EP2549970A2

EP2549970A2 - Apparatus for muscle stimulation

Info

Publication number: EP2549970A2
Application number: EP11726657A
Authority: EP
Inventors: Helmut Frey
Original assignee: Frey Helmut
Current assignee: Frey Helmut
Priority date: 2010-03-24
Filing date: 2011-03-23
Publication date: 2013-01-30
Anticipated expiration: 2031-03-23
Also published as: WO2011116755A3; DK2549970T3; CA2810949A1; CA2810949C; US20130079196A1; US9050483B2; WO2011116755A2; EP2549970B1; DE102010012676A1

Abstract

The invention relates to an apparatus for muscle stimulation, with at least one motor and with two motor-driven gears, wherein each of these gears comprises a frame and a tread plate mounted in the frame. Each of these gears is a rotatable four-bar linkage. The driven gear member is in each case a crank mounted in the frame. Moreover, a crank and a tread plate are in each case connected in an articulated manner by means of a coupling member. With the present invention, an apparatus for muscle stimulation is developed that can be operated both with low and also with high stroke frequencies.

Description

Device for muscle stimulation

5

Description:

The invention relates to a device for muscle stimulation with at least one motor and with two motor-driven

Driven, each of these gear includes a frame and mounted in the frame tread plate.

From US 3,540,436 AI such a device is known.

15 The single gear is a three-part cam gear with a full-turn. This requires u.a. due to the special machines required for this purpose, a high production cost. To prevent lifting of the tread plate, this is by means of a tension spring on the circumferential

20 cam pressed. A high stroke frequency can lead to the lifting of the footboard and rattle.

The present invention is therefore based on the problem to develop a device for muscle stimulation, which can be operated both with low and with high stroke frequencies.

30

- This problem is solved with the features of the main claim. For this purpose, each of these transmissions is a revolving ^J four-bar linkage. Each driven gear member is a crank mounted in the frame. In addition, each one is a crank

CONFIRMATION COPY and in each case a foot plate by means of a coupling member hingedly connected.

Further details of the invention will become apparent from the dependent claims and the following description of schematically illustrated embodiments.

Figure device for muscle stimulation;

Figure side view of the device;

Figure side view after half a turn of the crank; Figure cross section of the transmission;

Figure cross-section of gestellsei term

Footboard storage;

FIG. 6: adjustable eccentric;

FIG. 7: eccentric with end cap;

FIG. 8: mounting of the tread plate with elastomer body;

FIG. 9: Mounting of the tread plate with disc springs;

Figure 10: pedal plate bearing without rolling or plain bearings;

FIG. 11: mounting of the tread plate with leaf spring;

FIG. 12: partial section through FIG. 11;

Figure 13: Storage with sensors.

FIG. 1 shows an isometric view of a device (10) for muscle stimulation. The device (10) comprises a bottom plate (11) on which a motor (20) and two by means of this motor (20) and in each case a transmission (30, 130) driven tread plates (81, 181) are arranged. In this figure 1, the controls of the device (10) and the panel are not shown. The bolted to the bottom plate (11), for example, motor (20) is a frequency-controlled three-phase motor in the embodiment. By varying the driving frequency of the magnetic field of the

Motor (20) increases or decreases synchronous to this frequency speed of the motor (20). The device (10) can also be two

Have engines (20). Each of the two motors (20) then drives a tread plate (81, 181) by means of a gearbox (30, 130). The two servo motors (20) can be synchronized with each other.

The single motor (20) may be a geared motor which is directly connected e.g. drives a reduction gear. The

Output speed of the geared motor is then, for example, less than the synchronous speed described. The sub-reduction gear is a gear train with parallel, intersecting or intersecting axes.

The use of one or two DC motors with adjustable speed is conceivable.

In the illustration of Figure 1, the motor (20) with the gears (30, 130) by means of a traction mechanism drive (21) is connected. In the exemplary embodiment, the traction mechanism drive 21 is a belt drive, which has a belt pulley 23, a belt 24 and a belt pulley 25 on the output shaft 41 of the coupling mechanism 30 ). The belt drive (21) may have a V-belt, a flat belt, etc. The traction mechanism drive (21) can also be a chain drive.

