Compensation device for a dynamometer with vibration unit and its use in a vibrating dynamometer for the lower and upper extremities

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

TECHNICAL AREA

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

[0002] To positively and efficiently influence the individual performance structure of rehabilitation / geriatric patients or competitive athletes, it is necessary to transform as many dosed external training stimuli as possible in a balanced way, adapted to the different structural levels of the human organism. Both conditioning (strength, endurance, speed, flexibility) and coordinative (neuromotor) components should be considered in the application spectrum of the training methods.

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

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

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

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

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

[0008] German patent DE 196 39 477 A1 discloses a device comprising a seat, a handle, and a vibration unit that applies vibrations to the user's feet. The use of these five devices in conjunction with or as an ergometer, for example via a brake unit connected to the crankshaft, is not disclosed, and details of how the vibrations are generated are usually not provided.

[0009] From DE 103 13 524 B3 a training device is known in which one or more contact points to the trainee that can be subjected to vibrations are mechanically isolated by one or more damping elements, so that all assemblies for supporting the body parts of the user are set into vibration.

[0010] A vibration ergometer is known from WO 2006 / 69988 A1, in which a bottom bracket is rigidly connected to a vibration plate, which is set into oscillation by two counter-rotating vibration motors. A disadvantage is that an omnidirectional vibration is generated, the amplitude of which decreases depending on the mechanical load on the crank or the setting of the ergometer brake. The connection between the crank and the ergometer brake is only possible via a bicycle chain with a chain tensioner to compensate for the differences in length and position between the bottom bracket and the ergometer. This results in unpleasant noises, and additional safety measures are necessary to prevent the chain from jumping off the front chainring.

[0011] EP 2 158 944 A2 describes a vibration ergometer with amplitude-variable vibration. How the vibration is specifically generated and how this amplitude change is to be implemented is not disclosed therein.

[0012] US patent application 2015045190 discloses an eccentric tension pulley in a stationary exercise bike. The exercise bike may include an eccentric driver or a driven shaft that rotates a belt or chain. The tension pulley is coupled to the exercise bike and configured to rotate eccentrically in contact with the belt or chain. The exercise bike, in its various embodiments, is configured to generate a reciprocating motion, providing users with a vibrating exercise experience. A motor for the vibration is not mentioned; the vibration is generated by the pedaling motion, thus no vibration independent of cadence is disclosed.

[0013] WO-A-2009024877 discloses an exercise apparatus with a stationary frame, including a seat and a handle for a user attached to the frame. At least one flywheel is rotatably mounted on the frame and operatively connected to a crankshaft via a flexible drive element with at least one pedal. Vibration means are connected to the flywheel and / or the crankshaft, capable of exerting vibrations on the user. This design does not include a compensation unit; the described "electromechanical actuation means 24" are not a counterweight but a chain tensioner.

[0014] US Patent 2011152040 discloses a training system for exercising a user's body part, comprising a frame for positioning the training system on a surface during use, a bicycle device comprising at least one bicycle element configured to rotate about a bicycle axle, a vibration device for moving at least one bicycle element as a vibration, and also a method and use of the training system. There is no compensation unit in this design.

[0015] GB-A-2139513 shows a bicycle with a frame including pedals, a seat post, and a handlebar support, the latter being mounted for pivoting about a horizontal axis. A mechanism is also provided which can be optionally connected to the support to impart a rocking or vibrating motion. The mechanism includes a polygonal plate that can be detachably engaged with a bearing mounted on an extension of the support, the polygonal plate being rotatable via the pedals. For vibration or rocking to occur, the bearing must contact the circumference of the plate, but a pin is provided between the slots in the plate to prevent this. The pin is pushed towards the lower ends of the slots by a spring but can be pulled up by means of a cable operated from the handlebar.Instead of a direct connection to the pin, the cable can also be connected to it via a lever. Each foot of the supports can comprise telescopically coupled hollow housings, between which a compression spring is located. Here, too, the vibration is generated by the pedal crank, similar to US-A-2011152040. There is no motor for generating vibration, nor is there a compensation device. PRESENTATION OF THE INVENTION

[0016] All the aforementioned ergometer systems are based on the principle of positioning the user, along with the training device, on a vibration platform. All components used to support the user exert vibrational energy on the body parts or corresponding body segments in contact with these components. This results in whole-body vibration (WBV), which in some cases exceeds the occupational health limits permitted according to DIN ISO 2631. Resonance conflicts reduce the duration of use, resulting in a (time-limiting) reduction in efficiency. The design of multi-functional training devices (MVT) that isolates the user's characteristics to the uniform neuromotor stimulation of intramuscular coordination, focusing on the conditioning component of strength, leads to a lack of broad conditioning and coordinative multifunctionality within the WBV.State-of-the-art MVT products cover only a selective aspect of training therapy; a holistic training concept cannot be implemented with these devices. A combination with conventional training equipment is mandatory (e.g., with cardio equipment during warm-up / cool-down or supplementary mechanical resistance training). Additional problems arise because the significant vibrations not only cause undesirable effects on the device and the user, but also in the surrounding environment. Furthermore, the devices tend to move around the room due to the vibrations if they are not securely bolted or otherwise fixed in place.

