U.S. patent application number 12/795903 was filed with the patent office on 2010-12-09 for vibrationary exercise equipment.
Invention is credited to Roger Leslie Brown, David Paul Sumners.
Application Number | 20100311552 12/795903 |
Document ID | / |
Family ID | 43301157 |
Filed Date | 2010-12-09 |
United States Patent
Application |
20100311552 |
Kind Code |
A1 |
Sumners; David Paul ; et
al. |
December 9, 2010 |
VIBRATIONARY EXERCISE EQUIPMENT
Abstract
A muscle training apparatus arranged for cyclic concentric and
eccentric loading phases including load imposition means arranged
for a user to exercise against load variation means arranged for
varying the load as between concentric and eccentric loading
phases, a vibrator operational to apply vibration between the user
and the load, a controller operational to control the vibrator and
to vary the extent of vibration as between concentric and eccentric
phases.
Inventors: |
Sumners; David Paul;
(Middlesbrough, GB) ; Brown; Roger Leslie;
(London, GB) |
Correspondence
Address: |
BARKUME & ASSOCIATES, P.C.
20 GATEWAY LANE
MANORVILLE
NY
11949
US
|
Family ID: |
43301157 |
Appl. No.: |
12/795903 |
Filed: |
June 8, 2010 |
Related U.S. Patent Documents
|
|
|
|
|
|
Application
Number |
Filing Date |
Patent Number |
|
|
11733271 |
Apr 10, 2007 |
|
|
|
12795903 |
|
|
|
|
10507150 |
Apr 6, 2005 |
7214170 |
|
|
11733271 |
|
|
|
|
Current U.S.
Class: |
482/111 ;
482/110 |
Current CPC
Class: |
A63B 2225/30 20130101;
A61H 2201/0153 20130101; A63B 21/0087 20130101; A61H 2201/164
20130101; A63B 24/0075 20130101; A63B 21/00058 20130101; A63B
23/0494 20130101; A63B 24/00 20130101; A61H 1/024 20130101; A63B
21/00072 20130101; A63B 21/06 20130101; A63B 21/4017 20151001; A63B
21/0083 20130101; A63B 21/00069 20130101; A63B 2225/15 20130101;
A63B 23/03533 20130101; A61H 23/0263 20130101; A63B 21/00196
20130101; A63B 23/03508 20130101; A61H 23/04 20130101; A61H
2201/1676 20130101; A63B 23/12 20130101; A63B 21/0628 20151001 |
Class at
Publication: |
482/111 ;
482/110 |
International
Class: |
A63B 21/008 20060101
A63B021/008; A63B 21/00 20060101 A63B021/00 |
Claims
1-49. (canceled)
50. A muscle training apparatus arranged for cyclic concentric and
eccentric loading phases and comprising: load imposition means
arranged for a user to exercise against; load variation means
arranged for varying the load as between concentric and eccentric
loading phases; a vibrator operational to apply vibration between
the user and the load, and a controller operational to control the
vibrator and to vary the extent of vibration as between concentric
and eccentric phases.
51. A muscle training apparatus arranged for cyclic concentric and
eccentric loading phases and comprising: load imposition means
operational to impose a load upon muscles of a user; and an
hydraulic system operational to increase the imposed load during
the eccentric phase.
52. A muscle training apparatus as claimed in claim 50 and further
comprising an hydraulic piston/cylinder arrangement operationally
interposed between a user and the load imposition means.
53. A muscle training apparatus as claimed in claim 51 and further
comprising an hydraulic piston/cylinder arrangement operationally
interposed between a user and the load imposition means.
54. A muscle training apparatus as claimed in claim 50 and
operational to impose an increase during the eccentric phase of up
to 120% of the load moved in the concentric phase.
55. A muscle training apparatus as claimed in claim 51 and
operational to impose an increase during the eccentric phase of up
to 120% of the load moved in the concentric phase.
56. A muscle training apparatus as claimed in claim 50 and wherein
the vibration frequency is from 1 Hz to 100 Hz.
57. A muscle training apparatus as claimed in claim 50 and wherein
the vibrator is a rotary valve.
58. A muscle training apparatus as claimed in claim 50 and wherein
the vibration variation control is operational to vary the
vibration randomly.
59. Apparatus as claimed in claim 52 and having a bleed through
said piston.
60. Apparatus a claimed in claim 52 and further comprising a
non-return valve enabling a different resistance to be obtained as
between tensile and compression movement.
61. Apparatus as claimed in claim 52 and further comprising a
pressure relief valve located in said piston.
62. Apparatus as claimed in claim 50 and arranged to load the user
in both directions, push and pull, compression and tension.
63. Apparatus as claimed in claim 50 and which is portable for use
in one hand or between a user's two hands for arm strengthening and
"chest expanding".
64. Apparatus as claimed in claim 50 and equipped with an indicator
of the load being applied.
65. Apparatus as claimed in claim 50 and further comprising a
non-return valve arranged to enable the load to differ as between
the two directions.
66. Apparatus as claimed in claim 65 and further comprising a
control cock arranged to block or open said non-return valve and
convert the apparatus between unidirectional and bi-directional
strength training.
67. Apparatus as claimed in claim 50 and wherein said vibrator
comprises a solenoid valve.
68. Apparatus as claimed in claim 57 and wherein said rotary valve
comprises (i) a housing containing a fluid flow path with a central
axis, (ii) a plug having a sealing face cooperating with said
housing in the closed position to block the fluid path, and (iii) a
support shaft arranged to carry said plug means and being rotatable
on an axis which is normal to and spaced from the axis of said
valve seat and located outside of the flow path so that rotation of
the said shaft moves said plug means relative to said housing.
69. Apparatus as claimed in claim 57 and wherein said valve is
arranged to permit a small throughput of fluid therethrough when
the valve is ostensibly closed.
70. Apparatus as claimed in claim 50 and which is a muscle
strengthening apparatus having a bar arranged for bearing upon the
lower part of a user's shins whereby the user moves said bar
against an adjustable weight.
71. Apparatus as claimed in claim 50 and wherein said vibration is
arranged to be aligned with the direction of loading.
72. Apparatus as claimed in claim 50 and wherein the direction of
vibration is adjustable.
73. Apparatus as claimed in claim 50 and further comprising a data
entry device arranged for programming the operation thereof.
74. Apparatus as claimed in claim 50 and further comprising a
readout device arranged for indicating the weight and/or vibration
applied and the amplitude of apparatus expansion or
compression.
75. Apparatus as claimed in claim 53 and wherein said vibration
facility comprises a rod carrying a helix and a disc held to said
piston and mounted on said rod so that movement of said piston
along said cylinder causes said disc to rotate, there being
channels through said piston and said disc which are thereby
intermittently aligned.
76. An exercise apparatus comprising: resistance means arranged to
provide adjustable resistance to a movement by a user; vibration
means arranged to impart a vibration to the user's muscle or muscle
group being exercised; an input device arranged for converting an
input signal into controls for said resistance means and said
vibration means; an output device arranged to provide an indication
of the program completed; and wherein said vibration means
comprises a piston, connecting rod and cylinder arrangement and a
fluid flow connection between both sides of the piston and at least
one valve interposed in said fluid flow and arranged for
intermittent opening and closing at a frequency between 1 Hz and
100 Hz; and said resistance means is selected from free weights, a
weight machine, a spring resistance, an hydraulic resistance and a
pneumatic resistance.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This is a continuation-in-part of U.S. application Ser. No.
11/733,271 filed Apr. 10, 2007, which is a continuation-in-part of
U.S. application Ser. No. 10/507,150 filed Mar. 12, 2003, which are
both incorporated in their entirety.
BACKGROUND OF THE INVENTION
[0002] The present invention relates to exercise equipment and is
particularly concerned with such sports, exercise, wellbeing and
medical training and therapeutic equipment having the facility to
combine vibration with mechanical loading on the muscles and bone
structure of users.
[0003] The use of vibration in the context of strength training
(where the expression strength training is being used herein to
describe any exercise facility in which a load is applied to
muscles of a user) induces a non-voluntary muscular contraction
called the "tonic vibration reflex". Weight training with
additional vibration has been shown to augment strength and power
over and above that achieved with strength training alone. This
effect is achieved through the recruitment of additional muscle
fibres above the normal recruitment level. Vibration has also
become a common tool used in the retardation of muscle and bone
atrophy on earth and in space.
