METHOD AND WORK APPARATUS WITH SOUND ADAPTATION

Abstract

The disclosure relates to a method for sound adaptation, via a sound generator, of a handheld work apparatus driven by an electric drive motor and to a handheld work apparatus with a sound generator configured for this purpose. The work apparatus generates during operation an uncorrected operating sound. Via the sound generator, during operation a supplementary sound is generated in addition to the uncorrected operating sound and is overlaid on the operating sound to form an overall sound with an overall sound pressure level (LG.sub.p). In this case, the main component of the supplementary sound lies in an adaptation frequency spectrum (f.sub.A) below 1 kHz.

Claims

1. A method for sound adaptation of a handheld work apparatus via a sound generator, wherein the handheld work apparatus includes an electric motor configured to drive the work apparatus, wherein the work apparatus generates during operation an uncorrected operating sound with an operating sound pressure level, the method comprising: generating a supplementary sound via the sound generator in addition to the uncorrected operating sound during operation; and, overlaying the supplementary sound on the uncorrected operating sound to form an overall sound with an overall sound pressure level, wherein a main component of the supplementary sound lies in an adaptation frequency range below 1 kHz.

2. The method of claim 1, wherein the uncorrected operating sound has an A-weighted cumulative operating sound pressure level; an overall sound resulting from the uncorrected operating sound and the supplementary sound has a further A-weighted cumulative overall sound pressure level; and, the supplementary sound is set at such a level that the further A-weighted cumulative overall sound pressure level is not more than 1.0 dB greater than the A-weighted cumulative operating sound pressure level.

3. The method of claim 1, wherein the supplementary sound has sound energy distributed over a frequency range, at least 70% of the sound energy of the supplementary sound being generated in the adaptation frequency range.

4. The method of claim 1, wherein a speed of a drive shaft is used as a fundamental frequency for establishing the supplementary sound; and, the supplementary sound is set in dependence upon the fundamental frequency.

5. The method of claim 4, wherein the supplementary sound includes in the adaptation frequency range at least one single frequency band; the frequency band includes a reference frequency with a maximum sound pressure level; and, the reference frequency is set in dependence upon the fundamental frequency predetermined by the electric drive motor.

6. The method of claim 5, wherein, in steady-state operation of the work apparatus, the single frequency band of the supplementary sound includes an integral multiple of half the fundamental frequency; and, the reference frequency of the frequency band is an integral multiple of half the fundamental frequency.

7. The method of claim 6, wherein the supplementary sound in the adaptation frequency range includes a plurality of frequency bands including reference frequencies of which the integral multiples (n) are 1 and 2.

8. The method of claim 5, wherein the uncorrected operating sound has a profile of an operating sound pressure level that is distributed over the adaptation frequency range; and, the supplementary sound is adapted to the profile of the operating sound pressure level such that, at the reference frequency of the at least one frequency band, a corresponding overall sound pressure level produced is at least 3 dB higher than the corresponding operating sound pressure level.

9. The method of claim 5, wherein the uncorrected operating sound has a profile of an operating sound pressure level that is distributed over the adaptation frequency range; and, the supplementary sound is adapted to the profile of the operating sound pressure level such that, at the reference frequency of the at least one frequency band, a corresponding overall sound pressure level produced is not more than 40 dB higher than the corresponding operating sound pressure level.

10. The method of claim 5, wherein, in accelerating or decelerating operation of the work apparatus, the frequency band is shifted in a direction of higher or lower frequencies in comparison with steady-state operation.

11. A handheld work apparatus comprising: an electric drive motor; a sound generator; wherein the work apparatus generates, during operation, an uncorrected operating sound with an operating sound pressure level; said sound generator being configured to generate a supplementary sound via said sound generator in addition to the uncorrected operating sound during operation; and, overlay the supplementary sound on the uncorrected operating sound to form an overall sound pressure level, wherein a main component of the supplementary sound lies in an adaptation frequency range below 1 kHz.

12. The handheld work apparatus of claim 11, wherein said sound generator includes a speaker attached to the work apparatus and is configured to makes the supplementary sound perceptible to a user.

13. The handheld work apparatus of claim 12, wherein, in a customary working position of the work apparatus, said speaker is directed at a head of the user.

14. The handheld work apparatus of claim 12, wherein the work apparatus defines an upper side; and, said speaker is arranged on said upper side of the work apparatus.