[0017] The object of the present invention is to provide an improved vibration for an ergometer with a vibration unit, wherein a compensation device is provided which nevertheless ensures optimal bearing of the bottom bracket for the vibrations, wherein preferably both the amplitude and the frequency of the unit are adjustable in coordination with that of the vibration unit, and wherein the vibration acts essentially in one direction, preferably vertical, the amplitude of the vibration is essentially independent of the load on the vibration unit, and vibration frequencies of up to 50 Hz are achievable. 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.

[0018] 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.

[0019] The present invention primarily relates to a bicycle ergometer. However, the concepts described here can be applied analogously to an ergometer for the upper extremities, i.e., a hand ergometer. It is also possible to implement the present invention in a combined bicycle and hand ergometer with both crank mechanisms. If the proposed technology is used in a hand ergometer, the bottom bracket described below is not a bottom bracket in the strict sense, but rather a crank bearing for such a hand ergometer, and the pedaling device described below is not a pedaling device, but a rotating device for the hands.

[0020] According to the invention, such a device is characterized in that the vibration unit sets the pedaling device into vibration and the ergometer has, in addition to the vibration unit, a compensation device that at least partially compensates the vibrations of the vibration unit outside the pedaling device by means of negative interference.

[0021] The above-mentioned problems are largely solved by this selectively applied compensation vibration of the compensation device, which eliminates the vibration of the vibration device in the desired areas.

[0022] Such an ergometer is characterized in that the compensation device generates vibrations that have the same frequency and essentially the same amplitude as the vibrations of the vibration unit, with a phase shift of essentially 180°. In this way, the aforementioned negative interference, i.e., the cancellation of the vibrations at the unwanted points, is achieved.

[0023] Preferably, a common motor, or preferably a common shaft driven by a common motor, generates both the vibrations of the vibration unit and the vibrations of the compensation device.

[0024] 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 disc attached thereto, wherein the eccentric disc is rotatably coupled to a connecting rod, and furthermore preferably the connecting rod transmits the vibrations to the bearing of the pedaling device with a connecting rod head arranged opposite the eccentric disc on its connecting rod head, so that the vibrations are essentially exclusively transmitted to this bearing in a vertical direction.

[0025] The vibration unit can have at least one main shaft driven directly or indirectly by a motor with an eccentric disc attached to it, wherein the eccentric disc is rotatably coupled to a connecting rod.

[0026] Preferably, a further eccentric disc is arranged on the main shaft, with which a counterweight is set into a compensating vibration, wherein preferably this further eccentric disc is arranged on the main shaft with an eccentricity opposite to that of the eccentric disc for driving the connecting rod.

[0027] The further eccentric disc can drive another connecting rod, which is rotatably mounted on the further eccentric disc and is coupled to a counterweight, which is set into vibration in essentially the same direction as the vibration device at the bearing, but with an effect compensating for the vibration at the bearing, preferably by offsetting the vibration at the counterweight by 180° relative to the vibration at the bearing.

[0028] Another preferred embodiment is characterized in that, preferably at essentially the same height as the pedaling device, a brake is arranged 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 the counterweight is pivotably mounted about a horizontal pivot bearing, preferably arranged at the height of an axis of the brake.

[0029] Preferably, the pivot axis is arranged such that the counterweight in the bearing area performs the pivoting movement essentially exclusively in the vertical direction, wherein the counterweight preferably has a weight head in the bearing area, and further preferably this weight head at least partially fork-shaped around the bearing area from above and below.

[0030] The vibration unit can be arranged below the bearing, and the connecting rod head can be directly coupled to the bearing, preferably by forming a bearing shell for the bearing, and the connecting rod can essentially bear the entire vertically downward load on the bearing alone and without further guidance, with the axis of the main shaft preferably running parallel to the axis of the bearing.

[0031] The bearing of the pedal device can also be mounted in a vertical linear guide with a linear slide, wherein the linear slide is 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.

[0032] Generally, a base plate is preferably provided below which the main shaft and preferably also the motor are arranged and above which the pedaling device is arranged, wherein a recess is provided in the base plate through which the connecting rod passes and is directly coupled to the bearing with its connecting rod head.

[0033] Another preferred embodiment is characterized in that, preferably at essentially the same height as the pedaling device, a brake is arranged 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 pedaling device is pivotably mounted about a horizontal pivot axis, preferably arranged at the height of an axis of the brake, wherein preferably the pivot axis is arranged such that at the location of the bearing the pivoting movement is allowed essentially exclusively in the vertical direction.

[0034] The ergometer can also be characterized in that the pivot axis bearing of the bearing is given by an essentially fork-shaped construction in which the fork ends of the arms are rotatably mounted about the pivot axis, and the opposing joined arms are connected to the bearing, preferably by the joined area forming a bearing receptacle for the bearing of the pedaling device.

[0035] The vibration unit can be arranged below this brake, preferably above a base plate, and the coupling of the connecting rod to the bearing is preferably realized via at least one strut extending obliquely upwards, connecting the connecting rod head directly or indirectly to the bearing. Preferably, such a strut is rigidly connected to the pivot axis bearing.

