Vibration unit and its use in a vibration dynamometer for the lower and upper extremities

Abstract

The invention relates to a bicycle ergometer, comprising at least one pedaling device for a user and a vibration unit, wherein: the vibration unit has at least one main shaft (12), which is driven directly or indirectly by a motor (54) and has an eccentric disk (6) fastened thereto; the eccentric disk (6) is rotatably coupled to a connecting rod (1); and the connecting rod (1) transmits, by means of a rod eye (1a) disposed on opposite from the eccentric disk (6), the vibrations to the bearing (29) of the pedaling device such that the vibrations are applied substantially exclusively to this bearing (29) in the vertical direction.

Description

TECHNICAL FIELD

[0001] The present invention relates to an ergometer with a vibration unit, methods for operating such an ergometer, methods for producing such ergometers, and uses of such ergometers. STATE OF THE ART

[0002] In order to positively and efficiently influence the individual performance structure of rehabilitation / geriatric patients or competitive athletes, it is necessary to transform as many dosed external training stimuli as possible in a balanced way and adapted to the various structural levels of the human organism. In doing so, both conditioning (strength, endurance, speed, flexibility) and coordination (neuromotor) components should be taken into account in the application spectrum of the training tools.

[0003] A variety of vibration training devices have led to new training alternatives for physiological performance optimization by reactivating pathologically degenerated systems or increasing the capacity of intact functional systems in human structures. Although medical vibration training (MVT) is already in commercial use, the scientific validation of the method is still in the basic research stage.

[0004] Devices that transmit vibration energy to the user are known from a large number of publications: For example, US 4,570,927 shows a device in which the legs of a paraplegic patient are moved and vibrated by a crank unit driven by a motor.

[0005] NL 102 16 19 C describes a device in which vibration energy is transmitted to the upper extremities via a handlebar.

[0006] From DE 102 41 340 A1 a device is known in which a vibratode selectively transmits vibrations to stretched muscle structures.

[0007] Another vibration device is claimed in DE 102 25 323 B4, in which stochastic resonances are transmitted to the user via a mechanically complex construction.

[0008] DE 196 39 477 A1 discloses a device with a seat, a handlebar, and a vibration unit that applies vibrations to the user's feet. The use of these five aforementioned devices together with or as an ergometer, for example, via a brake unit connected to the crankshaft, is not disclosed, nor are details of how the vibrations are generated.

[0009] From DE 103 13 524 B3 a training device is known in which individual or several contact points subject to vibrations are mechanically isolated from the person exercising by one or more damping elements, so that all components for supporting the user's body parts are set into vibration.

[0010] WO 2006 / 69988 A1 discloses a vibration ergometer in which a bottom bracket is rigidly connected to a vibration plate, which is vibrated by two counter-rotating vibration motors. The disadvantage is that a non-directional vibration is generated, the amplitude of which decreases depending on the mechanical load on the pedal crank or the setting of the ergometer brake. The connection between the pedal crank and the ergometer brake is only possible with a bicycle chain with a chain tensioner to compensate for the length and position differences between the bottom bracket and the ergometer. This creates unpleasant noises and requires additional safety measures to prevent the chain from jumping off the front chainring.

[0011] EP 2 158 944 A2 describes a vibration ergometer with variable amplitude vibration. It does not disclose how the vibration is generated and how this amplitude change is achieved.

[0012] EP-A-2008695 relates to an exercise device comprising a mechanism rotated by a user of the exercise device via drive means rotating about a rotational axis, and vibration means by which the drive means can be set into vibration, wherein the vibration means comprise an electric motor rotating about a rotational axis, comprising at least one weight to be rotated about the rotational axis by the motor, wherein the weight is arranged eccentrically relative to the rotational axis. The electric motor is freely pivotable about a pivot pin extending parallel to the rotational axis of the electric motor, wherein the pivot pin is arranged above the electric motor below the rotational axis of the drive means, while the electric motor is pivotally connected thereto, a support carrying the rotational axis of the drive means, wherein the support is connected to a frame of the exercise device via spring means.

[0013] WO-A-2019219653 provides a self-propelled vibration mechanism that can be mounted on an existing pedal spindle, but operates independently of the existing pedal. Mechanical isolation or decoupling allows the vibration energy to be transferred to the foot instead of to the pedal spindle and the bicycle. In another embodiment, a fully removable pedal with a self-propelled vibration mechanism can replace an existing pedal.

[0014] US-A-2011152040 describes a training system for training a body part of a user, comprising a frame for positioning the training system in use on a surface, a bicycle device comprising at least one cycling element configured to rotate about a bicycle axis, a vibration device for moving the at least one cycling element as vibration, and also a method and use of the training system.

[0015] US-A-2020054920 provides an exercise machine of the type having pedals or footplates through which a person can transfer kinetic energy to the machine during use, the machine including means for vibrating the pedals or footplates during exercise. PRESENTATION OF THE INVENTION

[0016] All of the aforementioned ergometer systems are based on the principle of positioning the user, along with the training equipment, on a vibrating plate. All components used to support the user exert vibration energy on the body parts or corresponding body segments in contact with the components. This results in whole-body vibrations (WBV), which sometimes exceed the occupational health limits permitted by DIN ISO 2631. Resonance conflicts reduce the duration of use, resulting in a (time-limiting) reduction in efficiency. The design feature isolation of MVT devices to the uniform neuromotor stimulation of intramuscular coordination, with a focus on the conditioning strength component, leads to a lack of broad conditioning-coordinative multifunctionality of the WBV.State-of-the-art MVT products cover only a selective portion of training therapy; a holistic training concept cannot be implemented with these devices. Combination with conservative training equipment is mandatory (e.g., with cardio equipment during warm-up / cool-down or supplementary mechanical resistance training).

