Patent Description:
This application relates generally to stationary exercise machines having reciprocating members.

Certain stationary exercise machines with reciprocating leg and/or arm portions have been developed. Such stationary exercise machines include stair climbers and elliptical trainers, each of which typically offers a different type of workout. For example, a stair climber may provide a lower frequency vertical climbing simulation while an elliptical trainer may provide a higher frequency horizontal running simulation. Additionally, these machines may include handles that provide support for the user's arms during exercise.

<CIT> provides an example of a stationary exercise machine with reciprocating foot and/or hand members, where the foot motion can simulate a climbing motion. The reciprocating handles can move in coordination with the foot via a linkage to a crank wheel and variable resistance can be provided.

However, the connection between the handles and the leg portions of traditional stationary exercise machines may not enable sufficient exercise of the user's body. It may therefore be desirable to provide an improved stationary exercise machine which addresses one or more of the problems in the field and which generally improves the user experience.

This application generally provides a stationary exercise machine. In accordance with the present disclosure, a stationary exercise machine includes a frame, a crankshaft coupled with the frame and rotatable about a crankshaft axis, first and second crank arms rigidly coupled with respective opposite sides of the crankshaft, wherein rotation of at least one of the first or second crank arms causes rotation of the crankshaft about the crankshaft axis, first and second intermediate crank arms rigidly coupled with the first and second crank arms, respectively, and first and second handles operatively coupled with the first and second intermediate crank arms, respectively, at respective pivot axes to convert a user's input force at the first and second handles into a moment on the crankshaft, wherein the respective pivot axes are spaced a distance from the crankshaft axis and orbit the crankshaft axis to define respective virtual crank arms extending between the respective pivot axes and the crankshaft axis.

In some examples, the first and second intermediate crank arms are angularly offset from the first and second crank arms, respectively, to define an angle between the first and second intermediate crank arms and the first and second crank arms, respectively.

In some examples, the stationary exercise machine further includes first and second upper reciprocating members pivotally coupled with the first and second intermediate crank arms, respectively, at the respective pivot axes and pivotally coupled with the first and second handles, respectively. In some examples, the first and second intermediate crank arms are positioned laterally inside of the first and second upper reciprocating members, and the first and second crank arms are positioned laterally inside of the first and second intermediate crank arms. In some examples, the first and second upper reciprocating members are pivotally coupled with first and second extensions of the first and second handles, respectively. In some examples, the first and second upper reciprocating members comprise first and second rigid links, respectively.

In some examples, the moment comprises a first moment and the respective pivot axes comprise respective first pivot axes, and further comprising first and second pedals operatively coupled with the first and second crank arms, respectively, at respective second pivot axes to convert a user's input force at the first and second pedals into a second moment on the crankshaft. In some examples, the second moment is larger than the first moment. In some examples, the stationary exercise machine further includes first and second lower reciprocating members pivotally coupled with the first and second crank arms, respectively, at the respective second pivot axes, and coupled with the first and second pedals, respectively, at a location distal from the respective second pivot axes. In some examples, the first and second lower reciprocating members are positioned laterally between the first and second crank arms and the first and second intermediate crank arms, respectively. In some examples, the stationary exercise machine further includes first and second inclined members coupled with the frame, and first and second pairs of rollers coupled with the first and second lower reciprocating members, respectively, wherein the first and second pairs of rollers travel along a length of the first and second inclined members, respectively. In some examples, the first and second pairs of rollers each include first and second rollers coupled together with an axle, and the first and second rollers of the first and second pairs of rollers travel along separate inclined members of the first and second inclined members, respectively.

In some examples, the first and second crank arms each include a first end rigidly coupled with the crankshaft and a second end spaced from the crankshaft axis, and the first and second intermediate crank arms each include a first end rigidly coupled with the second end of a respective crank arm of the first and second crank arms, and a second end defining a respective pivot axis of the respective pivot axes. In some examples, the stationary exercise machine further includes first and second upper reciprocating members each including a first end pivotally coupled with the second end of a respective intermediate crank arm of the first and second intermediate crank arms, and a second end pivotally coupled to a respective handle of the first and second handles. In some examples, the stationary exercise machine further includes first and second lower reciprocating members each including a forward end pivotally coupled with the second end of a respective crank arm of the first and second crank arms and the first end of a respective intermediate crank arm of the first and second intermediate crank arms. In some examples, the forward ends of the first and second lower reciprocating members are positioned laterally between the second ends of the first and second crank arms and the first ends of the first and second intermediate crank arms, respectively. In some examples, the stationary exercise machine further includes first and second pedals coupled with rearward ends of the first and second lower reciprocating members, respectively.

In some examples, the stationary exercise machine further includes a resistance mechanism operatively coupled with the crankshaft to resist rotation of the crankshaft about the crankshaft axis.

The description will be more fully understood with reference to the following figures, in which components may not be drawn to scale, which are presented as various embodiments of the exercise machine described herein and should not be construed as a complete depiction of the scope of the exercise machine.