[0036] 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 pedaling device, and further preferably partially surrounds this bearing without touching it, and which is set into vibration in the opposite direction to the vibration generated at the bearing by the vibration unit.

[0037] The eccentric disc and / or any additional eccentric disc that may be present can be slidably and adjustably mounted on the main shaft along a direction perpendicular to the axis of rotation of the main shaft, preferably being realized by a cam 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 moved along the axis of the main shaft.

[0038] The at least one adjusting element can be mounted in a recess or through-hole in the main shaft so as to be adjustable and slidable via adjusting means, and a cam can adjust the eccentricity of the eccentric disc in or on the adjusting element by interaction with a sliding block on the eccentric disc.

[0039] 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 correlated by 180° offset, or that two individual adjusting elements are provided for the respective eccentric disc, via which the eccentricity of the discs can be individually adjusted.

[0040] Such an ergometer is designed 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, particularly in the range of 100-300 W.

[0041] Preferably, frequencies in the range of 5-50 Hz, preferably in the range of 7-25 Hz and / or amplitudes in the range of 1-10 mm, preferably 3-7 mm, can be set at the bearing.

[0042] Further embodiments are specified in the dependent claims. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Preferred embodiments of the invention are described below with reference to the drawings, which serve only for illustration and are not to be interpreted restrictively. The drawings show: Fig. 1 Essential elements of a vibration unit for an ergometer according to a first embodiment in an exploded view; Fig. 2 the vibration unit according to Figure 1 in a sectional view in a) in a detailed section according to A in Figure 2a ) in b); Fig. 3 essential elements of a vibration unit for an ergometer according to a second embodiment in an exploded view; Fig. 4 the vibration unit according to Figure 3 in a sectional view; Fig. 5 essential elements of a vibration unit for an ergometer according to a third embodiment in an exploded view; Fig. 6 the vibration unit according to Figure 5in a sectional view; Fig. 7 different arrangements of the vibration unit, wherein a) an embodiment is shown in which the bottom bracket is supported directly from below by the connecting rod via a rocker arm, b) an embodiment is shown in which the bottom bracket is supported without a rocker arm in a linear bearing to which the vibration unit is coupled from below, and c) an embodiment is shown in which the vibration unit is arranged below the brake, the bottom bracket is supported via a rocker arm, and a counterweight is provided; Fig. 8 a side view of the embodiment according to Figure 7 b) ; Fig. 9 Views of an embodiment according to Figure 7c, wherein in a) the suspension is shown without a counterweight for better visibility of the individual elements and in b) only the counterweight is shown; Fig. 10 different views of a further embodiment with vibration unit coupled to the rocker arm and counterweight, wherein in a) the right side view, in b) the left side view, in c) top view, in d) an exploded view, in e) a view from the top right at an angle and in f a view from the bottom right at an angle. DESCRIPTION OF PREFERRED EXECUTION FORMS

[0044] Fig. 1Figure 1 shows essential elements of a vibration unit in an exploded view. The main shaft 12 is supported by two bearings 11 and is rotated by a motor (not shown). The coupling to the motor can be either direct or indirect, for example via a V-belt. The motor is preferably a servo motor with a power output in the range of 300–1,600 W. The main shaft 12 is structured and has a section on its left side 40 where it is supported by the aforementioned bearings 11. The two ball bearings 11 support the main shaft 12 with the bearing housing 19 and prevent axial displacement of the main shaft 12. On the right side is a shoulder surface 12a. This shoulder surface 12a prevents axial displacement of the eccentric disc 6 shown above right and thus of the entire connecting rod 1.The eccentric disc 6 is slidably mounted on the sliding surface 12b of the main shaft. The sliding shells 9 are positively engaged in the eccentric disc 6 and allow the eccentric adjustment of the eccentric disc 6 from the axis of rotation of the main shaft 12. The force transmission of the rotation of the main shaft 12 to the eccentric disc 6 occurs via the sliding surface 12b through the sliding shells 9 and thus to the connecting rod 1. The eccentric disc 6 does not lie directly against the sliding surfaces 12b of the main shaft, but rather the sliding shells 9 are located between them. These shells can be made of two parts or one piece, as shown here. The contact surfaces 41 on the inside of the eccentric disc 6 are in contact with the outside of the sliding shells 9, and their contact surfaces 42 on the inside are in contact with the sliding surface 12b of the main shaft 12.

[0045] 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 to achieve an optimal sliding pairing on the sliding surface 12b.

[0046] The eccentric disc 6 has a sliding block 5 in its axial recess 43, inclined transversely to the axis. This sliding block determines the deflection of the eccentric disc 6 and thus the stroke of the connecting rod 1. The sliding block 5 bridges the recess 43 and is held in place by the screws 7. The fitted screws 7 secure the sliding block 5 in the eccentric disc 6 not only by friction but also by positive locking. A ball bearing is attached to the eccentric disc 6 with its bearing ring 3 to support the connecting rod 1. The ball bearing is screwed to the eccentric disc with its bearing ring 3 using the screws 2. On the other side, a clamping ring 8 is provided, which clamps the outer ring of the ball bearing 4 to the connecting rod 1 by means of the screws 10. The screws 10 clamp the ball bearing 4 onto the connecting rod 1 via the clamping ring 8.