The two pulleys (23, 25) are in the embodiment

V-ribbed discs (23, 25), wherein the output side

Disk (25), for example, 2.2 times the diameter of the motor side Washer (23) has. The V-ribbed belt (24) may, for example, have a steel insert.

To adjust the belt tension, the motor (20) may e.g. be displaceable in the longitudinal direction of the device (10). It is also conceivable to tension the traction means (24) by means of a self-tensioning device, cf. Figures 2 and 3. This then comprises e.g. a tension roller (26) and a spring (27). In Figures 2 and 3, the device (10) is shown in each case in a side view with different gear positions. In. Figure 2 is the viewer facing front tread plate (81) in its upper end position and the rear tread plate (181) in its lower end position. In the figure 3, the transmission (30, 130) are moved so far that the front tread plate (81) in its lower end position and the rear tread plate (181) is in its upper end position.

The individual transmission (30, 130), cf. 1 to 5, there is a rotatable four-bar linkage with a frame (31, 131), a crank (32, 132), a coupling (33, 133) and one through the tread plate (81, 181) and their bearing flanges (82, 83, 182, 183) formed further transmission element (34, 134). This transmission element (34, 134) is referred to below as a step plate element (34, 134). The single frame (31; 131) is formed in the embodiment by the bottom plate (11), a front bearing block (12) and a rear bearing block (13). The bearing flanges (82, 83, 182, 183) and the bearing blocks (12, 13) can be made in several parts. In the frame (31; 131), the crank (32; 132) is rotatably mounted in the crank joint (35; 135) and the tread plate element (81; 181) is rotatably mounted in the frame joint (38; 138). According to FIGS. 1-5, the pivoting and rotating axes of all the (35-38; 135-138) are arranged normal to the vertical center-long plane of the appliance (10).

The crank (32; 132) is formed by the drive shaft (41) with an eccentrically located bearing seat (42; 142). The drive shaft 41, which according to the sectional view of FIG. 4 connects both transmissions 30, 130, carries at one end the pulley 25. It is mounted for example by means of two deep groove ball bearings (43, 44) in the front bearing block (12). The inner rings (45) of the bearings (43, 44) bear against a shaft shoulder (46) and are fixed axially on the shaft (41) by means of a securing ring (47). In the exemplary embodiment, the outer rings (48) on the bearing block (12).

Outside the bearings (43, 44) are in the embodiment, the eccentrically arranged bearing seats (42, 142). For example, these are offset in a direction normal to the imaginary center line (49) of the drive shaft (41) against each other. In the exemplary embodiment, the phase angle of the extremes of the two eccentrically arranged bearing seats (42, 142) relative to one revolution of the drive shaft (41) is 180 degrees. The length of each crank (32; 132) is normal to

Center line (49) of the drive shaft (41) measured center line distance between the bearing seats (51) of the drive shaft (41) and the eccentrically arranged bearing seat (42; 142) of the respective linkage (30; In the embodiment illustrated in FIGS. 1-5, the sum of the diameter of an eccentrically arranged bearing seat (42, 142) and the double eccentricity is smaller than the diameter of the bearing seat (51) of the drive shaft (41).

The eccentrically arranged bearing seats (42, 142) each carry a roller bearing (52, 152) in the illustration of FIG. which in turn carries a respective bearing plate (53; 153). This forms the coupling member (33, 133) which is rotatably mounted by means of the coupling joint (36, 136) on the crank (32, 132). A second bearing seat (54; 154) of the bearing plate (53, 153) receives by means of a further rolling bearing (55, 155) a pivot pin (59, 159) of the front tread plate bearing (84, 184). The distance between the two mutually parallel pivot axes of the

Bearings (52, 55, 152, 155) is the length of the coupling member (33, 133). The rolling bearings (43, 44, 52, 55, 152, 155) are in the embodiment sealed on both sides deep groove ball bearings. But it can also roller bearings, angular contact ball bearings, needle roller bearings, etc. are used.

