Patent Grant
11945128
The invention generally relates to handles for razors, more particularly to handles with a pivoting portion.
Recent advances in shaving razors, such as a 5-bladed or 6-bladed razor for wet shaving, may provide for closer, finer, and more comfortable shaving. One factor that may affect the closeness of the shave is the amount of contact for blades on a shaving surface. The larger the surface area that the blades contact then the closer the shave becomes. Current approaches to shaving largely comprise of razors with a pivoting axis of rotation, for example, about an axis substantially parallel to the blades and substantially perpendicular to the handle (i.e., front-and-back pivoting motion). One factor that may affect the comfort of the shave is provision for a skin benefit, such as fluid or heat, to be delivered at the skin surface. However, effectively providing for a skin benefit can be hindered by the requirements for effective blade pivoting in a compact, durable razor.
What is needed, then, is a razor, suitable for wet or dry shaving, providing a skin benefit and pivoting for a close, comfortable shave. The razor, including powered and manual razors, is preferably simpler, cost-effective, reliable, compact, durable, easier and/or faster to manufacture, and easier and/or faster to assemble with more precision.
A handle is disclosed. The handle can include a body and a pivoting head pivotally coupled with the main body at a pivot axis. The pivoting head can include at least two mating parts defining an interior channel. A pivot spring can include a first coil spring and a second coil spring and a main bar portion that is at least partially disposed in the interior channel and interacts with the pivoting head to bias the pivoting head into a rest position. The main bar portion also can couple the first and second coil springs together in a spaced.
Other features and advantages of the present invention, as well as the invention itself, can be more fully understood from the following description of the various embodiments, when read together with the accompanying drawings, in which:
Except as otherwise noted, the articles “a,” “an,” and “the” mean “one or more.”
Referring to
In the illustrated embodiments the skin benefit delivery components extend from handle 12 through an opening in the cartridge unit 15 and can, therefore, be in close proximity to the skin of a user during shaving. The benefits will be delivered through a pivoting head as will be described herein. The mechanism to pivot the pivoting head relative to a handle comprises a benefit pivot delivery connection, a spring member, and one or more bearings. The benefit pivot delivery connection functions to deliver a benefit (such as heat or fluid) from the handle to a user's skin.
Two non-limiting embodiments of razors providing for a skin benefit are disclosed herein. The first, shown in
In like manner,
Referring now to
As shown in
Continuing to refer to
The pivoting head 22 can have a shape beneficially conducive to both attaching to the blade cartridge unit 15 and facilitating the delivery of a skin benefit from the handle 12 to and through the blade cartridge unit 15 attached to the handle 12.
The shape of the pivoting head 22 can alternatively be described as a “funnel,” or as “tapered,” or a “trapezoidal prism-shaped.” As understood from the description herein, the description “trapezoidal prism” is general with respect to an overall visual impression the pivoting head. For example, a schematic representation of a trapezoidal prism-shaped element is shown in
The description “trapezoidal prism” is used herein as the best description for the overall visual appearance of the pivoting head 22, but the description does not imply any particular geometric or dimensional requirements beyond what is described herein. That is, the pivoting head 22, including the cover member 40, need not have complete edges or surfaces. Further, edges need not be unbroken and straight, and sides need not be unbroken and flat.
Pivoting head 22 and the various parts as described herein can be made of thermoplastic resins, which can be injection molded. The thermoplastic resin can preferably be of a relatively high impact strength with a Charpy notched strength impact value higher than 2 kJ/m2 (as measured by ISO 179/1). The thermoplastic resin can have a relatively high tensile modulus above 500 MPa as measured using ISO 527-2/1-A (1 mm/min).
In an embodiment, resins of the polyoxymethylene (POM, also known as acetal) can be utilized for the pivoting head parts, and copolymer forms can be more readily injection molded due to improved heat stability over homopolymer versions. Acetal copolymer with Charpy notched strength impact values higher than 6 kJ/m2 (as measured by ISO 179/1), including with values equal to or greater than 13 kJ/m2, and including values greater than 85 kJ/m2 can be utilized. Further, it is contemplated that the thermoplastic material is relatively stiff having a tensile modulus above 900 MPa as measured using ISO 527-2/1-A (1 mm/min). Examples include HOSTAFORM® XT20 and HOSTAFORM® 59363.
Referring now to
The materials chosen for fluid benefit delivery member 76 can have good chemical resistance to a variety of chemicals found in a consumer environment for durability along with a low modulus of elasticity for providing low resistance to angular deflection about a pivot.
In an embodiment, the materials for fluid benefit delivery member 76 can include thermoplastic elastomers (TPE). The TPE materials can include styrenic block copolymers, including, for example, Poly(styrene-block-ethylenebutylene-block-styrene) (SEBS), Poly(styrene-block-butadiene-block-styrene) (SBS), or Poly(styrene-block-isoprene-block-styrene) (SIS).
