EP4304747A1

EP4304747A1 - Bearing for an ergometer having a vibration unit, and use thereof in a vibratory ergometer for the upper and lower extremities

Info

Publication number: EP4304747A1
Application number: EP22709730.0A
Authority: EP
Inventors: Oliver DUNKELBERG
Original assignee: Brainaix Swiss Ag
Current assignee: Brainaix Swiss Ag
Priority date: 2021-03-12
Filing date: 2022-03-03
Publication date: 2024-01-17
Also published as: WO2022189254A1; CN116963805A

Abstract

Disclosed is a bicycle ergometer comprising at least one pedaling mechanism for a user as well as a vibration unit, characterized in that the bearing (29) of the pedaling mechanism is mounted to be pivotable about a horizontal pivot axis (45).

Description

TITLE

STORAGE FOR AN ERGOMETER WITH VIBRATION UNIT AND ITS USE IN A VIBRATION ERGOMETER FOR THE LOWER AND

UPPER EXTREMITIES

TECHNICAL AREA

The present invention relates to an ergometer with a vibration unit, methods for operating such an ergometer and methods for producing such ergometers and uses of such ergometers.

STATE OF THE ART

In order to be able 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 and adapted manner to the different structural levels of the human organism. Both conditional (strength, endurance, speed, flexibility) and coordinative (neuromotor) components in the application spectrum of the training equipment should be taken into account.

A large number of vibration training devices has led to new training alternatives for physiological performance optimization through reactivation of pathologically degenerated or capacity increase of intact functional systems of human structures. Although medical vibration training (MVT) is already being used commercially, the scientific validation of the method is still at the basic research stage.

Devices that transmit vibrational energy to the user are known from a large number of publications:

For example, US Pat. No. 4,570,927 shows a device in which the legs of a paraplegic patient are moved and vibrated with a crank unit driven by a motor.

NL 102 16 19 C describes a device in which vibration energy is transmitted to the upper extremities via a handle bar.

DE 10241 340 A1 discloses a device in which a vibratode selectively transmits vibrations to stretched muscle structures.

A further vibration device is claimed in DE 102 25 323 B4, in which stochastic resonances are felt by the user via a mechanically complex construction be transmitted.

DE 196 39 All A1 shows a device with a seat, a handle bar and a vibration unit, with which the user's feet are subjected to vibrations. A 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 there usually any details of how the vibrations are generated.

DE 103 13 524 B3 discloses a training device in which one or more contact points to the person being trained that can be subjected to vibrations are vibration-mechanically isolated by one or more damping elements, so that all assemblies for supporting the body parts of the user are made to vibrate.

A vibration ergometer is known from WO 2006/69988 A1, in which a bottom bracket is firmly connected to a vibration plate, which is made to oscillate by two opposing 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 differences in length and position between the bottom bracket and the ergometer: This causes unpleasant noises and additional security measures are necessary to prevent the chain from jumping off the front chainring .

EP 2 158 944 A2 describes a vibration ergometer with variable-amplitude vibration. How the vibration is actually generated and how this amplitude change is to be realized is not disclosed there.

WO-A-2010110670 describes a stationary training and exercise device for simulating the driving of bicycles, motorcycles, car boats, airplanes and similar means of transport for people, the basic structure having a first frame to be supported on a floor and a first frame connected to the first frame on an axis second frame outrigger, whereas the second frame is rotatably tiltable relative to the first frame and the tilt controllable using a steering rod or steering wheel through a connection between a steering column and a first frame reference.

EP-A-2008695 relates to an exercise machine comprising a mechanism which is rotated by a user of the exercise machine via drive means rotating about an axis of rotation and vibrating means by which the drive means can be made to oscillate, the vibrating means comprising an electric motor , which rotates about an axis of rotation, with at least one weight, which is driven by the motor around the Axis of rotation is to be rotated, wherein the weight is arranged eccentrically relative to the axis of rotation. The electric motor is freely pivotable about a pivot extending parallel to the axis of rotation of the electric motor, the pivot being arranged above the electric motor below the axis of rotation of the drive means, while the electric motor is pivotably connected to a support which carries the axis of rotation of the drive means, the support is connected via spring means to a frame of the exercise machine.

US-A-2014024502 describes an exercise bike having a base post and an upright support structure. Connected to the upright support structure are a seat, a handlebar assembly, a pedal assembly, and a resistance assembly. The upright support structure may be pivotally connected to the base support to allow the upright support structure to move between different reclined positions. One or more vibrating assemblies may be connected to the exercise bike at various locations to vibrate desired parts of the exercise bike, such as the handlebar assembly, seat, or pedal assembly. The vibrations are imparted to a user while performing an exercise to provide various physiological benefits to the user.

CN-A-106618946 discloses a rehabilitation exercise bed for lower limb exercise. The rehabilitation exercise bed includes a bed body; a lower limb exercise system capable of moving in the horizontal direction relative to the bed body, disposed on the bed body, and comprising a lower limb exerciser and a lower limb exerciser position adjusting mechanism, the lower limb exerciser position adjusting mechanism lower limbs is mounted on the bed body, and the lower limb exerciser is fixedly connected to one end of the lower limb exerciser position adjusting mechanism. According to the scheme, the problems that an existing rehabilitation exercise bed in the exercise mode is single, large in size, large in occupied space, and the like can be solved.

