EP4304744A1

EP4304744A1 - Compensation device for an ergometer having a vibration unit, and use thereof in a vibration ergometer for the upper and lower limbs

Info

Publication number: EP4304744A1
Application number: EP22709728.4A
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: WO2022189252A1

Abstract

The invention relates to a bicycle ergometer comprising at least one pedal device for a user and comprising a vibration unit, characterised in that the vibration unit vibrates the pedal device and the ergometer has, in addition to the vibration unit, a compensation device which at least partially compensates, by means of negative interference, the vibrations from the vibration unit outside of the pedal device.

Description

TITLE

COMPENSATION DEVICE 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 a compensation device for 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.

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

DE 196 39 477 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.

US-A-2015045190 discloses an eccentric idler pulley in a stationary exercise bike. The exercise bike may include an eccentric driver or driven shaft that rotates a belt or chain. The idler pulley is coupled to the exercise bike and is configured to rotate eccentrically in contact with the belt or chain. The exercise bike of various embodiments is configured to produce a reciprocating motion, providing users with a vibrant exercise experience. A motor for the vibration is not mentioned. The vibration is generated by the pedaling movement, so no vibration independent of the cadence is disclosed.

WO-A-2009024877 discloses an exercise assembly having a stationary frame with a seat and a handle for a user attached to the frame. At least one flywheel is rotatably mounted to the frame and is supported by a flexible drive member having at least one pedal operatively connected to a crankshaft. Vibration means are connected to the flywheel and/or the crankshaft, suitable to impart vibrations to the user. There is no compensation unit in this construction, the "electromechanical actuation means 24" described are not a counterweight, but a chain tensioner.

US-A-2011152040 shows an exercise system for exercising a body part of a user, comprising a frame for positioning the exercise system in use on a surface, a bicycle device comprising at least one bicycle element configured to rotate about a bicycle axis, a vibration device for moving at least one cycling element as vibration and also a method and use of the training system. There is no compensation unit in this construction.

GB-A-2139513 shows a bicycle having a frame with pedals, a seat post and a handlebar support, the latter being mounted for pivotal movement about a horizontal axis and also having a mechanism selectively connectable to the support to give it a to impart a rocking or vibrating motion. The mechanism includes a polygonal plate releasably engageable with a bearing mounted on an extension of the beam, the polygonal plate being rotatable via the pedals. In order for vibration or rocking to take place, the bearing must touch the perimeter of the plate, but a pin is provided between the slots in the plates to prevent this. The pin is pushed to the bottom of the slots by a spring, but can be pulled up by a cable operated from the handlebars. Instead of a direct connection to the pen, the cable can also be connected to it via a lever. Each leg of the struts may comprise telescopically coupled hollow housings between which is located a compression spring. Here, too, the vibration is generated by the pedal crank, similar to US-A-2011152040. There is no motor for generating vibrations, nor is there a compensation device.

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 exceed the permissible occupational medical limit values according to DIN ISO 2631 stand. 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). Problems also arise from the fact that the significant vibrations not only lead to undesirable effects on the device and the user, but also in the environment and that the devices tend to move around in the rooms due to the vibrations if they are not fixed be screwed or otherwise fastened.

The object of the present invention is to provide an improvement in the vibration for an ergometer with a vibration unit, for which purpose a compensation device is provided which nevertheless ensures optimal mounting of the bottom bracket for the vibrations, with preferably both the amplitude and the frequency of the unit being coordinated that of the vibration unit is adjustable, and wherein the vibration acts essentially in one, preferably vertical, direction, 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 compensation device according to the invention in a vibration ergometer for the lower and upper extremities.

Specifically, the present invention 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, ie a hand-held 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. According to the invention, such a device is preferably characterized in that the vibration unit causes the treadle device to vibrate and the ergometer has a compensation device in addition to the vibration unit, which at least partially compensates for the vibrations of the vibration unit outside the treadle device by negative interference.

The problems mentioned above are largely solved by this selectively applied compensation vibration of the compensation device, which cancels the vibration of the vibration device in the correspondingly desired areas.