The tread plate element (34; 134) is mounted in the coupling element (33; 133) by means of a pivoting joint (37; 137) and in the frame (31; 131) by means of a pivoting joint (38; 138). The frame supports (38, 138) shown in section in FIG. 5 each comprise one by means of two e.g. sliding sleeves (85, 185) made of POM in the rear, for example, multi-part bearing flange (83, 183) and in the

rear bearing block (13) mounted pivot pin (86, 186).

The two tread plates (81, 181) are arranged axially symmetrically to the vertical center longitudinal plane of the device (10). The e.g. constant distance between the two tread plates (81, 181) to each other is less than two millimeters. The single tread plate (81, 181) is an at least approximately rectangular

Plate made of, for example, an aluminum alloy. In the embodiment, their length is

490 millimeters, their width is 200 millimeters and theirs

Thickness 10 mm. Its upper side (87, 187) has a recessed surface into which a non-slip rubber mat (88, 188), for example, is glued. Optionally, at the top (87, 187) of the tread plates (81, 181) each one or several eyelets or hooks can be arranged. In this example, each a thimble of a rope can be hung with handle. During assembly, for example, first the bearing blocks (12, 13) and the motor (20) are mounted on the base plate (11). In the front bearing block (12), the drive shaft (41) is inserted and pushed from both shaft ends depending on a deep groove ball bearings (43, 44) on the bearing seats (51) and secured by means of a respective retaining ring (47). After placing the bearing plates (53, 153), the deep groove ball bearings (52, 152) are pushed onto the eccentrically arranged bearing seats (42, 142) and, for example by means of

Secured securing rings (58; 158). After inserting the bearings (55, 155), the tread plates (81, 181) are placed. A collar bolt (59, 159) is inserted in each of the tread plate bearings (37, 137) and is e.g. secured by a hex nut (61, 161). In the frame (31; 131), the single tread plate (81; 181) is secured by means of the bolt (86; 186).

After mounting and securing the pulleys (23, 25) and the belt (24), the belt (24) is e.g. tensioned by moving the motor (20).

During operation of the device (10), the user stands with one foot on a tread plate (81, 181). The motor (20) drives the two coupling gears (30, 130) by means of the traction mechanism drive (21). Here, each crank (32, 132) is rotated by one revolution with one revolution of the drive shaft (41). The two

Coupling (33, 133) are forcibly guided by means of the cranks (32, 132), so that the tread plate bearings (37, 137) are raised and lowered from an eg neutral starting position. During a cranking reaches the associated Support plate bearing (37; 137) a maximum and a minimum. The total stroke of a support plate bearing (37, 137) is for example seven millimeters. For example, the

Stroke frequency of a tread plate (81, 181) between 3 hertz and 30 hertz.

During the oscillatory lifting movement, each of the two tread plates (81, 181) pivots about their frame-side

Storage (38; 138). For example, the swivel angle from the neutral position is +/- an angular degree.

In a change of the output speed of the motor (20) changes proportionally to the stroke frequency of the tread plates (81, 181). This influences the stimulation of the user's muscles.

FIG. 13 shows a step plate (81) with a bearing flange (83), wherein a pressure-sensitive sensor (89) is arranged between the two components (81, 83). Should be e.g. at a high stroke frequency the foot of the

The user (89) relieves the sensor (89) from the tread plate (81) and loads it abruptly when the foot recurs. The e.g. electrical output signal of the sensor, for example in the form of a

Pressure cell or a strain gauge is executed, changes. This signal change results in the driving of the motor (20) e.g. a reduction in engine speed. Only when the feet of the user are again fully on the tread plate, the original signal level of the responsive to deformations sensor (89) is reached again.

