Patent Grant
7878955
1. Field of the Invention
The present invention is related to the field of mechanical resistance forces used with exercise machines to provide resistance forces when a user is engaged in physical exercise during the time when the machine is in use.
2. Description of the Prior Art
In general, mechanical exercise devices which enable a user to select a specific amount of resistance force for an exercise machine has been known in the prior art. However, the prior art resistance exercise devices suffer from many disadvantages, including being bulky in size, inconvenient to change resistance forces during operation when the user desires to quickly change the resistance force, and are frequently comprised of heavy metal blocks which require the user top go to the weight stack and change the resistance. Other machines have bands to change the resistance. There is a significant need to provide a new type of mechanical resistance apparatus which is compact in size, is light weight and provides an easy way for a user to select a desired resistance force during an exercise routine.
The present invention is an integrated resistance spring force assembly machine which is incorporated into an exercise machine. The integrated spring force assembly is comprised of a plurality of internal transverse sections with each section having a respective constant force spring to output a respective magnitude of a spring resistance force, which serves as the respective force loads when in use, and a force selection mechanism which can be used to selectively activate the respective springs so that the respective force loads can be output to a combined level of resistance for an exercise routine.
Each of the internal transverse sections has an identical structural configuration, comprising a central pulley connected to first and second identical flat constant force springs which are respectively connected to respective first and second side pulleys, wherein the position of the first spring is symmetrical to the position of the second spring relative to a center of the central pulley. Therefore, the first and second springs will expand and each will apply an identical constant force to the central pulley if the central pulley is in rotation. In addition, each central pulley is comprised of a central opening having first and second longitudinal grooves which are positioned around an interior surface of the opening and are positioned 180 degrees apart from each other.
The force selection mechanism is comprised of a plurality of cams positioned in a given relationship to the respective central pulleys, wherein each cam is a cylindrical structure comprising a central square opening and an exterior cylindrical surface. A plurality of pockets are positioned around the respective upper and lower circumferences of the exterior surface of each cam. The pockets are located along an upper circumference and are positioned to be symmetrical with the pockets located along the lower circumference. The pockets are positioned at selected locations relative to the center of each respective cam. In addition, upper and lower ball bearings which are movably positioned along the respective upper and lower circumferences of each cam relative to each pocket serve to engage a given pocket. The respective ball bearings will move in and out of the pockets if each cam is in rotation to thereby cause a cam to be engaged or disengaged. Only one-half of a ball bearing is in a pocket and the other half is in a drive shaft if a force resistance pulley is disengaged. One-half of a ball bearing is in a drive shaft and the other half is engaged to a central pulley if the force resistance pulley is engaged.
The mechanism is further comprised of an elongated force selection square shaft that penetrates through the central openings of the respective cams, a cylindrical pipe (or drive shaft) that serves as a housing for the cams incorporated within the shaft and the respective ball bearings, and a top force selection knob which is mated with a top collar.
The cylindrical pipe (or drive shaft) is comprised of first and second longitudinal sets of transverse openings on the cylindrical wall which are positioned to be 180 degrees apart from each other. In addition, the transverse openings of the first longitudinal set are positioned to match the upper circumferences of the respective cams after the cams that are penetrated by the square shaft are positioned inside of the pipe. The respective pockets in the cam are aligned with the respective openings in the drive shaft. Therefore, half of the ball bearings of the respective cams will be pushed into the respective transverse openings of the cylindrical pipe housing when they are pushed by the respective sections of the exterior surface of the respective cams.
Specifically, one half of each ball bearing is positioned inside of the transverse opening of the housing, and another half of each ball bearing is positioned inside of the groove of the central pulley after the cylindrical pipe is inserted into the central openings of the respective central pulleys. Therefore, the ball bearing that is simultaneously positioned in the groove of the central pulley and the opening of the housing locks the central pulley and housing to thereby transfer a force of a given resistance associated with that section to the central pulley, wherein the force is specifically applied to an exterior force outputting pulley that is connected to an exterior end of the housing. In this setting, the force rotates the central pulley to thereby expand the first and second flat constant springs. Therefore, the expanded springs provide forces to the central pulley which serve as the force loads generated by the integrated resistance spring force assembly.