15. The handheld work apparatus of claim 12, wherein said speaker is integrated in a component of the work apparatus.

16. The handheld work apparatus of claim 11, wherein the work apparatus is a chain saw or a hedge trimmer.

17. An assembly for sound adaptation of a handheld work apparatus driven by an electric drive motor, the assembly comprising: a hand protection of the work apparatus; a sound generator having a speaker; wherein the work apparatus generates, during operation, an uncorrected operating sound with an operating sound pressure level; said sound generator being configured to generate a supplementary sound via said sound generator in addition to the uncorrected operating sound during operation; and, overlay the supplementary sound on the uncorrected operating sound to form an overall sound pressure level, wherein a main component of the supplementary sound lies in an adaptation frequency range below 1 kHz.

18. The assembly of claim 17, wherein said speaker is integrated in said hand protection.

19. The assembly of claim 17, wherein said sound generator has a generator and amplifier unit for activating said speaker; and, said generator and amplifier unit is integrated in said hand protection.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The invention will now be described with reference to the drawings wherein:

[0029] FIG. 1 shows in a perspective view an electric work apparatus configured according to the disclosure in the example of a chain saw with a speaker integrated in the hand protection for generating the supplementary sound according to the disclosure; and,

[0030] FIG. 2 shows in a diagrammatic representation the frequency spectra of the uncorrected operating sound, the supplementary sound and the overall sound thereby achieved.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0031] FIG. 1 shows in a perspective view a handheld work apparatus modified according to the disclosure with an only schematically indicated electric drive motor 2. Chosen here as an example of such a work apparatus is a chain saw 1 with a guide bar 10 and with a saw chain 11 running around the guide bar 10 and driven by the drive motor 2. However, an electric hedge trimmer or the like may also be provided, for which then the following description applies in an analogous way.

[0032] The drive motor 2 has a schematically indicated drive shaft 17, via which it drives the saw chain 11 by way of a sprocket that is not shown. In the present case this is a direct drive, in which the drive shaft 17 is at the same time also the motor shaft of the drive motor 2. In may however also be expedient to make the drive shaft 17 separate from the motor shaft and, for example in connection with a high-speed drive motor 2, to set it in rotation with reduced speed and increased torque by way of an interposed step-down gear mechanism.

[0033] The guide bar 10 extends along a longitudinal axis, which predetermines a longitudinal direction 12 of the chain saw 1. The vertical direction 13 lies in the plane of the guide bar 10 and approximately perpendicular to the longitudinal direction 12. The chain saw 1 is shown here in a customary working position, in which the longitudinal direction 12 is aligned approximately horizontally and the vertical direction 13 is aligned approximately vertically with respect to the direction of gravity. In this customary working position, the chain saw 1 is gripped from above by the user and held with one hand on a rear handle 8 and one hand on a front bale handle 9. As a result, in the customary working position, the only schematically indicated head 7 of the user is above the rear region of the chain saw 1.

[0034] The front hand on the bale handle 9 is protected by a hand protection 5 from the saw chain 11 driven by the electric drive motor 2 and running around the guide bar 10. In the event of kickback or other unforeseen movements of the chain saw 1 in an upward/rearward pivoting motion, the hand protection 5 is pressed against the user's front hand. As a result of this and or as a result of the mass inertia of the hand protection, it pivots forwards in relation to the chain saw and immediately releases a chain brake that is not shown.

[0035] Via the electric drive motor 2 and the saw chain 11 driven by it, during operation the chain saw 1 generates a sound, which is subjected to a sound adaptation in the way described in more detail below. Without this sound adaptation, the sound is referred to hereinafter in connection with FIG. 2 as uncorrected operating sound. For the sound adaptation and/or other purposes described further below, the chain saw 1 has a sound generator 3.

[0036] Part of the sound generator 3 is a speaker 4 and also a generator and amplifier unit 14, which is only schematically indicated as a block. The generator and amplifier unit 14 generates the frequency response of a sound and amplifies it to a suitable output level as an output signal in such a way that the speaker 4 outputs the output signal as sound of the desired volume or with the desired sound pressure level L.sub.P (FIG. 2).