Such sensors (89) can be arranged both in or on the frame-side (38) and in or on the coupling-side tread plate bearing (37). The sum signal of the Both sensors (89) is then largely independent of whether the user is further forward or further back on the tread plates (81, 181).

For the evaluation, it is also conceivable to use a desired signal as a function of the mass or the mass moment of inertia of the

User and the signal changes only after a run-in period of e.g. 10 seconds to determine.

FIG. 6 shows a partial section of a device (10) in the region of a drive shaft (41) formed from coaxial cylindrical sections. On the drive shaft (41) sits an eccentric ring (71) supporting the bearing plate bearing (52) which abuts against a shaft shoulder (72) and e.g. by means of a

15 shaft nut (73) with locking plate (74) is secured. Optionally, the eccentric ring (71) on the mother and / or shaft shoulder side have a planer toothing, which engages positively in a counter-toothing of the shaft shoulder (72) or a locking ring (74) of the shaft nut (73).

The eccentric ring (71) may be e.g. be positioned by means of a feather key on the drive shaft (41). For example, it can be exchangeable for an eccentric ring with different eccentricity.

25 To adjust the eccentricity and thus the length of the crank (32), loosen the shaft nut (73). The eccentric ring (71) may now be e.g. be infinitely twisted using a scale. As soon as the new crank length is set, the shaft nut (73) is reset. In a molding

For example, between the eccentric ring (71) and the shaft shoulder (72) is a stepwise adjustment of the

· ^■ 'crank length possible. With an adjustment of the eccentricity of the coupling joint (36), the stroke of the tread plate (81) is changed. provides. In the illustrated embodiment is a

Stroke adjustment between two and seven millimeters possible.

The two gears (30, 130) can have different crank lengths. For this purpose, the eccentric rings (71) can be set differently. Thus, the lift amount of both tread plates (81, 181) may be unequal.

It is also conceivable to set the two gears (30, 130) in such a way that the phase shift of the two maxima

and / or minima is not equal to 180 degrees. For this purpose, the two tread plates (81, 181) are adjusted so that the maximum of one tread plate (81, 181) does not coincide in time with the minimum of the other tread plate (181, 81).

Optionally, the drive shaft (41) in this case comprise an imbalance mass for mass balance.

FIG. 7 shows a drive shaft (41) with an eccentric ring (71) which is fixed by means of an end cap (75). The end cap (75) is fastened, for example, by means of a screw (76) on the end face (77) of the drive shaft (41).

Optionally, an attachment by means of two

Screws, a positive element, e.g. a pin and a screw (76), etc. conceivable. Also in this case, on the end cap (75) e.g. be attached to a scale on which by means of a counter mark the eccentric ring (71) can be adjusted.

It is also conceivable, the eccentric ring (71) by means of a

Quick release device to fix. Here, for example, the eccentric ring (71) is operated from the outside of the device (10) by loosening or tensioning an operating handle. The eccentric adjustment can for example be done from the outside by means of a tool. FIG. 8 shows the mounting of two tread plates (81, 181) with elastically deformable elements (90, 190). This comprises two composite bodies (101, 201) each

Elastomeric body (102, 202) and metal plates (103, 104, 203, 204) vulcanized on the end face. For example, the upper metal plate (103; 203) has a threaded bore (105; 205). The lower metal plate (104; 204) carries a threaded pin (106; 206) facing away from the elastomeric body (102; 202), which is screwed into the respective bearing block (13). A fastening screw (107, 207) for the tread plate (81, 181) is screwed into each of the threaded bores (105, 205). The elastomeric body (102, 202), for example, has a hardness between 40 and 60 Shore. The composite body (101, 201) thus prevents abrupt stresses on the user which could occur at the reversal points of the tread movement.

During operation of the device (10) with such a frame-side (38) and / or coupling-side tread plate mounting (37), the elastomer body (102, 202) allows a skewing of the two metal plates (103, 104, 203, 104) to one another Angle of eg three degrees. The composite body (101, 201) can thus be used to seal the e.g. replace sliding or rolling bearings shown in Figures 4 and 5 of the tread plates (81, 181). But it can also be arranged in addition to these.