The top force selection knob and its mating top collar are designed for rotatably selecting one or more cams to be engaged to the respective central pulleys so that variable magnitudes of the spring forces can be selected for use.
Therefore, it is an object of the present invention to provide an integrated spring force assembly machine to provide resistance forces to an exercise machine. The machine is comprised of a plurality of internal transverse sections having respective constant force springs to provide the respective magnitudes of the spring resistance force associated with each section. The internal transverse sections serve as the respective force loads of the resistance transferred to the exercise machine. A force selection mechanism can be used to selectively activate the respective springs so that the respective force loads can be output and provide the desired total level of resistance during an exercise routine.
Further novel features and other objects of the present invention will become apparent from the following detailed description, discussion and the appended claims, taken in conjunction with the drawings.
Referring particularly to the drawings for the purpose of illustration only and not limitation, there is illustrated:
a through 6f are a series of drawings that illustrate the respective structural characteristics of the upper series of pockets and sections of the exterior sides of the respective cams, wherein the drawings are illustrated in sub-
Although specific embodiments of the present invention will now be described with reference to the drawings, it should be understood that such embodiments are by way of example only and merely illustrative of but a small number of the many possible specific embodiments which can represent applications of the principles of the present invention. Various changes and modifications obvious to one skilled in the art to which the present invention pertains are deemed to be within the spirit, scope and contemplation of the present invention as further defined in the appended claims.
Referring to
Referring to FIGS. 1 and 2A-2C, the housing 32 of the assembly 30 is comprised of an outer longitudinal enclosed wall 42 and top and bottom transverse oval shaped covers 44 and 52, wherein the wall 42 further includes a plurality of longitudinal support posts 62, 64, 66, 68, 70 and 72 and a plurality of identical transverse support beams 74, 76, 78 and 80.
The transverse support beams are identical. By way of example, the transverse support beam 74 is a transverse frame structure preferably in the general shape of an oval. It includes a circumferential side wall 74z of the beam having a first proximal end 74x and a second distal end 74y. In a preferred embodiment, the wall has a short height. Six transverse extensions 74a, 74b, 74c, 74d, 74e and 74f having the respective central openings are positioned to extend outwardly on the exterior of the wall 74z, which are symmetrical relative to the longer symmetrical axis, the shorter symmetrical axis and the center of the
As illustrated in
It will be appreciated that the openings 74j and 74h are designed to lock the respective first and second interior axles that penetrate through the respective side pulleys of the assembly 30. It will be further appreciated that there are preferred grooves positioned at the respective top and bottom sides of the wall 74z so that the assembly outer wall 42 can be perfectly assembled.
Referring to
Referring to
As specifically illustrated in
In addition, an additional inward and downward extension 44k is positioned to connect to the side wall 44z, which is opposite to the outward extension 44f, wherein the outward extensions 44f and 44c and the downward extension 44k are aligned with the short symmetrical axis of the top cover 44.
Referring to
In the preferred embodiment, the housing 32 is an assembly comprising five transverse sections 42a, 42b, 42c, 42d and 42e, each having a respective identical sectional enclosed wall 56, 57, 58, 59 and 60, identical longitudinal support posts 62, 64, 66, 68, 70 and 72, and identical transverse support beams 74, 76, 78 and 80.
As illustrated in
Referring further to
As illustrated, the sectional enclosed wall 57 is identical to the sectional enclosed wall 56, comprising a proximal oval end 57x and a distal oval end (not shown). The transverse enclosed support beam 74 has the same transverse dimensions as the bottom cover. In addition, six identical outward extensions of which four—74a, 74b, 74c and 74d—are shown positioned identically to the respective six identical outward extensions of the respective top and bottom covers 44 and 52.