DESCRIPTION OF RELATED ART
[0004] Currently commercially available weight training devices
rely either on un-modulated loads or full body vibration. These
devices apply no vibrational loading at all, or fail to apply
directly specific frequencies to targeted muscle groups. Some such
full-body vibration systems can also quickly lead to discomfort and
other negative physical side effects.
[0005] A publication in Journal of Sport Sciences 1999, 17, 177-182
discloses the effect of vibrationary stimulation on bilateral
biceps curl exercises. According to this publication the
superimposed vibration during the exercise was transmitted to the
muscles by a specially designed vibratory stimulation device. This
consisted of an electric motor with a speed reduction facility and
eccentric wheel. The load was held by a cable passed through the
eccentric wheel via pulleys. The eccentric rotation elicited
peak-to-peak oscillations of 3 mm with a frequency of 44 Hz. After
vibration damping caused by cable transmission, the acceleration on
the handle was about 30 m/s.sup.-2 (RMS). Vibration from the
two-arms handle was transmitted through the contacting muscles
involved in the pulling action.
[0006] A particular disadvantage associated with the use of
vibration which is directly electrically generated is the
difficulty of applying the vibration directly to the user
throughout the various configurations of the equipment. There is a
mismatch between the mechanical and electrical operation which
impedes obtaining maximum benefit from the application of
vibration. Moreover non-smooth contraction of muscle has been
observed in weight training equipment utilizing electric motor
driven vibration devices.
[0007] We have now devised an improved apparatus for enabling
vibration to be transmitted to a person exercising.
SUMMARY OF THE PRESENT INVENTION
[0008] According to the present invention an exercise apparatus
comprises a fluid pump means operated by movement of the user and
control means arranged for intermittently varying fluid flow in the
pump means thereby to impart vibration to the user.
[0009] A vibration frequency to provide benefit may be from 1 Hz to
100 Hz, preferably from 10 Hz to 35 Hz. Where this is obtained in a
rotary or oscillating, eg solenoid, valve, closure of the valve
every 0.1 to 0.3 seconds for a period which may be 50%, but could
be more or less of the time, ie 0.05 to 0.015 seconds the user will
experience for a very short period an increase in resistance
superimposed on that of the real or simulated weight.
[0010] According to a feature of the invention the fluid pump means
may also incorporate static resistance means whereby the fluid pump
imposes the load as well as the vibration on the user.
[0011] Advantageously the exercise apparatus may comprise a piston
cylinder arrangement whereby tension and compression are effected
as between the piston, via a connecting rod, and the cylinder. Then
a fluid circuit connected to the interior of the cylinder on both
sides of the piston can be arranged to carry the vibration
facility.
[0012] By this means the exercise apparatus can readily be arranged
to load the user in both directions, push and pull, compression and
tension. It can be made relatively compact so as to be portable for
use in one hand or between a user's two hands for arm strengthening
and "chest expanding", although arrangements for such operation
between other parts of the anatomy are also readily possible.
[0013] The static load can be realized in a restrictor or pressure
relief valve means, which are advantageously adjustable to provide
different loads and equipped with an indicator of the load being
applied. By use of a non-return valve for example the load can be
arranged to differ as between the two directions, while a control
cock arranged to block or open the non-return valve can be employed
to convert the apparatus between uni-directional and bi-directional
strength training.
[0014] A perhaps non-adjustable part (or whole) of the resistance
to motion can be obtained in a bleed through the piston, with
differential load being obtained via a non-return valve and or a
pressure relief valve also if necessary located in the piston The
vibration can readily be arranged to differ as between push and
pull as well.
[0015] The fluid may be a gas such as air or nitrogen or a liquid
such as an hydraulic liquid. If, in the case of a liquid, damping
of the vibration is desired and is not achievable by padding with,
for example, foam, or by employing a viscous liquid as the medium,
a gas cushion or valve device may be incorporated to achieve
this.
[0016] Where gas is employed, it has been found that compressing
the gas to a pressure of 4.5 bar creates an effective transmission
of reactive force without excessive damping. Pressures from 2.5 bar
up to 4.5 bar provide progressively less damping action and thus
the absolute pressure to which the system is primed can be used to
effect the maximum reactive force generated and the damping
characteristic of the vibration effect felt by the user.
[0017] According to another feature of the invention the fluid pump
means may be interposed between an operating bar arranged to be
pushed and/or pulled by a user, and a base, which may be a static
part of the apparatus. It is preferable for the fluid pump means to
be linked to the operating bar substantially directly to avoid
losses and unwanted damping of the vibration. Such a fluid pump
vibration means can readily be constructed as a retrofit to an
existing weight training equipment.
[0018] The vibration may be generated in the fluid pump means by a
motorised valve incorporated therein. The valve may be a solenoid
valve, diaphragm valve or a rotary valve inter alia.
[0019] In the case of a solenoid valve of the type constructed to
operate with fluid flow in only one direction a bridge
configuration may be employed. Often also solenoid valves have
limited flow rate capacity for a given reasonable power or a high
flow resistance. The employment of an array of such valves in
parallel to overcome this can confer a particularly significant
advantage, discussed below, that of applying random vibration.
[0020] It is often desirable to employ vibration only when lifting
a weight or in a single direction of motion of the equipment and
this apparatus in accordance with the invention can readily be
arranged for this to occur. Where solenoid valves are used the
preferred unpowered valve status is OPEN such that until powered
the solenoid valve will allow free passage of fluid.
[0021] A preferred solenoid valve is the Festo.TM. low latency
solenoid valve type MHE2-S with a 2 ms (two microsecond) latency
and employing internal electronics to permit fast switching.
[0022] If one or more rotary valves are used instead of solenoid
valves, these can be readily be driven by one or more electric
motors, which may be AC or DC and brush, induction or homopolar
motors. Ideally the motor operation is so controlled that speed or
speeds can be set selected and controlled to an accuracy of 10%,
preferably 1%.
[0023] A yet alternative motor is a stepper motor employing
electronic commutation and multiple poles such as 2 pole, 4 pole,
or 5 pole fixed coil arrangements and multiple poles on the rotor.
This enables half- or micro stepping, allowing for example 200
micro steps per revolution of 1.8.degree. per step. The rate of
revolution can be set by a hardware or software clock signal
applied to selected coils by a dedicated integrated circuit or
discrete electronic hardware control circuits. This makes a stepper
motor particularly suitable in contexts where a variety of valve
speeds is desired. When operating a stepper motor the rate of coil
or coil-pair-energization and thus rotary speed is controlled by
the rate of application of electronic signals. As the rate of
energization may be varied to produce a range of speeds, and the
specific poles selected with respect to their disposition around
the rotor is also selectable, there is a measure of control
available that allows the angular speed to vary within less than
one revolution per second. Thus random or pseudo random variability
in valve opening and closing times may be effected through control
of the stepper motor coil energization order and speed.
[0024] As has been indicated above, it is particularly advantageous
for the applied vibration to be arranged for random or even pseudo
random amplitude and frequency. The effect on muscle development of
such an arrangement is particularly marked. By pseudo random is
meant a cycle of variation long enough to be substantially
unpredictable to the user. Pseudo random variation can be obtained
using two motorised valves, solenoid or rotary inter alia, in
parallel in the fluid flow circuit, and arranged to operate at
different speeds. Thus the combined resistance created varies over
time as valve open and closed times move into and out of
synchronicity.
[0025] The rotary motor driven valve itself may be an offset valve
of the type disclosed in PCT Patent Application PCT/GB2006/050314
and UK Patent Application 0520195.9. This valve comprises (i) a
housing containing a fluid flow path with a central axis, (ii) a
plug having a sealing face cooperating with said housing in the
closed position to block the fluid path, and (iii) a support shaft
arranged to carry said plug means and being rotatable on an axis
which is normal to and spaced from the axis of said valve seat and
located outside of the flow path so that rotation of the said shaft
moves said plug means relative to said housing. The shape of the
vibration pulse obtained with such a rotary valve will depend upon
the nature of the valve core offset and the shape and size of the
core recess.
[0026] Advantages of a valve of this kind are that (1) when fully
open there is no occlusion of the opening, and (2) the valve opens
and closes only once per revolution. This latter reduces or
obviates the gearing which might otherwise be required when
employing a motor the normal speed of which would otherwise impose
too high a vibration frequency.