Such an ergometer is preferably further characterized in that the compensating device generates vibrations having the same frequency and substantially the same amplitude as the vibrations of the vibrating unit, with a phase shift of substantially 180°. In this way, said negative interference, i.e. H. the elimination of the vibrations at the undesired places.

A common motor, preferably a common shaft driven by a common motor, preferably generates both the vibrations of the vibration unit and the vibrations of the compensation device.

A preferred embodiment of the proposed ergometer 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 further preferably the connecting rod having a Eccentric disc oppositely arranged connecting rod transmits the vibrations to the bearing of the pedal device, so that the vibrations are applied essentially exclusively to this bearing in the vertical direction.

The vibrating unit can have at least one main shaft driven directly or indirectly by a motor with an eccentric disc attached thereto, the eccentric disc being rotatably coupled to a connecting rod.

A further eccentric disk is preferably arranged on the main shaft, with which a counterweight is set into a compensating vibration, this further eccentric disk preferably being arranged on the main shaft with the eccentricity opposite to the eccentric disk for driving the connecting rod.

The further eccentric disc can drive a further connecting rod which is rotatably mounted on the further eccentric disc and is coupled to a counterweight which is made to vibrate in substantially the same direction as the vibration device on the bearing, but with a vibration on the bearing compensating Effect, preferably by offsetting the vibration at the counterweight by 180° from the vibration at the bearing.

A further preferred embodiment is characterized in that 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 is mounted so as to be pivotable about a horizontal pivot axis bearing, preferably arranged at the height of an axis of the brake.

The pivoting axis is preferably arranged in such a way that the counterweight in the area of the bearing performs the pivoting movement essentially exclusively in the vertical direction, with the counterweight preferably having a weight head in the area of the bearing, and this weight head also preferably enclosing the bearing area at least partially in the form of a fork at the top and bottom . The vibrating unit may be located below the bearing and the connecting rod head coupled directly to the bearing, preferably forming a bearing shell for the bearing, and the connecting rod bearing substantially all of the vertically downward load on the bearing alone and without further Guide wears, preferably the axis of the main shaft is parallel to the axis of the bearing.

The bearing of the pedal device can also be mounted in a vertical linear guide with a linear carriage, the linear carriage being fixedly connected to the bearing at the top and to the connecting rod head at the bottom, with the axis of the main shaft preferably running parallel to the axis of the bearing.

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

A further preferred embodiment is characterized in that a brake is again arranged, preferably essentially at the same height as the pedaling device, which is coupled to the pedaling device via a power transmission element, preferably in the form of a chain, a toothed belt or a V-belt , and wherein the bearing of the pedal device is pivotably mounted about a horizontal pivot axis, preferably arranged at the level of an axis of the brake, the pivot axis preferably being arranged such that at the location of the bearing the pivoting movement is essentially exclusively permitted in the vertical direction.

The ergometer can also be characterized in that the pivot axis bearing of the bearing by a substantially fork-shaped Construction is given in which the fork ends of the arms are rotatably mounted about the pivot axis, and the opposite merged arms are connected to the bearing, preferably in that the merged area forms a bearing seat for the bearing of the pedal device.

The vibration unit can be arranged below this brake, preferably above a base plate, and preferably the coupling of the connecting rod to the bearing can be implemented via at least one strut running obliquely upwards and connecting the connecting rod head directly or indirectly to the bearing. Such a strut is preferably rigidly connected to the pivot axis bearing.

Furthermore, it is preferred that the compensation device comprises a counterweight, in particular with a weight head, which is preferably arranged in the area of the bearing of the pedal device, and also preferably partially encompasses this bearing without touching it, and which vibrates in the opposite direction to that generated by the vibration unit Vibration at the bearing is offset.

The eccentric disc and/or an additional eccentric disc that may be present can be slidably and adjustably mounted on the main shaft in a direction perpendicular to the axis of rotation of the main shaft, with this mounting preferably being realized by a slotted guide, in which at least one adjustment element can be moved along the axis of the main shaft causes displacement of the eccentric disc along a direction perpendicular to the axis of rotation of the main shaft.