Therefore, it will be appreciated that after assembling the first (bottom) and second sections 42a and 42b of the housing 32, the sectional wall 56 of the bottom section can be fastened, wherein the top and bottom sides of the wall 56 are positioned inside of the respective grooves on the respective circumferential sides walls 74z of the beam 74 and sidewall (comparable to 44z) of the bottom cover 52, and all six longitudinal sectional support posts are threadedly connected between the respective extensions of the respective transverse bottom cover 52 and second transverse support 74. For example, the upward sectional support posts 64a are affixed by the extensions 52b and 74b after the oval shaped bottom cover 52 and transverse support beam 74 are positioned to be aligned with each other, wherein their respective proximal ends 52x and 74x and their respective distal ends are aligned with each other. Similarly, the six upward support posts are affixed by the respective paired extensions, wherein four pairs 52a and 74a, 52b and 74b, 52c and 74c, and 52d and 74d are visible in
In accordance with the above disclosed assembly procedure, it will be appreciated that all five sections 42a, 42b, 42c, 42d and 42e are fastened to form the housing 32. The order of fastening or engagement is provided wherein the bottom transverse cover 52 is connected to the first (bottom) upward sectional wall 56 which is connected to the second transverse support beam 74, which in turn is connected to the second upward sectional wall 57 connected to a third transverse support beam 76, which in turn is connected to a third upward sectional wall 58 connected to a fourth transverse support beam 78, which is connected to a fourth upward sectional wall 59 connected to a fifth transverse support beam 80, which in turn is connected to a fifth upward sectional wall 60 connected to the top cover 44. In summary, the exterior housing 32 includes a set of the upward sectional walls 56, 57, 58, 59 and 60, which are aligned together, wherein their proximal ends 56x, 57x, 58x, 59x and 60x are aligned together and also further aligned with the proximal ends 52x, 74x, 76x, 78x, 80x and 44x of the respective bottom cover 52, transverse support beams 74, 76, 78 and 80, and top cover 44.
In this arrangement, the first series 62 of the fastened longitudinal sectional support posts 62a, 62b, 62c, 62d, and 62e are aligned together. Similarly, the remaining five series of the longitudinal support posts are fastened to be aligned together, including the series 64 of 64a, 64b, 64c, 64d and 64e, the series 66 of 66a, 66b, 66c, 66d, and 66e, and the series 68 of 68a, 68b, 68c, 68d and 68e which are visible in
Referring to
As illustrated in
The central pulley 88 includes an upward circumferential exterior wall 88a connected to a middle interior transverse round plate 88c, which forms an outer wall or rim 88b extending around the circumference of the plate 88c of the pulley. A longitudinal post 88k is positioned on the transverse plate 88c adjacent the rim 88b, wherein the post 88k has a height that is higher that the height of the rim 88b. In addition, the interior transverse plate 88c at the center is crossed by a cylindrical protruding extension 88e having a central opening 88f including an interior circular surface 88g. On the interior surface 88g there are located the first and second longitudinal grooves 88h and 88i which are positioned 180-degrees apart, and are aligned with a direction of the 12 and 6 o'clock position, wherein the outward extension 72e is placed adjacent the 12 o'clock position, and the extension 66e is adjacent the 6 o'clock position.
It will be appreciated that, as compared with the central pulley 88, the first and second side pulleys 92 and 96 have an identical structural configuration including the same thickness as the central pulley 88, except for a smaller pulley diameter. Therefore, the side pulleys 92 and 96 have the respective circumferential outer walls 92a and 96a connected to the respective middle interior transverse round plates 92c and 96c, which forms the respective outer rims 92b and 96b respectively extending around the circumference of the plates 92c and 96c. In addition, the interior transverse plates 92c and 96c at their respective centers are crossed by the respective cylindrical protruding hollow extensions 92g and 96g having the respective central openings 92f and 96f.
Referring again to
As further illustrated, the first end 98a of the first spring 98 is affixed at approximately a 5 o'clock position of the exterior wall 88a of the central pulley 88. Symmetrically, the second end 100a of the second spring 100 is affixed at approximately an 11 o'clock position of the exterior wall 88a of the central pulley. To balance the clockwise force that is applied to the central pulley 88 by the first and second constant force springs 98 and 100, the longitudinal post 88k which is against a left side of the inward transverse extension 72k applies a counter-clockwise force to the central pulley. Therefore, the central pulley 88 is stationary before it is turned counter-clockwise by a user when engaged during an exercise routine.