Described herein are embodiments of stationary exercise machines having reciprocating foot and/or hand members, such as foot pedals that move in a closed loop path. The disclosed machines may provide variable resistance against the reciprocal motion of a user, such as to provide for variable-intensity interval training. Some embodiments may include reciprocating foot pedals that cause a user's feet to move along a closed loop path that is substantially inclined, such that the foot motion simulates a climbing motion more than a flat walking or running motion. Some embodiments may include hand members that are configured to move in coordination with the foot pedals and allow the user to exercise upper body muscles. Resistance to the hand members may be proportional to resistance to the foot pedals. Variable resistance may be provided via a rotating air-resistance based fan-like mechanism, via a magnetism based eddy current mechanism, via friction based brakes, and/or via other mechanisms, one or more of which may be rapidly adjusted while the user is using the machine to provide variable intensity interval training.

<FIG> show an exemplary embodiment of an exercise machine <NUM>. The machine <NUM> may include a frame <NUM>, and the frame <NUM> may include a base <NUM> for contact with a support surface, a lower support structure <NUM> extending from the base <NUM> to an upper support structure <NUM>, and inclined members <NUM> that extend between the base <NUM> and the lower support structure <NUM>. A cross brace <NUM> may connect the inclined members <NUM> to the lower support structure <NUM>. The various components shown in <FIG> are merely illustrative, and other variations, including eliminating components, combining components, rearranging components, and substituting components are all contemplated.

As reflected in the various embodiments described herein, the machine <NUM> may include an upper moment-producing mechanism <NUM>. The machine may also or alternatively include a lower moment-producing mechanism <NUM>. The upper moment-producing mechanism <NUM> and the lower moment-producing mechanism <NUM> may each provide an input into a crankshaft <NUM> to rotate the crankshaft <NUM> about axis A. Each mechanism <NUM>, <NUM> may have a single or multiple separate linkages that produce the moment on the crankshaft <NUM>. For example, the upper moment-producing mechanism <NUM> may include one or more upper linkages extending from the handles <NUM> to the crankshaft <NUM>. The lower moment-producing mechanism <NUM> may include one or more lower linkages extending from the pedal <NUM> to the crankshaft <NUM>. In one example, the machine <NUM> may include left and right upper linkages, each including a plurality of links configured to connect an input end (e.g., a handle end) of an upper linkage to the crankshaft <NUM>. Likewise, the machine <NUM> may include left and right lower linkages, each including a plurality of links configured to connect an input end (e.g., a pedal end) of a lower linkage to the crankshaft <NUM>. The crankshaft <NUM> may have a first side and a second side and may be rotatable about the crankshaft axis A. The first side of the crankshaft may be connected, for example, to the left upper and lower linkages, and the second side of the crankshaft may be connected, for example, to the right upper and lower linkages.

In various embodiments, the lower moment-producing mechanism <NUM> may include a first lower linkage and a second lower linkage corresponding to a left and right side of the machine <NUM>. Each of the first and second lower linkages may include one or more links operatively arranged to transform a force input from the user (e.g., from the lower body of the user) into a moment about the crankshaft <NUM>. For example, the first and second lower linkages may include one or more of first and second pedals <NUM>, first and second rollers <NUM>, first and second lower reciprocating members <NUM> (also referred to as foot members or foot links <NUM>), and/or first and second crank arms <NUM>, respectively. The first and second lower linkages may operably transmit a force input from the user into a moment about the crankshaft <NUM>. For example, the pedals <NUM> may provide an input into the crankshaft wheel <NUM> through a lower linkage of the first and second lower reciprocating member <NUM> and the first and second crank arms <NUM>.

The machine <NUM> may include a crank wheel <NUM> which may be rotatably supported by the frame <NUM> (for example at the connection of the lower support structure <NUM> to the upper support structure <NUM>) about the crank axis A. The first and second crank arms <NUM> may be fixed relative to the crankshaft <NUM>, which in turn may be fixed relative to the crank wheel <NUM>. The crank arms <NUM> may be positioned on opposite sides of the crank wheel <NUM>. The crank arms <NUM> may be rotatable about the crank axis A, such that rotation of the crank arms <NUM> causes the crankshaft <NUM> and the crank wheel <NUM> to rotate about the crank axis A. The first and second crank arms <NUM> may extend from the crankshaft <NUM> (e.g., from axis A) in opposite radial directions to their respective radial ends. For example, the first side and the second side of the crankshaft <NUM> may be fixedly connected to the output ends of the first and second crank arms <NUM> and the input ends of each crank arm <NUM> may extend radially from the connection between the respective crank arm <NUM> and the crankshaft <NUM>. First and second lower reciprocating members <NUM> may have forward ends (i.e., output ends) that are pivotally coupled to the radial ends (i.e., input ends) of the first and second crank arms <NUM>, respectively. The rearward ends (i.e., input ends) of the first and second lower reciprocating members <NUM> may be coupled to first and second foot pedals <NUM>, respectively. The rearward ends (i.e., input ends) of the first and second lower reciprocating members <NUM> may thus be interchangeably referred to as pedal ends.