[0047] The forces of the connecting rod 1 are transmitted via the eccentric disc 6, through the sliding shells 9, to the main shaft 12 and via the bearing assembly 11 to the bearing housing 19. The connecting rod head 1a serves to accommodate a bearing for the movable fixation with the linear unit or the rocker arm (see below).

[0048] A pin-shaped adjusting element 13 engages axially in a blind hole 38 of the main shaft 12 in a displaceable manner. The adjusting element 13 is connected to the bearing housing 15 by means of the fitted screws 14 in a force-fit and form-fit manner. The bearing housing 15 accommodates the bearing assembly 16 in the form of two ball bearing rings. A trapezoidal threaded nut 17 sits on this assembly and is mechanically (i.e., rotationally secured) to the bearing housing 19 (in Figure 1 (not shown) is connected. In Fig. 1Six bores for screwing the bearing housing 19 are shown. The bearing arrangement 16 is adjustable without axial play and is secured with a shaft clamping nut 20 and a retaining ring 21 (both in Fig. 1 not shown, see below. Fig. 2 The adjusting element 13 is attached to the trapezoidal spindle 18. The trapezoidal spindle 18 moves the adjusting element 13 axially to change the stroke of the connecting rod 1. Due to the bearing arrangement 16, the trapezoidal spindle 18 does not rotate with the main shaft 12. 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 to achieve an optimal sliding pair.

[0049] A cam opening in the form of a cutout surface 13a runs transversely through the adjusting element. This cutout surface has essentially the same width as the thickness of the sliding block 5 but is considerably longer. When the adjusting element 13 is inserted into the blind hole 38, it aligns with the larger opening 39. In other words, the sliding block 5 extends through the openings 39 and 13a. The cutout surface 13a is thus part of the adjusting element 13. The sliding block 5 is positioned in the cutout surface 13a, and the deflection of the eccentric disc 6 is achieved positively via the planar surfaces of the sliding block 5 and the cutout surface 13a of the adjusting element 13.

[0050] The eccentric disc 6 is thus mounted eccentrically on the main shaft 12. The lower ring of the connecting rod 1 is, in turn, rotatably mounted on the eccentric disc 6 via the bearing ring 4. When the main shaft 12 rotates, the eccentric disc 6 performs an eccentric movement, which is transmitted to the lower ring of the connecting rod 1 and thus translated into a translation or oscillation at the connecting rod head 1a. The frequency of these oscillations is determined by the rotational frequency of the main shaft 12, and thus by the frequency of the motor driving this shaft. The amplitude of the oscillation can be adjusted by the trapezoidal spindle 18. The further the adjusting element 13 is inserted 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 of the movement at the connecting rod head 1a.The vibration generated at the connecting rod head 1a can thus be finely adjusted and controlled with regard to both frequency and amplitude. Furthermore, the connecting rod possesses high mechanical stability and very high directional stability, meaning that the vibrations generated thus propagate precisely along the direction of the connecting rod. In other words, the proposed device allows for the generation of virtually one-dimensional vibrations with an adjustable frequency and amplitude along a precisely defined direction.

[0051] Fig. 2Figure a) shows the vibration unit in a cross-sectional view through the axis of the shaft in an overview, and figure b) shows the details according to A in a). Here it can be seen how such a vibration unit can be arranged below a base plate 28, which serves as the central mounting point for the vibration unit. The base plate has a recess 44 through which the connecting rod 1 projects freely upwards. On the underside of the base plate 28, there is a left bearing housing 19 for supporting the main shaft, and a right bearing housing 19a for supporting the trapezoidal threaded nut 17.

[0052] In the right-hand bearing housing 19, the main shaft 12 is supported by the bearings 11 mentioned above, with a shaft clamping nut 20 provided for fastening, which clamps the bearing assembly 11 to minimize the axial and radial play of the main shaft 12. Additionally, there is a retaining ring 21 that prevents the shaft clamping nut 20 from unintentionally loosening.

[0053] In Fig. 2 The bearing arrangement 11 is, for example, designed as an O-bearing arrangement. The force application is outside the bearing arrangement 11. This adjusts the radial and axial play of the main shaft 12.

[0054] The only desired vibration in the present invention is a deflection of the connecting rod head 1a that is essentially perpendicular to the base plate.

[0055] Fig. 3Figure 1 shows an exploded view of a second embodiment of a vibration unit, this time with two eccentric discs 6 mounted on the same shaft. In this case, two connecting rods 1 with significantly shorter connecting rod arms are coupled to these two eccentric discs 6. One connecting rod generates the actual effective vibration for the user, and the other connect rod generates 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. However, each eccentric disc 6 now has a separate sliding surface 12b on the main shaft 12, and the adjusting element 13 has two corresponding cutout surfaces 13a with opposite inclinations.In principle, the two eccentric disks 6 are mounted on the main shaft 12 analogously to the first embodiment described above, and their eccentricity is controlled by the adjusting element 13. It is important that the eccentricity of the two eccentric disks 6 is phase-shifted by 180°, which is ensured by the opposing inclination of the cutout surfaces 13a and the corresponding opposing inclination of the two sliding blocks 5 of the respective eccentric disk 6.When the adjusting element 13 is moved in the recess 38 of the main shaft 12 by actuating the trapezoidal spindle 18, which in this case is secured in the recess 38 of the main shaft 12 by a retaining ring 23, which prevents unintentional loosening of the shaft clamping nut 22, and a shaft clamping nut 22, which clamps the bearing assembly 16 in the mounting 15 to support the trapezoidal threaded spindle 18 with no axial and radial play, one eccentric disc is displaced in a first direction and the other eccentric disc in the opposite direction from the main axis. This results in a phase shift of the eccentricity of the two eccentric discs 6 by 180°, in a completely correlated manner; that is, the adjustment by the single adjusting element 13 with the opposing inclinations of the cutout surfaces 13a automatically results in exactly a phase shift of 180°, regardless of the set amplitude of the vibration.In this way, it is constructively ensured that the optimal phase shift of the two connecting rods is always present, so that the compensation by the counterweight is optimally given at every setting and at every vibration amplitude.