In an embodiment, the materials for fluid benefit delivery member 76 can include thermoplastic vulcanized (TPV) systems. In an embodiment the fluid delivery member can be injection molded as an overmold, e.g., in a two-shot injection molding operation, on base member 42 which can be a different material, including a relatively harder plastic. However, fluid benefit delivery member 76 can also be formed separately and joined to base member 42. Suitable TPV systems can include TPV systems based on polypropylene (PP) and ethylene propylene diene terpolymer (EPDM), TPV systems based on polypropylene and nitrile rubber, TPV systems based on polypropylene and butyl rubber, TPV systems based on polypropylene and halogenated butyl rubber, TPV systems based on polypropylene and natural rubber, or TPV systems based on polyurethane and silicone rubber. A TPV system based on polypropylene can have the greater chemical resistance against chemicals commonly used in shaving applications.
In an embodiment, materials for the fluid benefit delivery member 76 can include creep resistant materials having an increase in tensile strain of less than about 3% from an initial tensile strain when measured using ISO 89901 carried out at 1000 hours at 73 Fahrenheit.
In an embodiment, materials for the fluid benefit delivery member 76 can include materials having a hardness of about 10 on a Shore A durometer scale and about 60 on a Shore A durometer scale. The materials for any benefit delivery member, such as the fluid benefit delivery member 76 or heat delivery member 96 can be below 60 A, including values below 50 A.
In an embodiment, materials for the fluid benefit delivery member 76 can include elastomers having compression sets less than about 25% as measured by ASTM D-395.
In an embodiment, benefit delivery member has a moment of inertia from about 6 mm4 to about 40 mm4.
Other materials suitable for fluid benefit delivery member 76 can include thermoplastic polyurethane (TPU), melt processable rubber (MPR), plasticized polyvinyl chloride (PVC), olefinic block copolymers (OBC), ionomers, and thermoplastic elastomers based on styrenic block copolymers.
One or both ends 44 (corresponding to the end faces 38 of the schematic shape shown in
As can be understood from the description herein, the included angle 43 between the diverging surfaces (e.g., an angle of divergence) for the angularly diverging surfaces 48 and 50 can determine the angular rotation of pivoting head 22 about first axis of rotation 26. In an embodiment, the angle of divergence for the angularly diverging surfaces 48 and 50 can be up to 50 degrees or more. As can be understood, therefore, in an embodiment, pivoting head 22 can rotate from a first position at 0 degrees to a second position at about 50 degrees relative to the first position, and any position therebetween. At all positions a spring member 64 can apply a biasing force at a location corresponding to a main bar portion axis 86, as described more fully below, to urge pivoting head 22 toward the first, at rest, position. The position shown in
Referring to
As shown in
Referring now to
As shown in
Spring member 64 can be any spring member facilitating biasing of the pivoting head to the first rest position. Spring member can be, for example, any of torsion coil springs, coil spring, leaf spring, helical compression spring, and disc spring. In the illustrated embodiment, spring member 64 comprises torsion springs, and can have at least one coil spring 68. In an embodiment, two coil springs 68A and 68B are coupled together in a spaced relationship by a main bar portion 70 as shown in
Additionally, spring member 64 can be can be made of plastic, impact-resistant plastic, metal, and composite materials. In an embodiment, the spring member 64 can be made from materials that are resistant to stress relaxation such as metal, polyetheretherketone, and some grades of silicone rubber. Such an embodiment of spring member 64, comprised of stress relaxation resistant materials, can prevent the pivot head from undesirably taking a “set,” a permanent deformation of the spring member that prevents the pivot head from returning to its rest position when unloaded. In an embodiment, spring member 64 can be made of 200 Series or 300 Series stainless steel at spring temper per ASTM A313. In an embodiment, spring member 64 can be comprised of stainless steel wire (e.g., 302 stainless steel wire) having an ultimate tensile strength metal greater than 1800 MPa or an engineering yield stress between about 800 MPa and about 2000 MPa.
First arm 24A and second arm 24B can each be generally flat members having generally parallel planar opposite sides. Arms 24 can define an imaginary plane 66, as shown in
Arms 24 can have various shapes and features beneficially adapted to the pivoting head 22. Additionally, arms can be made of plastic, impact-resistant plastic, metal, and composite materials. In an embodiment, arms 24 can be comprised of metal. Arms 24 and can be made of a 200 or 300 Series stainless steel having an engineering yield stress measured by ASTM standard E8 greater than about 200 MPa, and preferably greater than 500 MPa and a tensile strength again measured by ASTM standard E8 greater than 1000 MPa.
As shown in
As shown in
Pivoting head 22 can be rotated about first axis of rotation 26 by a biasing force applied to the pivoting head to rotate the pivoting head 22 about the first axis of rotation 26 to a second position such that second diverging surface 50 rests in contacting relationship with arm 24. Upon removal of the biasing force, spring member 64 can act to rotate pivoting head back to the first position. In an embodiment, pivoting head 22 can be rotated about the first axis of rotation 26, which can be considered a first pivot axis, from the first position through an angle of rotation of between about 0 degrees and about 50 degrees and when rotated the pivot spring applies a biasing torque about the first axis of rotation 26 of less than about 30 N-mm at an angle of rotation of about 50 degrees. In an embodiment, pivoting head 22 can be rotated about the first axis of rotation 26, which can be considered a first pivot axis, from the first position through an angle of rotation of between about 0 degrees and about 50 degrees and when rotated the pivot spring applies a biasing torque about the first axis of rotation 26 of between about 2 N-mm and about 12 N-mm.