KR-A-20180100781 relates to a virtual reality linked intelligent driving simulator that allows a user to experience a virtual reality while moving in the same way as actually driving a bicycle, motorcycle, vehicle and the like in drives in a virtual space. The virtual reality linked intelligent driving simulator includes: a frame unit for providing a seat for a user; a tilting plate for supporting the frame unit to be turned forward and backward; a front/rear tilt implementation unit for rotating the frame unit in the forward and rearward direction with respect to the tilting plate unit according to a signal related to a front and rear inclination of a road surface of a virtual driving space inputted from the outside; a base unit for supporting the tilting board unit to be rotated left and right; and a left/right inclination implementing unit for supporting the left and right bottom surfaces of the tilting plate unit by a drive shaft supported to be rotated horizontally on the base plate unit and a plurality of cams coupled and rotated integrally therewith, and for adjusting a left and right inclination of the rocker plate unit by driving according to a signal related to a left and right inclination of the road surface of the virtual driving space and inputted from the outside. Thus, it is possible to impart a realistic driving feeling in a virtual driving space reality by implementing various driving environments and driving postures as if a user is actually driving.

PRESENTATION OF THE INVENTION

All ergometer systems mentioned above are based on the principle of positioning the user together with the training equipment used on a vibrating plate. All components used to support the trainee exert vibrational energy on the parts of the body or the corresponding body segments in contact with the components. This results in whole body vibrations (GKV or Whole Body Vibration "WBV"), some of which are above the permissible occupational medical limit values according to DIN ISO 2631. The resonance conflicts reduce the application duration with resulting (time-limiting) efficiency minimization. The constructive feature isolation of the MVT devices on the uniform neuromotoric stimulation of the intramuscular coordination, with a focus on the conditional force component, leads to a missing broad conditional-coordinative multifunctionality of the GKV. The MVT products of the state of the art only cover a selective part of the training therapy; a holistic training concept cannot be realized with these devices. A combination with conservative training equipment is obligatory (e.g. with cardio equipment in the warm-up/cool-down or additional mechanical resistance training).

The object of the present invention is to provide a mounting for an ergometer with a vibration unit, whereby an optimal mounting of the bottom bracket for the vibrations, for which both the amplitude and the frequency should be adjustable, is provided by the vibration essentially only in one, preferably vertical, direction acts, the amplitude of the vibration is essentially independent of the load of 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 bearing according to the invention in a vibration ergometer for the lower and upper extremities. The present invention accordingly relates to an ergometer, in particular a bicycle ergometer, with at least one pedaling device for a user and with a vibration unit according to claim 1.

In the main, the present invention relates to a bicycle ergometer. However, the concepts described here can be used analogously with an ergometer for the upper extremities, i. H. a hand ergometer. It is also possible to use the present invention with both crank devices in a combined bicycle and hand-held ergometer. If the proposed technology is used in a hand-held ergometer, then the bottom bracket used in the following is of course not a bottom bracket in the actual sense, but a crank bearing for such a hand-held ergometer, and the pedaling device mentioned below is then not a pedaling device, but a rotating device for the hands.

The invention is characterized in particular in that the bearing of the treadle device is pivotably mounted about a horizontal pivot axis, with the vibration about this pivot axis acting essentially only in one, preferably vertical, direction.

This storage allows the vibrations to be generated selectively around this horizontal pivot axis on the bottom bracket and then only act there.

According to a first preferred embodiment, a brake is arranged, preferably essentially 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. In addition, the bearing of the pedaling device is preferably pivotably mounted about a horizontal pivot axis arranged at the height of an axis of the brake.

In general, the pivot axis is preferably arranged horizontally.

The pivot axis bearing of the bearing can be given by a substantially fork-shaped construction, in which the fork ends of the arms are pivoted about the pivot axis, and the oppositely joined arms are connected to the bearing, preferably by the joined area having a bearing seat for the bearing of the pedal device forms.

Furthermore, the pivoting axis can preferably be arranged in such a way that the pivoting movement is essentially only permitted in the vertical direction at the location of the bearing. The vibration unit preferably has at least one main shaft which is driven directly or indirectly by a motor and has an eccentric disk attached thereto, the eccentric disk being rotatably coupled to a connecting rod.

Furthermore, the connecting rod preferably transmits the vibrations to the bearing of the pedal device with a connecting rod head arranged opposite the eccentric disc, so that the vibrations are essentially applied exclusively to this bearing in the vertical direction. Together with the bearing according to the invention, the vibrations can be optimally selectively placed on the bottom bracket.

A further preferred embodiment is characterized in that the vibration unit has at least one main shaft driven directly or indirectly by a motor with an eccentric disk attached thereto, the eccentric disk being rotatably coupled to a connecting rod, and the vibration unit being arranged below the bearing, and that the Connecting rod head is coupled directly to the bearing, preferably forms a bearing shell for the bearing, and the connecting rod bears substantially the entire vertically downward load on the bearing alone and without further guidance.

In general, preferably the axis of the main shaft is parallel to the axis of the bearing.

A further preferred embodiment is characterized in that the bearing of the pedal device is mounted in a vertical linear guide with a linear slide, the linear slide being fixedly connected to the bearing at the top and connected to the connecting rod head at the bottom, with the axis of the main shaft preferably being parallel to the Axis of the bearing runs.