One or more rollers <NUM> may be coupled to the first and second lower reciprocating members <NUM>, respectively. For example, the one or more rollers <NUM> may be coupled to first and second lower reciprocating members <NUM> proximate the first and second pedals <NUM> (for example, the one or more rollers <NUM> may extend from forward ends of the first and second pedals <NUM>. The first and second pedals <NUM> may be operable for a user to stand on and provide an input force to the first and second lower reciprocating members <NUM>. The rollers <NUM> may rotate on and travel along the inclined members <NUM>. For example, the rollers <NUM> may rollingly translate along the inclined members <NUM> of the frame <NUM> to define a travel path for the rollers <NUM>. Referring to <FIG>, a pair of rollers <NUM> and an axle <NUM> may be provided for each lower reciprocating member <NUM>. The rollers <NUM> may travel along separate inclined members <NUM>, which may be spaced apart from one another and coupled together by cross braces <NUM>, <NUM>. The cross braces <NUM>, <NUM> may be coupled with opposing ends of the inclined members <NUM>. One cross brace <NUM> may couple upper ends of the inclined members <NUM> to the lower support structure <NUM>, and the other cross brace <NUM> may couple lower ends of the inclined members <NUM> to the base <NUM>. In some embodiments, a single roller <NUM> is provided for each lower reciprocating member <NUM>. In alternative embodiments, other bearing mechanisms may be used to provide translational motion of the lower reciprocating members <NUM> along the inclined members <NUM> instead of or in addition to the rollers <NUM>, such as sliding friction-type bearings.

When the foot pedals <NUM> are driven by a user, the pedal ends of the lower reciprocating members <NUM> (also referred to as foot members <NUM>) may translate in a substantially linear path via the rollers <NUM> along the inclined members <NUM>. In alternative embodiments, the inclined members <NUM> may include a non-linear portion, such as a curved or bowed portion, such that the pedal ends of the lower reciprocating members <NUM> translate in non-linear path via the rollers <NUM> along the non-linear portion of the inclined members. In these embodiments, the non-linear portion of the inclined members may have any curvature, such as a curvature of a constant or non-constant radius, and may include convex, concave, and/or partially linear surfaces for the rollers <NUM> to travel along. In some embodiments, the non-linear portion of the inclined members may have an average angle of inclination of at least <NUM>°, and/or may have a minimum angle of inclination of at least <NUM>°, relative to a horizontal ground plane.

The forward (i.e., output ends) of the foot members <NUM> may move in circular paths about the crank axis A, which circular motion may drive the crank arms <NUM> and the crank wheel <NUM> in a rotational motion about axis A. The circular movement of the output ends of the foot members <NUM> may cause the pedals <NUM> to pivot as the rollers <NUM> translate along the inclined members <NUM>. The combination of the circular motion of the output ends of the lower reciprocating members <NUM>, the linear motion of the pedal ends along the inclined member <NUM>, and the pivotal motion of the pedals <NUM> may cause the pedals <NUM> to move in non-circular closed loop paths, such as substantially ovular and/or substantially elliptical closed loop paths. For example, with reference to <FIG>, a point F at the front of the pedals <NUM> may traverse a path <NUM> and a point R at the rear of the pedals may traverse a path <NUM>.

The closed loop paths traversed by different points on the foot pedals <NUM> may have different shapes and sizes, such as with the more rearward portions of the pedals <NUM> traversing longer distances. For example, the path <NUM> may be shorter and/or narrower than the path <NUM>. A closed loop path traversed by the foot pedals <NUM> may have a major axis defined by the two points of the path that are furthest apart. The major axis of one or more of the closed loop paths traversed by the pedals <NUM> may have an angle of inclination closer to vertical than to horizontal, such as at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, and/or at least <NUM>°, relative to a horizontal plane defined by the base <NUM>. As shown in <FIG>, to cause such inclination of the closed loop paths of the pedals, the inclined members <NUM> may include a substantially linear portion over which the rollers <NUM> traverse. The inclined members <NUM> may form a large angle of inclination α relative to the horizontal base <NUM>, such as at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, at least <NUM>°, and/or at least <NUM>°. This large angle of inclination which sets the path for the foot pedal motion may provide a user with a lower body exercise more akin to climbing than to walking or running on a level surface. Such a lower body exercise may be similar to that provided by a traditional stair climbing machine.

In various embodiments, the upper moment-producing mechanism <NUM> may include a first upper linkage and a second upper linkage corresponding to a left and right side of machine <NUM>. Each of the first and second upper linkages may include one or more links operatively arranged to transform a force input from the user (e.g., from the upper body of the user) into a moment about the crankshaft <NUM>. For example, the first and second upper linkages may include one or more of first and second handles <NUM>, first and second links <NUM>, first and second upper reciprocating members <NUM>, and/or first and second intermediate crank arms or links <NUM>, respectively. The first and second upper linkages may operatively transmit a force input from the user, at the handles <NUM>, into a moment about the crankshaft <NUM>. For example, the handles <NUM> may provide an input into the crankshaft <NUM> through an upper linkage of the first and second links <NUM>, the first and second reciprocating members <NUM>, and the first and second intermediate crank arms <NUM>. Rotation of the crankshaft <NUM> may cause the upper and lower linkages of the machine <NUM> to move relative to each other. The first and second handles <NUM> may be pivotally coupled to the frame <NUM>, such as the upper support structure <NUM>, and may pivot about a horizontal axis D (see <FIG>). The machine <NUM> may include first and second handles <NUM> fixedly coupled to the frame <NUM>, such as the upper support structure <NUM>, for a user to grasp with their hands while exercising their legs.