In an embodiment in which a fluid benefit delivery member 76 is coupled to the base member 42 of pivoting head 22, the fluid benefit delivery member 76 being flexibly coupled can provide a portion of the restorative, biasing torque as well. For example, in an embodiment the fluid delivery member can contribute about 30% of the restorative, biasing torque about the first axis of rotation 26. In an embodiment, the restorative, biasing torque about the first axis of rotation 26 can be about less than about 10 N-mm and can be about 6 N-mm with about 4.5 N-mm contributed by spring member 64 and about 1.5 N-mm contributed by the fluid benefit delivery member 76. As discussed below, the pivoting torque supplied by the spring member can be considered a first pivoting torque. The pivoting torque supplied by the benefit delivery member, including a fluid benefit delivery member 76 or a heat delivery member 96 can be considered a second pivoting torque. The benefit delivery member can be severable, that is, cut, removed, or otherwise uncoupled from its ability to supply a pivoting torque to the pivoting head. To supply a razor having sufficient torque to permit comfortable shaving, a ratio of the sum of said first and second pivoting torques divided by said angular deflection in radians to said second pivoting torque divided by said angular deflection in radians of said pivoting head with said pivot benefit delivery connection severed is greater than 2 and can be greater than 4. Torque can be measured according to the Static Torque Stiffness Method described below in the Test Methods section.
As shown in
In an embodiment, spring member can be made of materials including amorphous polymers with glass transition temperatures above 80 Celsius, metals, elastomers having compression sets less than 25% as measured by ASTM D-395 and combinations thereof.
In an embodiment, spring member comprises creep resistant materials having an increase in tensile strain of less than about 3% from an initial tensile strain when measured using ISO 89901 carried out at 1000 hours at 73 Fahrenheit.
Once cover member 40 is in mating relationship with base member 42, cover member and base member can be joined, such as by adhesive, press fit, or welding. In an embodiment, as shown in
Fluid containment in compartment 84 can be achieved by a sealing relationship between cover member 40 and base member 42.
An embodiment of a pivoting head 22 can be assembled onto handle 12 in a manner illustrated in
Referring now to
Referring now to
As shown in
Continuing to refer to
The heat delivery member 96 may include the face plate 102, the flexible conductive strip 98 heater, a heat dispersion layer 100, a compressible thermal insulation layer 99, and a portion of cover member 40. The face plate 102 may have a recessed inner surface 122 opposite the skin application surface 82 configured to receive the heater 98, the heat dispersion layer 100 and the compressible thermal insulation layer 99. The perimeter wall 110 may define the inner surface 122. The perimeter wall 110 may have one or more tabs 108 extending from the perimeter wall 110, transverse to and away from the inner surface 122. For example,
The heat dispersion layer 100 may be positioned on and in direct contact with the inner surface 122 of the face plate 102. The heat dispersion layer 100 may have a lower surface 124 directly contacting the inner surface 122 of the face plate 102 and an upper surface 126 (opposite lower surface 37) directly contacting the heater 98. The heat dispersion layer 100 can be defined as a layer of material having a high thermal conductivity and can be compressible. For example, the heat dispersion layer 100 may comprise graphite foil. Potential advantages of the heat dispersion layer 100 include improving lateral heat flow (spreading the heat delivery from the heater 98 across the inner surface 122 of the face plate 102, which is transferred to the skin application surface 82) resulting in more even heat distribution and minimization of hot and cold spots. The heat dispersion layer 100 may have an anisotropic coefficient of thermal conductivity in the plane parallel to the face plate 102 of about 200 to about 1700 W/mK (preferably 400 to 700 W/mK) and vertical to the face plate 102 of about 10 to 50 W/mK and preferably 15 to 25 W/mK to facilitate sufficient heat conduction or transfer. In addition, the compressibility of the heat dispersion layer 100 allows the heat dispersion layer 100 adapt to non-uniform surfaces of the inner surface 122 of the face plate 102 and non-uniform surfaces of the heater 98, thus providing better contact and heat transfer. The compressibility of the heat dispersion layer 100 also minimizes stray particulates from pushing into the heater 98 (because the heat dispersion layer 100 may be softer than the heater), thus preventing damage to the heater 98. In certain embodiments, the heat dispersion layer 100 may comprise a graphite foil that is compressed by about 20% to about 50% of its original thickness. For example, the heat dispersion layer 100 may have a compressed thickness of about 50 micrometers to about 300 micrometers more preferably 80 to 200 micrometers.
The heater 98 may be positioned between two compressible layers. For example, the heater 98 may be positioned between the heat dispersion layer 100 and the compressible thermal insulation layer 99. The two compressible layers may facilitate clamping the heater 98 in place without damaging the heater 98, thus improving securement and assembly of the heat delivery element 96. The compressible thermal insulation layer 99 may help direct the heat flow toward the face plate 102 and away from the cover member 40. Accordingly, less heat is wasted, and more heat may be able to reach the skin during shaving. The compressible thermal insulation layer 99 may have low thermal conductivity, for example, less than 0.30 W/mK and preferably less than 0.1 W/mK. In certain embodiments, the compressible thermal insulation layer 38 may comprise an open cell or closed cellular compressible foam. The compressible thermal insulation layer 99 may be compressed 20-50% from its original thickness. For example, the compressible thermal insulation layer 99 may have a compressed thickness of about 400 μm to about 800 μm.