The constant force springs 98 and 100 are pre-loaded so that the central pulley will be stationary against the stop 88k which rests against the extension (or stop dog) 72k. It will be appreciated that a driving force which is equal to twice the constant force of each spring is needed if it is desired to turn the central pulley 88 counter-clockwise to thereby expand the two springs. These two constant force springs 98 and 100 provide a fixed total force which, by way of example, can be 5 pounds to the central pulley 88 to cause such force to work against rotation of the pulley in the counter-clockwise rotation. It will be appreciated that the total force that is applied to the central pulley by the constant force springs serves as the resistance force during an exercise routine. In this situation, the longitudinal post 88k rotates as the central pulley 88 rotates in the counter-clockwise direction. The central pulley will stop its rotation when the post reaches a right side of the extension 72k. Therefore, the extension 72k serves as a stopper for the present invention.
It will be further appreciated that in an alternative embodiment illustrated in
Following the above explanation, it will be appreciated that forces of different magnitude can be achieved by engaging two sets of constant force springs, wherein each of the constant force springs has a different constant force as compared with the output force of the respective springs 98 and 100 that are disclosed in
Similarly, a third central pulley 116 in the third section 34c will provide a force of twenty pounds when rotated in the counter-clockwise direction since first and second constant force springs 118 and 120 output the same ten-pound resistance force against rotation. In the fourth section 34b, a fourth central pulley 128 will provide twenty-five pounds of the force when rotated in the counter-clockwise direction since the first and second constant force springs 134 and 136 output the same resistance force of twelve and a half pounds against rotation of the central pulley 128 in the counter-clockwise rotation. The fifth central pulley 140 will similarly provide a total resistance force of fifty pounds against rotation of the center pulley since the first and second constant force springs (not shown) output the same resistance force of twenty-five pounds. These are illustrative examples of force. It is within the spirit and scope of the present invention to provide many other sets of forces.
As illustrated in
Referring now to
Referring to
As disclosed, the first and second drawings 6a and 6b which are respectively labeled “5 # up” and “5 # low” are the respective transverse cross-sectional views of the respective upper and lower series of structural areas of the cams including the respective pockets and sections of the cam. The cross-sectional views are taken in alignment with the respective transverse upper and lower circumferences 202 and 204 of the cam 192. Referring to the drawing labeled as “5 # up”, there is illustrated the upper series having various indentations 2a, 4a, 5a, 7a, 9a, 10a, 12a, 14a, 15a, 16a, 17a, 19a, and 21a, which represent the respective pockets positioned and aligned with the upper circumference 202 on the exterior cylindrical side 200. In contrast to the indentations, there are illustrated outward peaks (or plateau) 1a, 3a, 6a, 8a, 11a, 13a, 18a, 20a ans 22a, which represent the corresponding sections of the cam exterior surface 200. As further illustrated, each of the indentations is deep enough so that half of the upper ball bearing 192a will fall into it. In addition, as illustrated, there are a total of 22 structural features in the upper series.
It will be appreciated that half of the upper ball bearing 192a will move in and out of the indentations (or pockets) if it travels around the circumference 202. Alternatively, instead of the movement of the ball bearing 192a, if the cam 192 is rotated around a central axis of the central square hole 194, half of the upper ball bearing 192a will also move in and out of the indentations. It will be appreciated that such in and out movement of the ball bearing is a method by which a specific magnitude of the spring force is selected.