A base plate can also be arranged, below which the main shaft and preferably also the motor is arranged and above which the pedaling device is arranged, wherein a recess can be provided in the base plate, through which the connecting rod passes and is coupled directly to the bearing with its connecting rod head is.

The vibration unit preferably has at least one main shaft which is driven directly or indirectly by a motor and has an eccentric disk attached thereto, the eccentric disk being rotatably coupled to a connecting rod, and the vibration unit being arranged below the brake, preferably above a floor plate, and preferably with the coupling of the connecting rod to the bearing is realized via at least one strut which runs obliquely upwards and connects the connecting rod head directly or indirectly to the bearing, and this strut is furthermore preferably rigidly connected to the pivot axis bearing. A further preferred embodiment is characterized in that the vibration unit has at least one main shaft driven directly or indirectly by a motor with an eccentric disk attached thereto, the eccentric disk being rotatably coupled to a connecting rod, and a further eccentric disk being arranged on the main shaft which a counterweight is placed in a compensating vibration, this further eccentric disc preferably being arranged on the main shaft with the eccentricity opposite to the eccentric disc for driving the connecting rod.

The further eccentric disc preferably drives a further connecting rod which is rotatably supported on the further eccentric disc and is coupled to a counterweight which is vibrated in substantially the same direction as the vibration device on the bearing, but with a vibration compensation on the bearing Effect, preferably by offsetting the vibration at the counterweight by 180° with respect to the vibration at the bearing.

A brake is arranged, preferably essentially 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 about a horizontal, preferably on the height of an axis of the brake is pivotably mounted, with the pivoting axis preferably being arranged in such a way that the counterweight in the region of the bearing executes the pivoting movement essentially exclusively in the vertical direction, with the counterweight preferably having a weight head in the region of the bearing, and Furthermore, this weight head preferably encompasses the storage area at least partially in the form of a fork at the top and bottom.

Instead of or in addition to such a compensation device with a counterweight, the vibrations on the components not actually vibrating to displacements 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 , for example provided by metal plates, sand containers, water containers and/or stone elements, which are provided, for example, in a frame that is mounted on the floor so that it can be adjusted in height. Such a frame can preferably be adjusted in height and/or leveled, if necessary even electrically, and moved to the desired location via rollers (for example, which can only be lowered for the purpose of moving). The plate can also contain damping elements, such damping elements are preferably provided in the corners of such a frame and/or the weight plate and/or damping mats can be used Support to be provided on the frame or on frame elements. Particularly suitable are 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. With such a construction, a mechanical high-pass filter can be provided, which largely prevents the vibrations both on the floor on which the device is standing and on components of the ergometer that are not intended to be set in vibration. In particular, the high-pass filter effectively filters out vibrations below 25 Hz, preferably below 20 Hz.

The vibrating unit can have at least one main shaft driven directly or indirectly by a motor with an eccentric disk attached thereto, the eccentric disk being rotatably coupled to a connecting rod, and the eccentric disk and/or an optionally present further eccentric disk on the main shaft along a direction perpendicular to the axis of rotation the main shaft is slidably and adjustably mounted, this mounting preferably being realized by a link guide, in which at least one adjusting element causes a displacement of the eccentric disc along a direction perpendicular to the axis of rotation of the main shaft when displaced along the axis of the main shaft.

The at least one adjusting element can be slidably mounted in a recess or passage opening in the main shaft via adjusting means, and a link in or on the adjusting element can adjust the eccentricity of the eccentric disc by interacting with a sliding block on the eccentric disc.

An eccentric disc for generating the desired vibration and another eccentric disc for the counterweight can also be mounted on the main shaft, and either an adjustment element can be provided with which the eccentricity of both eccentric discs can be adjusted offset by 180°, or two individual adjustment elements for the respective eccentric disc can be provided, via which the eccentricity of the discs can be adjusted individually.

Typically, such an ergometer is intended to be 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, preferably with a load in the range of 50 -500 W, especially in the range of 100-300 W.

The present invention further relates to the use of an ergometer as described above for therapeutic and/or form-building therapy, 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 can be set in stock. Further embodiments are specified in the dependent claims.

BRIEF DESCRIPTION OF THE DRAWINGS Preferred embodiments of the invention are described below with reference to the drawings, which are for explanation only and are not to be construed as limiting. In the drawings show:

1 essential elements of a vibration unit for an ergometer according to a first embodiment in an exploded view;

2 shows the vibration unit according to FIG. 1 in a sectional illustration in a) in a detailed section according to A in FIG. 2a) in b);

3 essential elements of a vibration unit for an ergometer according to a second embodiment in an exploded view;

FIG. 4 shows the vibration unit according to FIG. 3 in a sectional representation; FIG.

5 essential elements of a vibration unit for an ergometer according to a third embodiment in an exploded view;

FIG. 6 shows the vibration unit according to FIG. 5 in a sectional representation; FIG.