The cover member 40 may be mounted on top of the compressible thermal insulation layer 99 and secured to the face plate 102. Accordingly, the heater 98, the heat dispersion layer 100 and the compressible thermal insulation layer 99 may be pressed together between the face plate 102 and the cover member 40 and assembled as described more fully below. The heat dispersion layer 100, the heater 98, and the compressible thermal insulation layer 99 may fit snugly within the perimeter wall 110. The pressing of the various layers together may result in more efficient heat transfer across the interfaces of the different layers in the heat delivery element 96. In absence of this compression force the thermal transfer across the interfaces can be insufficient. Furthermore, the pressing of the layers together may also eliminate secondary assembly processes, such as the use of adhesives between the various layers. The compressible thermal insulation layer 99 may fit snugly within the perimeter wall 110.
Thus, in an embodiment, the first layer in contacting relationship with cover member 40 can be a compressible thermal insulation layer 99 such as a foam member. A portion of the heater in the form of a flexible conductive strip 98 can be sandwiched between a foam thermal insulation layer 99 and a graphite foil strip heat dispersion layer 100. The layers of foam thermal insulation layer 99, flexible conductive strip 98 and graphite foil strip can be connected in layered, contacting relationship to the narrow lower face of the cover member 40 by a faceplate 102. Faceplate 102 can have a smooth outer surface that corresponds to heating surface 82, and tabs 108 that can be used to connect the heat delivery components to the pivoting head 22.
Assembling a pivoting head for delivering a heat skin benefit can be described with reference to
Once cover member 40 is placed on top of the layered members in an on trough 104, faceplate 102 can be secured to the cover member 40 via tabs 108 as shown in the assembly view of
Once base member 40 is securely snapped into place on cover member 42, the illustrated embodiment of pivoting head 22 is ready to be coupled to handle 12. As shown in
As disclosed above, pivoting head 22 can be pivoted about a pivot axis, i.e., axis of rotation 26 under the biasing force of a spring member 64. However, other pivot mechanisms can be employed for both the first axis of rotation 26 and secondary axis of rotation 27. In general, pivoting head 22 can be in pivotal relation to the handle 12 via, for example, a spring, a joint, a hinge, a bearing, or any other suitable connection that enables the pivoting head to be in pivotal relation to the handle. The pivoting head may be in pivotal relation to the handle 12 via mechanisms that contain one or more springs and one or more sliding contact bearings, such as a pin pivot, a shell bearing, a linkage, a revolute joint, a revolute hinge, a prismatic slider, a prismatic joint, a cylindrical joint, a spherical joint, a ball-and-socket joint, a planar joint, a slot joint, a reduced slot joint, or any other suitable joint, or one or more springs and one or more rolling element bearings, such as a ball bearing, a cylindrical pin bearing, or rolling element thrust bearing. Sliding contact bearings can typically have friction levels of 0.1 to 0.3. Rolling element bearings can typically have friction of 0.001 to 0.01. Lower friction bearings are preferred the further a pivot mechanism is offset from its axis of rotation to assure smooth motion and prevent the bearing from sticking.
Typically, pivot mechanisms about first axis of rotation 26 allow rotational motions ranging from about 0 degrees from the cartridge rest position to about 50 degrees. A rotational stiffness for a pivot mechanism about first axis of rotation 26 may be measured by deflecting the pivot 25 degrees about the first axis of rotation 26 and measuring the required torque about this first axis of rotation 26 to maintain this position. The torque levels at 50 degrees of rotation can be generally less than 20 N-mm. The rotational stiffness (torque measured about the axis of rotation divided by degrees of angular rotation) associated with the first axis of rotation 26 can be generally less than 0.3 N-mm per degree of rotation and preferably between 0.05 N-mm per degree of rotation and 0.18 N-m per degree of rotation.
Typically, additional pivot mechanisms about secondary axis of rotation 27 (shown in
As disclosed above, components of the pivoting head 22 and the pivoting mechanism that enable rotation about first axis of rotation 26 for the embodiments were shown in detail. The handle 12 was connected to the pivoting head 22 by a pair of arms 24, a spring member 26, and a benefit pivot delivery connection. In the embodiments disclosed above, the spring member can be comprised of a metal. But the spring member 64 can also be comprised of a stress-relaxation resistant material such as a metal, polyetheretherketone, or silicone rubber, all of which can prevent the razor 10 or razor handle 12 from taking a “set,” or permanently deforming at deflected angle when the razor 10 or razor handle 12 is stored improperly due to the stress relaxation of the components that connect the pivoting head 22 to the proximal end of the handle.
The benefit pivot delivery connection can be a connection through which a skin deliver benefit component passes from the handle 12 to the pivoting head 22 to deliver a skin benefit through the cartridge 15 to the skin interfacing face 80. As discussed below, a fluid benefit delivery member 76 and a heat delivery member 96 can be configured so as to facilitate proper pivoting of the pivoting head about first axis of rotation 26 and secondary axis of rotation 27.