Referring to
Referring to the illustration of
Therefore, it will be appreciated that the upper and lower ball bearings 192a and 192b will have a synchronized outward or inward movement if the cam 192 rotates as the hollow square shaft 184 rotates around its longitudinal central axis, after the cam 192 and the ball bearings 192a and 192b are positioned inside of the cylindrical housing 172, wherein the upper and lower transverse openings 180a and 180b match the respective circumferences 202 and 204 of the cam 192. During the movement, half of the ball bearings 192a and 192b move inwardly to reside in one of the pockets when the respective openings 180a and 180b of the cylindrical housing 172 do not match one of the respective sections of the exterior side 200 of the cam 192. Half of the ball bearings 192a and 192b will move outwardly to reside in the respective transverse openings 180a and 180b of the housing if the openings of the cylindrical housing 172 match one of the respective sections of the exterior side 200 of the cam 192, for example, the respective plateau 1a and having top and bottom ends 176 and 178. The cylindrical drive shaft 172 acts as a bearing cage. The bearing is either halfway in the pipe and halfway in a pocket (disengaged) or halfway in the pipe wall and also halfway into the pulley (so it is engaged). A bearing never fully resides in a cam pocket.
It will be appreciated that the above illustration discloses the preferred embodiment of the cam 192 comprising the upper and lower sets of the structural features. However, it is within the spirit and scope of the present invention to only have one series of the pockets and peaks as an alternative embodiment for each cam of the present invention.
In reference to the structural characteristics and function of the first cam 192 that drives the ball bearings, it will be appreciated that the remaining five cams also have the respective upper and lower sets of the pocket structure with the same function to drive the respective ball bearings in movement. However, to simplify this disclosure of the structural features on each of the other cams, only the upper series of the structure including the pockets will be discussed. The structure of a lower series which is symmetrical to the structure of the upper series will not be discussed in detail.
As illustrated in
Referring to a drawing 6c labeled as “10#” in
If the first and second cams 192 and 206 are aligned together, wherein the plateau 1a of the first cam 192 is aligned with the pocket 1b of the second cam 206, and if the aligned first and second cams 192 and 206 are rotated synchronously, half of the ball bearing 192a of the first cam 192 will move outward when it contacts the plateau 1a. Oppositely, half of a ball bearing 206a of the second cam 206 will simultaneously move inward when it meets the pocket 1b. It will be appreciated that such different positions of the respective ball bearings cause different engagement combinations of cams and pulleys resulting in the respective different magnitudes of the spring resistance force for the user, which will be discussed in detail in a later section of the application.
Similarly, the third cam 220 is comprised of a central square hole 222 top (see
The fourth cam 234 is comprised of a central square hole 236 top (see
The fifth cam 248 is comprised of a central square hole 250 top (see
Referring to
The top collar 282 is comprised of transverse upper and lower ring members 284 and 288, wherein a cylindrical wall 286 connects to the respective exterior circumferences of the ring members. The upper ring member 284 further includes an interior circumference comprising a plurality of tooth receiving members 283, which match the respective tooth members 276 of the force selection knob 268. In a preferred embodiment, there are a total of 22 tooth receiving members.
As illustrated in
Referring to
As illustrated in
Therefore, the bottom round member 278 of the top force selection knob 268 extends through the central hole 51 of the top cover 44 to cover into the upper end 186 of the force selection shaft 184, after a spring 306 is placed to contact between the bottom side 280 of the knob and the top side 196 of the first cam 192. As illustrated in
In this setting, after installing the respective upper and lower positioned ball bearings for each cam, the exterior longitudinal cylindrical housing 172 is positioned to surround the five cams that are penetrated by the central square force selector 184. As illustrated in
Referring again to
It will be appreciated that, according to the situation wherein the locking pin 298 locks the lower ring member 288 of the collar, the interior grooves of the respective central pulleys are aligned with the direction of the 12-6 o'clock position, and the longitudinal posts of the respective central pulleys are against the left sides of the respective inward extensions, in accordance with the example as illustrated in
Referring specifically to
In addition, it will be appreciated that according to the above illustrated cam alignment, only half of the upper and lower ball bearings 192a and 192b of the first cam 192 are pushed by the respective plateaus 1a and 1a′ into the respective upper and lower openings 180a and 180b of the cylindrical housing 172 and the respective grooves 88h and 88i which function as internal engagement means or engagement mechanism. Referring to
It will be further appreciated that in this setting if a user during an exercise routine applies the body force of five pounds for rotating the exterior pulley 164 counter-clockwise through a force transferring means such as a cable 162 (see
The illustrations in
Referring to Table 1, there are illustrated positions labeled as “x” which indicate that the respective exterior side sections of the respective cams are positioned to align with the transverse openings of the housing 172. Therefore, half of the corresponding ball bearings are pushed to reside in the respective openings of the housing 172 and half of the corresponding ball bearing reside in the grooves of the respective central pulleys of the internal structure. This results in connection of the respective internal pulleys to the housing (or drive shaft) 172 of the force selection mechanism 36, so that the exterior pulleys are engaged to provide the corresponding magnitudes of the spring resistance forces when the corresponding constant force springs are expanded.