[0017] The object of the present invention is to provide an ergometer with a vibration unit in which both the amplitude and frequency of the vibration are preferably adjustable, in which the vibration acts essentially exclusively in one direction, wherein the amplitude of the vibration is essentially independent of the load on the vibration unit, and vibration frequencies of up to 50 Hz can be achieved. A further object of the present invention is the use of the vibration unit according to the invention in a vibration ergometer for the lower and upper extremities.

[0018] Specifically, the present invention relates to an ergometer, in particular a bicycle ergometer, having at least one pedal device for a user and having a vibration unit according to claim 1. The features of the characterizing part of the claim are not disclosed in the above-cited prior art.

[0019] The present invention mainly relates to a bicycle ergometer. The concepts described here can, however, be used analogously in an ergometer for the upper extremities, i.e. a hand ergometer. It is also possible to use the present invention in a combined bicycle and hand ergometer with both crank devices. If the proposed technology is used in a hand ergometer, the bottom bracket used subsequently is of course not a bottom bracket in the true sense, but rather a crank bearing for such a hand ergometer. According to the invention, such an ergometer is characterized in particular in that the vibration unit has at least one main shaft driven directly or indirectly by a motor and having an eccentric disc fastened thereto, wherein the eccentric disc is rotatably coupled to a connecting rod.The connecting rod, with a connecting rod head arranged opposite the eccentric disc, transmits the vibrations generated by the rotation of the engine and the eccentricity of the eccentric disc to the bearing of the crank or pedal device, so that the vibrations are essentially applied exclusively to this bearing in the vertical direction.

[0020] This creates a very concentrated vibration at the bottom bracket, which also has a precise vertical direction and thus causes as little overall body vibration as possible. The connecting rod and eccentric disc used provide a very stable and easily controllable structure that can easily withstand even heavy loads over extended periods. Furthermore, such a structure can be designed so that amplitude and frequency can be easily adjusted, and the additional elements described below can be easily integrated.

[0021] According to a first preferred embodiment, such an ergometer is characterized in that the vibration unit is arranged below the bearing, and that the connecting rod head is directly coupled to the bearing, preferably forming a bearing shell for the bearing. Preferably, the connecting rod bears substantially the entire vertically downward load on the bearing alone and without any additional guidance.

[0022] In general, the axis of the main shaft preferably runs parallel to the axis of the bearing.

[0023] The bearing of the pedal device can also be mounted in a vertical linear guide with a linear slide, wherein the linear slide is firmly connected to the bearing at the top and is connected to the connecting rod head at the bottom, wherein the axis of the main shaft preferably runs parallel to the axis of the bearing.

[0024] In such an ergometer, a base plate can also preferably be arranged, below which the main shaft and preferably also the motor are arranged and above which the pedal device is arranged, wherein a recess can be provided in the base plate through which the connecting rod passes and is coupled with its connecting rod head directly to the bearing.

[0025] The invention is characterized in that a brake is arranged, preferably substantially at the same height as the pedal device, which is coupled to the pedal device via a power transmission element, preferably in the form of a chain, a toothed belt, or a V-belt. The bearing of the pedal device is pivotally mounted about a horizontal pivot axis, preferably arranged at the height of an axis of the brake. The pivot axis is preferably arranged such that pivoting movement at the location of the bearing is permitted substantially exclusively in the vertical direction.

[0026] The pivot axis support of the bearing can be provided by a substantially fork-shaped construction in which the fork ends of the arms are rotatably mounted around the pivot axis, and the opposing joined arms are connected to the bearing, preferably in that the joined area forms a bearing receptacle for the bearing of the pedal device. Additional struts can be provided in this construction for stabilization, both perpendicular to the axis of the bearing and parallel to it.

[0027] The vibration unit can also be arranged below such a brake, preferably above a base plate, wherein the coupling of the connecting rod to the bearing can preferably be realized via at least one strut running obliquely upwards, connecting the connecting rod head directly or indirectly to the bearing, and wherein furthermore this strut can preferably be rigidly connected to the pivot axis bearing. According to a further preferred embodiment, a further eccentric disc is arranged on the main shaft, with which a counterweight is set into a compensating vibration, wherein this further eccentric disc is preferably arranged on the main shaft with an eccentricity opposite to that of the eccentric disc for driving the connecting rod. By means of such a compensation device, it is possible to ensure that the vibrations are present exactly where and to the extent where they are desired, namely at the bottom bracket.In other words, the compensation device prevents the vibrations from being transmitted to other elements of the ergometer, such as the base plate, the user's seat or the handlebars, and it can also prevent the device from vibrating to such an extent that these other components are damaged or that the device has a tendency to shift on its own during use.

[0028] A first preferred embodiment of such a compensation device is characterized in that the further eccentric disc drives a further connecting rod which is rotatably mounted on the further eccentric disc and is coupled to a counterweight which is set into vibration substantially in the same direction as the vibration device on the bearing, but with an effect compensating for the vibration on the bearing, preferably in that the vibration on the counterweight is offset by 180° with respect to the vibration on the bearing.

[0029] Furthermore, a brake can be arranged, preferably substantially at the same height as the pedal device, which is coupled to the pedal device via a power transmission element, preferably in the form of a chain, a toothed belt or a V-belt, and the counterweight is pivotally mounted about a horizontal pivot axis bearing, preferably arranged at the height of an axis of the brake, wherein the pivot axis is preferably arranged such that the counterweight in the region of the bearing performs the pivoting movement substantially exclusively in the vertical direction, wherein preferably the counterweight has a weight head in the region of the bearing, and further preferably this weight head encompasses the bearing area at least partially in a fork-like manner above and below.