[0027] Whatever the type of valve employed, when a liquid rather
than a gas is employed as the fluid, it may be advantageous to
permit a small throughput of fluid even when the valve is
ostensibly closed. With a rotary valve this may be achieved with an
appropriate passage through the obturator or a groove
therearound.
[0028] Many weight training equipments carry some form of dampening
structure to provide user comfort, particularly those equipments
which bear upon the user's shins for example. Normally this might
comprise a plastics foam, particularly one which under the
influence of body warmth and pressure distorts to mould itself to
the profile of that part of the body applying the force. It would
be expected that the use of such foams would largely attenuate the
transmission of vibrations. However Conforfoam.TM. type "CF-47
green" produced by E.A.R. Speciality Composites has been found to
have good vibration transmission characteristics without
compromising comfort.
[0029] It may in fact be advantageous, not least from the point of
view of simplicity of retrofit or upgrade assembly, when employing
a foam having good vibration transmission characteristics, to
locate a vibration generating device within the operating arm of an
exercise machine, including within the foam itself.
[0030] There is some evidence to suggest that random direction
vibration may be counter-productive to the efficacy of vibrated
training and that applying the vibration in the direction of muscle
stress yields the better results with reduced fatigue and reduced
potential nausea. A linear vibration mechanism can be achieved
using a fluid circuit as herein described though retrofit in the
arm or foam can be simpler if an electric motor is used to generate
the vibration. The motor may be arranged to drive a crank coupled
through a connecting rod to a crosshead to which is attached a
relatively large mass, the crosshead being constrained by guide
bars to shuttle linearly. Other mechanisms for translating rotary
motion to linear may of course be used.
[0031] A typical application of this embodiment of the invention is
in a leg-extension training apparatus. An arm pivoted at a point
coinciding with the user's knee joints is, in this application,
associated with training weights and carries a padded bar arranged
for bearing low on the legs of the user, a linear vibration device
being located within or inside the padding and arranged so that in
operation the vibration is in the same direction as the force
applied to lift the weight.
[0032] By employing motorised variable flow resistance control
valves in conjunction with microprocessor based controllers the
equipment may be arranged to read smart cards, swipe cards or other
data entry means including keypads, touch screens, voice control or
wirelessly linked data transfer using RFID or other technologies.
In this way the apparatus may be adjusted to suit an individual
user's training and physiological characteristics and specified
programme, according to real time software algorithms, look up
tables or other rules or pre-programmed sequences.
[0033] It may be desired to incorporate readout devices for
indicating the weight and/or vibration applied and the amplitude of
apparatus expansion or compression. To those skilled in the art
there are many ways of detecting the position and direction of
motion of parts of strength training apparatus in accordance with
the invention, including microswitches, electrically resistive
means, capacitive and inductive sensors, opto-electronic devices,
Hall Effect magnetic devices, reed switches or other similar
components which may be read sequentially or incrementally by
interaction with moving parts of the equipment. Electronic means
including simple circuit arrangements creating sequential state
machines or more sophisticated arrangements including stored memory
devices such as RAM or other temporary storage means may be used,
preferably with a microprocessor to control the recording or
processing of information about the order of events such that this
information may be used to switch the vibration inducing solenoid
OPEN for a particular part of the cycle of operation or control
other features of the performance, such as mark-space ratio or if
the weight simulating valves are motorised the balance between
vibrated and background resistance generated by the apparatus or
other parameter thereof. In this case the electronic means of
control can be arranged to apply selectively the vibration
resistance to the user and control the level and timing of all
resistive elements of the load application.
DESCRIPTION OF THE DRAWING
[0034] Various embodiments of the invention will now be described
by way of example with reference to the accompanying drawings, of
which:
[0035] FIG. 1 is a side view of an embodiment of the invention
attached to an exercise machine;
[0036] FIG. 2 is a front view of FIG. 1;
[0037] FIG. 3 is one disc used in a different embodiment of the
invention;
[0038] FIG. 4 is a second disc;
[0039] FIG. 5 shows the discs of FIGS. 2 and 3 in position;
[0040] FIG. 6 shows a breathing apparatus using the invention;
[0041] FIG. 7 shows a hydraulic damping system applied to a weight
machine;
[0042] FIG. 8 is a schematic view of a simple "stand alone" two-way
vibrationary muscle training device;
[0043] FIG. 9 is a schematic view of a simple "stand alone" one-way
vibrationary muscle training device;
[0044] FIG. 10 is a schematic view of a closed circuit vibration
device for fitment in a weight training apparatus and pneumatic
solenoid valve operated;
[0045] FIG. 11 is a schematic view of a closed circuit vibration
device for fitment in a weight training apparatus and having
hydraulic and by-pass valves;
[0046] FIG. 12 is a schematic view of a closed circuit vibration
device operated by a motorised rotary valve;
[0047] FIG. 13 depicts a cutaway valve core used in an offset
rotary valve arranged for one closure per revolution;
[0048] FIG. 14 is a schematic section of a rotary valve having a
core as shown in FIG. 6;
[0049] FIG. 15 is a schematic diagram of the fitment of a closed
circuit vibration device to a weight training apparatus;
[0050] FIG. 16 is a schematic view of a closed circuit vibration
device having two rotary motorised valves in parallel, for inducing
pseudo-random vibration;
[0051] FIG. 17 shows a parallel valve Magnitude vs Frequency
spectrum;
[0052] FIG. 18 shows a parallel valve configuration waveform;
[0053] FIG. 19 shows a full bridge fluid circuit for permitting
uni-directional flow of fluid regardless of piston direction;
[0054] FIG. 20 is a power amplifier circuit for driving a 24v
solenoid valve from a 5v control signal;
[0055] FIG. 21 is a graph of a simple control signal employed in
switching a solenoid valve and the latency of valve operation;
[0056] FIG. 22 is a schematic cross section of a padded vibration
arm with a rotary eccentric bob-weight;
[0057] FIG. 23 is a schematic view of a linear vibration device
showing a crank, a connecting rod, a crosshead and guide bars;
[0058] FIG. 24 is a diagram of a linear vibration device added to a
leg extension machine;
[0059] FIG. 25 is a block diagram illustrating a swipe card
information entry system;
[0060] FIG. 26 is a schematic view of an embodiment of the
invention with piston located valves and mounted in weight training
apparatus;
[0061] FIG. 27 is a schematic view of a stand alone embodiment of
the invention with piston located valves;
[0062] FIG. 28 is a schematic view of a variable vibration
embodiment;
[0063] FIG. 29 is a schematic diagram of a one way vibration
embodiment;
[0064] FIG. 30 is a schematic diagram of an incrementally loaded
embodiment;
[0065] FIG. 31 is a schematic diagram of a variably incrementally
loaded embodiment;
[0066] FIG. 32 is a diagram with a further development, taking as
its starting point the system illustrated in FIG. 31;
[0067] FIG. 33 is a diagram of a system in which the actual weights
is replaced by a compressible system, particularly a gas system;
and
[0068] FIG. 34 is also a diagram of a system in which the actual
weights is replaced by a compressible system, particularly a gas
system.
DETAILED DESCRIPTION OF SPECIFIC EMBODIMENTS
[0069] Referring to FIGS. 1 and 2 a belt (1) is connected at one
end to the weights lifted by the user and the other end is attached
to the hand grips moved by the user. A roller (2) has rubber pads
(3) positioned around its circumference. Roller (4) is positioned
so that the band (1) is gripped between rollers (2) and (4). In
use, as the user pulls on the weights, the band moves and causes
the rollers (2) and (4) to rotate. As the band passes over the pads
(3) a vibration is given to the band which vibration is passed onto
the user via the hand grips. This vibration acts on the muscles
being exercised and the frequency of vibration can be controlled by
the number of pads (3).
[0070] Referring to FIGS. 3, 4 and 5 a first disc (5) has two holes
(6) in it and a second disc (7) has holes (8) of varying size in
it. The two discs are located on a common axis and the disc (5) is
connected to a motor. As the disc (5) is rotated by the motor, the
holes (8) are periodically coincident with the holes (6).