[0037] In an aspect of the disclosure, a supplementary sound described below in connection with FIG. 2 is generated by the sound generator 3 and made perceptible to the user of the chain saw 1. Alternatively or additionally, the sound generator 3 may be connected to a radio receiver 15, schematically indicated as a block, or to some other unit for playing music, such as for example an MP3 player. In this case, the sound generator 3 may output a radio program, music and/or the like and be used for example for entertainment during breaks in work.

[0038] The speaker 4 may for example be integrated in hearing protection, which is worn on the user's ears. For good perceptibility of the sound generated, in particular the supplementary sound (FIG. 2) even without such adapted hearing protection, the speaker 4 in the embodiment shown is arranged on the upper side of the chain saw 1. It is also integrated in a component of the chain saw 1, for which a housing part or the like may be expedient. In the embodiment shown, the speaker 4 is integrated in the hand protection 5. This means that part of the hand protection 5, here an injection-moulded part, receives the speaker 4 and thereby serves as a housing for it. The corresponding portion of the hand protection 5 is for this purpose configured as a protective mesh, which is transmissive to sound but otherwise protects the speaker 4 from external influences.

[0039] It may be expedient to position the generator and amplifier unit 14 and/or the radio receiver 15 in the housing of the work apparatus or at some other suitable location. In the embodiment shown, in addition to the speaker 4, the generator and amplifier unit 14 and the radio receiver 15 are also integrated in the hand protection 5. For supplying the radio receiver 15 with a received signal, also integrated in the hand protection 5 is a schematically indicated antenna 16. This forms an independent functional unit, which as an exchangeable unit can be exchanged for a conventional hand protection 5, and whereby a conventional work apparatus can be retrofitted with the sound function described here. Depending on the configuration, it is therefore an assembly for playing a radio or music program and/or, in a way corresponding to the embodiment shown here, an assembly for sound adaptation of the work apparatus in the way described in more detail further below.

[0040] The speaker 4 may have various suitable structural forms and is constructed here in the usual way with a diaphragm, a permanent magnet and an electrical coil. The speaker has a central transmission direction 6, which in the present case points in the direction normal to the plane of the diaphragm. The speaker 4 is fastened to the chain saw 1 in such a way that, in the customary working position shown, it is directed with its transmission direction 6 towards the head 7 of the user. For this purpose, the transmission direction 6 is directed at least upwards in the vertical direction 13, here also additionally rearwards in the longitudinal direction 12. There is no lateral inclination, or at least it is less pronounced than the rearward inclination, and so the transmission direction 6 lies at least principally in the plane defined by the longitudinal direction 12 and the vertical direction 13.

[0041] FIG. 2 shows in a diagrammatic representation the spectral distributions, that is, the frequency responses of the sounds generated during operation by the chain saw 1 as shown in FIG. 1. In this case, the frequency f of the sounds in Hz is plotted on the horizontal abscissa and the sound pressure level L.sub.P of the respective sounds in dB is plotted on the vertical ordinate. This is a sound pressure level L.sub.P determined in accordance with ISO 22868, measured with a measuring microphone at a simulated location of the user's ear, to be specific in the vertical direction 13 approximately 700 mm above the bale handle 9 and in the longitudinal direction 12 approximately in the middle of the apparatus body, which is behind the guide bar 10 to the rear. Without already going into detail now, it can be seen at first glance that the spectral distribution of the sound pressure level L.sub.P of the electrically driven work apparatus taken as a basis here can be divided into two regions. Above a frequency f of approximately 1 kHz, the level profile does have various peaks and ripples, but apart from that is on average within a comparatively narrow band of level values. Below this frequency f of approximately 1 kHz, however, the sound pressure level L.sub.P has a tendency to fall significantly to lower frequencies, that is apart from a few peaks.

[0042] Firstly, the spectral distribution, that is, the frequency response of the uncorrected operating sound, will be discussed. This is the operating sound generated by the work apparatus, without the sound generator 3 (FIG. 1) being active. The profile of the operating sound pressure level LB.sub.P of the operating sound is shown by a solid line. For the example of a measurement taken here as a basis, the electric drive motor 2 or the drive shaft 17 operates at a speed of 12 500 rpm or 12 500 1/min, which corresponds to a fundamental frequency f.sub.0 of 208 Hz. At the fundamental frequency f.sub.0, the frequency spectrum of the operating sound, that is, the profile of the operating sound level LB.sub.P, naturally has a peak over the frequency f. Further peaks are found at integral multiples n of half the fundamental frequency f.sub.0, that is, at f.sub.n=1, f.sub.n=2, f.sub.n=3 and so on, which is generated by corresponding harmonics of the drive motor 2 and the tool, that is, in this instance the saw chain 11. These are regarded in the context of the disclosure as characteristic of the acoustic feedback of the chain saw 1 to the user.