[0030] Instead of or in addition to such a compensation device with a counterweight, the vibrations on components not subject to vibration can also be prevented by placing the ergometer on a weight plate, typically with a weight of at least 50 kg, preferably more than 100 kg, provided, for example, by metal plates, sand containers, water containers, and / or stone elements, which are mounted, for example, in a frame whose height is adjustable and mounted on the base. Such a frame can preferably be adjusted in height and / or leveled, possibly even electrically, and moved to the desired location via rollers (e.g., rollers that can be lowered only for movement).The plate can additionally contain damping elements; preferably, such damping elements are provided in the corners of such a frame and / or the weight plate, and / or damping mats can be provided for resting on the frame or frame elements. Damping mats with a fine-cell elastomer structure with enclosed gas volumes, for example, based on polyetherurethane with a thickness in the range of 10-30 mm, are particularly suitable. With such a construction, a mechanical high-pass filter can be provided that largely prevents vibrations from being transmitted both to the floor on which the device stands and to components of the ergometer that should not be subjected to vibration. The high-pass filter effectively filters out vibrations below 25 Hz, preferably less than 20 Hz.

[0031] A further preferred embodiment of such an ergometer is characterized in that the eccentric disc and / or any additional eccentric disc present is mounted on the main shaft so as to be displaceable and adjustable along a direction perpendicular to the rotational axis of the main shaft. This mounting is preferably implemented by a sliding guide, in which at least one adjusting element, upon displacement along the axis of the main shaft, causes a displacement of the eccentric disc along a direction perpendicular to the rotational axis of the main shaft. This control of the eccentricity can be used to control the amplitude of the applied vibration of both the vibration device and the compensation device.The control can be carried out via an additional servo motor, and it can also be regulated, for example, via a program depending on a desired course of therapy or training, if necessary coordinated with the frequency of the vibration.

[0032] Such an adjustment can be characterized in that the at least one adjusting element is mounted in a recess or through-opening in the main shaft in an adjustable manner via adjusting means, and a link in or on the adjusting element adjusts the eccentricity of the eccentric disc by interacting with a sliding block on the eccentric disc.

[0033] An eccentric disc for generating the desired vibration and a further eccentric disc for the counterweight can be mounted on the main shaft, and either an adjusting element can be provided with which the eccentricity of both eccentric discs can be adjusted correlated by 180°, or two individual adjusting elements can be provided for the respective eccentric disc, via which the eccentricity of the discs can be adjusted individually.

[0034] Such ergometers are preferably designed or operated at a frequency of 1-50 Hz with a vibration amplitude at the bearing in the range of 1-10 mm, preferably in the range of 3-7 mm, whereby these values ​​are to be understood as the values ​​generated by the vibration unit at the bearing of the pedal device. These values ​​are preferably combined with a load in the range of 50-500 W, in particular in the range of 100-300 W.

[0035] Furthermore, the present invention relates to the operation of such an ergometer or the use of such an ergometer as described above, wherein preferably frequencies in the range of 5-50 Hz, preferably in the range of 7-25 Hz and / or with amplitudes in the range of 1-10 mm, preferably 3-7 mm are set on the bearing.

[0036] Further embodiments are specified in the dependent claims. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] Preferred embodiments of the invention are described below with reference to the drawings, which are for illustrative purposes only and are not to be construed as limiting. In the drawings: Fig. 1 essential elements of a vibration unit for an ergometer according to a first embodiment in an exploded view; Fig. 2 the vibration unit according to Figure 1 in a sectional view in a) in a detailed section according to A in Figure 2a ) in b); Fig. 3 essential elements of a vibration unit for an ergometer according to a second embodiment in an exploded view; Fig. 4 the vibration unit according to Figure 3 in a sectional view; Fig. 5 essential elements of a vibration unit for an ergometer according to a third embodiment in an exploded view; Fig. 6 the vibration unit according to Figure 5in a sectional view; Fig. 7 different arrangements of the vibration unit, wherein in a) an embodiment is shown in which the bottom bracket is mounted via a swing arm directly from below from the connecting rod, in b) an embodiment is shown in which the bottom bracket is mounted without a swing arm in a linear bearing, to which the vibration unit is coupled from below, and in c) an embodiment is shown in which the vibration unit is arranged below the brake, the bottom bracket is mounted via a swing arm and a counterweight is provided; Fig. 8 a side view of the embodiment according to Figure 7 b) ; Fig. 9Views of an embodiment according to Figure 7c, where in a) the suspension is shown without a counterweight for better visibility of the individual elements and in b) only the counterweight is shown; Fig. 10 different views of a further embodiment with a vibration unit and counterweight coupled to the rocker, where in a) the right side view, in b) the left side view, in c) a view from above, in d) an exploded view, in e) a view diagonally from the top right and in f a view diagonally from the bottom right are shown. DESCRIPTION OF PREFERRED EMBODIMENTS

[0038] Fig. 1shows essential elements of a vibration unit in an exploded view. The actual main shaft 12 is supported by two bearings 11 and is rotated by a motor (not shown). The coupling to the motor can be either direct or indirect, for example via a V-belt. The motor is preferably a servomotor with an output in the range of 300 - 1,600 W. The main shaft 12 is structured and has an area on the left side 40 in which it is supported by the aforementioned bearings 11. The two ball bearings 11 serve to support the main shaft 12 with the bearing housing 19 and prevent axial displacement of the main shaft 12. On the right side is a shoulder surface 12a. This shoulder surface 12a prevents axial displacement of the eccentric disc 6 shown above on the right and thus of the entire connecting rod 1.The eccentric disc 6 is slidably mounted on the sliding surface 12b of the main shaft. The sliding shells 9 are held in the eccentric disc 6 with a positive fit and enable the eccentric adjustment of the eccentric disc 6 from the rotational axis of the main shaft 12. The power transmission of the rotation of the main shaft 12 to the eccentric disc 6 takes place via the sliding surface 12b via the sliding shells 9 and thus to the connecting rod 1. The eccentric disc 6 does not lie directly on the sliding surfaces 12b of the main shaft, but rather the sliding shells 9 are located between them. These can be constructed in two parts, as shown here, or as a single part. The contact surfaces 41 on the inside of the eccentric disc 6 are in contact with the outside of the sliding shells 9, and their contact surfaces 42 on the inside are in contact with the sliding surface 12b of the main shaft 12.