[0071] Referring to FIG. 6, the discs are mounted in a chamber (11)
with an air conduit (10) passing through it with one end connected
to mouthpiece (9). The air conduit is positioned so that it
connects to a hole (8) and so, as one of the holes (6) is
coincident with the hole (8) a continuous air passage is formed
and, as the hole (6) moves out of coincidence, there is an
interruption to the air supply and this periodic interruption
causes a vibration effect in the breathing muscles of the user. The
rate of flow of the air to the user can be controlled by the size
of the hole (8) used and the frequency of vibration controlled by
the speed of rotation of the disc (5).
[0072] Referring to FIG. 7 a weight lifting machine comprises a
fixed framework (21), a sliding member (22) and attached adjustable
weight (23) which may slide up and down guide rails (24) when a
person pulls on cable (25) which is guided over pulley (26), being
connected to the sliding member (22) and weight (23). The sliding
member (22) is attached to a piston (27) which is located in a
cylinder (28).
[0073] When cable (25) is pulled, the sliding member (22) with
attached weight (23) is moved upwards against gravity providing a
working load to the user's muscles, the piston (27) displacing air
in cylinder (28) out through port (29). The air displacement is
checked by a control valve (30) which is driven on and off at the
desired frequency by a controller (32), causing the air flow to be
intermittently interrupted before release to atmosphere via port
(31). The switched air-flow checking action of control valve (30)
provides a time variant damping load over and above that provided
by the lifted weight (33), translating vibration into the
operator's muscles employed in the lifting action.
[0074] The embodiments depicted in FIGS. 8 and 9 are stand alone
vibrationary muscle training devices which may be used for example
between the two hands or, with suitable means for attachment to the
limbs, between any two limbs or even between a limb and another
part of the body, or between one part and another of a jointed
limb.
[0075] Thus, FIGS. 8 and 9 show a piston 100, connecting rod 101
and cylinder 102 arrangement wherein the left hand end of the
cylinder 102 is arranged for association with one limb of a user,
for example, and the connecting rod 101 is arranged for association
with another of the user's limbs. A bypass conduit 103 from the
cylinder at both sides of the piston has, in the case of the FIG. 8
embodiment, two parallel sections, the first incorporating a
controllable valve 104 and the second a controllable valve 105 and
a solenoid valve 106. The solenoid valve 106 is arranged for being
pulsed open and closed at one or more desired frequencies while the
valve 105 is arranged to control the amount of fluid passing
through the solenoid valve 106. The section with the valve 104 has
the function of applying the main resistive force in the apparatus
and the valve 104 is adjustable to vary this force. By adjusting
both valves 104, 105 a ratio of main resistance to pulsed
resistance can be varied.
[0076] The FIG. 9 embodiment has a uni-directional, or non-return
valve 107, in parallel with the other two parallel sections. This
permits free movement of the piston 100 in one direction for
situations where strength training is only required in the one
direction.
[0077] FIGS. 10 to 14 relate particularly, but not necessarily
exclusively, to a vibration device adapted for fitment to a
strength training apparatus, in particular a weight training
apparatus, perhaps by retrofit.
[0078] In FIGS. 10, 11 and 12 there is a piston 200, connecting rod
201, and cylinder 202 arrangement. A bypass conduit 203 from the
cylinder 202 at both sides of the piston 200 has, in the case of
the FIG. 3 embodiment, a solenoid valve 204. The function of the
solenoid valve 204 is, by rapid cyclic opening and closing, to
impart vibration to the fluid in the cylinder. The solenoid valve
204 is accordingly arranged for being pulsed open and closed at one
or more desired frequencies.
[0079] The FIG. 11 embodiment has, as well as the solenoid valve
204 for imparting vibration, a variable opening valve 205 for
effecting control over the resistance experienced.
[0080] The embodiment illustrated in FIG. 10 is particularly suited
for use with a gas such as air or nitrogen, where no additional
damping might be required. The gas is pressurized to 4.5 bar. This
is sufficient to prevent excessive damping.
[0081] The embodiment illustrated in FIG. 11 is particularly suited
for use with an hydraulic liquid. As damping is apt to be required
when a liquid is used, the variable opening valve 205 caters for
this.
[0082] The embodiment illustrated in FIG. 12 has a rotary valve 210
in place of the solenoid valve 204. An electric motor and any
necessary gearbox 211 drives a valve core with a cut-away
permitting selective passage of fluid depending on the relative
angle of the core with respect to the fluid flow ports. The
rotational speed of the valve core sets the derived frequency of
the vibration. The electric motor is of the variable speed
variety.
[0083] FIGS. 13 and 14 illustrate a particular form of a valve 210
for which the rotational speed equates to the vibration frequency.
The valve has a cylindrical core 212 which has a recess 212a and is
offset to a bore 213 of the valve so that when the recess 212a is
presented to the fluid flow bore 213, fluid passes freely through
the bore 213. This valve is of the type disclosed in PCT Patent
Application PCT/GB2006/050314 and UK Patent Application
0520195.9.
[0084] In a variation to the valve 210 particularly useful where
the fluid is a liquid, the core 212 shown in FIG. 6 has a
circumferential groove, illustrated by dotted lines 214. This has
the function of dampening the vibration and rendering it less harsh
to the user.
[0085] The devices shown in FIGS. 10, 11 and 12 are adapted for
fitment between the static frame 300 and the user operated part 301
of a typical strength training apparatus as shown in FIG. 8. The
actual device shown is a weight training device where the user
operated lever arm 301 is pivotally attached to the frame 300. A
wire 302 attached at one end to the arm 301 distal from the pivot
point passes over a frame mounted pulley 303 and is attached at its
other end to a variable weight block 304.
[0086] FIG. 16 depicts a pseudo random vibration apparatus. A fluid
conduit 220 connected into the cylinder 202 at both ends thereof
has two parallel circuit arms 221, 222 in each of which is a rotary
valve 223, 224 driven by a variable motor 225, 226. The speeds of
the motors 225, 226 are controlled by a controller 227 adopted to
control the base speeds of the two motors in accordance with a
desired vibration variation.
[0087] FIG. 17 is a graph of a typical pseudo random vibration
variation achieved with the apparatus described with reference to
FIG. 16 when the two valves 223, 224 are run at different
rotational speeds. The graph represents the Magnitude vs Frequency
spectrum experienced when these two rotational speeds are quite
close and as shown is typical of the situation which arises
whenever the ratio of frequencies is low.
[0088] FIG. 18 translates the graph of FIG. 10 into a waveform of
flow amplitudes vs time.
[0089] The fluid circuitry illustrated in FIG. 19 has a plurality
of solenoid valves 250 in parallel in a one-way valve 251 bridge
circuit associated with a fluid conduit 203. Primarily this
circuitry ensures that vibration is only applied in one direction,
the direction of pressure, and is absent during the relaxation
movement. The employment of a plurality of solenoid valves 250 in
this way enables amplitude and randomness of vibration to be
controlled. The circuit includes a fluid charging/pressurising
valve 252.
[0090] FIG. 20 shows a typical solenoid valve drive circuit
permitting a TTL 0 to 5v DC signal to drive a 24v DC solenoid valve
with catch or flywheel diode to prevent a back emf from the
inductive solenoid coil from damaging the transistor.
[0091] Referring to FIG. 21, as a solenoid valve takes time to
operate, due to the mass of the valve plug and the inductive nature
of the drive coil there is a delay, often called latency, which
limits the maximum speed at which the valve can operate. In many
fast solenoid valves the latency is in the range 2 mS (two
microseconds) to 4 mS. In such cases to turn ON and OFF and
complete one cycle the fastest theoretical on-off cycle or period
will be in the range 4 mS to 8 mS, giving a maximum frequency of
250 Hz to 125 Hz respectively. In practice there are other delays
in reversing the field in a solenoid coil, and damping constraints,
that limit the maximum frequency of operation to 50 Hz. Under load
this may drop to 25 Hz. If higher speeds are required without
resort to specialised solenoid valves, then the motorised rotary
valves also discussed above may be employed.
[0092] FIG. 22 shows a cross section of a bar or lever 400 in a
strength training device subject to vibration in accordance with
the invention. The bar or lever 400 is surrounded by a closed cell
foam 401 supporting an outer tube 402 which is in turn covered by a
foam pad 403. The foam pad 403 is formed of Conforfoam.TM. type
CF-47 green. This foam, whilst conforming to the local shape of,
say, the user's lower shins, is particularly capable of
transmitting vibration without significantly damping it.
