a graphical representation of the opening cross section of the main valve in the load case,
    Fig. 13 is a graphical representation of the torque curve in the load case.
    FIG. 1 a represents a functional diagram of a pneumatic tool according to the invention, as shown for example in FIGS. 1 b and 1 c. Fig. 1b shows an angle grinder as a pneumatic tool. The angle grinder is in Fig. 1c explosively divided into its elements, namely in the first housing part 100 with the air inlet and the actuating lever, the second housing part 101 with the electronics and the tool head 102, to which a grinding wheel (not shown) can be fastened. Of course, an output spindle in a straight version can also be installed instead of the angle grinding head. To illustrate the functional diagram, two exemplary embodiments are described in more detail in FIGS. 2a to 2c and 3a to 3c.
    Reference numeral 1 schematically shows the drive housing with the drive elements of the compressed air driven tool.
    A possible construction of the tool is shown in Fig. 1b. Different types of tools may be associated with such drive elements. The first housing part 101 comprises an air inlet channel 3, is supplied through the air from a compressed air source, not shown, leading to a main valve 5. This is axially guided in a bore 7, which forms a displacement. The main valve 5 comprises an annular first sealing region 9 and, axially spaced therefrom, a second piston-like sealing region 11, wherein both sealing regions 9 and 11 are sealingly guided on the wall of the bore 7. The sealing elements on the sealing regions 9, 11 are not shown for the sake of clarity and also known from the prior art of pneumatic valves. The air inlet channel 3 opens into the bore 7 between the two opposing shoulders 9 'and 11' of the two sealing regions 9, 11. Preferably, the bore 7 in the region of the mouth of the air inlet duct 3 as circumferential annular groove 65 radially expanded to the incoming air flow over to distribute the entire circumference of the bore 7. At the second sealing portion 11 is axially acting a coil spring 13 with its first end. The second end is supported at the right end of the bore 7 in the footwell 14.
    By the coil spring 13, the main valve 5 is pressed against the first end of the head space 17 of the bore (left in the figures), as long as through the air inlet 3 no or only a very small inflow of compressed air. The lying on the left side in the figures sealing region 9, spaced by a disc-shaped end portion 15, held to the rear end of the head space 17 of the bore 7. From the spaced area, that is to say the annular head space 17, a first venting channel 19 leads to a valve space 21. A second venting channel 23 leads from the valve space 21 into the open, that is to say out of the housing 1.
    The bore 7 for the main valve 5 is also connected via a pressure channel 25 also connected to the valve chamber 21. The pressure channel 25 opens into the annular groove 65th
    In the valve chamber 21 is a control valve 27 as a control member, for example, a pivotable about an axis 29 lever-like valve body with two to the ends of the pressure channels 23,25 alternately applied to certain sealing elements 28, 30 are arranged. The control valve 27 comprises a first end 27 'with the sealing element 28 and a second end 27 "with the sealing element 30. Depending on the pivotal position of the control valve 27, the first vent 27 can be closed with the first end 27' or with the second end 27" Pressure channel 25. A spring element 31, which may be formed by a helical spring acting on the first end 27 'or a plate spring package, pushes the second end 27 "upwards and closes off the pressure channel 25 from the valve space 21. The control valve 27 can be actuated by an electromagnet 33 are pivoted about an axis 29 against the force of the spring element 31 so that the pressure channel 25 is exposed and the second venting channel 23 is closed The winding 35 of the electromagnet 33 is fed by a current source via a microcontroller 37. For example, a potentiometer is connected to the microcontroller 37 39 connected, with which the voltage across the winding 35 via the lines 41 of the Magnet 33 is activated. When de-energized magnet 33, the pressure channel 25 is kept closed to the valve chamber 21, so that no pressure build-up in the head space 17 and consequently the main valve 5 prevents the necessary for the drive supply of air to a turbine wheel 51.
    The construction of an operating voltage for the microcontroller 37 is carried out in the supply air flow via a generator 43, the windings 45 may be fixed, for example, on the housing 1 and with a rotor 47 interaction. The rotor 47 is arranged on the shaft 49 of the turbine wheel 51. The turbine wheel 51 is supported by at least one bearing 53 on the housing 1. From the generator 43, the AC voltage generated there is fed to a rectifier 55. The rectifier 55 is further connected to a voltage regulator 57, which feeds the microcontroller 37 with a constant DC voltage, which is independent of the instantaneous speed of the shaft 49 of the turbine wheel 51. The turbine wheel 51, as shown in the figures, directly on the output shaft 49 of the tool or in a bypass on the supply channel 61 for compressed air to the turbine wheel 51 (not shown).