For example, if only the first (top) cam 192 is selected, the result is that the top interior central pulley 88 is engaged to thereby output the total force of 5 pounds to the exterior pulley 164. This is the resistance force encountered by the user during an exercise routine. As another example, if all five cams are selected, it results in all five central pulleys being engaged to output a total force of 110 pounds. It will be appreciated that other subsets of forces and total forces of any desired amount are within the spirit and scope of the present invention.
It will be appreciated that each tooth member of the force selection knob 268 is labeled by a number selected from 1 to 22, wherein the number corresponds to the position number listed in Table 1. This means that when one of the tooth members 276 is selected, the corresponding cam or cams will be engaged to thereby engage the corresponding central pulley or pulleys.
Referring to
After selecting a desired magnitude of the resistance force, the top knob 268 is released to thereby mate with the upper transverse ring member 284 of the collar 282, which results in the tooth members 276 being positioned into the respective tooth receiving members 283. It will be appreciated that releasing the top knob 268 results in the release of the locking pin 298. Therefore, the housing (or drive shaft) 172 that is engaged by selected ball bearings to the corresponding central pulley or pulleys can transfer the selected magnitude of the spring force to the exterior pulley 164, which generates the resistance force provided to the user during an exercise.
It will be appreciated that the above only discloses the preferred embodiment of the present invention. However, various variations are readily available. For example, the illustrated five cams can be arranged to be an integrated one for easily manufacturing. In addition, as compared with the disclosed five sections of the transverse force load mechanisms, more or less the force load sections are also appropriate according to the spirit and scope of the present invention.
Defined in detail, the present invention is an integrated resistance spring force machine comprising: (a) a plurality of internal transverse sections with each section having a respective constant force spring to output a respective magnitude of a spring resistance force which serves as the respective force loads when in use, and a force selection mechanism which is used to selectively activate one or more respective constant force springs so that the respective force loads of the selected constant force springs can be output to a combined level of resistance; (b) each of the internal transverse sections has an identical structural configuration comprising a central pulley connected to first and second identical flat constant force springs which are respectively connected to respective first and second side pulleys, each central pulley having a pair of oppositely disposed internal grooves, wherein the position of the first spring is symmetric to the position of the second spring relative to a center of the central pulley so that the first and second springs will expand and each will apply an identical constant force to the central pulley if the central pulley is in rotation; (c) the force selection mechanism comprised of a plurality of cams positioned in a given relationship to the respective central pulleys, wherein each cam is a cylindrical structure comprising a central square opening and an exterior cylindrical surface with a plurality of alternating pockets and plateaus positioned around respective upper and lower circumferences of the exterior surface of each cam, respective upper and lower ball bearings which are movably received in the respective upper and lower circumferences of each cam so that half of the respective ball bearings will be either in or out of the pockets when its respective cam is rotated; (d) an elongated force selection square shaft that penetrates through the central openings of the respective cams, a cylindrical housing that surrounds the cams and serves as a housing for the cams, and a force selection knob which is mated with a collar and coordinated with the cams to cause the cams to rotate by a given turn when the force selection knob is rotated by a given rotational turn; and (e) the cylindrical housing comprised of first and second longitudinal sets of transverse longitudinally spaced apart openings on a cylindrical wall of the housing, wherein each opening from a first set is positioned 180 degrees apart from each opening in the second set, the respective transverse openings of the first longitudinal set are respectively positioned to match the upper circumferences of the respective cams and the transverse openings of the second longitudinal set are respectively positioned to match the lower circumferences of the respective cams so that some of the ball bearings of the respective cams will be aligned with a plateau of a cam and thereby half of such ball bearings will be pushed so that it rests partially in a respective transverse opening of the housing and partially in an internal groove of a central pulley, and half of some of the ball bearings will remain in a pocket of a cam and half of the ball bearings will remain in an opening of the housing if a plateau is not aligned with an opening in the housing whereby the engagement of a ball bearing in an opening of the housing and a corresponding internal groove of a central pulley causes a resistance force from the constant force springs associated with that cam to be engaged.