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

Furthermore, it is preferred if an eccentric disc for generating the desired vibration and another eccentric disc for the counterweight are mounted on the main shaft, and either an adjusting element is provided with which the eccentricity of both eccentric discs can be adjusted offset by 180°, or that two individual adjusting elements are provided for the respective eccentric disc, via which the eccentricity of the discs can be adjusted individually.

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 100-300 W range.

Furthermore, the present invention relates to the operation or use of a Ergometer as described above 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 be placed 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 shows different views of a further embodiment with a vibration unit coupled to the rocker arm and a counterweight, in a) the right-hand side view, in b) the left-hand side view, in c) 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 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 over the screws 2 with the eccentric disc screwed. 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 is made of metal in order to achieve an optimal sliding pairing.

A connecting link opening in the form of a cutout surface 13a runs transversely in the adjusting 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 eccentric disc 6 is displaced 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 on the Big end 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 discs 6 are arranged on the same main shaft 12, but there are now a separate sliding surface 12b for each eccentric disk 6 on the main shaft 12, and the adjustment element 13 has two correspondingly assigned cut-out 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 exemplary embodiment, and their 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, it is structurally ensured 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 for 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 one another via the two eccentric discs on the same main shaft 12, and how the V-belt pulley 24 for coupling a servo motor protrudes on the left-hand side , and how the trapezoidal spindle for adjusting the eccentricity protrudes on the right-hand side. 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. 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 the vibrating unit according to the first embodiment described above, i. H. 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 expanded with a second connecting rod and a counterweight 36 as a second carriage on the linear guide implement vibration-compensating.

A further possibility of providing such a vibration device on an ergometer is shown in FIG. 7a. Here, too, the connecting rod 1 generates a vibration (compare arrow) running essentially strictly in the vertical direction. 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 swingarm. 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 comprises a means for coupling the vibration of the vibration device and the geometric configuration and the levers used ensure that the vibration, although applied to the device in an oblique direction on the connecting rod, is translated into a strictly vertical vibration at the bottom bracket. Compare 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. Here, the counterweight is mounted, in turn coupled, via a mounting body 47, which is also designed with a plurality of struts via connecting rod receptacle 37a for the counterweight to the vibrating unit. 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 19a Right bearing housing

1 connecting rod for counterweight 20 shaft clamping nut

1a connecting rod head 21 circlip

2 bolts 22 shaft lock nut

3 bearing ring 23 snap ring

4 ball bearing 24 V-belt pulley

5 sliding block 25 clamping nut

6 eccentric disc 26 connecting rod bearing 6 eccentric disc for 27 connecting rod bearing counterweight 28 bottom plate

7 fitting bolts 29 crank bearings

8 clamping ring 30 brake

9 sliding shells 31 power transmission element

10 bolts 32 swing arm 11 bearing assembly 33 crank 12 main shaft 34 linear slide 12a shoulder surface 35 linear guide 12b sliding surface 36 counterweight

13 Adjusting element 37 connecting rod seat, rocker 13a Cutout area 37a connecting rod seat

14 counterweight fitting bolts

15 bearing seat 38 axial blind hole in 12

16 bearing assembly 39 radial through hole

17 trapezoidal nut 40 fastening area of 12

18 Trapezoidal spindle 41 Contact surfaces from 6 to 9 19 Left bearing housing 42 Contact surfaces from 9 to 12b Recess in 6 counterweight to recess in 28 for 1 weight head brake axis 50 weight head strut from 32 51 V-belt for actuation of ', 46" arms from 32 trapezoidal nut weight strut to axis 52 motor for actuation of brake trapezoidal nut over weight strut from 51 axis of the brake to 53 V-belt for drive motor connecting rod mount of the main shaft 12 counterweight 54 motor for drive of weight strut of the main shaft 12 connecting rod mount of

Claims

PATENT CLAIMS

1. Ergometer, in particular a bicycle ergometer, with at least one pedaling device for a user and with a vibration unit, characterized in that the vibration unit causes the pedaling device to vibrate and the ergometer has a compensation device in addition to the vibration unit, which compensates for the vibrations of the vibration unit outside of the Pedal device at least partially compensated by negative interference.