With reference to <FIG> and <FIG>, the handles <NUM> may be rigidly connected to the input end of respective first and second links <NUM> such that reciprocating pivotal movement of the handles <NUM> about the horizontal axis D causes corresponding reciprocating pivotal movement of the first and second links <NUM> about the horizontal axis D. For example, the first and second links <NUM> may be cantilevered off of the first and second handles <NUM> at the pivot aligned with pivot axis D. Each of the first and second links <NUM> may form angle ω with the respective handles <NUM>. The angle ω may be measured from a plane passing through the axis D and the curve in the handle <NUM> proximate the connection to the link <NUM>. The angle ω may be any angle such as angles between <NUM> and <NUM> degrees. The angle ω may be an angle that is most comfortable to a single user or an average user. In some embodiments, the first and second links <NUM> may be formed integrally with the first and second handles <NUM>, respectively. The first and second links <NUM> may be referred to as first and second extensions <NUM> of the first and second handles <NUM>.

The first and second links <NUM> may be pivotally coupled at their radial ends (i.e., output ends) to the first and second upper reciprocating members <NUM>, respectively, to permit relative pivotal motion between the links <NUM> and the upper reciprocating members <NUM>. The first and second upper reciprocating members <NUM> may be formed as rigid links. With reference to <FIG>, upper ends of the upper reciprocating members <NUM> may be pivotally coupled to the links <NUM> at axis C. As the handles <NUM> articulate back and forth (i.e., reciprocate pivotally about axis D), the links <NUM> move in corresponding arcs about the pivot axis D, which in turn articulates the upper reciprocating members <NUM>. As the upper ends of the upper reciprocating members <NUM> articulate back and forth about the pivot axis D, lower ends <NUM> of the upper reciprocating members <NUM> orbit around the crank axis A along a circular path having a radius defined by the distance between crank axis A and pivot axis B. In other words, pivot axes B, which are defined at the pivot connection of the first and second upper reciprocating members <NUM> to the first and second intermediate crank arms <NUM>, respectively, circularly orbit around crank axis A. The orbiting axes B may be parallel to the fixed crank axis A and offset radially in opposite directions from the fixed crank axis A (see <FIG> and <FIG>). Each axis B may be located proximal to an end of a respective upper reciprocating member <NUM> and intermediate crank arm <NUM>.

As shown in <FIG> and <FIG>, the first and second intermediate crank arms <NUM> may be pivotally coupled to the first and second upper reciprocating members <NUM>, respectively, at axes B, and to the first and second lower reciprocating members <NUM>, respectively, at axes E. The first and second intermediate crank arms <NUM> may be oriented perpendicular to axes B and E. As shown in <FIG>, the first and second intermediate crank arms <NUM> may be positioned inside of the first and second upper reciprocating members <NUM>, respectively, and outside of the first and second lower reciprocating members <NUM>, respectively. The first and second lower reciprocating members <NUM> may be positioned outside of the first and second crank arms <NUM>, respectively.

With continued reference to <FIG>, <FIG>, and 5A, the first and second intermediate crank arms <NUM> may be fixed relative to the first and second crank arms <NUM>, respectively, such that respective crank arms <NUM>, <NUM> rotate in unison around the crank axis A to rotate the crank wheel <NUM> and the crankshaft <NUM> when the pedals <NUM> and/or the handles <NUM> are driven by a user. As shown in <FIG>, respective cranks arms <NUM>, <NUM> may be fixedly coupled to each other at axes E to define a fixed angle β between the respective crank arms <NUM>, <NUM>. In some examples, the angle β formed between the respective crank arm <NUM> and intermediate crank arm <NUM> may be in the range of approximately <NUM>° to <NUM>° (see <FIG>).

When the pedals <NUM> and/or the handles <NUM> are driven by a user, the crank axes B and E orbit about the crank axis A. With reference to <FIG> and <FIG>, as the crank wheel <NUM> and the crankshaft <NUM> rotate about the crank axis A, the reciprocating axes B and E move in circular orbits of different radii about the crank axis A. The distance between crank axis A and each axis B defines the length of the moment arm of each intermediate crank arm <NUM> which exerts a moment on the crankshaft <NUM>, and this moment arm may be considered a virtual crank arm. The distance between crank axis A and each axis E defines the length of the moment arm of each crank arm <NUM> which exerts a moment on the crankshaft <NUM>. As illustrated in <FIG>, the distance between crank axis A and each axis E is larger than the distance between crank axis A and each axis B, resulting in the crank arms <NUM> applying a larger moment on the crankshaft <NUM> than the intermediate crank arms <NUM>.

The upper linkage assemblies of the machine <NUM> may be configured in accordance with the examples herein to cause the handles <NUM> to reciprocate in opposition to the pedals <NUM> such as to mimic the kinematics of natural human motion. For example, as the left pedal <NUM> is moving upward and forward, the left handle <NUM> pivots rearward, and vice versa. The machine <NUM> may include a user interface mounted near the top of the upper support member <NUM>. The user interface may include a display <NUM> to provide information to the user, and may include user inputs to allow the user to enter information and to adjust settings of the machine, such as to adjust the resistance.