7 shows different arrangements of the vibration unit, in which a) shows an embodiment in which the bottom bracket is mounted directly from below by the connecting rod via a rocker, b) shows an embodiment in which the bottom bracket is mounted in a linear bearing without a rocker is, 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 on a rocker and a counterweight is provided;

FIG. 8 shows a side view of the embodiment according to FIG. 7b);

Fig. 9 views of an embodiment according to Figure 7c, wherein in a) for the better

Visualization of the individual elements the suspension is shown without a counterweight and in b) only the counterweight is shown;

10 different views of a further embodiment with a vibration unit coupled to the rocker and a counterweight, in a) the right side view, in b) the left side view, in c) view from above, in d) an exploded view, in e) a view are shown from diagonally above right and in f a view diagonally from below right. DESCRIPTION OF PREFERRED EMBODIMENTS FIG. 1 shows 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 engine can be either direct or indirect, for example via a V-belt. The motor is preferably a servomotor with a power in the range of 300-1,600 W. The main shaft 12 is structured and has an area on the left-hand side 40 in which it is supported by the bearings 11 mentioned. The two ball bearings 11 serve to support the main shaft 12 with the bearing housing 19 and prevent an axial displacement of the main shaft 12. A shoulder surface 12a follows on the right-hand side. This shoulder surface 12a prevents axial displacement of the eccentric disk 6 shown above on the right and thus of the entire connecting rod 1. The eccentric disk 6 is movably placed on the sliding surface 12b of the main shaft. The sliding cups 9 are positively held in the eccentric disc 6 and enable eccentric adjustment of the eccentric disc 6 from the axis of rotation 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 cups 9 and thus to the connecting rod 1. The eccentric disk 6 does not lie directly on the sliding surfaces 12b of the main shaft, but between them are the sliding shells 9, which, as shown here, can be made in two parts but also in one piece. The contact surfaces 41 on the inside of the eccentric disk 6 are correspondingly in contact with the outside of the sliding cups 9 and their contact surfaces 42 on the inside are in turn in contact with the sliding surface 12b of the main shaft 12.

The sliding shells 9 are preferably made of a material with sliding properties, for example 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.

The eccentric disc 6 has in its axial recess 43 a sliding block 5 which runs transversely to the axis and is inclined relative to the latter and 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 by the screws 7 . The fitted screws 7 fix the sliding block 5 in the eccentric disc 6 not only with a force fit but also with a form fit. A ball bearing is fastened with the bearing ring 3 on the eccentric disc 6 to support the connecting rod 1. To do this, the ball bearing with the bearing ring 3 is screwed to the eccentric disk 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 via 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. 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 arrangement 11 to the bearing housing 19 . The connecting rod head 1a is used to accommodate a bearing for the movable fixation with the linear unit or the rocker (see below).

A pin-shaped adjustment element 13 engages in an axial blind hole 38 of the main shaft 12 in a displaceable manner. The adjustment element 13 is positively and non-positively connected to the bearing mount 15 via the fitted screws 14 . The bearing mount 15 accommodates the bearing arrangement 16 in the form of two ball bearing rings. A trapezoidal thread nut 17 sits on this, which is mechanically (= non-rotatably) connected to the bearing housing 19 (not shown in FIG. 1). 1 shows 6 more bores for the screw connection to the bearing housing 19. The bearing arrangement 16 can be adjusted without play in the axial direction and is equipped with a shaft clamping nut 20 and a locking ring 21 (both not shown in FIG. 1, see FIG. 2). attached to 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. The trapezoidal spindle 18 does not rotate with the main shaft 12 as a result of the bearing arrangement 16. The adjusting element 13 is preferably made of a material with sliding properties, for example a plastic with sliding properties ( e.g. PTFE), and the sliding block

5 made of metal to achieve an optimal sliding pairing.

A connecting link opening in the form of a cutout surface 13a runs transversely in the adjustment element. This cut-out area has a width that is essentially the same as the thickness of the sliding block 5, but is much longer. When the adjustment element 13 is pushed into the blind hole 38, it is aligned with the larger opening 39. In other words, the sliding block 5 passes through the openings 39 and 13a. The cut-out surface 13a is therefore part of the adjustment element 13. The sliding block 5 is positioned in the cut-out surface 13a, and the deflection of the eccentric disc 6 is achieved via the planar surfaces of the sliding block 5 and the cut-out surface 13a of the adjustment element 13 in a form-fitting manner.

The eccentric disk 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 disk 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 is thus translated into a translation or oscillation at the connecting rod head 1a. The frequency of these oscillations is determined by the frequency of rotation of the main shaft 12, and hence the frequency of the motor driving that shaft. The amplitude of the oscillation can be adjusted by the trapezoidal spindle 18. The further the adjusting element 13 is pushed into the blind hole 31, the more the sliding block 5 becomes the eccentric disk

6 shifted from the axis of the main shaft 12, and the greater the amplitude of the Eccentricity and thus also the movement on the connecting rod 1a. The vibration generated at the connecting rod head 1a can thus be finely adjusted and controlled both in terms of frequency and in terms of amplitude. In addition, the connecting rod has a high mechanical stability and a very high directional stability, ie the vibrations generated in this way run exactly along the direction of the connecting rod, ie the proposed device allows quasi one-dimensional vibrations with an adjustable frequency and an adjustable amplitude along an exactly to generate a defined direction.

2 shows in a) the vibration unit in a sectional view through the axis of the shaft 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 a central mounting receptacle for the vibration unit. The bottom 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-hand bearing housing 19 for supporting the main shaft and, on the other hand, a right-hand bearing housing 19a for supporting the trapezoidal thread nut 17.

In the case of the right-hand bearing housing 19, the main shaft 12 is mounted via the bearings 11 already mentioned above, with a shaft clamping nut 20 being provided for fastening, which tightens the bearing arrangement 11 in order to minimize the axial and radial play of the main shaft 12. In addition, there is a locking ring 21 that prevents the shaft lock nut 20 from loosening unintentionally.