[0093] In the particular case shown in FIG. 22, a vibration device
is attached to the interior of the outer tube 402 in a recess in
the foam 401. The vibration device comprises a bob-weight 410
associated with an electric motor 411.
[0094] The linearity of this vibration, constrained for alignment
with the direction of the user's muscle strengthening procedure, is
obtained with a device as depicted in FIG. 22. An electric motor
driven crank 420 in turn drives a connecting rod 421 linked to a
crosshead 422 constrained for reciprocal linear motion by guide
bars 423.
[0095] The tube 402 may be formed of a metal such as an aluminium
alloy and the foam 401 may be a sponge rubber or a "sorbo
rubber".
[0096] In a modification of the device illustrated in FIG. 22 the
configuration of the vibration device is adjustable so that the
vibration direction can be regulated.
[0097] Application of the devices illustrated with reference to
FIGS. 22 and 23 to a leg muscle strengthening apparatus is
illustrated in FIG. 24. This shows a lever 430 associated with an
adjustable weight block 431 and arranged to pivot around a point
432 adjacent a user's knees. The lever 430 carries an arm disposed
for contact with a lower region of a user's shins, the arm being as
described with reference to FIG. 22. The vibration device
illustrated in FIGS. 22, 23 is arranged to vibrate linearly along
the arrowed line 433 in FIG. 24. It is also adjustable so that the
vibration direction can be regulated. FIG. 25 is a block diagram
illustrating a microprocessor based control system for the entry of
a user's programme and accordingly the control of loading and
vibration. Alternative or complementary inputs, in the form of a
swipe card entry unit and a keypad entry unit enable the user to
input his individual programme and to vary it if desired. A USB
entry/save to external device unit provides to the user both an
indication of his progress with the apparatus and any required
modification to the swipe card or user programme store.
[0098] The microprocessor is configured to control the valves and
read any sensors on the apparatus, which responds using stored
programme control configured or modified by keyboard, USB etc
inputs or swipe card. The swipe card can store any personal custom
configuration for the adjustment and regulation of frequency, load
and other parameters such as sensor sensitivity, number of repeat
cycles to be done at each setting etc and store any results
generated on the card as required if swiped before quitting,
perhaps even setting an adjusted programme for a future visit.
[0099] The ROM memory contains the operating system and standard
settings and process control information.
[0100] The RAM memory is used for storing operational parameters
and other data associated with the micro operation during use as
well as usually temporarily storing configuration and personal data
uploaded from the swipe card during use including possibly billing
information for equipment use sent out either via the networking
port/wireless port etc to a central gym management data system.
[0101] The Flash/EEPROM memory is used to store patches uploaded
from the repro port to correct or upgrade the operating
system/process control code in the event of errors or other need
for modifications to the electronic control systems.
[0102] The network port may be used to transfer realtime data to a
central PC or other data store for tracking, billing or performance
mapping of either the machine or individual users. This may be
interactive such that changes to the behaviour of the machine may
be directly effected or a new training configuration be downloaded
to the swipe card for the next usage session by that user.
[0103] It may also be arranged to provide random variation of the
vibration.
[0104] It will be appreciated that any of the devices described
with reference to the accompanying FIGS. 8 to 25 may be employed in
both stand alone strength training devices and in equipment, such
as gymnasium or physiotherapy weight training equipment in which
the weight or other load is applied separately to the vibration
facility.
[0105] In that respect, FIGS. 26 and 27 show similar embodiments of
the invention, one mounted in a weight training apparatus (FIG. 26)
and the other (FIG. 27) as a stand alone device.
[0106] Thus the device illustrated in FIG. 26 is a weight training
apparatus in which a frame 500 carries an adjustable weight block
501 and a pulley 502 over which runs a metal rope 503 attached at
one end to the weight block 501 and at the other to a lever device
(not shown) for operation by a user. Between the weight block 501
and the frame 500 is a vibration generator in the form of a piston
504, hollow connecting rod 505, cylinder 506 and connecting rod
base 507.
[0107] A pair of channels 508 communicate between both faces of the
piston 504 and there is a pair of solenoid valves 509 arranged for
controlling the flow in the channels 508. Electric leads 510 pass
between the valves 509 and a junction 511 in the base 507.
Electricity supply is derived at 512 and controlled at the control
panel 513, which also provides a display of operating
conditions.
[0108] The fluid in the cylinder being gas a cock 514 is provided
by which the gas can be pressurized to 4.5 bar.
[0109] When the weights 501 are lifted and the solenoid valves 509
powered flow from one face of the piston 504 to the other is
interrupted continuously and a vibration imparted to the rope 503.
There being the two solenoid valves 509, the piston cylinder
arrangement can be switched to either simple vibration mode or
pseudo random mode.
[0110] The device illustrated in FIG. 27 comprises a closed
cylinder 600 having a base 600a and in which slides a piston 601.
The piston is mounted rigidly on a hollow connecting rod 602 which
emerges from the cylinder 600 and to which is rigidly mounted a
handle 603. A rod 604 is rigidly attached to the cylinder base 600a
enter and run in the hollow of the connecting rod 602. The rod 604
has a helix formed thereon. A disc 605 is held to the piston 601 so
as to be free to rotate with respect thereto. The disc 605 is
mounted on the rod 604 in such a manner that longitudinal movement
of the piston 601 with respect to the rod 604 will cause the disc
605 to rotate. The disc 605 is of smaller diameter than the piston
601. Channels 606 provided with non-return valves 606a pass through
the piston 601 outboard of the disc 605 to permit a continuous but
restricted fluid flow therethrough in a compression direction and
free flow therethrough in a tensile direction. Channels 607 through
the piston 601 inboard of the circumference of the disc 605 are
arranged to align intermittently with channels 608 through the disc
605. A plug 609 in the handle 603 enables charging the cylinder 600
with fluid and pressurizing same.
[0111] The rod 604 and the disc 605 are made or coated with a low
friction material such as PTFE or nylon. Typically the angle of the
helix to the axis of the rod 604 is 8.degree..
[0112] In operation of the device illustrated in FIG. 27, when
fully charged with fluid, a compressive force between the handle
603 and the base 600a of the cylinder 600 moves the piston/disc
601/605 assembly toward the base 600a, the resistive load depending
upon the size of the channels 606. This movement causes rotation of
the disc 605 with respect to the piston 601, intermittently
aligning the channels 607 and 608 and thereby creating an
intermittent resistance to the compressive movement. When returning
the apparatus to fully extended the non-return valves 606a open to
permit relatively unrestricted fluid flow through the channels
606.
[0113] If adjustability were to be required of a device such as
that illustrated in FIG. 27, this may the most simply be obtained
via an adjustable valve in a channel connecting both ends of the
cylinder 600 and exterior thereto, unless remote controlled valves
were installed in the piston 601 somewhat as illustrated in FIG.
26.
[0114] U.S. Pat. No. 4,930,770 (Baker) discusses various categories
of exercise devices used for muscular development.
[0115] Isokinetic devices regulate or control the rate of muscular
contraction regardless of the force applied to the device by a
user's muscular contraction. For example, in an isokinetic device
where a weight is attached to a bar and where the user initiates
actions with the bar, the isokinetic device only regulates the
speed of the movement of the bar. U.S. Pat. No. 4,483,532 teaches
the use of a centrifugal brake to increase movement resistance as
the velocity of the exercise bar is increased above some preset
value. U.S. Pat. No. 4,363,480 teaches the use of a centrifugally
regulated frictional resistance device to control the speed of a
treadmill regardless of the amount of force exerted by the
user.
[0116] Another class of devices provide for positive only
non-eccentrically loaded use. These devices provide for the
regulation of the resistance force against the user, only when the
bar is moving, but do not control the bar speed during the
exercise, such as when a muscle contracts during a positive
exercise. For example, U.S. Pat. No. 4,354,676 teaches the use of a
computer controlled valve to regulate the internal pressure of a
hydraulic cylinder connected to the exercise bar. U.S. Pat. No.
4,609,190 teaches the use of a double acting hydraulic cylinder
with an assorted control valve for each cylinder to resist the
exercise bar movement by providing a different resisting force for
resisting movement. However, most of these hydraulic devices
provide for positive exercise only.