Referring now further to <FIG>, the upper moment-producing mechanism <NUM> of the machine <NUM> may be configured to produce a first mechanical advantage. As illustrated in <FIG>, the handles <NUM> pivot about axis D in response to force being exerted against the handles <NUM> by a user. The pivotal motion of the links <NUM>, which are fixedly connected to the handles <NUM>, causes the upper reciprocating members <NUM> to drive the intermediate crank arms <NUM> about the crank axis A. The intermediate crank arms <NUM> may be pivotally connected to the first and second lower reciprocating members <NUM> and fixedly connected to the crank arms <NUM> at axes E, and thus the intermediate crank arms <NUM> drive the crank arms <NUM>, which rotate the crankshaft <NUM> about crank axis A. During rotation of the crankshaft <NUM>, the axes B travel around the crank axis A in a circular path with the distance between axes B and crank axis A defining the effective moment arm of the intermediate crank arms <NUM>. In other words, a virtual crank arm may be defined between axis A and axis B. Freedom of relative rotational movement between the ends <NUM> of the upper reciprocating members <NUM> and the intermediate crank arms <NUM> permits the circular motion of the axes B about crank axis A.

<FIG> show the intermediate crank arms <NUM> in different positions around the crank axis A. The different positions of the intermediate crank arms <NUM> represent rotation of the crankshaft <NUM> which is fixedly attached to the intermediate crank arms <NUM> through the crank arms <NUM>. Due to the fixed attachment, the intermediate crank arms <NUM> transmit a force received from the first and second handles <NUM> to the crankshaft <NUM>. As previously discussed, the intermediate crank arms <NUM> may be fixedly positioned relative to the crank arms <NUM>. For example, as shown in <FIG>, the intermediate crank arms <NUM> may be set at a fixed angle β relative to the crank arms <NUM>. As the upper reciprocating members <NUM> and the crank arms <NUM> rotate, for example <NUM> degrees, the crank arms <NUM> may stay at the same relative angle to the intermediate crank arms <NUM>. The angle β may be any angle (i.e., <NUM>-<NUM> degrees). In some examples, the angle β may be between <NUM>° and <NUM>° (see <FIG>). In one example, the angle β may be <NUM>°.

The lower moment-producing mechanism <NUM> of the machine <NUM> may be configured to produce a second mechanical advantage. As illustrated in <FIG>, the pedals <NUM> pivot around the rollers <NUM> in response to force being exerted against the first and second lower reciprocating members <NUM> through the pedals <NUM>. The force on the first and second lower reciprocating members <NUM> drives the first and second crank arms <NUM>, respectively. The crank arms <NUM> are pivotally connected at axes E to the first and second lower reciprocating members <NUM> and fixedly connected to the crankshaft <NUM> at axis A. As the first and second lower reciprocating members <NUM> are articulated, the force exerted on the pedals <NUM> drives the crank arms <NUM>, which rotate the crankshaft <NUM> about axis A. <FIG> show the crank arms <NUM> in different positions around the crank axis A. The different positions of the crank arms <NUM> represent rotation of the crankshaft <NUM> which is fixedly attached to the crank arms <NUM>. Due to the fixed attachment, the crank arms <NUM> transmit a force received from the first and second lower reciprocating members <NUM> to the crankshaft <NUM>.

The mechanical advantage of the upper and lower moment-producing linkages or mechanisms <NUM>, <NUM> may be manipulated by altering the characteristics of the various elements. For example, in the upper moment-producing linkage or mechanism <NUM>, the leverage applied by the handles <NUM> may be established by length of the handles or the location from which the handles <NUM> receive the input from the user. The leverage applied by the first and second links <NUM> may be established by the distance from axis D to axis C. The leverage applied by the intermediate crank arms <NUM> may be established by the distance between axis B and axis A. The upper reciprocating members <NUM> may connect the first and second links <NUM> to the intermediate crank arms <NUM> over the distance from axis C to axis B. The ratio of the distance between axes D and C compared to the distance between axes B and A (i.e., D-C:B-A) may be, in one example, between <NUM>:<NUM> and <NUM>:<NUM>. In another example, the ratio may be between <NUM>:<NUM> and <NUM>:<NUM>. In another example, the ratio may be between <NUM>:<NUM> and <NUM>:<NUM>. In another example, the ratio may be about <NUM>:<NUM>. Similar ratios may apply to the ratio of axis B to axis A compared to axis A to axis E (i.e., B-A:A-E).