    The turbine wheel 51 with its not shown in detail, but purely schematically shown blades 59 is driven by the supply air flow, which is guided by the feed channel 61. The feed channel 61 is connected to the bore 7 in the housing 1. The mouth of the feed channel 61 in the bore 7 is located in a first annular recess 67 in the bore 7. In addition to the opening in the figures from below into the bore 7 feed channel 61, a further feed channel 61 'in the blade chamber 63, in which the blades 59 circulate, be guided. The second feed channel 61 'opens axially offset into the second annular recess 69 in the bore 7. The two annular recesses 67 and 69 are in the non-pressurized area, that is without compressed air supply or compressed air supply having a piston-shaped shape, covered.
    In the first exemplary embodiment according to FIGS. 2 a to 2 d, a chamfering or a conical section 71 is formed on the end face of the cylindrical jacket of the second sealing region 11. At this point, a narrow annular passage for the supplied through the air inlet passage 3 of the bore 7 compressed air is thereby created. This incoming air passes via the first feed channel 61 to the blades 59 in the blade chamber 63 and from there, after passing through the blades 59, through an exhaust air channel 73 into the atmosphere. The air flow supplied to the turbine wheel 51 through the first supply passage 61 causes the turbine wheel 51 to rotate, thereby generating the generator 43 in response to the rotational speed of the turbine wheel 51, rectified in the rectifier 55 and independent of the voltage regulator 57 Speed of the turbine wheel 51 is kept constant. With this voltage held constant, the microcontroller 37 is powered. With its output voltage can be controlled with the potentiometer 39 or other corresponding electronic element, the solenoid 33 to control the supply air to the main valve 5.
    The operation of the electronic control of the pneumatic tool according to the first embodiment will be described below.
    Before the start of work with the tool, that is, before the turbine wheel 51 compressed air is supplied through the inlet channel 3, for example, from the service network, the main valve 5 is in the position shown in Figs. 2a and 2d, namely acted upon by the spring 13 in abutment with the left end in the bore 7. Once compressed air is introduced through the air inlet 3, a minimal amount can flow through the annular gap formed by the conical portion 71 to the first feed channel 61 and the turbine wheel 51 in rotation (start phase. 4-8). This rotational movement of the turbine wheel 51 is sufficient to apply the necessary minimum voltage to the microcontroller 37. In this case, the main valve 5 remains in the starting position according to FIGS. 2a and 2d, even when the pressure between the first and the second sealing region 9,11 has reached the network pressure. The position of the main valve 5 thus remains independent of the pressure in the annular space 65, since the projected cross-sectional areas 9 ', 11' of the two sealing regions 9, 11 are the same size and the head space 17 is connected to the atmosphere.
    The space 14 in the bore 7, in which the coil spring 13 is arranged, is held by a vent opening 77 connected to the atmosphere without pressure or at atmospheric pressure. The annular head space 17 behind the first sealing region 9 is also connected to the atmosphere at this time via the first venting channel 19, the valve chamber 21 and the second venting channel 23, and is depressurized. The pressure channel 25, which leads from the bore 7 into the valve chamber 21, is closed by the control valve 27 or its sealing element 30 at the second end 27 "Once the operating voltage V-ι necessary for the operation of the microcontroller 37 is reached, it can Turning on and off of the electromagnet 33, the rotational speed preset by the potentiometer 39. The rotational speed is measured by a suitable rotational speed sensor 75 on the shaft 49. The switching on and off of the electromagnet 33 alternately causes the opening and closing of the pressure channel 25 and The resulting pressurization of the main valve 5 with compressed air is described below: When a load is now applied to the shaft 49, the speed initially falls, in order to be able to compensate for this, that is, the torque is increased increase to maintain the desired speed, with the Mikrocon Troller 37 by appropriate activation of the electromagnet 33, the control valve 27 is pivoted clockwise, whereby compressed air from the air inlet 3 via the annular groove 65 through the pressure channel 25 into the valve chamber 21 and further from there through the first vent passage 19 in the annular space 17 behind the first sealing region 9 can flow (Fig. 2a). As a result, the main valve 5 acted upon with compressed air at the front side shifts against the force of the helical spring 13 to the right. Now, the compressed air from the bore 7 can not only pass through the first supply channel 61 to the turbine wheel 51, but according to Fig. 2c and the second annular channel 69 is pressurized with compressed air, through which the compressed air flows into the second supply channel 61 '. The turbine wheel 51 is now acted upon by a larger amount of compressed air, which increases the torque on the shaft 49. In practice, this is achieved in that the control valve 27 performs a torsional vibration and thereby equalizes the compressed air supplied to the rear end of the first sealing region 9 to the required torque. This can be the case several times per second (see Fig. 6).