[0039] The sliding shells 9 are preferably made of a material with sliding properties, for example of a plastic with sliding properties (e.g. PTFE), and the main shaft 12 is made of metal in order to achieve an optimal sliding pairing on the sliding surface 12b.

[0040] The eccentric disc 6 has, in its axial recess 43 and inclined transversely to the axis, a sliding block 5 which determines the deflection of the eccentric disc 6 and thus the stroke of the connecting rod 1. The sliding block 5 bridges the recess 43 and is held in place by the screws 7. The fitting screws 7 fix the sliding block 5 in the eccentric disc 6 not only non-positively but also positively. A ball bearing is fastened to the eccentric disc 6 with the bearing ring 3 to support the connecting rod 1. For this purpose, the ball bearing is screwed to the eccentric disc with the bearing ring 3 using the screws 2. On the other side, a clamping ring 8 is provided which fixes the outer ring of the ball bearing 4 to the connecting rod 1 using the screws 10 in a non-positive manner. The screws 10 clamp the ball bearing 4 onto the connecting rod 1 via the clamping ring 8.

[0041] The forces of the connecting rod 1 are transmitted via the eccentric disc 6, via the sliding shells 9, to the main shaft 12, and via the bearing assembly 11 to the bearing housing 19. The connecting rod head 1a serves to accommodate a bearing for the movable fixation with the linear unit or the rocker arm (see below).

[0042] A pin-shaped adjusting element 13 engages axially in an axial blind hole 38 of the main shaft 12. The adjusting element 13 is connected to the bearing housing 15 via the fitting screws 14 in a force-locking and form-locking manner. The bearing housing 15 accommodates the bearing arrangement 16 in the form of two ball bearing rings. A trapezoidal threaded nut 17 is seated on this nut, which is mechanically (= rotationally secure) connected to the bearing housing 19 (in Figure 1 not shown). In Fig. 1Shown are 6 holes for the screw connection with the bearing housing 19. The bearing arrangement 16 is adjustable in the axial direction without play and is secured with shaft clamping nut 20 and retaining ring 21 (both in Fig. 1 not shown, cf. Fig. 2 ) is mounted on the trapezoidal spindle 18. The trapezoidal spindle 18 moves the adjusting element 13 in the axial direction to change the stroke of the connecting rod 1. Due to the bearing arrangement 16, the trapezoidal spindle 18 does not rotate with the main shaft 12.

[0043] The adjusting element 13 is preferably made of a material with sliding properties, for example of a plastic with sliding properties (e.g. PTFE), and the sliding block 5 is made of metal in order to achieve an optimal sliding pairing.

[0044] A link opening in the form of a cutout surface 13a runs transversely in the adjustment element. This cutout surface has a width essentially the same as the thickness of the sliding block 5, but is considerably longer. When the adjustment element 13 is inserted into the blind hole 38, it is aligned with the larger opening 39. In other words, the sliding block 5 extends through the openings 39 and 13a. The cutout surface 13a is thus part of the adjustment element 13. The sliding block 5 is positioned in the cutout surface 13a, and the deflection of the eccentric disc 6 is achieved in a form-fitting manner via the planar surfaces of the sliding block 5 and the cutout surface 13a of the adjustment element 13.

[0045] The eccentric disc 6 is thus eccentrically mounted on the main shaft 12. The lower ring of the connecting rod 1 is in turn rotatably mounted on the eccentric disc 6 via the bearing ring 4. When the main shaft 12 rotates, the eccentric disc 6 performs an eccentric movement, which is transmitted to the lower ring of the connecting rod 1 and thus translated into a translation or oscillation at the connecting rod head 1a. The frequency of these oscillations is determined by the rotation frequency of the main shaft 12 and thus by the frequency of the motor driving this shaft. The amplitude of the oscillation can be adjusted using the trapezoidal spindle 18. The further the adjusting element 13 is pushed into the blind hole 31, the more the eccentric disc 6 is shifted from the axis of the main shaft 12 via the sliding block 5, and the greater the amplitude of the eccentricity and thus also the movement at the connecting rod head 1a.The vibration generated at the connecting rod head 1a can thus be finely adjusted and controlled in terms of both frequency and amplitude. Furthermore, the connecting rod exhibits high mechanical stability and very high directional stability, meaning that the vibrations generated in this way run exactly along the direction of the connecting rod. This means that the proposed device allows for the generation of quasi-one-dimensional vibrations with an adjustable frequency and an adjustable amplitude along a precisely defined direction.

[0046] Fig. 2shows in a) the vibration unit in a sectional view through the shaft axis in an overview, and in b) the details according to A in a). Here, it can be seen how such a vibration unit can be arranged below a base plate 28, which serves as the central fastening receptacle for the vibration unit. The base plate has a recess 44 through which the connecting rod 1 protrudes freely upwards. On the underside of the base plate 28, there is, on the one hand, a left bearing housing 19 for the bearing of the main shaft, and, on the other hand, a right bearing housing 19a for the bearing of the trapezoidal thread nut 17.

[0047] In the right-hand bearing housing 19, the main shaft 12 is supported by the above-mentioned bearings 11. A shaft lock nut 20 is provided for fastening, which clamps the bearing assembly 11 to minimize the axial and radial play of the main shaft 12. Additionally, there is a retaining ring 21 that prevents accidental loosening of the shaft lock nut 20.