The upper moment-producing mechanism <NUM> and the lower moment-producing mechanism <NUM>, functioning together or separately, transmit input by the user at the handles <NUM> and/or the pedals <NUM> to a rotational movement of the crankshaft <NUM>. In accordance with various embodiments, the upper moment-producing mechanism <NUM> drives the crankshaft <NUM> with a first mechanical advantage (e.g., as a comparison of the input force to the moment at the crankshaft). The first mechanical advantage may vary throughout the cycling of the handles <NUM>. For example, as the first and second handles <NUM> reciprocate back and forth around axis D through the cycle of the machine, the mechanical advantage supplied by the upper moment-producing mechanism <NUM> to the crankshaft <NUM> may change with the progression of the cycle of the machine. The lower moment-producing mechanism <NUM> drives the crankshaft <NUM> with a second mechanical advantage (e.g., as a comparison of the input force at the pedals <NUM> to the torque at the crankshaft <NUM> at a particular instant or angle). The second mechanical advantage may vary throughout the cycle of the pedals <NUM> as defined by the vertical position of the rollers <NUM> relative to their top vertical and bottom vertical position. For example, as the pedals <NUM> change position, the mechanical advantage supplied by the lower moment-producing mechanism <NUM> may change with the changing position of the pedals <NUM>. The various mechanical advantage profiles may rise to a maximum mechanical advantage for the respective moment-producing mechanisms at certain points in the cycle and may fall to minimum mechanical advantages at other points in the cycle, In this respect, each of the moment-producing mechanisms <NUM>, <NUM> may have a mechanical advantage profile that describes the mechanical effect across the entire cycle of the handles <NUM> and/or pedals <NUM>. The first mechanical advantage profile may be different than the second mechanical advantage profile at any instance in the cycle and/or the profiles may generally be different across the entire cycle. The exercise machine <NUM> may be configured to balance the user's upper body workout (e.g. at the handles <NUM>) by utilizing the first mechanical advantage differently as compared to the user's lower body workout (e.g. at the pedals <NUM>) utilizing the second mechanical advantage. In various embodiments, the upper moment-producing mechanism <NUM> may substantially match the lower moment-producing mechanism <NUM> at such points where the respective mechanical advantage profiles are near their respective maximums. Regardless of difference or similarities in respective mechanical advantage profiles throughout the cycling of the exercise machine, the inputs to the handles <NUM> and pedals <NUM> still work in concert through their respective mechanisms to drive the crankshaft <NUM>.

The exercise machine <NUM> may include a resistance mechanism operatively arranged to resist the rotation of the crankshaft <NUM>. In some embodiments, the exercise machine <NUM> may include one or more resistance mechanism such as an air-resistance based resistance mechanism, a magnetism based resistance mechanism, a friction based resistance mechanism, and/or other resistance mechanisms. The crank wheel <NUM> may be coupled to one or more resistance mechanisms to provide resistance to the reciprocating motion of the pedals <NUM> and handles <NUM>. For example, resistance may be applied via an air brake, a friction brake, a magnetic brake, or the like. As shown in <FIG> and <FIG>, the machine <NUM> may include an air-resistance based resistance mechanism, such as air brake <NUM>, rotationally coupled to the frame <NUM>. The machine <NUM> may additionally or alternatively include a magnetic-resistance based resistance mechanism, or magnetic brake <NUM> (see e.g., <FIG>). The rotor <NUM> and the air brake <NUM> may be driven by rotation of the crankshaft <NUM> and each may be operable to resist the rotation of the crankshaft <NUM>. In the illustrated embodiment, the rotor <NUM> and the air brake <NUM> are driven by a belt or chain <NUM> that is routed around the crank wheel <NUM> and a pulley <NUM> (see, e.g., <FIG>). The ratio of the diameters of the crank wheel <NUM> and the pulley <NUM> may be used as a gearing mechanism to adjust the ratio of the angular velocity of the rotor <NUM> and the air brake <NUM> to the angular velocity of the crank wheel <NUM>. For example, one rotation of the crank wheel <NUM> may cause several rotations of the rotor and/or the air brake <NUM> to increase the resistance provided by the resistance mechanism. In addition, a tensioner or idler system may be used to take up extra slack in the belt or chain <NUM> and to increase the wrap angle of the belt or chain <NUM> about the crank wheel <NUM> and/or the pulley <NUM>.

One or more of the resistance mechanisms can be adjustable to provide different levels of resistance at a given reciprocation frequency. Further, one or more of the resistance mechanisms can provide a variable resistance that corresponds to the reciprocation frequency of the exercise machine, such that resistance increases as reciprocation frequency increases. For example, one reciprocation of the pedals <NUM> and/or handles <NUM> may cause several rotations of the rotor <NUM> and/or air brake <NUM> to increase the resistance provided by the magnetic brake <NUM> and/or air brake <NUM>. The air brake <NUM> may be adjustable to control the volume of air flow that is induced to flow through the air brake at a given angular velocity in order to vary the resistance provided by the air brake.

The air brake <NUM> may include a radial fin structure that causes air to flow through the air brake when it rotates. For example, rotation of the air brake <NUM> may cause air to enter through lateral openings on the lateral side of the air brake near the rotation axis and exit through radial outlets opening to a radial perimeter of the air brake. The induced air motion through the air brake <NUM> may cause resistance to the rotation of the crank wheel <NUM> and thus crankshaft <NUM>, which is transferred to resistance to the reciprocating motions of the pedals <NUM> and handles <NUM>. As the angular velocity of the air brake <NUM> increases, the resistance force may increase in a non-linear relationship, such as a substantially exponential relationship.

In some embodiments (not shown), an air brake may include an inlet plate that is adjustable in an axial direction (and optionally also in a rotational direction). An axially adjustable inlet plate may be configured to move in a direction parallel to the rotation axis of the air brake. For example, when the inlet plate is further away axially from the air inlet(s), increased air flow volume is permitted, and when the inlet plate is closer axially to the air inlet(s), decreased air flow volume is permitted. In some embodiments (not shown), an air brake may include an air outlet regulation mechanism that is configured to change the total cross-flow area of the air outlets at the radial perimeter of the air brake, in order to adjust the air flow volume induced through the air brake at a given angular velocity.