In Fig. 2, the bearing arrangement 11 is designed, for example, as an O-bearing arrangement. The application of force is outside of the bearing assembly 11. As a result, the radial and axial play of the main shaft 12 is adjusted.

In the present invention, the only desired vibration is a deflection of the connecting rod head 1a that is essentially perpendicular to the base plate.

3 shows an exploded view of a second exemplary embodiment of a vibration unit, this time with two eccentric discs 6 mounted on the same shaft the actual effective vibration for the user, and the other connecting rod serves to generate the counter-movement of the counterweight, which will be explained further below. The two eccentric disks 6 are arranged on the same main shaft 12, but there is now a separate sliding surface 12b for each eccentric disk 6 on the main shaft 12, and the adjusting element 13 has two correspondingly assigned cut-out surfaces 13a with opposite inclinations. In principle, however, the two eccentric discs 6 are analogous as already described in the first exemplary embodiment, is mounted on the main shaft 12 and its eccentricity is controlled by the adjusting element 13 . It is now important that the eccentricity of the two eccentric disks 6 is phase-shifted by 180°, which is ensured by the opposite inclination of the cut-out surfaces 13a and the corresponding opposite inclination of the two sliding blocks 5 of the respective eccentric disk 6. If the adjusting element 13 is actuated by actuating the trapezoidal spindle 18, which in this case is replaced by a retaining ring 23, which prevents the shaft clamping nut 22 from being loosened unintentionally, and a shaft clamping nut 22, which clamps the bearing arrangement 16 in the position receptacle 15, the trapezoidal threaded spindle 18 axially and To store radially free of play, is fixed, shifted in the recess 38 of the main shaft 12, so the one eccentric disc is shifted in a first direction and the other eccentric disc in the opposite direction of the main axis. This leads to a phase shift of the eccentricity of the two eccentric disks 6 by 180°, in a fully correlated manner, ie the adjustment by the single adjustment element 13 with the opposite inclinations of the cutout surfaces 13a automatically results in a phase shift of exactly 180° , regardless of the adjusted 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.

The second exemplary embodiment also differs from the first, among other things, in that the main shaft 12 is coupled somewhat differently. There is also a V-belt pulley 24 which serves to couple a servomotor to the main shaft via a V-belt. The V-belt pulley 24 is secured by a tension nut. For example in the form of a taper lock socket.

The second embodiment thus differs from the first embodiment in that it is possible to compensate for unwanted vibrations. The term unwanted vibrations is understood to mean, in particular, the vibration of the base plate 28 directed in the opposite direction to the desired vibration, as well as other vibrations not directed perpendicularly 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 structure, which cannot be statically compensated for due to the amplitude modulation of the stroke.

Fig. 4 shows the second embodiment in a sectional view, here you can see, among other things, how the two connecting rods are mounted parallel to each other via the two eccentric discs on the same main shaft 12 as on the left side V-belt pulley 24 protrudes for the coupling of a servomotor, and how on the right side the trapezoidal spindle for adjusting the eccentricity protrudes. It can thus be seen that an extremely compact structural solution is provided, in which the two connecting rods that absorb high loads are stably mounted.

In FIG. 4, the bearing surface of the connecting rod head bearing 26 is designed larger than the connecting rod head bearing 27 in order to absorb the higher forces occurring during operation under load (for example under the influence of body weight).

The adjusting element 13 lengthens the respective sliding blocks for the crank or for the counterweight in the opposite direction. The two eccentric disks must be rotated axially by 180° to each other so that they can be deflected in opposite directions. This offset arrangement of the eccentric disks 6 can be seen better in FIG.

5 shows a third exemplary embodiment of a vibration unit in an exploded view, which, in contrast to the second exemplary embodiment, is provided so that the eccentricity of the two connecting rods 1 or the associated eccentric discs can be adjusted individually for both. For this purpose, the main shaft 12 is no longer mounted on one side and is open on the other side for control via the adjusting element 13, but the main shaft is mounted at both ends, as can be seen in particular from FIG. 6, a sectional view the bearing rings 11. The main shaft is no longer designed with a blind hole, but with an axial through-opening, so that individual adjusting elements 13 for adjusting the eccentricity of each eccentric disk 6 can now be inserted from both sides. Correspondingly, there are trapezoidal spindles 18 on both sides, which control the respectively assigned adjustment element 13 . However, the two adjusting elements in FIG. 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. It is thus possible to fine-tune the vibration compensation by means of the counterweight and, in particular, to adjust it to ambient parameters or user parameters in such a way that the compensation is always optimally guaranteed.

The third embodiment thus differs from the second embodiment in that the amplitude of both connecting rods can be controlled independently of one another. According to this embodiment, unwanted oscillations can be compensated for by compensation. The main difference in terms of embodiment like. 3 and 4 is that the adjusting element 13 is formed in two parts. Both adjusting elements 13 require a separate O-bearing and control via motors. The left acme spindle 18 controls the deflection of the counterweight, the right acme spindle 18 controls the deflection of the crankshaft. In this embodiment, the main shaft 12 is driven centrally between the two connecting rods 1.