[0117] Whereas many of these positive only exercise devices utilize
a hydraulic cylinder to vary the resistance force, some machines
use an electrically controlled friction brake which is typically
coupled between the exercise bar and the user. The resisting force
is varied by the amount of friction applied to a rotating member on
the exercise bar. U.S. Pat. No. 4,261,562 teaches the use of a DC
generator as a variable force resistance device in which the
electrical loading coupled to the generator is varied. U.S. Pat.
No. 4,063,726 also utilizes a hydraulic cylinder and having an
electronically controlled valve to vary the resistance force.
[0118] A third category of exercise devices deals with positive and
negative stroke operating devices. This category contains a wide
variety of mechanical, electronic, and electro-mechanical devices
to provide exercise in both positive and negative directions. For
example, U.S. Pat. No. 3,858,873 provides for a use of a spiral cam
coupled between the exercise bar and a stack of metal weights to
provide an increasing force during a positive exercise stroke. U.S.
Pat. No. 3,848,467 uses a speed controlled motor in the negative
stroke and a friction brake in the positive stroke of an exercise.
U.S. Pat. No. 4,569,518 utilizes a variable torque transmitting
clutch for both positive and negative stroke control. U.S. Pat. No.
4,235,437 teaches the use of a hydraulic pump and electrically
controlled valves to vary the force or the speed of positive and
negative strokes.
[0119] Although various exercise devices are described above in
relation to a number of example exercise categories, most of these
devices stress a particular type of exercise for achieving maximum
muscle development. It is generally known that maximum isolation of
a given muscle by a particular exercise device produces the
greatest amount of strength increase during exercise. Secondly,
because the strength of the muscle varies, depending on its degree
of contraction, and because the amount of force that the muscle can
apply varies by the bone-joint angle, the resisting force must vary
as a function of the contraction of the muscle to attain maximal
strength gained during the exercise.
[0120] The various exercise devices described above, although based
on various exercise theories, provide for muscular development by
providing a resistive force to a contracting muscle. Muscle
contraction can be generally classified as being concentric,
isometric, or eccentric. Concentric contraction refers to a
situation of the muscle when it shortens its length. A simple
example of concentric contraction is when a weight is lifted from a
rest position. Because the weight is accelerated from its initial
position, positive work is achieved as the contracting muscle
expends energy in lifting the weight. This is referred to as
positive exercise.
[0121] Isometric contraction occurs when two forces are at
equilibrium so that movement cannot occur. Although work is not
performed, the muscle under contraction still expends energy in
counteracting the other force. Isometric contraction provides for a
holding exercise, which is neither positive or negative. A third
type of contraction is eccentric contraction. A simple example is
the lowering of a weight to its rest position. In eccentric
contraction, the weight is decelerated and the total work performed
is negative because the muscle absorbs energy in decelerating the
weight. Therefore negative exercise is performed by eccentric
contraction. In eccentric contraction, muscle is lengthened from
its contracted or previously contracted position. That is, the
muscle is being lengthened by a load or a force greater than the
muscle's holding force.
[0122] In a concentric contraction exercise, positive strength is
used in which the muscle is shortened against a force or
resistance, such as in lifting a weight. In a concentric exercise
system, also called a positive exercise system, an object is moved
by the muscular contraction, such as by lifting, so that it will
cause the muscle to expend energy and this energy is stored in the
object. In this instance, the lifting force of the muscle must
exceed the resistive force of the object. When the force expended
by the muscle equals the weight of the object, this holding
strength of the muscle provides the isometric contraction. In an
isometric contraction, no movement occurs but energy is expended by
the muscle.
[0123] An eccentric exercise involving negative strength will occur
when the force exerted by the muscle is less than the resistive
force of the object, which was previously lifted. As the object is
lowered, the potential energy stored in the object is converted to
kinetic energy and absorbed by the muscle. The muscle lengthens
from the previously contracted position. An eccentric exercise
system is based on a force overcoming a contracted muscle. That is,
the force (weight) is greater than the muscle's holding force.
[0124] It is generally known that not only is the direction of
exercise important, but emphasis is placed on the type of resistive
force (or load) opposing the muscle to be exercised. An eccentric
load provides a stretching or pulling force against the contracting
muscle and can occur during positive or negative exercise stroke.
An eccentrically loaded exercise system is one in which an object
moved by the muscular contraction stores this energy, not merely
dissipating it, that is the exercise system possesses potential
energy which is available to do work on the contracted muscle
whenever the muscle force becomes less than the force supplied by
the exercise machine.
[0125] In actual life, the combination of eccentric and concentric
contractions operate together, such as when lifting and lowering a
weight. Further, the combination of eccentric and concentric
contractions form a natural type of muscle function called a
"stretch-shortening cycle". The stretch-shortening cycle allows the
concentric contraction to take place with greater force or power
output, as compared to initiating a movement by concentric
contraction alone. This phenomenon is believed to occur partly due
to the elastic nature of the muscle during and immediately after
the eccentric contraction. The lengthening of the contracted muscle
modifies the condition of the muscle such that the stretched muscle
increases its tension and stores potential energy. Part of this
stored energy can be recovered provided that the concentric
contraction occurs rapidly after the eccentric contraction.
[0126] Further, in comparing negative exercise to positive
exercise, negative only exercise produces at least as much, if not
greater, muscle growth than positive only exercise. Strength
increase of as much as 40% has been documented by the use of
negative exercise (Ettington Darden; The Nautilus Bodybuilding
Book; Chapters 13-14; Contemporary Books, Inc; 1982). Furthermore,
the negative exercise provides other advantages, such as stretching
for the improvement of flexibility; pre-stretching for
high-intensity muscular contraction; resistance in the position of
full contraction for full range exercise; and maximum application
of resistance throughout a full range of possible movement.
[0127] Muscles can generate more force eccentrically than
concentrically, whilst superimposed vibration enables a user to
lift a smaller weight than would have been the case without
vibration, the muscle responding as if a much heavier weight had
been lifted. This means that an exercise machine can be somewhat
safer, with less risk of injury, when superimposed vibration is
incorporated, merely because lighter weights can be employed.
Additionally, imposing a vibration during an eccentric phase can
have greater effects than during the concentric phase for
stimulation of the neuromuscular system, leading to greater
training adaptations, i.e. strength. This can all be particularly
important in use by rehabilitation, elderly and clinical
populations where only small weights can be lifted. From a
mechanical viewpoint additional vibration stimulation can lead to a
more efficient return of a weight to the rest configuration.
[0128] Accordingly, providing an additional resistance and
vibration during a lowering, eccentric phase can be very beneficial
for health and performance. This has implications for injury
prevention and recovery, clinical populations and sports
performance.
[0129] The embodiment shown in FIG. 28 comprises a double ended
cylinder 800, a piston 801 therein associated with a shaft 802, a
hydraulic fluid conduit 803 connected into both ends of the
cylinder 800, a rotary valve 804 having a valve core 804a and sited
in the conduit 803 and driven by a motor 805, a motor variable
speed control 806 and a bleed valve/filler point 807 arranged for
loading the circuit with hydraulic fluid and bleeding air from the
conduit 803. There is accordingly a closed circuit filled with
fluid--typically a conventional glycol, silicone or other similar
liquid based hydraulic fluid. The fluid flow is therefore
interrupted by the rotation of the valve core 804a as the ports are
cyclically revealed and closed.
[0130] The electric motor 805 provides mechanical rotation to the
valve core, the rotational speed being controlled by variable speed
control 306.
[0131] A preferred embodiment employs a stepper motor as the
electric motor 805 with the speed controller switching coils of the
stepper motor providing an accurate and controlled rate of
rotational speed proportional to the frequency of the power signals
applied to the stepper motor field coils, the number of field coils
and the number of poles in the rotor.
[0132] Other motors and control means are possible.
[0133] The variable speed control 806 can be pre-set at
manufacture, set for a particular training session type or machine
type, set for a particular training regime associated with a user
exercise profile and be interactive depending on feedback sensors
measuring such parameters as applied force, load--e.g.
weights--setting, rate of work, time duration of exercise or other
appropriate measured individual user exercise or machine
parameters.
[0134] A preferred embodiment of the speed controller 806 employs a
microprocessor based electronic hardware and software solution to
machine control that permits the described interactive system to
respond in real-time to user and sensor inputs. The system may
employ an embedded microcontroller or a PC based solution, with a
software application providing user or system manager programming
through a software user interface, interaction and response
depending on user and sensor inputs and stored programme
control.