FIG. 9 shows a coupling-side tread plate mounting (37) which is designed as elastically deformable elements (90, FIG.

190) comprises two plate spring packets (111). For example, from below each screw (112) through the bearing flange (82) and the plate spring package (III) is screwed into the tread plate (81). By means of screws (112) is the Preload the cup spring packs (111) adjustable. Thus, the tread plate storage (37) can be made harder or softer. In the illustration of Figure 9, a plate spring (113) of a plate spring package (111) is oriented upwards and the diaphragm spring (114) which bears against it. But it is also conceivable, for example, in each case two superimposed upward (113) and in each case two superimposed downward disc springs (114)

combine .

In the illustration of Figure 9, the coupling-side tread plate bearing (37) instead of a rolling bearing (55) can be performed with a leaf spring. This is then attached to the bearing plate (53) and the bearing flange (82). The bending line is then, for example, parallel to the bottom plate (11).

The screw head (115) may e.g. on a vaulted

Washer (116) rest with a slot, cf.

Figure 10. The latter may have a surface with a low coefficient of static friction. In an embodiment of the tread plate bearings (37, 38) without sliding and / or roller bearings, the bearing described can take over the joint function.

The use of a composite body of an elastomeric body and frontal metal plates with a through hole instead of the plate spring assemblies (111) is conceivable. Figures 11 and 12 show a device (10) whose coupling-side tread plate joints (37) comprise leaf springs (121). In the figure 11, the pulley (25) and the support bearing (64) are removed. FIG. 12 shows a partial section of FIG. 11 in the region of the bearing plate (53). The single one elastically deformable element (90; 190), that is, the single curved leaf spring (121; 221), for example, is fixed at least approximately vertically to the bearing plate (53).

In addition, it is secured here by means of a retaining plate (122). In the exemplary embodiment, the bearing plate (53)

by means of a guide pin (62) in the front bearing block (12) guided in the vertical direction.

On the tread plate side, the leaf springs (121, 221) on the underside of the tread plates (81, 181) are e.g. in two each

Guide rails (123, 223) stored. An adjustment plate (124) which can be adjusted in the longitudinal direction of the tread plate (81; 181) is pressed onto the leaf spring (121) by means of the guide elements (123) so that it retains its position relative to the tread plate (81; 181). By axial adjustment of the adjusting plate (124), the resilient length of the leaf spring and thus its spring stiffness can be adjusted. The shorter the resilient length, the higher the spring stiffness of the storage. Optionally, a multilayer leaf spring package can be used. To increase the rigidity of the bearing, two or more leaf springs (121) can be arranged side by side. Such a coupling-side tread plate bearing (37) can for example be combined with a frame-side tread plate bearing (38) with a composite body (101).

In the illustration of Figure 12, three identical rolling bearings (43, 52, 63) are used to support a tread plate (81, 181). The running as a floating bearing bearing (64) in the embodiment has a relation to these camps smaller inner and outer diameter. But it is also conceivable for use all rolling bearing identical bearing elements.

Also, in such a device (10), the crank length and / or the phase angle difference can be adjustable.

The traction mechanism drive (21) can be arranged between the two transmissions (30, 130). If appropriate, each transmission (30, 130) can also be driven by means of its own traction mechanism drive (21). The device (10) can also be designed without traction mechanism drive (21).

Combinations of the various embodiments are conceivable.