[0056] The second embodiment differs from the first, among other things, in that the main shaft 12 is coupled somewhat differently. Here, there is an additional V-belt pulley 24, which serves to couple a servo motor 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 bushing.

[0057] The second embodiment differs from the first in that it allows for the compensation of unwanted vibrations. The term "unwanted vibrations" refers in particular to vibrations of the base plate 28 that oppose the desired vibration, as well as any other vibrations not perpendicular to the base plate 28. These unwanted vibrations arise from the unbalanced eccentric, with the eccentric's imbalance being primarily caused by the adjustability of the connecting rod and its design, which cannot be statically compensated due to the amplitude modulation of the stroke.

[0058] Fig. 4The second embodiment is shown in a sectional view. Among other things, it can be seen how the two connecting rods are mounted parallel to each other on the same main shaft 12 via the two eccentric discs, how the V-belt pulley 24 protrudes on the left side for coupling a servo motor, and how the trapezoidal spindle for adjusting the eccentricity protrudes on the right side. This demonstrates that an extremely compact design solution is provided, in which the two connecting rods, which bear high loads, are stably mounted.

[0059] In Fig. 4 The bearing surface of the connecting rod head bearings 26 is designed to be larger than that of the connecting rod head bearings 27 in order to absorb the higher forces occurring during operation under load (for example, under the influence of body weight).

[0060] The adjusting element 13 extends the respective sliding blocks for the crank and for the counterweight in opposite directions. The two eccentric discs must be axially rotated 180° relative to each other in order to deflect in opposite directions. This offset arrangement of the eccentric discs 6 is in Fig. 5 to be more easily recognizable.

[0061] Fig. 5 Figure 1 shows an exploded view of a third embodiment of a vibration unit, which, unlike the second embodiment, is designed so that the eccentricity of the two connecting rods 1 and the associated eccentric discs can be individually adjusted for each. For this purpose, the main shaft 12 is no longer supported on one side and open on the other for control via the adjusting element 13, but rather the main shaft is, as can be seen in particular from the following: Fig. 6 ,As can be seen in a sectional view, the main shaft is supported at both ends by bearing rings 11. Instead of a blind hole, the main shaft has an axial through-hole, allowing individual adjustment elements 13 to be inserted from both sides to set the eccentricity of each eccentric disc 6. Correspondingly, there are trapezoidal spindles 18 on both sides that control the respective adjustment element 13. The two adjustment elements, in turn, have cutout surfaces 13a with opposing inclinations, so that the eccentricity can always be set individually but with a 180° phase shift. This ensures that the phase shift is always 180°, but that the vibration amplitude can be set differently for the two connecting rods.This makes it possible to fine-tune the vibration compensation using the counterweight and, in particular, to adjust it to environmental or user parameters so that the compensation is always optimally guaranteed.

[0062] The third embodiment differs from the second embodiment in that the amplitude of both connecting rods can be controlled independently of each other. According to this embodiment, unwanted vibrations can be compensated for by vibration damping. The essential difference with regard to the embodiment according to... Fig. 3 and 4The adjusting element 13 is designed in two parts. Both adjusting elements 13 require separate bearings and are controlled by motors. The left trapezoidal spindle 18 controls the deflection of the counterweight, and the right trapezoidal spindle 18 controls the deflection of the crankshaft. In this embodiment, the main shaft 12 is driven centrally between the two connecting rods 1.

[0063] The compensation can be adjusted manually, but it's also possible to control the trapezoidal spindle or multiple trapezoidal spindles via an additional actuator. For example, such an actuator can be controlled electronically, perhaps by a vibration sensor or multiple vibration sensors, and a corresponding control system. In particular, it's possible to regulate such a system using a self-learning algorithm so that the vibrations measured by the sensors are minimal where they shouldn't occur (e.g., on the base plate) and maximal, or precisely within the desired range, where they should occur (e.g., at the bottom bracket).

[0064] Fig. 6 This is a sectional drawing of exploded view 5. The lengths of the two adjusting elements 13 are different: This is shown in Fig. 6a stroke of the connecting rods from zero. To change the stroke, the right adjusting element 13 is moved to the right and the left adjusting element 13 is also moved to the right by a rotation of the trapezoidal spindle 18; this changes the deflection of the eccentric discs, which are in Fig. 6 This can be seen from the different position of the play of the sliding shells 9 (the right sliding shells show the play at the top, the left ones at the bottom).