[0135] Specific embodiment forms are envisaged such that variants
of this vibrational load system may be retro-fitted to a plurality
of current gym load-training equipment or be incorporated into
new-design systems employing essentially current product forms as
well as completely new mechanisms designed to specifically exploit
the specific attributes of vibrational training.
[0136] The shaft 802 is directly or indirectly coupled to the
mechanism of gym equipment including normal weights or other forms
of load application retained through cables, linkage mechanisms,
gears or other established means.
[0137] When a user moves a weight on a weights machine or performs
other similar load stressing, the muscle group involved recruits
muscle fibre to perform the work, dropping fibres as they become
exhausted and recruiting further muscle in replacement over time.
Typically only a proportion of the muscle fibre is engaged at any
one time, thus it takes some time to exercise all of the muscle
group one wishes to strengthen.
[0138] The "tendon-tap" response is a well known physiological
behaviour whereby frequent cyclical application and removal of a
small load cannot be distinguished from a continuously increasing
load. The body responds by continuing to recruit muscle for as long
as the cyclical load is applied. The application of vibration in
this invention accordingly allows more rapid recruitment and
exercise of the majority of a muscle group compared to conventional
training means. Also, as the majority of muscle in any target group
in engaged, the likelihood of muscle damage through over-work is
minimized and greater weight or frictional loads may be
applied.
[0139] In this embodiment the user works against a normal load such
as lifting a weight or working against a frictional load mechanism.
This engages muscle fibre from the specific target muscle group or
groups involved. In addition, the user is attempting to move the
piston 801 through the cylinder 800. When rotary valve 804 with
valve core 804a is open this action displaces fluid around the
circuit to fill the opposite chamber of the cylinder with little or
no appreciable level of resistance. However, when the valve core
804a has rotated to close the valve ports the user is attempting to
compress an essentially incompressible fluid and perceives a
reactive load directly proportional to that applied by the user in
attempting to create further motion.
[0140] As the valve core 804a is rotating and the ports are
cyclically opened and closed the user perceives an alternating
resistance to motion which invokes the tendon-tap response by their
body, recruiting greater percentages of muscle fibre compared to
conventional weights or other linear load application methods.
[0141] The frequency of the perceived resistance with a simple
on-axis rotating valve core 804a (as shown) will be at double the
rotational frequency of the valve core. More cross ports in the
valve core will proportionally increase the effective resistance
frequency while an offset valve core configured as shown in figure
will present a 1:1 relationship between the valve-core rotational
speed and perceived load frequency.
[0142] An efficacious applied load frequency has been determined by
experiment to be between 1 Hz and 100 Hz but is preferably between
15 Hz and 50 Hz. As the human body increasingly dampens the
amplitude of the load applied as the frequency increases, it
becomes progressively harder to translate a reactive force at
>>35 Hz. However, below about 10 Hz the tendon tap response
fails to occur due to the normal repeat speed of neurological
signalling within the human body. The load application mechanism
also creates some damping such that the stiffer the mechanism
between the user and the piston, the more force will be
effected.
[0143] The described system operates through frequency modulation
of the applied load. The amplitude of the load, with the noted
caveats about damping factors, is also determined by how fast and
hard the user attempts to operate the machine.
[0144] Conventional known frictional and load application methods
are amplitude modulated through either variable weights, variable
leverage ratios, variable fluid flow apertures or variable
frictional control mechanisms.
[0145] Various modifications to the embodiment described with
reference to FIG. 28 may be envisaged. For example, as shown in
FIG. 29, a release mechanism comprising a one-way valve 810
bypasses the cylinder 800 such that in a typical weights machine
configuration, the vibration system only applies a load in the lift
direction and allows free descent of the piston and thence the
operating lever, in the weight "falling" direction.
[0146] In the orientation shown in FIG. 29 the one-way valve is
shut when the operating rod 802 moves the piston 801 UP forcing
fluid through the rotary valve 804. However when the operating rod
802 is moved DOWN the fluid flow reverses and bypasses the rotary
valve 4 through the one way valve 810.
[0147] When connected to the mechanism of exercise
equipment--typically a leg extension machine--the expected
configuration would be such that when lifting a weight or working
against a spring load or other resistive means the operating rod
802 moves UP in the orientation shown in the diagram providing the
described pulsing additional load, whilst when lowering the weight
the one way valve 810 operates and permits free release of the
weights and mechanism allowing to return to its start position
without significant resistance.
[0148] Several rotary valves operating in parallel at different
constant frequencies to create specific harmonic frequencies, or to
create synthesised approximations to square wave, sine wave,
sawtooth wave or other pulse shapes through addition techniques or
pseudo random frequencies through frequency modulation of the valve
speeds.
[0149] An in-circuit variable aperture valve is possible to set the
level of fluid flow resistance controlling the amplitude of the
vibratory reaction force.
[0150] Computer or microcontroller management or a combination
thereof is also possible to create sophisticated FM and AM load
control.
[0151] The embodiment illustrated in FIG. 30 comprises the cylinder
800 and piston 801 and shaft 802, the conduits 803, the rotary
valve 804 (and the filler/bleed 807--not shown), and the one way
valve 810, together with an hydraulic pump 811 and a pressure
switch 812. In this instance the pump 811 and the one way valve 810
are in series with the rotary valve 804 and in parallel with each
other.
[0152] In the orientation shown in FIG. 30, as the operating rod
802 is moved UP and the piston 801 displaces fluid from the top of
the cylinder 800 it will flow through the one way valve 810 and be
subject to pulsed interruptions effected by the rotary valve
804.
[0153] In one embodiment of the system illustrated in FIG. 30 the
rotary pump 811 is continuously pushing fluid in a clockwise loop
also passing through the one way valve 810 and does not essentially
disrupt or affect the flow of fluid from the cylinder 800 through
the rotary valve 804 and thence to the lower part of the cylinder
800 completing the fluid circuit and introducing the previously
described pulsed load.
[0154] However on the downward stroke of the operating lever 802
and the piston 801, fluid flow in the main circuit is reversed,
passing from the lower part of the cylinder 800, through the rotary
valve 804 until it reaches the valve side junction of the rotary
pump 811 and the one way valve 810 and is pumped by the rotary pump
811. If the pump flow rate is set higher than the natural unaided
return flow rate a positive pressure will be felt by the user
moderated by the pulsing caused by the rotary valve 804.
[0155] In another embodiment of the system illustrated in FIG. 30,
to prevent any flow issues in the one way valve 810 and the rotary
pump 811 fluid circuits, the pump 811 may be switched OFF when the
piston 801 is on the UP stroke and flowing through the one way
valve 810. While this is occurring there will be a NEGATIVE
pressure below the piston. Upon lowering the operating rod 802 and
hence the piston 801 a POSITIVE pressure will be generated below
the piston 801 that may be used to turn on the pressure operated
switch 812 in this arm of the fluid circuit that may be used to
turn ON the rotary pump 811 to generate an excess downwards force
on the piston 801, moderated by the pulsing effect of the rotary
valve 804.
[0156] To effect an additional force on the downward stroke of the
piston/operating rod in circuit configurations of a similar nature
to those shown in particular in FIG. 30 one discriminates between
flow directions and pressures within the circuit in order to employ
specific components that may create excess pressure and enhance
flow only on the downward stroke. Typically the apparatus applies
up to a 120% increase in the load during the eccentric part of a
weight lifting cycle, preferably 50-120%.
[0157] In the embodiment shown in FIG. 30 as just above described
two elements are potentially used:
1. A one way valve 810 that discriminates fluid flow
directions--and hence operational--flow DIRECTION to create
different circuit forces on the piston 801 and hence on the
operating rod 802 and user exercise mechanism dependent on user
interaction with these component parts. The rotary pump 811 is
allowed to continue rotating at all times, but is provided with a
circular fluid flow route to prevent this creating forces at the
wrong time. The balance of fluid flows may however prove to be
difficult to control to a satisfactory level of accuracy with such
a simple system. 2. A second embodiment that combines the first
embodiment described above with a pressure switch 812 that detects
the pressure change associated with a reversal of the equipment
operation solves some of these issues by turning off the rotary
pump 811 when not required--for example for the UP stroke and on
again when on the down stroke.
[0158] It is then obvious to one skilled in the art that enhanced
control options may be effected by replacement of the pressure
switch with a pressure transducer and that would allow proportional
control of the pump and hence more precise control of the
system.