Referring to
In like manner, as depicted in
Additional features found to further minimizing the effect of the fluid benefit delivery member 76 on the biasing torque force required to pivot the pivoting head 22 about the first axis of rotation 26 can be understood with reference to
In a similar manner, as shown in
The dimensions of a chamfer can be defined as shown in the view of
Further, an additional feature found to minimize the effect of the fluid benefit delivery member 76 on the biasing torque force required to pivot the pivoting head 22 about the first axis of rotation 26 can be understood from
Any of the above described configurations of the fluid delivery member and handle can be combined with any of various configurations of the fluid delivery member itself, as depicted in
In
Alternative embodiments of fluid benefit delivery member 76 utilizing coil springs to reinforce strength and provide for flexibility are depicted in
The joining of the fluid benefit delivery member 76 to the pivoting head 22 can be a two-component embodiment, as shown in
In an embodiment, the fluid benefit delivery member 76 and the base member 42 of the pivoting head 22 can be overmolded in a two-shot injection mold to form a three-component assembly that can form pivoting head 22. In this manner the base member can be a relatively hard material and the fluid benefit delivery member 76 can be a relatively soft material. A portion of the polymer injection molded for the fluid delivery member forms the gasket member 92 of the base member 42, as described above. Referring to
In an embodiment, the fluid flow path of the pivoting head 22 can be configured to provide for relatively unobstructed, smooth, continuous fluid flow from the fluid benefit delivery member 76 to openings 78 in face 80 of pivoting head 22, which can be a skin interfacing face. As shown in
In general, the internal fluid conduit associated with fluid benefit delivery member 76 can have an internal hydraulic diameter from about 1 mm to about 3 mm. In general, the fluid benefit delivery member can have a minimum hydraulic diameter along the exterior of the fluid benefit delivery member from about 1.5 mm to about 3.5 mm
In general, the materials used for the fluid benefit delivery member 76 can be elastomers with compression set of about less than 25%, and preferably about less than 10% measured by ASTM D-395. In an embodiment, silicone elastomer has been found to be suitable for the fluid benefit delivery member 76.
In general, other materials useful for the fluid delivery member include thermoplastics or thermosets with relatively high creep resistance, e.g., increase in tensile strain less than about 3%, and preferably less than about 1%, from initial tensile strain when measured using ISO 899-1 carried out at 1000 hours @ 73F.
The torques discussed above referred to as first and second pivoting torques can be referred to as relating to rotational stiffness. In general, since the benefit delivery member, such as the flexible conductive strip 98 of heat delivery member 96 and fluid benefit delivery member 76, can be comprised of materials that stress relax, it can be advantageous if the rotational stiffness of the pivoting head 22 is greater than twice, or more preferably greater than 5 times, the rotational stiffness of the pivoting head 22 with the benefit delivery member removed. The rotational stiffness of the pivoting head 22 without the benefit delivery member can be measured by severing, e.g., cutting out, the benefit delivery member such that it exerts no biasing force between the pivoting head 22 and the handle 12. Generally, the rotational stiffness of the pivot mechanism is desirably greater than twice the rotational stiffness of the pivot mechanism with the benefit pivot delivery connection disconnected at the proximal end of the handle and at the pivoting head 22. This latter configuration greatly reduces the probability and conditions under which the razor 10 or razor handle 12 can take a “set.” The rotational stiffness of a pivot mechanism (with or without benefit pivot delivery connection) can be measured by the Static Torque Stiffness Method described below.
It should be understood that every maximum numerical limitation given throughout this specification includes every lower numerical limitation, as if such lower numerical limitations were expressly written herein. Every minimum numerical limitation given throughout this specification includes every higher numerical limitation, as if such higher numerical limitations were expressly written herein. Every numerical range given throughout this specification includes every narrower numerical range that falls within such broader numerical range, as if such narrower numerical ranges were all expressly written herein.
Test Methods:
Static Torque Stiffness Method:
Without intending to be bound by any theory, it is believed that the torque stiffness of a bearing or pivot mechanism described herein can be applied to characterize a bearing or pivot mechanism within a razor, razor cartridge, or razor handle. The specific article being tested will be referred to as the test component for the rest of this method. Also, in the description of the method below, the term “pivot mechanism” is understood to encompass both bearing and pivot mechanisms.
The static torque stiffness method can be used to measure torque stiffness. In this method, different sections of the test component are rotated relative to each other about an axis of rotation (such as axis of rotation 26, for example) of the pivot mechanism and torques versus angles of rotation between sections are measured. Referring to
In
The static torque stiffness method consists of (1) identifying the instant center of rotation over the full angular range of the motion of the pivot mechanisms, (2) clamping the test component into an appropriate test fixture that has the torque sensor centered about axis of rotation, (3) making the individual measurement of torque and rotation, and (4) calculating the torque stiffness. The environmental testing conditions for the static torque stiffness method comprise of making measurements at a room temperature of 23 Celsius and relative humidity of 35% to 50% and using test components that are in a dry, “as-made” condition.
Step 1: Identify the instant center of rotation over the full angular range of motion of the pivot of mechanism.