[0043] The chain saw 1 and its sound generator 3 are configured for performing the method according to the disclosure, whereby in addition to the uncorrected operating sound a supplementary sound is generated via the sound generator 3 and is made perceptible for the user by way of the speaker 4. The supplementary sound adds to the uncorrected operating sound to form an overall sound with an overall sound pressure level LG.sub.P, the frequency response of which, that is, level profile over the frequency f, is shown in FIG. 2 by a dashed line.

[0044] Firstly, it is evident in FIG. 2 that the main component of the supplementary sound lies in an adaptation frequency range f.sub.A below 1 kHz. The supplementary sound has sound energy E distributed over its frequency range, which can be understood here as the area between the solid line of the operating sound pressure level LB.sub.P of the operating sound and the dashed line of the overall sound pressure level LG.sub.P of the overall sound pressure level. It is noticeable that, above the adaptation frequency range f.sub.A, that is, above approximately 1 kHz, the supplementary sound does not play a role, or plays only a minor role. This specifically means that at least 70%, preferably at least 80% and in the embodiment shown at least 90% of the sound energy E of the supplementary sound is generated in the adaptation frequency range f.sub.A. The falling region of the uncorrected operating sound already mentioned above is therefore as it were at least partially filled acoustically, while the higher frequency range above 1 kHz remains substantially unchanged.

[0045] Since the sound correction according to the disclosure takes place primarily in the adaptation frequency range f.sub.A, that is, below 1 kHz, this has a first important consequence: since at these low frequencies the uncorrected operating sound pressure level LB.sub.P is comparatively low, the perceived overall volume is scarcely increased at all by playing the supplementary sound. In the example specifically shown, the uncorrected operating sound has an A-weighted cumulative operating sound pressure level LkB.sub.pA, determined over the audible frequency range, of 94.9 dB(A), while a corresponding A-weighted cumulative overall sound pressure level LkG.sub.pA of the overall sound resulting from the uncorrected operating sound and the supplementary sound E is scarcely any more, to be specific only 95.4 dB(A). Altogether, the supplementary sound is set to such a level that the A-weighted cumulative overall sound pressure level LkG.sub.pA is not more than 1.0 dB(A) and in the present case not more than 0.5 dB(A) greater than the A-weighted cumulative operating sound pressure level LkB.sub.pA.

[0046] The region of the uncorrected operating sound B of a level falling to lower frequencies is not simply just uniformly “filled” within the adaptation frequency range f.sub.A. Rather, the speed of the drive shaft 17 for the tool, that is, here for the saw chain 11, is used as a fundamental frequency f.sub.0 for establishing the supplementary sound E, while the supplementary sound E is then set as dependent on the fundamental frequency f.sub.0 as follows:

[0047] The supplementary sound is generated in such a way that it includes in the adaptation frequency range f.sub.A at least one single frequency band F.sub.n, such a frequency band F.sub.n in each case having a reference frequency f.sub.n. The term reference frequency f.sub.n is used here to mean the frequency f at which the sound pressure level is a maximum within this frequency band F.sub.n. According to the representation as shown in FIG. 2, the supplementary sound within the adaptation frequency range f.sub.A has a number of such frequency bands F.sub.n=1, F.sub.n=2, F.sub.n=3, F.sub.n=4, F.sub.n=5 with associated reference frequencies f.sub.n=1, f.sub.n=2, f.sub.n=3, f.sub.n=4, f.sub.n=5, which are evident as peaks with limited bandwidth. Instead of a configuration with a specific bandwidth, frequency bands F.sub.n in the form of approximated spikes without a relevant bandwidth may also be expedient. In any case, the reference frequencies f.sub.n are set as dependent on the fundamental frequency f.sub.0 predetermined by the drive motor 2 or by the speed of the drive shaft 17. This means firstly that, with a changing speed or fundamental frequency f.sub.0, the reference frequencies f.sub.n are also shifted correspondingly. A higher speed or fundamental frequency f.sub.0 leads to higher reference frequencies f.sub.n and a lower speed or fundamental frequency f.sub.0 leads to correspondingly lower reference frequencies f.sub.n.