Incidentally, the compensation can be set manually, but it is also possible for the trapezoidal spindle or the several trapezoidal spindles to be controlled via an additional servomotor. It is thus possible, for example, to control such a servomotor in a controlled manner, for example via a vibration sensor or a plurality of vibration sensors, and a corresponding controller. In particular, it is also possible to regulate such a control in a self-learning algorithm in such a way that the vibrations measured by the vibration sensors are minimal where they should not occur (e.g. on the floor panel) and where they should occur ( for example at the bottom bracket) are maximum or exactly in the desired range.

6 is a sectional view of the exploded view 5. The length of the two adjusting elements 13 is different: FIG. 6 shows a stroke of the connecting rods of zero. In order to change the stroke, the right-hand adjusting element 13 is moved to the right and the left-hand adjusting element 13 is also moved to the right by rotating the trapezoidal spindle 18; this changes the deflection of the eccentric disks, which can be seen in FIG. 6 by the different position of the play of the sliding cups 9 (the right sliding cups show the play at the top, the left ones at the bottom).

FIG. 7 now shows different possibilities for arranging such a vibration unit on a (bicycle) ergometer.

A first possibility shown in FIG. 7b and also in FIG. 8 in a side view consists in arranging the vibration unit below a base plate 28 so that the connecting rod 1 passes through a recess in this base plate upwards in a vertical direction. The bottom bracket 29 of the ergometer is selectively slidably 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.

A construction is thus provided which selectively allows only vibrations in a strictly vertical direction, and the entire suspension and load of the vibration unit is taken over 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, such as a chain, belt, toothed belt.

With this construction it is possible to use a vibrating unit according to that described above use the first embodiment, ie with only a single connecting rod for the vibration at the bottom bracket. But it is also possible to use a vibration unit according to the second or according to the third embodiment. It is possible, as shown in Fig. 8, to mount a counterweight 36 phase-shifted by 180° in such a housing via an additional connecting rod, so that although the vibrations via the first connecting rod shown at the front in Figure 8 are transmitted in the desired frequency and amplitude to the Bottom bracket are transmitted, but that in relation to the environment and in particular, for example, the base plate 28, the vibrations are extinguished almost analogous to noise canceling. This is because in practice there are considerable problems 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 the corresponding legs connected to it transmit the vibrations to the floor and building, etc., but there are also unpleasant noise emissions due to the vibration of other components, such as the brakes in particular, etc. There are more Problems with vibration because such devices have a tendency to be shifted by the shaking and to sort of wander around. Last but not least, the vibrations cause mechanical damage to the device itself and the other components of the device, as well as other nearby devices to which the vibrations are unintentionally transmitted. Typically, such vibrations in the range of up to 50 Hz are suitable for this device. Low frequencies of 7-12 Hz with amplitudes in the range of up to 7-10 mm have proven to be particularly suitable for neurostimulation, typically in a load range of approx 100 W. Higher frequencies in the range of 15-25 Hz can also be used for athletes, for example, with typically somewhat lower vibration amplitudes of up to 3-4 mm. Then loads in the range of 200-300 W braking power are used. This means that the vibrations and amplitudes in a range that is mechanically critical for other components and the compensation by one or more counterweights are extremely important.

In FIG. 7 b , the crank bearing is thus fastened to a linear bearing 35 via a carriage 34 , 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 a movement directed exclusively perpendicularly to the base plate 28 results. The structure can also be implemented with a second connecting rod and a counterweight 36 as a second carriage on the linear guide to compensate for vibration.

A further possibility of providing such a vibration device on an ergometer is shown in FIG. 7a. Here, too, the connecting rod 1 is an im Strictly vertical running vibration (compare arrow) generated. However, the connecting rod 1 serves as the sole bearing for the bottom bracket in the vertical direction, so that an extremely slim construction is provided. In order to make this construction possible, there is now an additional rocker 32. This rocker 32 is a second bearing of the bottom bracket essentially around the axis 45 of the brake. The rocker 32 has two arms 46, a first arm 46' and a second arm 46". The two arms engage at different ends of the axle 45 on this axle and pivotally support the bottom bracket 29. Due to the fact that the axle of the Bottom bracket 29 and the axis of the brake 45 are arranged approximately at the same height, it is thus ensured that the rocker 32 allows mobility of the bottom bracket 29 on the bottom bracket in essentially only a vertical direction, so that the strictly vertical vibration is ensured If, for example, the brake is located closer to the base plate or substantially below the bottom bracket of such an ergometer, the rocker 32 should not be attached to the axis of the brake, but to a separate axle bearing approximately at the level of the bottom bracket, just to ensure that the bottom bracket only vertical vibrations are possible.

In Fig. 7a the center of the connecting rod head 1a is identical to the center of the crank bearing. The crank bearing is only supported by the connecting rod and the swing arm. All forces except those in the direction of the connecting rod are absorbed by the rocker. 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.

A further possibility of providing such a vibration device on an ergometer is shown in FIG. 7c. Here, the vibration device is placed below the brake and the bottom bracket is virtually free-floating. This creates a particularly compact and elegant design. The rocker 32 is in turn attached to the axle 45 of the brake and supports the bottom bracket 29 in such a way that it can only be moved in the vertical direction. The bottom bracket 29 is now supported in the vertical direction in this construction in that the rocker 32 has a strut which is directed obliquely downwards towards the vibration device and which is coupled to one of the two connecting rods of the vibration device via a connecting rod receptacle 37 . In other words, the rocker 32 includes a means for coupling the vibration of the vibrating device and the geometric design and the levers used ensure that the vibration, although it is applied to the device in an oblique direction on the connecting rod, at the bottom bracket in a strict vertical vibration is translated. Compare this in particular also Fig. 9a, in which this construction is shown, only the rocker 32 with the strut 46 being illustrated for better visibility.