The instant center of rotation is the location of the axis of rotation of the pivot mechanism at an individual angle of rotation. The identification of the axis of rotation for an individual torque versus angle measurement can be important because many pivot mechanisms have virtual pivots where the axis of rotation is offset or even outside the pivot mechanism, many pivot mechanisms have no obvious features such as a pin or a shaft that indicate the location of the axis of rotation, and some more complex pivot mechanisms have an axis of rotation that changes location during the motion.
As shown in
Step 2: Clamp the test component in appropriate test fixture with torque sensor centered on axis of rotation
As shown in
The angles of rotation measured in accordance with the static torque stiffness method are the angles of deflection of the moving first section 401 of the test component that rotate relative to the at rest position of said first section. In other words, the angle that is being measured is defined as the relative angle of the first section from the at rest position of the first section. The zero angle position of the first section is defined to be the rest position of the first section relative to the handle when (1) the test component is fixed in space, (2) the first section is free to rotate about its axis of rotation relative to the fixed test component, (3) the axis of rotation of the first section is oriented colinear to the axis of rotation of the torque tester for range of angles being measured and (4) no external forces or torques other than those transmitted from the second section and gravity act on the first section. Prior to measurement, all rotations of the first section to one side of the zero angle position are designated as positive, while the rotations of the first section to the other side of the zero angle position are designated as negative. The sign convention of the torque measurement is positive for positive rotations of the first section and negative for negative rotations of the first section.
Step 3: Make the individual measurement of torque versus angle.
The following is the sequence for measurement of the torque-angle data of a safety razor.
Determine the angles at which to perform torque measurement by first determining the full angular range of the pivot mechanism; then by dividing this range into thirty about equal spaced intervals for measurement, resulting in a total of thirty one angles; and selecting the middle seventeen angles for measurement. Measurement of torque and angle at these seventeen angle can provide an accurate calculation of the torque stiffness over the middle 50% of the total angular range of the pivot mechanism.
For each of the angles, fasten the test component into the appropriate clamps (424 and 425) to ensure the instant center of rotation for the angle being measured is coincident to the axis of rotation of the tester, TT.
Attach the clamps to the torque tester in the zero angle position. Make the first measurement at the first positive value of the angle position being measured by moving the first section from the zero angle position to this first positive angle position.
Wait 20 seconds to 1 minute at this angle position. Record the torque value. Move the first section back to the zero angle position and wait 1 minute. Move to the next angle position at which a measurement is being made. Repeat the foregoing steps until all measurements are made.
Step 4. Calculate the measured data from the torque stiffness.
To determine the torque stiffness value, plot the seventeen torque measurements (y-axis) versus the corresponding seventeen angle measurements (x-axis). Create the best fit straight line through the data using a least squares linear regression. The torque stiffness value is the slope of the line Y═K*X+B, in which Y=torque (in N*mm); X=angle (in degrees); K=torque stiffness value (in N*mm/degree); and B=torque (in N*mm) at zero angle from the best fit straight line.
The dimensions and values disclosed herein are not to be understood as being strictly limited to the exact numerical values recited. Instead, unless otherwise specified, each such dimension is intended to mean both the recited value and a functionally equivalent range surrounding that value. For example, a dimension disclosed as “40 mm” is intended to mean “about 40 mm.”
Every document cited herein, including any cross referenced or related patent or application, is hereby incorporated herein by reference in its entirety unless expressly excluded or otherwise limited. The citation of any document is not an admission that it is prior art with respect to any invention disclosed or claimed herein or that it alone, or in any combination with any other reference or references, teaches, suggests or discloses any such invention. Further, to the extent that any meaning or definition of a term in this document conflicts with any meaning or definition of the same term in a document incorporated by reference, the meaning or definition assigned to that term in this document shall govern.
While particular embodiments of the present invention have been illustrated and described, it would be obvious to those skilled in the art that various other changes and modifications can be made without departing from the spirit and scope of the invention. It is therefore intended to cover in the appended claims all such changes and modifications that are within the scope of this invention.
Representative embodiments of the present disclosure described above can be described as follows:
A. A handle, the handle comprising:
B. The handle of paragraph A, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis.
C. The handle of paragraph A or B, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis and wherein the pivot axis is generally parallel to one of the first and second coil axes.
D. The handle of any of paragraphs A-C, wherein the first coil axis and the second coil axis is substantially parallel to and offset from the pivot axis a distance of from about 1 mm to about 5 mm.
E. The handle of any of paragraphs A-D, wherein the first coil axis and the second coil axis is substantially parallel to and offset from the pivot axis a distance of about 2 mm.
F. The handle of any of paragraphs A-E, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
G. The handle of any of paragraphs A-F, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 12 N-mm.
H. The handle of any of paragraphs A-G, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 10 N-mm.
I. The handle of any of paragraphs A-H, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
J. The handle of any of paragraphs A-I, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
K. A handle comprising:
L. The handle of paragraph K, wherein the coil spring defines a coil axis and the pivot axis is generally parallel to the coil axis.
M. The handle of paragraph K or L, wherein the coil spring defines a longitudinal coil axis that is substantially parallel to and offset from the pivot axis a distance of about 1 mm to about 5 mm.
N. The handle of any of paragraphs K-M, wherein the coil spring defines a longitudinal coil axis that is substantially parallel to and offset from the pivot axis a distance of about 2 mm.