Defined broadly, the present invention is an integrated resistance spring force machine comprising: (a) a plurality of internal transverse sections with each section having a respective constant force spring to output a respective magnitude of a spring resistance force which serves as the respective force loads when in use, and a force selection mechanism which is used to selectively activate one or more respective constant force springs so that the respective force loads of the selected constant force springs can be output to a combined level of resistance; (b) each of the internal transverse sections has a structural configuration comprising a central pulley connected to first and second flat constant force springs which are respectively connected to respective first and second side pulleys so that the first and second springs will expand and each will apply a constant force to the central pulley if the central pulley is in rotation, each central pulley having a pair of spaced apart engagement mechanisms; (c) the force selection mechanism comprised of a plurality of cams positioned in a given relationship to the respective central pulleys, wherein each cam is comprised of a central opening and an exterior surface with a plurality of alternating pockets and plateaus positioned around respective upper and lower areas of the exterior surface of each cam, respective upper and lower ball bearings which are movably received in the respective upper and lower area of the exterior surface of each cam so that half of the respective ball bearings will be either in a pocket or out of a pocket and on a plateau when its respective cam is rotated; (d) an elongated force selection shaft that penetrates through the central openings of the respective cams, an external sleeve that surrounds the cams and serves as a housing for the cams, and a force selection knob which is coordinated with the cams to cause the cams to rotate by a given turn when the force selection knob is rotated by a given rotational turn; and (e) the sleeve comprised of first and second longitudinal sets of transverse longitudinally spaced apart openings on a wall of the sleeve, wherein each opening from a first set is positioned at a given distance apart from each opening in the second set, the respective transverse openings of the first longitudinal set are respectively positioned to match the upper surface areas of the respective cams on a respective engagement mechanism of a central pulley and the transverse openings of the second longitudinal set are respectively positioned to match the lower surface areas of the respective cams and a respective engagement mechanism of the central pulley so that half of selected of the ball bearings of the respective cams will be pushed from a plateau into the respective transverse openings of the sleeve and corresponding engagement mechanism of a central pulley, half of some of the ball bearings will remain in a pocket of a cam and half in a transverse opening of the sleeve if a plateau is not aligned with an opening in the sleeve whereby the engagement of a half of a ball bearing in an opening of a sleeve and half of a ball bearing in a corresponding engagement mechanism of a central pulley cause a resistance force from the constant force springs associated with that cam to be engaged.