In some embodiments, the air brake <NUM> may include an adjustable air flow regulation mechanism, such as the inlet plate or other mechanism described herein, that can be adjusted rapidly while the machine <NUM> is being used for exercise. For example, the air brake <NUM> may include an adjustable air flow regulation mechanism that can be rapidly adjusted by the user while the user is driving the rotation of the air brake, such as by manipulating a manual lever, a button, or other mechanism positioned within reach of the user's hands while the user is driving the pedals <NUM> with the user's feet. Such a mechanism may be mechanically and/or electrically coupled to the air flow regulation mechanism to cause an adjustment of air flow and thus adjust the resistance level. In some embodiments, such a user-caused adjustment may be automated, such as using a button or mechanism <NUM> on a console near the handles <NUM> coupled to a controller and an electrical motor coupled to the air flow regulation mechanism. In other embodiments, such an adjustment mechanism may be entirely manually operated, or a combination of manual and automated. In some embodiments, a user may cause a desired air flow regulation adjustment to be fully enacted in a relatively short time frame, such as within a fraction of a second or multiple seconds.

The magnetic brake <NUM> may include the rotor <NUM> rotationally coupled to the frame <NUM> and a brake caliper <NUM> coupled to the frame <NUM>. The magnetic brake <NUM> may provide resistance to rotation of the crankshaft <NUM> by magnetically inducing eddy currents in the rotor <NUM> as the rotor rotates. The brake caliper <NUM> may include magnets positioned on opposite sides of the rotor <NUM>. As the rotor <NUM> rotates between the magnets, the magnetic fields created by the magnets induce eddy currents in the rotor <NUM>, producing resistance to the rotation of the rotor <NUM>. To adjust resistance, the magnitude of the magnetic field may be varied (e.g., increased or decreased) to an outer portion of the rotor <NUM>. The magnitude of the resistance to rotation of the rotor <NUM> may increase as a function of the angular velocity of the rotor <NUM>, such that higher resistance is provided at high reciprocation frequencies of the pedals <NUM> and handles <NUM>. The magnitude of resistance provided by the magnetic brake <NUM> may also be a function of the radial distance from the magnets to the rotation axis of the rotor <NUM>. As this radius increases, the linear velocity of the portion of the rotor <NUM> passing between the magnets increases at any given angular velocity of the rotor <NUM>, as the linear velocity at a point on the rotor <NUM> is a product of the angular velocity of the rotor <NUM> and the radius of that point from the rotation axis. In some embodiments, the brake caliper <NUM> may be pivotally mounted, or otherwise adjustably mounted, to the frame <NUM> such that the radial position of the magnets relative to the rotation axis of the rotor <NUM> may be adjusted to move the magnets to different radial positions relative to the rotor <NUM> to change the resistance provided by the magnetic brake <NUM> at a given reciprocation frequency of the pedals <NUM> and handles <NUM>.

In some embodiments, the brake caliper <NUM> may be adjusted rapidly while the machine <NUM> is being used for exercise to adjust the resistance. For example, the radial position of the magnets of the brake caliper <NUM> relative to the rotor <NUM> may be rapidly adjusted by the user while the user is driving the reciprocation of the pedals <NUM> and/or handles <NUM>, such as by manipulating a lever, a button, or other mechanism <NUM> positioned within reach of the user's hands (see e.g., <FIG>) while the user is driving the pedals <NUM> with the user's feet. Such an adjustment mechanism may be mechanically and/or electrically coupled to the magnetic brake <NUM> to cause an adjustment of eddy currents in the rotor <NUM> and thus adjust the magnetic resistance level. The user interface <NUM> may include a display to provide information to the user and may include user inputs to allow the user to enter to <NUM> adjust settings of the machine, such as to adjust the resistance. In some embodiments, such a user-caused adjustment can be automated, such as using a button on the user interface <NUM> that is electrically coupled to a controller and an electrical motor coupled to the brake caliper <NUM>. In other embodiments, such an adjustment mechanism may be entirely manually operated, or a combination of manual and automated. In some embodiments, a user may cause a desired magnetic resistance adjustment to be fully enacted in a relatively short time frame, such as within a half-second, within one second, within two seconds, within three second, within four seconds, and/or within five seconds from the time of manual input by the user via an electronic input device or manual actuation of a mechanical device. In other embodiments, the magnetic resistance adjustment time periods can be smaller or greater than the time periods provided above.

The exercise machine <NUM> shown in <FIG> may include an outer housing (not shown) positioned around a front portion of the machine. The housing may house and protect portions of the frame <NUM>, the pulley <NUM>, the belt or chain <NUM>, lower portions of the upper reciprocating members <NUM>, the air brake <NUM>, the magnetic brake <NUM>, motors for adjusting the air brake and/or magnetic brake, wiring, and/or other components of the machine <NUM>. The housing may include an air brake enclosure that includes lateral inlet openings to allow air into the air brake <NUM> and radial outlet openings to allow air out of the air brake. The housing may include a magnetic brake enclosure to protect the magnetic brake <NUM>, where the magnetic brake is included in addition to or instead of the air brake <NUM>. The crank wheel <NUM>, crank arms <NUM>, and/or intermediate crank arms <NUM> may be exposed through the housing such that the upper and lower reciprocating members <NUM>, <NUM> can drive the respective components in a circular motion about the axis A without obstruction by the housing.