List of reference numbers:

10 device for muscle stimulation

11 base plate

12 bearing block, front

13 bearing block, rear

20 engine

21 Traction drive, belt drive

22 motor shaft

23 Pulley, drive side; V-ribbed pulley

24 traction devices, belts, V-ribbed belts

25 Pulley, driven side; V-ribbed pulley

26 tension roller

27 spring

30 gearbox, coupling gearbox

31 frame

32 crank

33 coupling, coupling link

34 gear element, tread plate element

35 crank joint, pivot bearing

36 Coupling joint, pivot bearing

37 footplate joint; Footplate bearing, front;

Swivel bearing, coupling-sided footplate bearing

38 frame joint, swivel bearing

41 drive shaft

42 bearing seat, eccentrically arranged

43 Rolling bearings, deep groove ball bearings

44 Rolling bearings, deep groove ball bearings

45 inner rings

46 wave shoulder

47 circlip 48 outer rings

49 center line of (41)

51 bearing seats of (41)

5 52 Rolling bearings, deep groove ball bearings

53 bearing plate

54 bearing seat

55 Rolling bearings, deep groove ball bearings 58 Circlip

0 59 collar bolts

61 hex nut

62 guide bolts

63 rolling bearings

15 64 support bearings

71 eccentric ring, eccentric ring

72 wave shoulder

73 shaft nut

20 74 Locking plate, circlip

75 end cap

i ' ^: 76 screw

77 front side of (41)

25 81 Tread plate, transmission element

82 bearing flange front

83 bearing flange, rear

84 tread plate bearing, front

85 sliding sleeve

30 86 pivot pins

87 top

88 rubber mat

89 Pressure-sensitive sensor 90 elastically deformable element

101 composite body

102 elastomer body

5 103 metal plate

104 metal plate

105 threaded hole

106 threaded pin

107 fixing screw

10

111 plate spring packages

112 screw

113 plate spring

114 plate spring

15 115 screw head

116 Washer

121 leaf springs

122 holding plate

0 123 guide rail

124 adjusting plate

130 gears

131 frame

25 132 crank

133 Coupling, coupling link

I'l 134 gear element, pedal plate element

135 crank joint

136 coupling joint

30 137 Footplate joint

138 frame joint

142 Bearing seat, arranged eccentrically 152 Rolling bearings, deep groove ball bearings

153 bearing plate

154 bearing seat

155 Rolling bearings, deep groove ball bearings 5 158 Circlip

159 collar bolts

161 hex nut

181 tread plate

0 182 Bearing flange, front

183 bearing flange, rear

184 tread plate bearing, front

185 sliding sleeve

186 pivot pins

5 187 top

188 rubber mat

190 elastically deformable element 0 201 composite body

202 elastomer body

j- '203 metal plate

204 metal plate

205 Threaded hole

5 206 threaded pin

207 fixing screw

221 leaf spring

223 guide rail

30

Claims

Claims:

1. device (10) for muscle stimulation with at least one

Motor (20) and with two motor-driven gearboxes (30,

130), each of said gears (30; 130) comprising a frame (31;

131) and in the frame (31; 131) mounted tread plate member (34; 134), characterized

- That each of these transmissions (30; 130) is a circulatable four-bar linkage,

- That in each case the driven gear member in the frame (30; 130) mounted crank (32; 132) and

- That in each case a crank (32; 132) and in each case a tread plate element (34; 134) by means of a coupling member (33; 133) are hingedly connected.

2. Device (10) according to claim 1, characterized in that the length of both cranks (32; 132) is adjustable.

3. Device (10) according to claim 1, characterized in that the phase angle position of the two cranks (32; 132) is adjustable to each other.

4. Apparatus according to claim 1, characterized in that the rotational speed of each transmission (30; 130) is adjustable.

5. Apparatus (10) according to claim 1, characterized in that e comprises two motors (20) each driving a gear (30; 130).

6. Apparatus (10) according to claim 1, characterized in that the storage of each tread plate element (34; 134) in the frame (31; 131) at least one elastically deformable

Element (90; 190).

7. Apparatus (10) according to claim 1, characterized in that in each case the coupling member (33; 133) and the tread plate member (34; 134) by means of an elastically deformable

Elements (90, 190) are connected.

8. Device (10) according to claim 7, characterized in that the rigidity of the elastically deformable element (90; 190) is adjustable.

Apparatus (10) according to claim 1, characterized in that at least one bearing (37; 38; 137; 138) of each tread element (34; 134) comprises a sensor (89) responsive to deformations.