[0065] Fig. 7 This shows different ways of arranging such a vibration unit on a (bicycle) ergometer.

[0066] A first in Fig. 7b and also in Fig. 8As shown in a side view, the vibration unit can be positioned below a base plate 28, such that the connecting rod 1 passes vertically through a recess in this base plate. The ergometer's bottom bracket 29 is selectively and vertically displaceable within a linear slide 34, which is mounted on the base plate via a linear guide 35. This linear slide 34 is rigidly connected at the top to the ball bearing 29 and coupled at the bottom to the connecting rod head 1a.

[0067] This provides a design that selectively allows vibrations only in a strictly vertical direction, and the entire suspension and load of the vibration unit are absorbed by the front area below the bottom bracket. Such a vibration unit can be combined with a conventional brake 30, which is coupled via a power transmission element, for example, a chain, belt, or toothed belt. With this design, it is possible to use a vibration unit according to the first embodiment described above, i.e., with only a single connecting rod for vibration at the bottom bracket. However, it is also possible to use a vibration unit according to the second or third embodiment. This is because, as in Fig. 8 It is shown that it is possible to mount a counterweight 36 in such a housing via another connecting rod, phase-shifted by 180°, so that the vibrations via the first in Figure 8The connecting rod shown in the foreground is used to transmit vibrations to the bottom bracket at the desired frequency and amplitude, but the vibrations are effectively canceled out in relation to the surroundings, and in particular, for example, the base plate 28, similar to noise cancellation. In practice, such devices present significant problems due to the artificially generated vibration. On the one hand, the artificially generated vibration leads to unpleasant noise emissions, especially because the base plate, or the legs connected to it, transmit the vibrations to the ground and buildings, etc. On the other hand, there are also unpleasant noise emissions from the vibration of other components, such as the brakes. Furthermore, the vibration causes problems because such devices tend to be displaced by the shaking and essentially wander around.Finally, the vibrations on the device itself and on its other components lead to mechanical damage, and the same applies to other nearby devices to which the vibrations are unintentionally transmitted. Typically, suitable vibrations for this device are in the range of up to 50 Hz. Low frequencies of 7-12 Hz with amplitudes of up to 7-10 mm prove particularly suitable for neurostimulation, typically at a load of approximately 100 W. Higher frequencies in the range of 15-25 Hz can also be used, for example, for athletes, then typically with somewhat lower vibration amplitudes of up to 3-4 mm. In this case, loads in the range of 200-300 W braking power are used. Therefore, the vibrations and amplitudes are in a mechanically critical range for other components, and compensation by one or more counterweights is extremely important.

[0068] In Fig. 7b The crankshaft bearing is thus attached to a linear bearing 35 via a slide 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 movement is directed exclusively perpendicular to the base plate 28. The setup can also be implemented with a second connecting rod and a counterweight 36 as a second slide on the linear guide to compensate for vibrations.

[0069] Another way to incorporate such a vibration device on an ergometer is in Fig. 7aAs shown, the connecting rod 1 also generates a vibration that is essentially strictly vertical (see arrow). However, the connecting rod 1 serves as the sole vertical bearing for the bottom bracket, thus providing an extremely slim design. To enable this design, a swing arm 32 is added. This swing arm 32 is a second bearing for the bottom bracket, essentially around the axle 45 of the brake. The swing arm 32 has two arms 46, a first arm 46' and a second arm 46". The two arms engage the axle 45 at opposite ends and pivot the bottom bracket 29.Because the axle of the bottom bracket 29 and the axle of the brake 45 are located at approximately the same height, the swing arm 32 ensures that the bottom bracket 29 can move only in a substantially vertical direction, thus guaranteeing strictly vertical vibration. If, for example, the brake on such an ergometer is located closer to the base plate or substantially below the bottom bracket, the swing arm 32 should not be attached to the axle of the brake, but rather to a separate axle bearing approximately at the level of the bottom bracket, precisely to ensure that only vertical vibrations are possible at the bottom bracket.

[0070] In Fig. 7aThe center of the connecting rod head 1a is identical to the center of the crankshaft bearing. The crankshaft bearing is supported only by the connecting rod and the rocker arm. All forces except those in the connecting rod direction are absorbed by the rocker arm. The adjustable braking force of the brake 30 is transmitted to the crankshaft 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.

[0071] Another way to incorporate such a vibration device on an ergometer is in Fig. 7cThe vibration device is positioned below the brake, and the bottom bracket is essentially free-floating. This results in a particularly compact and elegant design. The swing arm 32 is attached to the brake axle 45 and supports the bottom bracket 29 in such a way that it can only move vertically. In this design, the bottom bracket 29 is supported vertically by a strut on the swing arm 32 that angles downwards towards the vibration device and is coupled to one of the two connecting rods of the vibration device via a connecting rod receptacle 37. In other words, the swing arm 32 incorporates a means for coupling the vibration of the vibration device, and the geometric design and the levers used ensure that the vibration, although acting at an angle on the connecting rod at the device, is translated into a strictly vertical vibration at the bottom bracket.See also in particular . Fig. 9a , in which this construction is shown, with only the swing arm 32 with the strut 46 illustrated for better visibility.