[0159] Other sensors such as fluid flow sensors may be employed to
detect additional parameters to facilitate more sophisticated
control means.
[0160] Embedded Microprocessor or PC systems may be employed to
provide complex software management of the system performance and
interactive control means.
[0161] The system illustrated in FIG. 31 is similar to that of FIG.
30 but contains a flow control valve 813 to adjust the amount of
permissible bypass fluid compared to flow into the top of the
cylinder 800. Control of the valve 813 may be preset or
interactive, typically triggered by a pressure switch 812 and
through a control algorithm running on a microprocessor controller
device (not shown) to give more sophisticated interactive control,
typically using an analogue pressure sensor in place of the switch
812. This embodiment, therefore, permits fine adjustment of the
fluid flow paths and hence the delivered force experienced by the
user on the downward stroke of the piston 801.
[0162] The system illustrated in FIG. 32 represents a yet further
development, taking as its starting point the system illustrated in
FIG. 31, with like numbers representing the same elements. However
also incorporated in the hydraulic circuit is a flow sensor 814.
The figure also illustrates items which are also likely to be
associated with the systems illustrated in FIGS. 29-31, namely a
pivoted lever 820 associated with the shaft 802, a cable 821 and
pulley system 822 and weights 823, an input/output (I/O) level and
power interface 824 and a user interface and display 825. The I/O
level and power device 824 interfaces between the motorised valves
813, pump 811, rotary valve 804 (outputs) and flow 814 and pressure
812 sensors (inputs) to the uP (computer) system containing system
firmware, operational software with any algorithms controlling
hardware interactions under program control and interactions with
the user entered through a User Interface (UI). This enables
real-time interactions as well as pre-programmed performance
characteristics.
[0163] Via the User Interface and display 825 the user can select
operating modes such as: [0164] Resistance in up and down
activation modes [0165] Vibration frequency in up and down
vibration modes [0166] Pressure and Flow threshold trigger or
mapping between applied load (user) and the machine
[0167] In the systems illustrated in FIGS. 33 and 34 the system of
actual weights is replaced by a compressible system, particularly a
gas system.
[0168] Referring to FIG. 33, when the lever 850 is moved DOWN the
piston rod 851 attached to the piston 852 is moved up in the
cylinder 853 displacing fluid 854 through the rotary valve 855
driven by the motor 856 that creates a cyclical checking force at
it rotates and presents an open then closed port to the fluid 854.
The fluid 854 then passes through a variable flow control valve 857
that provides a controllable resistance to flow that the user must
work against and thence through a one way valve 858 into the top
chamber 859 of a pressure vessel 860. The increased volume of fluid
displaces the moveable separator 861, typically a sliding piston or
diaphragm, to compress a compressible medium, typically air or
nitrogen gas or a mechanical spring or alternatively a lifted
weight or other mechanical configuration storing energy.
[0169] A vent 862 is provided under the piston to permit free
motion without development of over or under pressures beneath the
piston 852.
[0170] Applied pressure may pass back through the one way valve 863
and variable flow control valve 864 but fluid flow is checked by
the upward motion of the piston 852 and forward flow of fluid
induced by the force created by the user at the lever 850.
[0171] When the user stops moving the lever 850 DOWN there is an
over-pressure in the compressible medium contained in lower chamber
865 of the pressure vessel 860 that displaces the moveable
separator 861 UP moving fluid from the upper chamber 859 through
the one way valve 863 and the variable flow control valve 864 via
the rotary valve 855 that provides a similar alternating cyclical
flow characteristic to that provided during the previously
described downward motion of the Lever 1. Thus the piston 852 is
pushed DOWN and the user must work against this force as the lever
returns upwards to its original position.
[0172] FIG. 33 shows separate variable flow control valves 857 and
864 in the two halves of the circuit such that in co-operation with
the one way valves 858 and 863 different flow resistances may be
set for each direction of lever travel thus varying the imposed
load on the user.
[0173] The benefits of this system over conventional physical
training devices are: [0174] The fluid flow resistances may be
easily altered to suit different users and training regimes; [0175]
The upward and downward strokes of the machine may be altered to
provide differing perceived loads to provide an enhanced
symmetrical training effect on the loaded muscle groups; [0176] The
vibrational component introduced by the provision of a motor driven
rotary valve 855 enhances the training effect and muscle
recruitment as described above.
[0177] Referring to FIG. 34 the configuration is generally the same
as in FIG. 33 but a slide valve 870 has been substituted for the
two one way valves 858, 863.
[0178] In this embodiment, downward motion of the lever 850 moves
the piston 852 upwards in the cylinder 853 displacing fluid 854
through the rotary valve 855 driven by the motor 856 thus inducing
a cyclical checking force to the fluid flow, perceived by the user
as a vibratory load. In the phase of operation shown in FIG. 34
fluid may pass through the upper valve port 871 of the slide valve
870 due to the position of the Slide Valve Core 872.
[0179] The variable flow control valve 857 restricts fluid flow in
this part of the circuit relating to an upward stroke of the piston
852 and may be controlled to provide a variable perceived
resistance to motion in this direction at the lever 850.
[0180] Fluid is then forced into the pressure vessel 860 upper
chamber 859, displacing the moveable separator 861 and thus
compressing the compressible medium in the lower chamber 865.
However, in this embodiment, pressure is not transmitted back to
the user through the variable flow control valve 864 but is checked
by the closed lower valve port 873 of the slide valve 870.
[0181] When the piston 852 reaches the top of its stroke it strikes
the upper operating rod 874 that moves the slide valve core 872 via
the upper linkage 875 and the upper valve linkage 876. This closes
the upper valve port 871 and opens the lower valve port 873
enabling fluid flow from the pressure vessel 860 upper chamber 859
through the variable flow control valve 864, driven by the stored
pressure in the compressible medium in the lower chamber 865 and
transmitted through the moveable separator 861. The returning
displaced fluid passes through the rotary valve 855 driven by the
motor 856 to provide a vibratory checking effect and downward force
on the piston 852.
[0182] It will be noted that as the lower linkage 877 and the upper
linkage 875 are connected to the slide valve core through the lower
valve linkage 878 and the valve upper linkage 876 respectively the
changing of the slide valve core 872 position through the piston
852 striking the upper operating rod 874 also moves the lower
linkage 877 and thus the lower operating rod 879, moving this into
the cylinder 853.
[0183] When the piston 852 reaches the bottom of its stroke it
strikes the projecting tip of the operating rod 879 resetting the
system to its original configuration as shown in FIG. 34, resetting
the slide valve 872 to allow recharging of the pressure vessel 860
by means described above.
[0184] An advantage of the embodiment shown in FIG. 34 compared to
that of FIG. 33 is that the back pressure, and therefore the loads,
perceived by the user in either of the two main states of the
machine, being dictated by the position of the slide valve 872 such
that the variable flow control valves 857 and 864 do not interact
at any phase of the operation, may be more precisely controlled for
optimal load conditions applied to the user.
[0185] Pressure and flow sensors, motorised control valves and
variable motor speed controls may be substituted for manual control
and a fixed speed rotary valve motor to permit interactive control
by a microprocessor system and software algorithm to provide
fine-control over each phase of the system operation including
parameters such as: [0186] Flow Resistance [0187] Flow Rate [0188]
Vibration Frequency
[0189] To one skilled in the art, additional features may be
envisaged such as a safety pressure release valve fitted to the
lower chamber 865 of the pressure vessel 860, a variable volume
lower chamber 865 set by an additional moveable piston or diaphragm
arrangement to control the amount of stored energy in the pressure
vessel and the relationship between the fluid volume and the
compressible medium volume if a gas is employed, a microprocessor
and software or mechanically controlled variable linkage to a
weights or spring mechanism. Similarly the operating rods 874 and
879 may be replaced by Hall Effect sensors triggered by magnets in
the piston 852 associated with amplifiers or by other sensor and
valve operation means to open and close a pair of solenoid or other
electrically driven valves in place of the slide valve 872 and
relating to the position of the piston 852 and these may be
incorporated into a control system operated by a microprocessor
employing a software control algorithm.
[0190] As described above with reference to FIG. 25 the systems
described with reference to FIGS. 28 to 34 may be programmed to be
adaptable to a specific training regime and store and modify the
program automatically according to the performance of the user as
detected by the fitted system sensors.
* * * * *