    The second embodiment of the pressure-driven tool according to FIGS. 3a-3d differs from the first embodiment in that the annular head space 17 is connected at the rear end of the first sealing region 9 with the interposition of a throttle 79 with the atmosphere. The control valve 27 is consequently effective only on one side and can open or close the pressure channel 25 to the valve chamber 21 in this embodiment. When opening the pressure channel 25 flows from the bore 7 compressed air in the valve chamber 21 and from there through the first vent passage 19 in the annular headspace 17. Part of the guided into the annulus 17 compressed air can escape throttled, so that the force acting on the main valve 5 smaller than in the first embodiment.
    In practice, it makes sense to use a larger control valve for the second embodiment variant in order to be able to compensate for the constant exhaust air flow caused by the throttle.
    In the graphs in Fig. 4 are shown in broken lines, the speed curve without electronic control, that is, during the startup and even in case of failure of the generator 43, and the course of the speed on the time axis shown in solid line. It can clearly be seen that in the starting phase, the speed during the build-up of the network pressure, the pressure in the bore 7 between the two sealing regions 9 and 11 is increasing and then, for example. after 1.5 seconds, when the voltage of the generator 43 has reached, for example, 5 volts, the speed increases steeper upward, because the control valve 27 is pivoted by the solenoid 33 in a clockwise direction and thereby built up in the bore 7 pressure (network pressure) the valve chamber 21 into the first vent passage 19 and from there into the annular headspace 17 can pass. The pressure increase in the head space 17 causes a shift of the main valve 5 to the right against the force of the spring 13. By the displacement of the main valve 5 passes from the bore 7 compressed air first through the first feed channel 61 to the turbine wheel 51 and-if this additional air supply to the turbine wheel 51st for reaching the set speed is not enough - continue through the second feed channel 61 'to the turbine 51. As soon as the set speed, in the example 5000 revolutions per minute is reached, the control valve 27 is closed via the microcontroller 37, so that on the back of the Main valve 5, that is, on the left side in the head space 17 in Figs. 2 and 3, the pressure drops and so the main valve 5 is moved by the force of the spring 13 back to the left, so far so that the set speed maintained becomes, thus on a horizontal line runs. The set speed is between the minimum speed (lower dotted line, for example at 30,000 revolutions per minute and the upper dotted line, for example at 75,000 revolutions per minute), which must not be exceeded.
    In the illustration according to FIG. 5, which shows the dimension of the opening cross-section at the main valve 5 over the time s, it can be seen that, regardless of the action on the bore 7 with compressed air, there is always a small air flow from the bore 7 to the first recess 67 and from there through the first feed channel 61 to the turbine wheel 51 and can set this in rotation and consequently the generator 43 generates a voltage which is kept constant by the voltage regulator 57. By opening the control valve 27 more compressed air can flow through the pressure channel 25 in the first vent passage 19 and causes a pressure build-up in the annular headspace 17. Thereby, the main valve 5 is pressed quickly to the right against the force of the spring 13, resulting in an increase of Opening cross-section, that is an enlarged passage from the bore 7 at least into the first recess 67 and from there to the turbine wheel 51 causes. The opening cross section is then immediately reduced again by the microcontroller 37, which controls the control valve 27 on the basis of the speed measured at the shaft 49, by reducing the supply of compressed air in the annular head space 17. Until the opening cross-section has reached a level at which the rotational speed of the shaft is at the set value, e.g. 50 000 revolutions per minute.
    FIG. 5 shows the curve of the voltage on the generator 43. The solid line shows that at the beginning after switching on the compressed air, the voltage gradually increases and, for example, after about 1.5 seconds on reaching the set voltage regulator 57 of 5 volts constant. If the voltage was not kept constant by the speed regulator 57 by means of a higher rotational speed on the shaft 49, the voltage at the rotational speed would increase, for example, to approximately 25 volts, thereby damaging the microcontroller 37 or at least putting it out of operation.