[0072] Fig. 7c This shows a variant in which the vibration drive is located not below the ball bearing, but outside the crank area. This eliminates components below the crankshaft, thus enabling a very compact design. The connecting rod is movably connected to the rocker arm at the connecting rod mount 37 of the rocker arm.

[0073] In such a design, a corresponding counterweight 36 is advantageously mounted in a very similar manner and driven by the second connecting rod, which is phase-shifted by 180°. See in particular Fig. 9bThe figure shows this counterweight construction, omitting the swingarm for the bottom bracket. The counterweight 36, or more precisely the counterweight head 50, is, in this case, similar to the swingarm, connected to the brake axle 45 via a first strut 47. On the other side, between the counterweight head 50 and a connecting rod mount 37a for the counterweight, there is a further strut 49, directed downwards, as well as a third strut 48, which connects the counterweight's connecting rod mount to the brake axle 45 to ensure the necessary stability of the bearing. The counterweight, in particular its counterweight head 50, is thus optimally positioned in a space-saving manner, yet excellently supported, between the two arms 46' and 46" of the swingarm, and can therefore provide the optimal compensating effect.

[0074] In Fig. 10Figure 1 illustrates another embodiment of an ergometer. The components corresponding to those described above are marked with the same reference numerals. In this embodiment, the rocker arm is designed with several struts on both sides, including additional vertical and horizontal struts. However, the connection to the connecting rod 1 is fundamentally analogous to that described above in connection with the... Figure 7 and 9The counterweight is similarly designed; here, the weight head 50 is constructed as a layered body, allowing for on-site adjustments to its mass by adding further layers. Furthermore, the weight head 50 is designed as a fork, with arms that at least partially encircle the bottom bracket 29 from above and below. This allows the counterweight to be positioned as close as possible to the bottom bracket, ensuring optimal vibration compensation. The counterweight is mounted on a support body 47, also featuring multiple struts, which is in turn connected to the vibration unit via the connecting rod mount 37a. This support body extends through struts of the swingarm, resulting in an optimally compact and space-saving design.

[0075] Also visible in this embodiment is the actuator 52 with the associated V-belt 51 for adjusting the trapezoidal threaded nut and, accordingly, for adjusting the eccentricity and the associated amplitude of the vibration. Also visible is the motor 54 for driving the main shaft 12, and the corresponding V-belt 53. REFERENCE MARK LIST 1 connecting rod 19a Right bearing housing 1' Connecting rod for counterweight 20 Shaft clamping nut 1a Connecting rod head 21 retaining ring 2 screws 22 Shaft clamping nut 3 bearing ring 23 retaining ring 4 ball bearings 24 V-belt pulley 5 Sliding stone 25 Tension nut 6 Eccentric disc 26 Connecting rod head bearing 6' Eccentric disc for counterweight 27 Connecting rod head bearing 28 base plate 7 dowel pins 29 Crank bearings 8 Tension ring 30 brake 9 Sliding shells 31 Power transmission element 10 screws 32 Swing 11 Storage arrangement 33 crank 12 Main wave 34 Linear slide 12a shoulder area 35 Linear guide 12b sliding surface 36 counterweight 13 Adjustment element 37 Connecting rod mount swingarm 13a Cutout area 37a Connecting rod bearing counterweight 14 dowel pins 15 Storage 38 axial blind hole in 12 16 Storage arrangement 39 radial through-hole 17 Trapezoidal thread nut 40 Mounting area of ​​12 18 Trapezoidal spindle 41 Plant areas from 6 to 9 19 Left bearing housing 42 Plant areas from 9 to 12b 43 Exclusion in 6 Counterweight to the weight head 44 Exclusion in 28 for 1 45 axle of the brake 50 Weight head 46 Strut of 32 51 V-belt for actuating trapezoidal threaded nut 46', 46" Arms of 32 47 Weight strut to the axle of the brake 52 Motor for actuation of trapezoidal threaded nut via 48 Weight strut from the brake axle to the connecting rod mount of the counterweight 51 53 V-belt for drive motor from main shaft 12 54 Motor for driving main shaft 12 49 Weight strut from the connecting rod mount of the

Claims

1. Ergometer, in particular a bicycle ergometer, with at least one pedalling device for a user and with a vibration unit, characterised in that the vibration unit causes the pedalling device to vibrate and the ergometer has, in addition to the vibration unit, a compensation device which at least partially compensates for the vibrations of the vibration unit outside the pedalling device by means of negative interference, and that the compensation device generates vibrations that have the same frequency and essentially the same amplitude as the vibrations of the vibration unit, with a phase shift of essentially 180°.

2. Ergometer according to claim 1, characterised in that a common motor (54), preferably a common shaft driven by a common motor, generates both the vibrations of the vibration unit and the vibrations of the compensation device.

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

4. Ergometer according to one of the preceding claims, characterised in that the vibration unit has at least one main shaft (12) driven directly or indirectly by a motor (54) with an eccentric disc (6) attached to it, wherein the eccentric disc (6) is rotatably coupled to a connecting rod (1), and in that, preferably, a further eccentric disc (6') is arranged on the main shaft (12) is arranged with which a counterweight (36) is set into a compensating vibration, wherein preferably this further eccentric disc (6') is arranged on the main shaft (12) with eccentricity opposite to that of the eccentric disc (6) for driving the connecting rod.