Embodiments that include a variable resistance mechanism that provide increased resistance at higher angular velocity and a rapid resistance mechanism that allow a user to quickly change the resistance at a given angular velocity allow the machine <NUM> to be used for high intensity interval training. In an exercise method, a user can perform repeated intervals alternating between high intensity periods and low intensity periods. High intensity periods can be performed with the adjustable resistance mechanism, such as the magnetic braking system <NUM> and/or the air brake <NUM>, set to a low resistance setting (e.g., with the inlet plate blocking air flow through the air brake <NUM>). At a low resistance setting, the user can drive the pedals <NUM> and/or handles <NUM> at a relatively high reciprocation frequency, which can cause increased energy exertion because, even though there is reduced resistance from the air brake <NUM>, the user is caused to lift and lower his own body weight a significant distance for each reciprocation, like with a traditional stair climber machine. The rapid climbing motion can lead to an intense energy exertion. Such a high intensity period can last any length of time, such as less than one minute, or less than <NUM> seconds, while providing sufficient energy exertion as the user desires.

Low intensity periods can be performed with the adjustable resistance mechanism, such as the magnetic braking system <NUM> and/or the air brake <NUM>, set to a high resistance setting (e.g., with the inlet plate allowing maximum air flow through the air brake <NUM>). At a high resistance setting, the user can be restricted to driving the pedals <NUM> and/or handles <NUM> only at relatively low reciprocation frequencies, which can cause reduced energy exertion because, even though there is increased resistance from the air brake <NUM>, the user does not have to lift and lower his own body weight as often and can therefor conserve energy. The relatively slower climbing motion can provide a rest period between high intensity periods. Such a low intensity period or rest period can last any length of time, such as less than two minutes, or less than about <NUM> seconds. An exemplary interval training session can include any number of high intensity and low intensity periods, such less than <NUM> of each and/or less than about <NUM> minutes total, while providing a total energy exertion that requires significantly longer exercise time, or is not possible, on a traditional stair climber or a traditional elliptical machine.

For purposes of this description, certain aspects, advantages, and novel features of the embodiments of this disclosure are described herein. The disclosed methods, apparatuses, and systems should not be construed as limiting in any way. Instead, the present disclosure is directed toward all novel and nonobvious features and aspects of the various disclosed embodiments, alone and in various combinations and sub-combinations with one another. The methods, apparatuses, and systems are not limited to any specific aspect or feature or combination thereof, nor do the disclosed embodiments require that any one or more specific advantages be present or problems be solved.

As used herein, the terms "a", "an" and "at least one" encompass one or more of the specified element. That is, if two of a particular element are present, one of these elements is also present and thus "an" element is present. The terms "a plurality of' and "plural" mean two or more of the specified element.

As used herein, the term "and/or" used between the last two of a list of elements means any one or more of the listed elements. For example, the phrase "A, B, and/or C" means "A," "B," "C," "A and B," "A and C," "B and C" or "A, B and C.

All relative and directional references (including: upper, lower, upward, downward, left, right, leftward, rightward, top, bottom, side, above, below, front, middle, back, vertical, horizontal, height, depth, width, and so forth) are given by way of example to aid the reader's understanding of the particular embodiments described herein. They should not be read to be requirements or limitations, particularly as to the position, orientation, or use of the invention unless specifically set forth in the claims. Connection references (e.g., attached, coupled, connected, joined, and the like) are to be construed broadly and may include intermediate members between a connection of elements and relative movement between elements. As such, connection references do not necessarily infer that two elements are directly connected and in fixed relation to each other, unless specifically set forth in the claims.

Unless otherwise indicated, all numbers expressing properties, sizes, percentages, measurements, distances, ratios, and so forth, as used in the specification or claims are to be understood as being modified by the term "about. " Accordingly, unless otherwise indicated, implicitly or explicitly, the numerical parameters set forth are approximations that may depend on the desired properties sought and/or limits of detection under standard test conditions/methods. When directly and explicitly distinguishing embodiments from discussed prior art, numbers are not approximations unless the word "about" is recited.

Claim 1:
A stationary exercise machine (<NUM>) comprising:
a frame (<NUM>);
a crankshaft (<NUM>) coupled with the frame (<NUM>) and rotatable about a crankshaft axis (A);
first and second crank arms (<NUM>) rigidly coupled with respective opposite sides of the crankshaft (<NUM>), wherein rotation of at least one of the first or second crank arms (<NUM>) causes rotation of the crankshaft (<NUM>) about the crankshaft axis (A);
characterised by first and second intermediate crank arms (<NUM>) rigidly coupled with the first and second crank arms (<NUM>), respectively; and
first and second handles (<NUM>) operatively coupled with the first and second intermediate crank arms (<NUM>), respectively, at respective pivot axes (B,C,D,E) to convert a user's input force at the first and second handles (<NUM>) into a moment on the crankshaft (<NUM>), wherein the respective pivot axes (B,C,D,E) are spaced a distance from the crankshaft axis (A) and orbit the crankshaft axis (A) to define respective virtual crank arms extending between the respective pivot axes (B,C,D,E) and the crankshaft axis (A).