7c thus shows a variant in which the vibration drive is not arranged below the ball bearing but outside the crank area. This eliminates components below the crankshaft, making a very compact design possible. The connecting rod is movably connected to the rocker at the connecting rod receptacle 37 of the rocker.

In such a construction, a corresponding counterweight 36 is advantageously mounted in a very similar manner and is controlled by the second connecting rod, which is phase-shifted by 180°. See in particular Fig. 9b, which shows this construction of the counterweight and omits the rocker arm for the bottom bracket. In this case, the counterweight 36, or rather the weight head 50 of the counterweight, is attached to the axle 45 of the brake via a first strut 47, similar to the swing arm. On the other hand, between the weight head 50 and a counterweight connecting rod seat 37a, there is another strut 49 directed downwards, and a third strut 48 which brings the counterweight connecting rod seat to the axis 45 of the brake for the necessary to ensure storage stability. The counterweight, in particular its weight head 50, is thus optimally space-saving and nevertheless arranged in an excellent manner between the two arms 46' and 46" of the rocker, and can also provide the optimal compensation effect there.

A further exemplary embodiment of an ergometer is illustrated in FIG. The components corresponding to those described above are denoted by the same reference numerals. In this embodiment, the rocker is designed with multiple struts on both sides, including additional vertical struts and horizontal struts. In principle, however, the connection to the connecting rod 1 is analogous to that described above in connection with FIGS. 7 and 9. The counterweight is also mounted similarly, here the weight head 50 is constructed as a layered body, which makes it possible to also attach to the mass of the weight head, if necessary make adjustments on site by adding more layers. Furthermore, the weight head 50 is designed as it were as a fork, the arms of which at least partially encompass the bottom bracket 29 at the top and bottom. In this way, the counterweight can be arranged as close as possible and in the region of the bottom bracket, so that the vibration can be optimally compensated. The counterweight is mounted here via a mounting body 47, which is also designed with a plurality of struts, and is in turn coupled to the vibration unit via the connecting rod receptacle 37a for the counterweight. To a certain extent, this mounting body penetrates the struts of the swingarm and is thus optimally stored in a space-saving and compact manner. Also recognizable in this embodiment is the servomotor 52 with the associated V-belt 51 for setting the trapezoidal thread nut and correspondingly for setting the eccentricity and the associated amplitude of the vibration. The motor 54 for driving the main shaft 12 and the corresponding V-belt 53 can also be seen.

REFERENCE LIST

1 Connecting rod 22 Shaft clamping nut r Connecting rod for counterweight 23 Circlip

1a connecting rod head 24 V-belt pulley

2 bolts 25 tension nut

3 bearing ring 26 connecting rod bearing

4 ball bearings 27 connecting rod bearings

5 sliding block 28 floor plate

6 eccentric disc 29 crank bearing 6 eccentric disc for 30 brake

Counterweight 31 power transmission element

7 fitting bolts 32 swingarm

8 clamping ring 33 crank

9 slide shells 34 linear slides

10 screws 35 linear guide 11 bearing arrangement 36 counterweight 12 main shaft 37 connecting rod seat swing arm 12a shoulder surface 37a connecting rod seat 12b sliding surface counterweight

13 adjusting element 38 axial blind hole in 12 13a cutout area 39 radial through-opening

14 fitting screws 40 fastening area of 12

15 bearing mount 41 contact surfaces from 6 to 9

16 bearing arrangement 42 contact surfaces from 9 to 12b

17 trapezoidal thread nut 43 recess in 6

18 trapezoidal spindle 44 recess in 28 for 1

19 Left bearing housing 45 Axle of the brake 19a Right bearing housing 46 Strut of 32

20 Shaft Locking Nut 46', 46" Arms of 32 21 Retaining Ring 47 Weight Strut to Axle brake 51 V-belt for actuation of weight strut from trapezoidal nut axis of brake to 52 motor for actuation of connecting rod receptacle of trapezoidal thread nut via counterweight 51 weight strut of 53 V-belt for drive motor connecting rod receptacle of main shaft 12 counterweight to 54 motor for driving weight head main shaft 12 weight head

Claims

PATENT CLAIMS

1. Ergometer, in particular bicycle ergometer, with at least one pedaling device for a user and with a vibration unit, characterized in that the bearing (29) of the pedaling device is pivotably mounted about a horizontal pivot axis (45).

2. Ergometer according to claim 1, characterized in that a brake (30) is arranged essentially at the same height as the pedaling device, which brake (30) is arranged via a power transmission element (31), preferably in the form of a chain, a toothed belt or a V-belt. is coupled to the pedaling device, and wherein the bearing (29) of the pedaling device is mounted pivotably about a horizontal pivoting axis arranged at the height of an axis (45) of the brake (30), the pivoting axis (45) preferably being arranged horizontally.

3. Ergometer according to one of the preceding claims, characterized in that the pivot axis mounting of the bearing (29) is given by an essentially fork-shaped construction, in which the fork ends of the arms (46', 46") are preferably mounted rotatably about the pivot axis, and the opposed joined arms are connected to the bearing (29), preferably in that the joined area forms a bearing seat for the bearing (29) of the pedal device.