5. Ergometer according to claim 4, characterised in that the further eccentric disc (6') drives a further connecting rod (1'), which is rotatably mounted on the further eccentric disc (6') and is coupled to a counterweight (36), which is set into vibration in essentially the same direction as the vibration device at the bearing (29), but with an effect that compensates for the vibration at the bearing (29), preferably by the vibration at the counterweight (36) being offset by 180° relative to the vibration at the bearing (29).

6. Ergometer according to one of the preceding claims 4-5, characterised in that, preferably at substantially the same height as the pedalling device, a brake (30) is arranged which is coupled to the pedalling device via a force transmission element (31), preferably in the form of a chain, a toothed belt or a V-belt, and the counterweight (36) is pivotably mounted about a horizontal pivot axis bearing, preferably arranged at the height of an axis (45) of the brake (30), wherein the pivot axis (45) is preferably arranged such that the counterweight (36) performs the pivot movement in the region of the bearing (29) essentially exclusively in the vertical direction, wherein the counterweight (36) preferably has a weight head (50) in the region of the bearing (29), and furthermore, this weight head (50) preferably surrounds the bearing region at least partially in a fork-shaped manner at the top and bottom.

7. Ergometer according to one of the preceding claims and claim 4, characterised in that the vibration unit is arranged below the bearing (29) and that the connecting rod head (1a) is directly coupled to the bearing (29), preferably forms a bearing shell for the bearing (29), and that the connecting rod (9) bears substantially the entire vertically downward load on the bearing (29) alone and without further guidance, wherein preferably the axis of the main shaft (12) runs parallel to the axis of the bearing (29).

8. Ergometer according to one of the preceding claims and claim 4, characterised in that the bearing (29) of the pedalling device is mounted in a vertical linear guide (35) with a linear slide (34), wherein the linear slide (34) is firmly connected to the bearing (29) at the top and connected at the bottom to the connecting rod head (1a), wherein preferably the axis of the main shaft (12) runs parallel to the axis of the bearing (29), wherein a base plate (28) is preferably arranged, below which the main shaft (12) and preferably also the motor are arranged, and above which the pedalling device is arranged, wherein a recess (44) is provided in the base plate (28), through which the connecting rod (1) passes and is coupled directly to the bearing (29) with its connecting rod head (1a).

9. Ergometer according to one of the preceding claims 3-8, characterised in that the eccentric disc (6) and / or any other eccentric disc (6') 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 realised by a sliding guide (5, 13a) in which at least one adjustment element (13), when displaced along the axis of the main shaft (12), causes the eccentric disc (6) to be displaced along a direction perpendicular to the axis of rotation of the main shaft.

10. Ergometer according to claim 9, characterised in that the at least one adjustment element (13) is mounted in an adjustable and displaceable manner in a recess (38) or through-opening in the main shaft (12) via adjustment means (18), and a cam (13a) in or on the adjustment element adjusts the eccentricity of the eccentric disc (6) by interacting with a sliding block (5) on the eccentric disc (6).

11. Ergometer according to one of the preceding claims 9 or 10, characterised in that an eccentric disc (6) for generating the desired vibration and a further eccentric disc (6') for the counterweight are mounted on the main shaft (12), and that either an adjustment element (13) is provided with which the eccentricity of both eccentric discs can be adjusted in a correlated manner with a 180° offset, or that two individual adjustment elements are provided for the respective eccentric discs (6, 6'), via which the eccentricity of the discs can be adjusted individually.

12. Ergometer according to one of the preceding claims, characterised in that a brake (30) is arranged, preferably at substantially the same height as the pedalling device, which is coupled to the pedalling device via a force transmission element (31), preferably in the form of a chain, a toothed belt or a V-belt, and wherein the bearing (29) of the pedalling device is mounted so as to be pivotable about a horizontal pivot axis, preferably arranged at the height of an axis (45) of the brake (30), wherein the pivot axis (45) is preferably arranged such that, at the location of the bearing (29), the pivoting movement is essentially only permitted in the vertical direction, preferably further characterised 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 around the pivot axis, and the opposite arms joined together are connected to the bearing (29), preferably by the joined area forming a bearing receptacle for the bearing (29) of the pedalling device and / or preferably further characterised in that the vibration unit is arranged below this brake (30), preferably above a base plate (28), and wherein preferably the coupling of the connecting rod (1) to the bearing (29) is realised via at least one strut (46) extending obliquely upwards and connecting the connecting rod head (1a) directly or indirectly to the bearing (29), and wherein furthermore preferably this strut (46) is rigidly connected to the pivot axis bearing.

13. Ergometer according to one of the preceding claims, characterised in that the compensation device comprises a counterweight (36), in particular with a weight head (50), which is preferably arranged in the area of the bearing (29) of the pedalling device, and further preferably partially surrounds this bearing (29) without touching it, and which is set into vibration at the bearing (29) in opposition to the vibration generated by the vibration unit.

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

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