    In Fig. 6, the switching state of the control valve 27 is shown graphically. At the beginning in the starting phase, when the control valve 21 keeps the supply of compressed air to the main valve 5 closed, because the electromagnet 33 from the generator 43 is still de-energized, this remains in the starting position. Once, as shown in Fig. 5, the voltage at the generator 43 has reached, for example 5 volts, the control valve 27 switches to the open position, because it is pivoted by the solenoid 33 in a clockwise direction. If the control valve 27 were kept permanently in the open position, then, as shown in FIG. 1, the rotational speed would increase beyond the desired or set rotational speed and possibly above the maximum rotational speed. By oscillating behavior of the control valve 27 as shown in FIG. 6, the set speed can be maintained.
    9 to 13 show the course of the rotational speed of the shaft 49, the DC voltage according to the voltage regulator 57 and the switching state of the electromagnet 33, where in Fig. 11 can be clearly seen that when the speed decreases at the shaft 49, For example, by a corresponding attacking load, through the control valve 27, the compressed air supply in the headspace 17 of the main valve 5 is opened longer than at the same speed to compensate for the speed drop and then the opening and closing of the pressure supply takes place in a modified rhythm.
    In Fig. 12 is shown at the point of loading of the shaft 49, as the opening cross-section to at least one of the feed channels 61, 61 'enlarged short-term and then held for a certain time, as long as a higher torque is required on this increased Ouerschnitt, until the load is eliminated and the speed or the torque can be lowered. In FIG. 13, the torque curve can be seen accordingly.
    The detection of the speed is carried out according to FIGS. 2a, 2b and 3a, 3b by the sensor 75, which is designed as a separately arranged part as a Hall sensor. In the embodiment according to FIGS. 2d and 3d, the speed measurement takes place on the basis of the alternating current signal of the generator 43, in that the ascending edges of the alternating current signal are detected and the speed is calculated from the time difference.
    Legend of the Reference Numerals I Drive housing 3 Air inlet duct 5 Main valve 7 Bore 9 First sealing area 9 'Shoulder II Second sealing area 11' Shoulder 13 Coil spring 14 Pressure-free foot space 15 Disc-shaped end area 17 Head space 19 First venting channel 21 Valve space 23 Second venting channel 25 Pressure channel 27 Control valve 27 'first end 27' second end 28 sealing element 29 axis 30 sealing element 31 spring element 33 electromagnet 35 winding 37 microcontroller 39 potentiometer 41 line 43 generator 45 winding 47 rotor 49 shaft 51 turbine wheel 53 bearings 55 rectifier 57 voltage regulator 59 blades 61 first supply channel 6Γ second supply channel 63 Bucket chamber 65 Ring groove 67 first recess 69 second recess 71 Conical section 73 Exhaust air channel 75 Sensor 77 Air vent 78 Second annular channel 79 Throttle 90 Signal conditioning 91 Analog / digital converter 92 SuitS '/ decay time accelerator 100 Housing part 101 Housing part 102 Tool head
    权利要求:
    Claims (14)
    [1]
    1. A method for controlling the rotational speed of the output shaft (49) on a tool driven by compressed air, wherein a driven by the compressed air generator (43) in the tool an alternating voltage is generated with an electromagnetic control element (27) is activated, with which the amount of air for the drive of a turbine wheel (51) on the output shaft (49) is controllable, characterized in that the AC voltage in a rectifier (55) is converted into a DC voltage that the DC voltage by a voltage regulator ( 57) is held constant regardless of the rotational speed of the output shaft (49), that with the constant DC voltage, a microcontroller (37) is fed, that with a speed sensor (75) the instantaneous speed of the output shaft (49) is detected and that the Microcontroller (37) with the electromagnetically driven control valve (27) controls the amount of air supplied to the turbine wheel (51) and the set predetermined Dr Number of shaft (49) holds constant.
    [2]
    2. The method according to claim 1, characterized in that with the regulated by the control valve (27) amount of air, a main valve (5) which is slidably inserted in a bore (7) in the housing (1) of the tool, the air flow to the turbine wheel (51 ) is regulated by one or more feed channels (61,61 ') are completely or partially exposed to the compressed air during the displacement of the main valve (5), whereby the amount of air at the turbine wheel (51) with an increase of the load on the drive shaft (49) is increased and the predetermined speed is maintained.
    [3]
    3. A pneumatic tool with a drive housing (1), comprising a turbine wheel (51) for driving the output shaft (49), an air inlet duct (3) for compressed air and an exhaust duct (73), a generator used in the supply air for the compressed air (43 ) for generating an alternating electrical voltage and a rectifier (55) for the operation of a microcontroller (37), characterized by a voltage regulator for generating a constant output voltage independent of the rotational speed of the shaft (49) for the operation of the microcontroller (37) for the control of an actuator (27) for the actuation of a main valve (5) on the basis of the measured data of a speed sensor (75) on the shaft (49).