[0048] In Fig. 2 For example, the bearing arrangement 11 is designed as an O-bearing arrangement. The force is applied outside the bearing arrangement 11. This adjusts the radial and axial play of the main shaft 12.

[0049] The only desired vibration in the present invention is a deflection of the connecting rod head 1a that is substantially perpendicular to the base plate.

[0050] Fig. 3shows an exploded view of a second embodiment of a vibration unit, this time with two eccentric discs 6 mounted on the same shaft. In this case, two connecting rods 1 with significantly shorter connecting rod arms are coupled to these two eccentric discs 6. One connecting rod serves to generate the actual effective vibration for the user, and the other connecting rod serves to generate the countermovement of the counterweight, which will be explained further below. The two eccentric discs 6 are arranged on the same main shaft 12, but here there is a separate sliding surface 12b for each eccentric disc 6 on the main shaft 12, and the adjusting element 13 has two correspondingly assigned cutout surfaces 13a with opposite inclinations.In principle, however, the two eccentric discs 6 are mounted on the main shaft 12 in a manner analogous to that already described in the first embodiment, and their eccentricity is controlled by the adjusting element 13. It is important that the eccentricity of the two eccentric discs 6 is 180° out of phase, which is ensured by the opposing inclination of the cutout surfaces 13a and the correspondingly opposing inclination of the two sliding blocks 5 of the respective eccentric disc 6.If the adjusting element 13 is displaced in the recess 38 of the main shaft 12 by actuating the trapezoidal spindle 18, which in this case is fastened by a retaining ring 23 which prevents accidental loosening of the shaft clamping nut 22, and a shaft clamping nut 22 which clamps the bearing arrangement 16 in the bearing holder 15 in order to support the trapezoidal thread spindle 18 axially and radially without play, then one eccentric disc is displaced in a first direction and the other eccentric disc in the opposite direction from the main axis. This leads to a phase shift of the eccentricity of the two eccentric discs 6 by 180°, in a completely correlated manner, ie the adjustment by the single adjustment element 13 with the opposing inclinations of the cutout surfaces 13a automatically leads to a phase shift of exactly 180°, regardless of the set amplitude of the vibration.In this way, the design ensures that the optimal phase shift of the two connecting rods is always present, so that the compensation by the counterweight is optimal for every setting and every vibration amplitude.

[0051] The second embodiment differs from the first, among other things, in that the main shaft 12 is coupled slightly differently. Here, there is also a V-belt pulley 24, which serves to connect a servo motor to the main shaft via a V-belt. The V-belt pulley 24 is secured by a clamping nut, for example, in the form of a taper-lock bushing.

[0052] The second embodiment differs from the first embodiment in that it allows for compensation of unwanted vibrations. The term "unwanted vibrations" refers in particular to vibrations of the base plate 28 that oppose the intended vibration, as well as other vibrations that are not perpendicular to the base plate 28. The unwanted vibrations are caused by the unbalanced eccentric, with the imbalance of the eccentric being primarily caused by the adjustability of the connecting rod and its design, which cannot be statically compensated due to the amplitude modulation of the stroke.

[0053] Fig. 4shows the second embodiment in a sectional view. Here, among other things, it can be seen how the two connecting rods are mounted parallel to one another via the two eccentric discs on the same main shaft 12, how the V-belt pulley 24 protrudes on the left side for coupling a servo motor, and how the trapezoidal spindle for adjusting the eccentricity protrudes on the right side. It can be seen that an extremely compact design solution is provided in which the two connecting rods, which can bear high loads, are stably mounted.

[0054] In Fig. 4 the bearing surface of the connecting rod end bearings 26 is larger than the connecting rod end bearings 27 in order to absorb the higher forces occurring during operation under load (for example under the influence of body weight).

[0055] The adjusting element 13 extends the respective sliding blocks for the crank and the counterweight in the opposite direction. The two eccentric discs must be axially rotated by 180° to each other in order to be able to deflect in the opposite direction. This offset arrangement of the eccentric discs 6 is Fig. 5 to recognize better.

[0056] Fig. 5 shows an exploded view of a third embodiment of a vibration unit, which, in contrast to the second embodiment, is designed so that the eccentricity of the two connecting rods 1 or the associated eccentric discs can be individually adjusted for both. For this purpose, the main shaft 12 is no longer supported on one side and open on the other side for control via the adjusting element 13, but the main shaft is, as can be seen in particular from Fig. 6 ,a sectional view, supported at both ends via the bearing rings 11. The main shaft no longer has a blind hole, but rather an axial through-opening, so that individual adjustment elements 13 for adjusting the eccentricity of each eccentric disc 6 can now be inserted from both sides. Accordingly, there are trapezoidal spindles 18 on both sides, which control the respectively assigned adjustment element 13. The two adjustment elements, however, in turn have cutout surfaces 13a with opposite inclination, so that in principle the eccentricity can be adjusted individually but always 180° out of phase. This ensures that the phase shift is always 180°, but that the amplitude of the vibration can be set differently for the two connecting rods.This makes it possible to adjust the vibration compensation even more finely using the counterweight and, in particular, to adapt it to environmental parameters or user parameters so that the compensation is always optimally guaranteed.

[0057] The third embodiment differs from the second embodiment in that the amplitude of both connecting rods can be controlled independently of each other. According to this embodiment, unwanted vibrations can be compensated for by vibration compensation. The key difference compared to the embodiment according to Fig. 3 and 4is that the adjusting element 13 is constructed in two parts. Both adjusting elements 13 require separate O-bearings and motor control. The left trapezoidal spindle 18 controls the deflection of the counterweight, while the right trapezoidal spindle 18 controls the deflection of the crankshaft. In this embodiment, the main shaft 12 is driven centrally between the two connecting rods 1.