O. The handle of any of paragraphs K-N, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
P. The handle of any of paragraphs K-O, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 8 N-mm.
Q. The handle of any of paragraphs K-P, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 6 N-mm.
R. The handle of any of paragraphs K-Q, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
S. The handle of any of paragraphs K-R, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
T. A handle, the handle comprising:
U. The handle of paragraph T, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis.
V. The handle of paragraph T or U, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis and wherein the pivoting head is rotatable about a first pivot axis, the first pivot axis being generally parallel to one of the first and second coil axes.
W. The handle of any of paragraphs T-V, wherein the first coil axis and the second coil axis is substantially parallel to and offset from the pivot axis a distance of from about 1 mm to about 5 mm.
X. The handle of any of paragraphs T-W, wherein first coil axis and the second coil axis is substantially parallel to and offset from the pivot axis a distance of about 2 mm.
Y. The handle of any of paragraphs T-X, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 40 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
Z. The handle of any of paragraphs T-Y, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 40 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 12 N-mm.
AA. The handle of any of paragraphs T-Z, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 40 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 8 N-mm.
BB. The handle of any of paragraphs T-AA, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
CC. The handle of any of paragraphs T-BB, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
DD. A handle, the handle comprising:
EE. The handle of paragraph DD, wherein the first and second surfaces are first and second angularly diverging surfaces.
FF. The handle of paragraph DD or EE, wherein the pivot spring comprises a first coil spring and a second coil spring and a main bar portion that couples the first and second coil springs together in a spaced relationship.
GG. The handle of any of paragraphs DD-FF, wherein the pivot spring comprising a first coil spring and a second coil spring and a main bar portion that couples the first and second coil springs together and wherein the first coil spring defines a first longitudinal coil axis and the second coil spring defines a second longitudinal coil axis, and wherein the first longitudinal coil axis is generally coaxial with the second longitudinal coil axis.
HH. The handle of any of paragraphs DD-GG, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis and wherein the first pivot axis is generally parallel to one of the first and second coil axis.
II. The handle of any of paragraphs DD-HH, wherein the first longitudinal coil axis and the second longitudinal coil axis is substantially parallel to and offset from the pivot axis a distance of from about 1 mm to about 5 mm.
JJ. The handle of any of paragraphs DD-II, wherein the first longitudinal coil axis and the second longitudinal coil axis is substantially parallel to and offset from the pivot axis a distance of about 2 mm.
KK. The handle of any of paragraphs DD-JJ, wherein the first and second angularly diverging surfaces of the first and second limit members diverge at an angle of about 45 degrees.
LL. The handle of any of paragraphs DD-KK, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
MM. The handle of any of paragraphs DD-LL, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 12 N-mm.
NN. The handle of any of paragraphs DD-MM, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 10 N-mm.
OO. The handle of any of paragraphs DD-NN, wherein the pivot spring is selected from the group consisting of coil spring, leaf spring, helical compression spring, and disc spring.
PP. The handle of any of paragraphs DD-OO, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
QQ. The handle of any of paragraphs DD-PP, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
RR. A handle comprising:
SS. The handle of paragraph RR, wherein longitudinal coil axis is substantially parallel to and offset from the pivot axis a distance of from about 1 mm to about 5 mm.
TT. The handle of paragraph RR or SS, wherein the longitudinal coil axis that is substantially parallel to and offset from the pivot axis a distance of about 2 mm.
UU. The handle of any of paragraphs RR-TT, the first and second angularly diverging surfaces of the first and second limit members each diverge at an angle of about 45 degrees.
VV. The handle of any of paragraphs RR-UU, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
WW. The handle of any of paragraphs RR-VV, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 8 N-mm.
XX. The handle of any of paragraphs RR-WW, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 6 N-mm.
YY. The handle of any of paragraphs RR-XX, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
ZZ. The handle of any of paragraphs RR-YY, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
AAA. A handle, the handle comprising:
BBB. The handle of paragraph AAA, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis.
CCC. The handle of paragraph AAA or BBB, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis and wherein the pivoting head is rotatable about a first pivot axis, the first pivot axis being generally parallel to one of the first and second coil axes.
DDD. The handle of any of paragraphs AAA-CCC, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis and wherein the pivoting head is rotatable about a first pivot axis, the first pivot axis being generally parallel to one of the first and second coil axes and offset from one of the first and second coil axes a distance of from about 1 mm to about 5 mm.
EEE. The handle of any of paragraphs AAA-DDD, wherein the first coil spring defines a first coil axis and the second coil spring defines a second coil axis, and wherein the first coil axis is generally coaxial with the second coil axis and wherein the pivoting head is rotatable about a first pivot axis, the first pivot axis being generally parallel to one of the first and second coil axes and offset from one of the first and second coil axes a distance of from about 2 mm.
FFF. The handle of any of paragraphs AAA-EEE, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
GGG. The handle of any of paragraphs AAA-FFF, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 12 N-mm.
HHH. The handle of any of paragraphs AAA-GGG, wherein the pivoting head is rotatable about a first pivot axis from the rest position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 10 N-mm.