    [4]
    4. A pneumatic tool according to claim 3, characterized in that the generator (43) on the output shaft (49) or on one of the shaft (49) independent second shaft is arranged in a bypass.
    [5]
    5. A pneumatic tool according to claim 4, characterized in that in the drive housing (1) a main valve (5) receiving bore (7) is formed, that the bore (7) by an air inlet (3) is connectable to a compressed air source, and that with a pressure channel (25) and with a first vent channel (19), the bore (7) is connected to a valve chamber (21) that in the valve chamber (21) an electromagnetically controllable control valve (27) for opening and closing the pressure channel (25) or for closing a second venting channel (23) is inserted, wherein the control valve (27) in dependence of the rotational speed of the shaft (49), measured with the speed sensor (75), is controllable.
    [6]
    6. A pneumatic tool according to claim 5, characterized in that the main valve (5) between a head space (17) and a pressure-free space (14) in the bore (7) is displaceably guided.
    [7]
    7. A pneumatic tool according to claims 5 or 6, characterized in that the valve chamber (21) through the first vent passage (19) with the bottom-side head space (17) is connected to the bottom of the main valve (5).
    [8]
    8. A pneumatic tool according to one of claims 5 to 7, characterized in that the valve chamber (21) through the second vent passage (23) is connected to the environment.
    [9]
    9. Pneumatically driven tool according to one of claims 6 to 8, characterized in that the main valve (5) comprises a first (9) and spaced therefrom a second flange-shaped sealing region (11) whose outer surfaces sealingly slidably on the wall of the bore (7) abutment and that in a pressure-free space (14) in the bore (7), a coil spring (13) between the main valve (5) and a bore (7) frontally bounding wall is inserted.
    [10]
    10. A pneumatic tool according to claim 8 or 9, characterized in that the first sealing region (9), the main valve (5) on the head side to the bore (7) sealingly, that the second sealing region (11) is arranged such that the first junction in the hole (7) of a first feed channel (61) partially and the mouth of a second feed channel (61 ') completely closes when the main valve (5) head side and pressure chamber side is depressurized.
    [11]
    11. A pneumatic tool according to claim 10, characterized in that the air inlet channel (3) and / or the first (61) and / or the second feed channel (61 ') each in an annular groove (65) and a first recess (67) or open a second recess (69) on the main valve (5).
    [12]
    12. A pneumatic tool according to one of claims 10 or 11, characterized in that the feed channels (61,61 ') in a blade chamber (63) of a turbine wheel (51) open.
    [13]
    13. A pneumatic tool according to one of claims 3 to 11, characterized in that the control valve (27) in the valve chamber (21) is pivotally mounted such that either the pressure channel (25) or the second ventilation channel (23) by one with an electromagnet (33) operated on the control valve (27) mounted sealing elements (28, 30) are closable.
    [14]
    14. A pneumatic tool according to one of claims 3 to 13, characterized in that the speed measurement is calculated by the AC signal by the time difference of the rising edges is detected.
    类似技术:
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    同族专利:
    公开号 | 公开日
    US20200215677A1|2020-07-09|
    EP3642456B1|2021-08-04|
    CH713910A1|2018-12-28|
    EP3642456A1|2020-04-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE1551199A1|1966-04-01|1970-02-26|Ritter Ag|Device for automatic speed stabilization of an air motor|
    US20110088921A1|2008-07-25|2011-04-21|Sylvain Forgues|Pneumatic hand tool rotational speed control method and portable apparatus|
    EP2449999A1|2010-11-05|2012-05-09|W & H Dentalwerk Bürmoos GmbH|Fluid driven medical, in particular dental handgrip|
    EP2727552B1|2012-11-05|2014-10-08|W & H Dentalwerk Bürmoos GmbH|Medical, in particular dental handpiece|
    DE102014117603A1|2014-12-01|2016-06-02|Mega-Line Racing Electronic Gmbh|Hand tools, in particular impact wrenches|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    CH00815/17A|CH713910A1|2017-06-22|2017-06-22|Pneumatically driven tool.|PCT/EP2018/066213| WO2018234289A1|2017-06-22|2018-06-19|Compressed air-driven tool|
    US16/623,120| US20200215677A1|2017-06-22|2018-06-19|Compressed air-driven tool|
    EP18734153.2A| EP3642456B1|2017-06-22|2018-06-19|Compressed air-driven tool|
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