2. Ergometer according to claim 1, characterized in that the compensating device generates vibrations having the same frequency and essentially the same amplitude as the vibrations of the vibration unit, with a phase shift of essentially 180°.

3. Ergometer according to one of the preceding claims, characterized in that a common motor (54), preferably a common motor driven by a common shaft (12) generates both the vibrations of the vibration unit and the vibrations of the compensation device.

4. 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 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 preferably on the main shaft (12) a further eccentric disc (6 ') is arranged, with which a counterweight (36) is offset in a compensation vibration, wherein preferably this further eccentric disk (6') is arranged on the main shaft (12) with the eccentricity opposite to the eccentric disk (6) for driving the connecting rod.

6. Ergometer according to claim 5, characterized in that the further eccentric disc (6') drives a further connecting rod (T) which is rotatably mounted on the further eccentric disc (6') and is coupled to a counterweight (36) that in Substantially in the same direction as the vibrating device is set to vibrate 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.

7. Ergometer according to one of the preceding claims 5-6, characterized in that a brake (30) is arranged, preferably essentially at the same height as the pedal device, which brake (30) is arranged via a force 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 height of an axis (45) of the brake (30), the pivot axis (45) preferably being so is 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.

8. Ergometer according to one of the preceding claims and claim 5, characterized in 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 a bearing shell for the bearing (29) and that the connecting rod (9) bears substantially the entire vertically downward load on the bearing (29) alone and without further guidance, preferably with the axis of the main shaft (12) being parallel to the axis of the bearing (29 ) runs or 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 firmly connected to the bearing (29) at the top and to the connecting rod head ( 1a) is connected, the axis of the main shaft (12) preferably running parallel to the axis of the bearing (29), preferably a base plate (28) is arranged, below which the main shaft (12) and preferably also the motor is arranged and above which the pedal device is arranged, wherein a recess (44) is provided in the base plate (28) through which the Connecting rod (1) passes through and is coupled directly to the bearing (29) with its connecting rod head (1a).

9. Ergometer according to one of the preceding claims, characterized in that, preferably essentially at the same height as the pedaling device, a brake (30) is arranged, which has 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 pivotably mounted about a horizontal pivoting axis, preferably arranged at the height of an axis (45) of the brake (30), the pivoting axis (45) preferably being positioned so is arranged such that at the location of the bearing (29) pivoting movement is essentially exclusively permitted in the vertical direction, preferably further characterized in that the pivot axis 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 joined arms with d em bearing (29), preferably in that the combined area forms a bearing mount for the bearing (29) of the pedal device and/or characterized in that the vibration unit is arranged below this brake (30), preferably above a base plate (28), and wherein the connecting rod (1) is preferably coupled 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), and further preferably this strut (46) is rigidly connected to the pivot axis bearing.

10. Ergometer according to one of the preceding claims, characterized in that the compensation device comprises a counterweight (36), in particular with a weight head (50), which is preferably arranged in the region of the bearing (29) of the pedaling device, and further preferably partially this bearing embraces it without touching it, and which vibrates in the opposite direction to the vibration generated by the vibration unit on the bearing (29).

11. Ergometer according to one of the preceding claims, characterized characterized in that the eccentric disc (6) and/or a further eccentric disc (6') that may be present is mounted on the main shaft (12) so that it can be displaced and adjusted in a direction perpendicular to the axis of rotation of the main shaft (12), this mounting preferably being supported by a link guide (5,13a) in which at least one adjustment element (13) causes 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 adjusted and displaced via adjusting means (18), and a link (13a) in or adjusts the eccentricity of the eccentric disc (6) on the adjustment 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.