4. Ergometer according to one of the preceding claims, characterized in that the pivot axis (45) is arranged such that at the location of the bearing (29) the pivoting movement is essentially exclusively permitted in the vertical direction.

5. Ergometer according to one of the preceding claims, characterized in that the vibration unit has at least one directly or indirectly driven by a motor (54) main shaft (12) with an eccentric disc (6) attached thereto, the eccentric disc (6) being rotatable on a Connecting rod (1) is coupled, and that the connecting rod (1) transmits the vibrations to the bearing (29) of the pedal device with a connecting rod head (1a) arranged opposite the eccentric disc (6), so that the vibrations are essentially exclusively at this bearing (29) in vertical direction.

6. Ergometer according to one of the preceding claims, characterized in that the vibration unit has at least one directly or indirectly driven by a motor (54) main shaft (12) with an eccentric disc (6) attached thereto, the eccentric disc (6) being rotatable on a Connecting rod (1) is coupled, and that the vibration unit is arranged below the bearing (29), and that the connecting rod head (1a) is coupled directly to the bearing (29), preferably forming a bearing shell for the bearing (29), and that the connecting rod (9) carries essentially the entire vertical downward load on the bearing (29) alone and without further guidance, the axis of the main shaft (12) preferably running parallel to the axis of the bearing (29), or characterized in that the bearing (29) of the pedal device is mounted in a vertical linear guide (35) with a linear carriage (34), the linear carriage (34) being fixedly connected to the bearing (29) at the top, and un th is connected to the connecting rod head (1a), the axis of the main shaft (12) preferably running parallel to the axis of the bearing (29).

7. Ergometer according to claim 6, characterized 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 pedaling device is arranged, with the base plate (28) having a recess (44) is provided, through which the connecting rod (1) passes and is coupled directly to the bearing (29) with its connecting rod head (1a).

8. Ergometer according to one of the preceding claims 2-7, characterized 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 thereto, the eccentric disc (6) is rotatably coupled to a connecting rod (1), and that the vibration unit is arranged below the brake (30), preferably above a base plate (28), and wherein preferably the coupling of the connecting rod (1) to the bearing (29) via at least one strut (46) running obliquely upwards and connecting the connecting rod head (1a) directly or indirectly to the bearing (29) is realized, and this strut (46) is preferably rigidly connected to the pivot axis bearing.

9. Ergometer according to one of the preceding claims, characterized characterized 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 and/or that the vibration unit has at least one main shaft (12) driven directly or indirectly by a motor (54) with an eccentric disk (6) attached thereto, the eccentric disk (6) being rotatably coupled to a connecting rod (1), and a further eccentric disk (6') being arranged on the main shaft (12), with which a counterweight (36 ) is set into a compensating vibration, with this further eccentric disk (6') preferably being arranged on the main shaft (12) with the eccentricity opposite to the eccentric disk (6) for driving the connecting rod, with the further eccentric disk (6') also preferably having a further connecting rod (1 ') drives, which is rotatably mounted on the further eccentric disc (6') and is coupled to a counterweight (36) that essentially chen in the same direction as the vibrating device on the bearing (29), but with a compensating effect on the vibration on the bearing (29), preferably by causing the vibration on the counterweight (36) to rotate 180° with respect to the vibration on the bearing (29 ) is offset.

10. Ergometer according to Claim 9, characterized in that a brake (30) is arranged, preferably essentially at the same level as the pedaling device, which brake (30) via a power transmission element (31), preferably in the form of a chain, a toothed belt or a V-belt , is coupled to the pedaling device, and the counterweight (36) is mounted pivotably about a horizontal pivot axis bearing, preferably arranged at the level of an axis (45) of the brake (30), the pivot axis (45) preferably being arranged such that the counterweight (36) in the area of the bearing (29) performs the pivoting movement essentially exclusively in the vertical direction, with the counterweight (36) preferably having a weight head (50) in the area of the bearing (29), and further preferably this weight head (50) surrounds the storage area at least partially in the form of a fork at the top and bottom.

11. Ergometer according to one of the preceding claims, characterized in that the vibration unit has at least one directly or indirectly driven by a motor (54) main shaft (12) with an eccentric disc (6) attached thereto, the eccentric disc (6) being rotatable on a connecting rod (1) is coupled, and the eccentric disk (6) and/or a further eccentric disk (6'), if present, is mounted on the main shaft (12) in a displaceable and adjustable manner along a direction perpendicular to the axis of rotation of the main shaft (12), wherein this bearing is preferably realized by a link guide (5,13a), in which at least one adjustment element (13) causes a displacement of the eccentric disc (6) along a direction perpendicular to the axis of rotation of the main shaft when displaced along the axis of the main shaft (12).

12. Ergometer according to claim 11, characterized in that the at least one adjusting element (13) is mounted in a recess (38) or passage opening in the main shaft (12) so that it can be displaced in an adjustable manner via adjusting means (18), and a link (13a) in or adjusts the eccentricity of the eccentric disc (6) on the adjusting element by interacting with a sliding block (5) on the eccentric disc (6).

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

14. Ergometer according to one of the preceding claims, characterized in that for operation at a frequency of 1-50 Hz with a vibration amplitude on 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 for therapeutic and/or form-building therapy, preferably with 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 on the bearing (29) can be adjusted.