Defined more broadly, the present invention is an integrated resistance spring force machine comprising: (a) a plurality of internal transverse sections with each section having a respective constant force spring to output a respective magnitude of a spring resistance force which serves as the respective force loads when in use, and a force selection mechanism which is used to selectively activate one or more respective constant force springs so that the respective force loads of the selected constant force springs can be output to a combined level of resistance; (b) each of the internal transverse sections has a structural configuration comprising a central pulley connected to at least one constant force spring which is connected to at least one side pulley so that the at least one spring will expand and will apply a constant force to the central pulley if the central pulley is in rotation; (c) the force selection mechanism comprised of a plurality of cams positioned in a given relationship to the respective central pulleys, wherein each cam is comprised of a central opening and an exterior surface with a plurality of pockets positioned around an area of the exterior surface of each cam, respective ball bearings which are movably received in the respective area of the exterior surface of each cam so that half of the respective ball bearings will be either in or out of the pockets when its respective cam is rotated; (d) an elongated force selection shaft that penetrates through the central openings of the respective cams, an external sleeve that surrounds the cams and serves as a housing for the cams, and a force selection knob which is coordinated with the cams causes the cams to rotate by a given turn when the force selection knob is rotated by a given rotational turn; and (e) the sleeve comprised of at least one set of transverse longitudinally spaced apart openings on a wall of the sleeve, the respective transverse openings are respectively positioned to match the exterior surface area containing pockets of each respective cam so that half of some of the ball bearings of the respective cams will be pushed into the respective transverse openings of the sleeve and each central pulley having at least one engagement mechanism which receives half of a ball bearing if it is pushed out of a pocket and into an opening in the sleeve, whereby the engagement of half of a ball bearing in an opening of a sleeve and half of a ball bearing pushed into the engagement mechanism of a central pulley causes a resistance force from the at least one constant force spring associated with that cam to be engaged, and some of half of the ball bearings will remain in a pocket of a cam and half in an opening in the sleeve if it is not engaged.
Defined even more broadly, the present invention is an integrated resistance spring force machine comprising: (a) a plurality of internal transverse sections with each section having a respective constant force spring to output a respective magnitude of a spring resistance force which serves as the respective force loads when in use, and a force selection mechanism which is used to selectively activate one or more respective constant force springs so that the respective force loads of the selected constant force springs can be output to a combined level of resistance; (b) each of the internal transverse sections has a structural configuration comprising a central pulley connected to first and second flat constant force springs which are respectively connected to respective first and second side pulleys so that the first and second springs will expand and each will apply a constant force to the central pulley if the central pulley is in rotation; and (c) the force selection mechanism comprised of means by which at least one respective pulley of one or more internal transverse sections is engaged to thereby cause a resistance force from the constant force springs associated with that internal transverse section to be engaged.
Defined even more broadly, the present invention is an integrated resistance spring force machine comprising: (a) a plurality of internal transverse sections with each section having a respective constant force spring to output a respective magnitude of a spring resistance force which serves as the respective force loads when in use, and a force selection mechanism which is used to selectively activate one or more respective constant force springs so that the respective force loads of the selected constant force springs can be output to a combined level of resistance; (b) each of the internal transverse sections has a structural configuration comprising a central pulley connected to at least one constant force spring which is connected to a respective side pulley so that the spring will expand and will apply a constant force to the central pulley if the central pulley is in rotation; and (c) the force selection mechanism comprised of means by which at least one respective pulley of one or more internal transverse sections is engaged to thereby cause a resistance force from the at least one constant force spring associated with that internal transverse section to be engaged.
Defined even more broadly, the present invention is an integrated resistance spring force assembly machine comprising: (a) a plurality of internal transverse sections with each section having a respective constant force spring to output a respective magnitude of a spring resistance force, which serves as the respective force loads when in use, and a force selection mechanism which can be used to selectively activate the respective springs so that the respective force loads can be output to a combined level of resistance for an exercise routine; (b) each of the internal transverse sections has a structural configuration comprising a central pulley engaging at least one constant force spring so that the spring will expand and will apply a constant force to the central pulley if the central pulley is in rotation; and (c) the force selection mechanism comprised of means by which at least one respective pulley of one or more internal transverse sections is engaged to thereby cause a resistance force from the constant force spring associated with that internal transverse section to be engaged.
Of course the present invention is not intended to be restricted to any particular form or arrangement, or any specific embodiment, or any specific use, disclosed herein, since the same may be modified in various particulars or relations without departing from the spirit or scope of the claimed invention hereinabove shown and described of which the apparatus or method shown is intended only for illustration and disclosure of an operative embodiment and not to show all of the various forms or modifications in which this invention might be embodied or operated.
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| 6126580 | Francis et al. | Oct 2000 | A |
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| 6929589 | Bruggemann et al. | Aug 2005 | B1 |