[0058] The compensation can be adjusted manually, but it is also possible for the trapezoidal spindle or multiple trapezoidal spindles to be controlled by another servomotor. For example, it is possible to control such a servomotor in a controlled manner, for example, via a vibration sensor or a plurality of vibration sensors and a corresponding control system. In particular, it is also possible to regulate such a control system using a self-learning algorithm so that the vibrations measured by the vibration sensors are minimal where they should not occur (for example, on the base plate) and maximal or exactly within the desired range where they should occur (for example, at the bottom bracket).

[0059] Fig. 6 is a sectional view of the exploded view 5. The length of the two adjustment elements 13 is different: Shown in Fig. 6a stroke of the connecting rods of zero. To change the stroke, the right adjusting element 13 is moved to the right and the left adjusting element 13 is also moved to the right by rotating the trapezoidal spindle 18; this changes the deflection of the eccentric discs, which are in Fig. 6 can be seen from the different position of the play of the sliding shells 9 (the right sliding shells show the play at the top, the left ones at the bottom).

[0060] Fig. 7 now shows different possibilities of arranging such a vibration unit on a (bicycle) ergometer.

[0061] A first in Fig. 7b and also in Fig. 8The possibility shown in a side view is to arrange the vibration unit below a base plate 28, so that the connecting rod 1 passes upwards in a vertical direction through a recess in this base plate. The bottom bracket 29 of the ergometer is selectively mounted in a strictly vertical direction in a linear slide 34, which is mounted on the base plate via a linear guide 35. This linear slide 34 is firmly connected to the ball bearing 29 at the top and coupled to the connecting rod head 1a at the bottom.

[0062] This provides a design that selectively allows vibrations only in a strictly vertical direction, and the entire suspension and load of the vibration unit is transferred via the front area below the bottom bracket. Such a vibration unit can be combined with a conventional brake 30, which is coupled via a power transmission element, for example, a chain, belt, or toothed belt.

[0063] With this construction, it is possible to use a vibration unit according to the first embodiment described above, ie, with only a single connecting rod for the vibration at the bottom bracket. However, it is also possible to use a vibration unit according to the second or third embodiment. Fig. 8 As shown, it is possible to mount a counterweight 36 in such a housing via another connecting rod, 180° out of phase, so that the vibrations are transmitted via the first Figure 8The connecting rod shown in the front is transmitted to the bottom bracket at the desired frequency and amplitude, but with regard to the environment and in particular, for example, the base plate 28, the vibrations are canceled out in a manner similar to noise cancellation. In practice, considerable problems arise with such devices due to the artificially generated vibration. On the one hand, the artificially generated vibration leads to unpleasant noise emissions, in particular because the base plate or corresponding legs connected to it transmit the vibrations to the ground and buildings, etc., but there are also unpleasant noise emissions due to the vibration of other components, in particular the brakes, etc. Furthermore, problems arise due to the vibration because such devices have a tendency to be displaced by the shaking and to essentially wander around.Finally, the vibrations cause mechanical damage to the device itself and to the other components of the device, and the same applies to other devices located nearby to which the vibrations are unintentionally transmitted.

[0064] Typically, such vibrations suitable for this device are in the range of up to 50 Hz. Low frequencies of 7-12 Hz with amplitudes in the range of up to 7-10 mm have proven particularly suitable for neurostimulation, typically in a load range of approximately 100 W. Higher frequencies in the range of 15-25 Hz can also be used for athletes, for example, but then typically with somewhat lower vibration amplitudes of up to 3-4 mm. Loads in the range of 200-300 W of braking power are used in these cases. Thus, the vibrations and amplitudes are in a mechanically critical range for other components, and compensation by one or more counterweights is extremely important.

[0065] In Fig. 7bThe crank bearing is thus attached to a linear bearing 35 via a slide 34, with the linear bearing 35 being arranged perpendicular to the base plate 28. The connecting rod is connected to the linear slide in such a way that the movement is directed exclusively perpendicular to the base plate 28. The design can also be implemented in a vibration-compensating manner with a second connecting rod and a counterweight 36 as a second slide on the linear guide.

[0066] Another possibility to provide such a vibration device on an ergometer is in Fig. 7ashown. Here, too, the connecting rod 1 generates a vibration that essentially runs strictly in the vertical direction (see arrow). However, the connecting rod 1 serves as the sole vertical bearing for the bottom bracket, thus providing an extremely slim design. To enable this design, there is now an additional swing arm 32. This swing arm 32 is a second bearing for the bottom bracket, essentially around the axis 45 of the brake. The swing arm 32 has two arms 46, a first arm 46' and a second arm 46". The two arms engage the axis 45 at different ends and pivotally support the bottom bracket 29.Due to the fact that the axis of the bottom bracket 29 and the axis of the brake 45 are arranged at approximately the same height, this ensures that the swing arm 32 allows the bottom bracket 29 to move essentially only vertically at the bottom bracket, thus ensuring strictly vertical vibration. If, for example, the brake on such an ergometer is arranged closer to the base plate or essentially below the bottom bracket, the swing arm 32 should not be attached to the brake axis, but rather to a separate axle bearing approximately at the height of the bottom bracket, precisely to ensure that only vertical vibrations are possible at the bottom bracket.

[0067] In Fig. 7aThe center of the connecting rod head 1a is identical to the center of the crank bearing. The crank bearing is supported only by the connecting rod and the rocker arm. All forces except those in the connecting rod direction are absorbed by the rocker arm. The adjustable braking force of the brake 30 is transmitted to the crank 33 via the force transmission element 31. The braking effect can be adjusted by suitable measures known to those skilled in the art, such as gear ratios between the crankshaft and the brake.