III. The handle of any of paragraphs AAA-HHH, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
JJJ. The handle of any of paragraphs AAA-III, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
KKK. A handle, the handle comprising:
LLL. The handle of paragraph KKK, wherein the first coil spring defines a first longitudinal coil axis and the second coil spring defines a second longitudinal coil axis, and wherein the first longitudinal coil axis is generally coaxial with the second longitudinal coil axis.
MMM. The handle of paragraph KKK or LLL, wherein the first coil spring defines a first longitudinal coil axis and the second coil spring defines a second longitudinal coil axis, and wherein the first longitudinal coil axis is generally coaxial with the second longitudinal coil axis and wherein the pivoting head is rotatable about a first pivot axis, the first pivot axis being generally parallel to and offset from the first and second longitudinal coil axes.
NNN. The handle of any of paragraphs KKK-MMM, wherein the first longitudinal coil axis and the second longitudinal coil axis are each offset from the pivot axis a distance of from about 1 mm to about 5 mm.
OOO. The handle of any of paragraphs KKK-NNN, wherein the first longitudinal coil axis and the second longitudinal coil axis are each offset from the pivot axis a distance of about 2 mm.
PPP. The handle of any of paragraphs KKK-OOO, wherein the pivoting head is rotatable about the first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
QQQ. The handle of any of paragraphs KKK-PPP, wherein the pivoting head is rotatable about the first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 12 N-mm.
RRR. The handle of any of paragraphs KKK-QQQ, wherein the pivoting head is rotatable about the first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 10 N-mm.
SSS. The handle of any of paragraphs KKK-RRR, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
TTT. The handle of any of paragraphs KKK-SSS, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
UUU. A handle comprising:
VVV. The handle of paragraph 11, wherein the pivot spring comprises at least one coil spring defining a longitudinal coil axis that is parallel to and is offset from the pivot axis a distance of from about 1 mm to about 5 mm.
WWW. The handle of paragraph UUU, wherein the pivot spring comprises at least one coil spring defining a longitudinal coil axis that is parallel to and is offset from the pivot axis a distance of about 2 mm.
XXX. The handle of paragraph UUU or WWW, wherein the pivot spring is selected from the group consisting of coil spring, leaf spring, helical compression spring, and disc spring.
YYY. The handle of any of paragraphs UUU-XXX, wherein the pivoting head is rotatable about the pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
ZZZ. The handle of any of paragraphs UUU-YYY, wherein the pivoting head is rotatable about the pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 12 N-mm.
AAAA. The handle of any of paragraphs UUU-ZZZ, wherein the pivoting head is rotatable about the pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 10 N-mm.
BBBB. The handle of any of paragraphs UUU-AAAA, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
CCCC. The handle of any of paragraphs UUU-BBBB, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
DDDD. A handle, the handle comprising:
EEEE. The handle of paragraph DDDD, wherein the first coil spring defines a first longitudinal coil axis and the second coil spring defines a second longitudinal coil axis, and wherein the first longitudinal coil axis is generally coaxial with the second longitudinal coil axis.
FFFF. The handle of paragraph DDDD or EEEE, wherein the first coil spring defines a first longitudinal coil axis and the second coil spring defines a second longitudinal coil axis, and wherein the first longitudinal coil axis is generally coaxial with the second longitudinal coil axis and wherein the pivot axis is generally parallel to one of the first and second longitudinal coil axes.
GGGG. The handle of any of paragraphs DDDD-FFFF, wherein the first coil spring defines a first longitudinal coil axis and the second coil spring defines a second longitudinal coil axis, and wherein the first longitudinal coil axis is generally coaxial with the second longitudinal coil axis and wherein the pivot axis is generally parallel to and offset from one of the first and second longitudinal coil axes a distance of from about 1 mm to about 5 mm.
HHHH. The handle of any of paragraphs DDDD-GGGG, wherein the first coil spring defines a first longitudinal coil axis and the second coil spring defines a second longitudinal coil axis, and wherein the first longitudinal coil axis is generally coaxial with the second longitudinal coil axis and wherein the pivot axis is generally parallel to and offset from one of the first and second longitudinal coil axes a distance of about 2 mm.
IIII. The handle of any of paragraphs DDDD-HHHH, wherein the pivoting head is rotatable about a first pivot axis and the main bar is substantially linear and having a main bar axis, the first pivot axis being generally parallel to the main bar axis.
JJJJ. The handle of any of paragraphs DDDD-IIII, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of up to about 25 N-mm.
KKKK. The handle of any of paragraphs DDDD-JJJJ, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 2 N-mm and about 12N-mm.
LLLL. The handle of any of paragraphs DDDD-KKKK, wherein the pivoting head is rotatable about a first pivot axis from the first position through an angle of rotation to an angle of between about 0 degrees and about 45 degrees and when rotated the pivot spring applies a biasing torque about the first pivot axis of between about 3 N-mm and about 10 N-mm.
MMMM. The handle of any of paragraphs DDDD-LLLL, wherein the pivot spring is made of a metal selected from the group consisting of steel and stainless steel.
NNNN. The handle of any of paragraphs DDDD-MMMM, wherein the pivot spring comprises stainless steel having a yield stress of between about 800 MPa and about 2300 MPa.
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