[0048] For the steady-state case of a constant speed or fundamental frequency f.sub.0 shown in FIG. 2, it is provided in the embodiment shown that at least one of the frequency bands F.sub.n of the supplementary sound includes an integral multiple n of half the fundamental frequency f.sub.0. In the present case, this applies to a number of frequency bands F.sub.n of the supplementary sound, and in particular to the first five frequency bands F.sub.n=1, F.sub.n=2, F.sub.n=3, F.sub.n=4, F.sub.n=5, in the case of which therefore the integral multiples n of half the fundamental frequency f.sub.0 are in the present case 1 to 5. Of course, still further frequency bands with additional integral multiples n may also be provided. Similarly, it may be expedient in the context of the disclosure to omit individual frequency bands. In any case, such frequency bands of the supplementary sound with integral multiples of n equals 1 and 2 and in particular of n equals 1 to 3 should preferably be present.

[0049] The associated reference frequencies f.sub.n, here f.sub.n=1, f.sub.n=2, f.sub.n=3, f.sub.n=4, f.sub.n=5 do not have to coincide exactly with the integral multiples n of half the fundamental frequency f.sub.0, though the integral multiples n of half the fundamental frequency f.sub.0 in the steady state should lie at least within the frequency bands F.sub.n, here F.sub.n=1, F.sub.n=2, F.sub.n=3, F.sub.n=4, F.sub.n=5. In the present case, however, the mentioned coincidence applies, and accordingly the reference frequencies f.sub.n=1, f.sub.n=2, f.sub.n=3, f.sub.n=4, f.sub.n=5 of the frequency bands F.sub.n=1, F.sub.n=2, F.sub.n=3, F.sub.n=4, F.sub.n=5 are set to the assigned integral multiples n of half the fundamental frequency f.sub.0. In any case it is achieved that the peaks at the integral multiples n of half the fundamental frequency f.sub.0, that is, at f.sub.n=1, f.sub.n=2, f.sub.n=3 and so on, which are perceived to be characteristic of the operating state and are important for acoustic feedback, are amplified in the profile of the operating sound level L.sub.B and are made better perceptible in the form of the overall sound G with a corresponding profile of the overall sound level L.sub.G.

[0050] Furthermore, it is also evident that certain lower and upper limits for the intensity of the supplementary sound are maintained. On the one hand, the supplementary sound is adapted to the profile of the operating sound pressure level LB.sub.p in such a way that, at the selected reference frequencies f.sub.n of the frequency band F.sub.n, the corresponding overall sound pressure level LG.sub.p produced is at least 3 dB higher than the corresponding operating sound pressure level LB.sub.p. By way of example, reference may be made here to the reference frequency f.sub.0=f.sub.n=2, where the overall sound pressure level LG.sub.p is approximately 80 dB, and consequently 28 dB, that is, at least 3 dB, higher than the corresponding operating sound pressure level LB.sub.p at a level of 52 dB. On the other hand, a certain upper limit is also not exceeded: at the selected reference frequencies f.sub.n of the frequency bands F.sub.n, the corresponding overall sound pressure level LG.sub.p produced is not more than 40 dB and in particular not more than 30 dB higher than the corresponding operating sound pressure level LB.sub.p. Once again, reference may be made here by way of example to the reference frequency f.sub.0=f.sub.n=2, where the overall sound pressure level LG.sub.p is approximately 80 dB and consequently 28 dB, that is, not more than 30 dB, higher than the corresponding operating sound pressure level LB.sub.p at a level of 52 dB.

[0051] The state described above can also be maintained in non-steady-state operation, when accelerating and/or decelerating. Preferably, however, here the frequency band F.sub.n or the frequency bands F.sub.n=1, F.sub.n=2, F.sub.n=3, F.sub.n=4, F.sub.n=5 are shifted in the direction of higher or lower frequencies in comparison with steady-state operation. As a result, the dynamics of working operation are acoustically emphasised more significantly.

[0052] It is understood that the foregoing description is that of the preferred embodiments of the invention and that various changes and modifications may be made thereto without departing from the spirit and scope of the invention as defined in the appended claims.