[0068] Another possibility to provide such a vibration device on an ergometer is in Fig. 7cshown. Here, the vibration device is arranged below the brake, and the bottom bracket is virtually free-floating. This results in a particularly compact and elegant design. The swing arm 32 is in turn attached to the axle 45 of the brake and mounts the bottom bracket 29 such that it can only be moved in the vertical direction. In this design, the bottom bracket 29 is supported in the vertical direction by the fact that the swing arm 32 has a strut directed obliquely downwards towards the vibration device, which is coupled to one of the two connecting rods of the vibration device via a connecting rod holder 37. In other words, the swing arm 32 comprises a means for coupling the vibration of the vibration device, and the geometric design and the levers used ensure that the vibration, although it is applied to the connecting rod in an oblique direction on the device, is translated into a strictly vertical vibration at the bottom bracket.See in particular . Fig. 9a , in which this construction is shown, whereby only the rocker arm 32 with the strut 46 is illustrated for better visibility.

[0069] Fig. 7c This shows a variant in which the vibration drive is not located below the ball bearing, but outside the crank area. This eliminates components below the crankshaft, thus enabling a very compact design. The connecting rod is movably connected to the swing arm at the connecting rod mount 37 of the swing arm.

[0070] In such a construction, a corresponding counterweight 36 is advantageously mounted in a similar manner and controlled by the second connecting rod, which is 180° out of phase. Compare in particular Fig. 9b, in which this counterweight design is shown and the swing arm for the bottom bracket is omitted. The counterweight 36, or rather the weight head 50 of the counterweight, is in this case attached to the axle 45 of the brake via a first strut 47, similar to the swing arm. On the other side, between the weight head 50 and a connecting rod holder 37a for the counterweight, there is another strut 49 pointing downwards, as well as a third strut 48, which connects the connecting rod holder of the counterweight to the axle 45 of the brake in order to ensure the necessary stability of the bearing. The counterweight, in particular its weight head 50, is thus arranged in an optimally space-saving yet excellently mounted manner between the two arms 46' and 46" of the swing arm, where it can also provide the optimal compensation effect.

[0071] In Fig. 10Another embodiment of an ergometer is illustrated. The components corresponding to the components described above are identified by the same reference numerals. In this embodiment, the swing arm is designed with several struts on both sides, including additional vertical struts and horizontal struts. However, the connection to the connecting rod 1 is essentially analogous to that described above in connection with the Figures 7 and 9The counterweight is also mounted in a similar way; here the weight head 50 is constructed as a layered body, which makes it possible to make adjustments to the mass of the weight head on site if necessary by adding further layers. Furthermore, the weight head 50 is designed as a fork, the arms of which at least partially encompass the bottom bracket 29 at the top and bottom. This allows the counterweight to be positioned as close as possible to and in the region of the bottom bracket so that vibration compensation can be optimal. The counterweight is mounted here via a mounting body 47, which is also constructed with several struts and is in turn coupled to the vibration unit via the connecting rod holder 37a for the counterweight. This mounting body essentially reaches through the struts of the swing arm and is thus optimally mounted in a space-saving and compact manner.

[0072] Also visible in this embodiment is the servo motor 52 with the associated V-belt 51 for adjusting the trapezoidal thread nut and, accordingly, for adjusting the eccentricity and the associated vibration amplitude. Also visible is the motor 54 for driving the main shaft 12 and the corresponding V-belt 53. LIST OF REFERENCE SYMBOLS 1 connecting rod 16 Bearing arrangement 1' Connecting rod for counterweight 17 Trapezoidal thread nut 1a connecting rod head 18 trapezoidal spindle 2 screws 19 Left bearing housing 3 bearing ring 19a Right bearing housing 4 ball bearings 20 Shaft clamping nut 5 Sliding block 21 retaining ring 6 Eccentric disc 22 Shaft clamping nut 6' Eccentric disc for 23 retaining ring Counterweight 24 V-belt pulley 7 fitting screws 25 clamping nut 8 clamping ring 26 connecting rod bearing 9 Sliding shells 27 connecting rod bearing 10 screws 28 base plate 11 Bearing arrangement 29 Crank bearing 12 Main shaft 30 brake 12a shoulder area 31 Power transmission element 12b Sliding surface 32 swingarm 13 Adjustment element 33 crank 13a Cutout area 34 Linear slide 14 fitting screws 35 Linear guide 15 Stock taking 36 Counterweight 37 Connecting rod mount swing arm Connecting rod of the counterweight 37a Connecting rod counterweight 49 Weight strut from the connecting rod of the counterweight to the weight head 38 axial blind hole in 12 39 radial through opening 40 Mounting area of ​​12 41 Investment areas from 6 to 9 50 Weight head 42 Investment areas from 9 to 12b 51 V-belt for actuation of trapezoidal thread nut 43 Recess in 6 44 Recess in 28 for 1 52 Motor for actuating trapezoidal thread nuts over 51 45 Brake axis 46 Strut of 32 46', 46" Arms of 32 53 V-belt for drive motor of main shaft 12 47 Weight strut to the brake axis 54 Motor for driving main shaft 12 48 Weight strut from the brake axis to the

Claims

1. Ergometer, in particular bicycle ergometer, with at least one pedalling device for a user and with a vibration unit, characterised in that the vibration unit has at least one main shaft (12) driven directly or indirectly by a motor (54) with an eccentric disc (6) attached to it, wherein the eccentric disc (6) is rotatably coupled to a connecting rod (1), and the connecting rod (1) transmits the vibrations to the bearing (29) of the pedalling device via a connecting rod head (1a) arranged opposite the eccentric disc (6), so that the vibrations are applied essentially exclusively to this bearing (29) in a vertical direction that a brake (30) is arranged essentially at the same height as the pedalling device and is coupled to the pedalling device via a force transmission element (31), wherein the bearing (29) of the pedalling device is mounted so as to be pivotable about a horizontal pivot axis.

2. Ergometer according to claim 1, characterised in that the vibration unit is arranged below the bearing (29) and that the connecting rod head (1a) is directly coupled to the bearing (29), preferably forms a bearing shell for the bearing (29), and that the connecting rod (9) bears substantially the entire vertical downward load on the bearing (29) alone and without further guidance, the axis of the main shaft (12) preferably extending parallel to the axis of the bearing (29).

3. Ergometer according to one of the preceding claims, characterised in that the bearing (29) of the pedalling device is mounted in a vertical linear guide (35) with a linear slide (34), wherein the linear slide (34) is fixedly connected to the bearing (29) at the top and is connected at the bottom to the connecting rod head (1a), wherein preferably the axis of the main shaft (12) runs parallel to the axis of the bearing (29).

4. Ergometer according to one of the preceding claims 2 or 3, characterised in that a base plate (28) is arranged below which the main shaft (12) and preferably also the motor is arranged and above which the pedalling device is arranged, wherein a recess (44) is provided in the base plate (28) through which the connecting rod (1) passes and is coupled directly to the bearing (29) with its connecting rod head (1a).

5. Ergometer according to one of the preceding claims, characterised in that the bearing (29) of the pedalling device is mounted so as to be pivotable about a horizontal pivot axis arranged at the height of an axis (45) of the brake (30), wherein the pivot axis (45) is arranged such that at the location of the bearing (29), the swivelling movement is essentially only permitted in a vertical direction.

6. Ergometer according to claim 5, characterised in that the pivot bearing of the bearing (29) is provided by a substantially fork-shaped construction in which the fork ends of the arms (46', 46") are rotatably mounted about the pivot axis and the opposite arms joined together are connected to the bearing (29), preferably by the joined area forming a bearing receptacle for the bearing (29) of the pedalling device.

7. Ergometer according to one of the preceding claims 5 or 6, characterised in that the vibration unit is arranged below this brake (30), preferably above a base plate (28), and wherein the coupling of the connecting rod (1) to the bearing (29) is preferably realised via at least one strut (46) extending obliquely upwards and connecting the connecting rod head (1a) directly or indirectly to the bearing (29), and wherein, furthermore, this strut (46) is preferably rigidly connected to the pivot bearing.

8. Ergometer according to one of the preceding claims, characterised in that the ergometer is mounted on a base plate which acts as a mechanical high-pass filter for the vibrations generated by the vibration unit, and / or that a further eccentric disc (6') is arranged on the main shaft (12), with which a counterweight (36) is set into a compensating vibration, wherein this further eccentric disc (6') is preferably arranged on the main shaft (12) with eccentricity opposite to the eccentric disc (6) for driving the connecting rod.

9. Ergometer according to claim 8, characterised in that the further eccentric disc (6') drives a further connecting rod (1') which is rotatably mounted on the further eccentric disc (6') and is coupled to a counterweight (36) which is set into vibration substantially in the same direction as the vibration device at the bearing (29), but with a counteracting effect that compensates for the vibration at the bearing (29), preferably by the vibration at the counterweight (36) being offset by 180° relative to the vibration at the bearing (29).

10. Ergometer according to one of the preceding claims 8-9, characterised in that the brake (30) is coupled to the pedalling device via a force transmission element (31), preferably in the form of a chain, a toothed belt or a V-belt, and the counterweight (36) is pivotably mounted about a horizontal pivot axis bearing, preferably arranged at the height of an axis (45) of the brake (30), wherein the pivot axis (45) is preferably arranged such that the counterweight (36) performs the pivoting movement in the region of the bearing (29) essentially exclusively in a vertical direction, wherein the counterweight (36) preferably has a weight head (50) in the region of the bearing (29), and furthermore, this weight head (50) preferably surrounds the bearing region at least partially in a fork-shaped manner at the top and bottom.

11. Ergometer according to one of the preceding claims, characterised in that the eccentric disc (6) and / or a further eccentric disc (6') which may be present is mounted on the main shaft (12) so as to be displaceable and adjustable along a direction perpendicular to the axis of rotation of the main shaft (12), wherein this mounting is preferably realised by a coulisse guide (5, 13a) in which at least one adjustment element (13), when displaced along the axis of the main shaft (12), causes the eccentric disc (6) to be displaced in a direction perpendicular to the axis of rotation of the main shaft.

12. Ergometer according to claim 11, characterised in that the at least one adjustment element (13) is mounted in an recess (38) or through-opening in the main shaft (12) so as to be adjustable and displaceable by means of adjustment means (18), and a cam (13a) in or on the adjusting element adjusts the eccentricity of the eccentric disc (6) by interaction with a sliding block (5) on the eccentric disc (6).

13. Ergometer according to one of the preceding claims 11 or 12, characterised in that the eccentric disc (6) for generating the desired vibration and the further eccentric disc (6') for the counterweight are mounted on the main shaft (12), and that either an adjustment element (13) is provided with which the eccentricity of both eccentric discs can be adjusted in correlation with each other and offset by 180°, or that two individual adjustment elements are provided for the respective eccentric discs (6, 6') ( ), by means of which the eccentricity of the discs can be adjusted individually.

14. Ergometer according to one of the preceding claims, characterised in that it is designed for operation at a frequency of 1-50 Hz with a vibration amplitude at the bearing (29) in the range of 1-10 mm, preferably in the range of 3-7 mm, preferably with a load in the range of 50-500 W, in particular in the range of 100-300 W.

15. Use of an ergometer according to one of the preceding claims, wherein frequencies in the range of 5-50 Hz, preferably in the range of 7-25 Hz, and / or amplitudes in the range of 1-10 mm, preferably 3-7 mm, are preferably set at the bearing (29).

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