Patent Description:
Recent advances in shaving razors, such as a <NUM>-bladed or <NUM>-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.

<CIT> discloses a hair removal device comprising: a handle; a head positioned on one end of the handle, said hair removal device having a pivot axis about which said head is mounted; one or more orifice in the skin- facing surface of the head are positioned at or close to the pivot axis; a collapsible reservoir suitable for containing a fluid to be dispensed during use of the hair removal device through said one or more orifice; an enclosure system selected from a deformable rigid container or a non - deformable rigid container.

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.

According to the present invention a handle Is provided. The handle comprises:.

wherein the cover member comprises a face defining at least one exterior opening and the pivoting head comprises an interior compartment in fluid communication with the main body and the exterior opening. The pivoting head further comprises at least one interior channel, and a pivot spring which is at least partially disposed in the interior channel, 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, wherein the pivot spring is coupled with the pivoting head and interacts with the main body to bias the pivoting head about the pivot axis into a rest position.

A handle is disclosed. The handle has a main body and a pivoting head pivotally coupled with the main body about a pivot axis. The pivoting head has a substantially trapezoidal prism shape and include a base member and a cover member that overlies the base member in a mating relationship. The cover member includes a face defining at least one exterior opening and the pivoting head has an interior compartment in fluid communication with the main body and the exterior opening.

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 <FIG>, an embodiment of a shaving razor <NUM> is shown. The shaving razor can have a handle <NUM> and a blade cartridge unit <NUM> which can releasably attach to the handle <NUM> and can contain one or more blades <NUM>. The description herein relates primarily to the handle <NUM>, and features associated with the handle <NUM> that facilitate pivoting of the blade cartridge unit <NUM> relative to the handle <NUM>, and provision of skin benefit delivery components to the skin of a user of the razor <NUM>.

In the illustrated embodiments the skin benefit delivery components extend from handle <NUM> through an opening in the cartridge unit <NUM> 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 <FIG> can deliver a fluid to the skin of the user. As shown in <FIG> which shows the underside of the razor depicted in <FIG>, a portion of the handle <NUM> can extend through blade cartridge unit <NUM> and be exposed as face <NUM>. Face <NUM> can be a skin interfacing surface, intended to be contacting or proximate the skin of a user using the shaver, discussed more fully below. As shown in <FIG> and in more detail in <FIG> in which the blade cartridge unit <NUM> has been removed, face <NUM> is a surface of a pivoting head <NUM> and can have openings <NUM> through which a fluid can be dispensed for skin benefit during and after shaving. Pivoting head <NUM> can pivot about a pivot axis, referred to herein as a pivot axis or a first axis of rotation <NUM> with respect to handle <NUM>, as well as a secondary axis of rotation <NUM> that is generally perpendicular to the first axis of rotation <NUM>. Fluid flow from the reservoir in handle <NUM> can be achieved by pressing the skin benefit actuator <NUM>, which can be a depressible button, and which presses on a fluid reservoir inside handle <NUM> to urge fluid flow toward and through the pivoting head <NUM>, as described more fully below. The reservoir may be of any type. One example is described in co-owned, co-pending <CIT>.

In like manner, <FIG> shows another embodiment of a shaving razor that can have a handle <NUM> and a blade cartridge unit <NUM> which can releasably attach to the handle <NUM> and can contain one or more blades <NUM>. In the embodiment of <FIG>, the pivoting head <NUM> can comprise a heat delivery element which can deliver a heat benefit to the skin or a heat skin benefit. As with the razor shown in <FIG>, pivoting head <NUM> can pivot about the first axis of rotation <NUM> with respect to handle <NUM>, as well as a secondary axis of rotation <NUM> that is generally perpendicular to the first axis of rotation <NUM>. As shown in <FIG> which shows the underside of the razor depicted in <FIG>, a portion of the handle <NUM> can extend through blade cartridge unit <NUM> and be exposed as heating surface <NUM>, discussed more fully below. As shown in <FIG> and in more detail in <FIG> in which the blade cartridge unit <NUM> has been removed, heating surface <NUM> is a surface of a pivoting head <NUM> and can be heated to deliver a heat skin benefit during or after shaving. Heating can be achieved by pressing the skin benefit actuator <NUM>, which can be a depressible button, and which closes a powered circuit inside handle <NUM> to a flexible circuit to the pivoting head <NUM>, as described more fully below. The handle <NUM> may hold a power source, such as one or more batteries (not shown) that supply power to a heat delivery element, as discussed below. In certain embodiments, the heat delivery element may comprise a metal, such as aluminum or steel. The razor handle disclosed herein can include the heat delivery element disclosed co-owned, co-pending US Application having a Docket No. 14532FQ.

Referring now to <FIG>, an embodiment of a handle for a razor providing a fluid skin benefit will be described in more detail. It should be noted that many of the components described in relation to the razor <NUM> providing a fluid skin benefit can also be incorporated into a razor <NUM> providing for heat skin benefit, particularly as they relate to the handle and pivoting head described herein, including the shape of the pivoting head, and the spring mechanism that urges the pivoting head into a rest position, and the limit members that limit the range of rotation of the pivoting head, all as described more fully below.

As shown in <FIG>, the handle <NUM> can comprise a main body <NUM> that can include a main frame <NUM> and a secondary frame <NUM>. The main body <NUM> including its component main frame <NUM> and secondary frame <NUM> members can comprise a durable material such as metal, cast metal, plastic, impact-resistant plastic, and composite materials. The main frame <NUM> can be made of metal and can provide a significant portion of the structural integrity of the handle. In an embodiment the main frame <NUM> is comprised of zinc. In an embodiment the main frame <NUM> is comprised of die cast zinc. The secondary frame <NUM> can be made of a plastic material and can overlie most of the main frame <NUM> and provide for a significant portion of the size and comfort of the handle <NUM>.

Continuing to refer to <FIG>, a pivoting head <NUM> can be connected to the main body <NUM> by one or more arms <NUM>. Pivoting head <NUM> can pivot about the first axis of rotation <NUM> that is defined by the connection of the pivoting head <NUM> to pins <NUM> disposed at distal portions <NUM> of arms <NUM>, as described more fully below. As discussed above, blade cartridge unit <NUM> attaches to the pivoting head <NUM> such that the blade cartridge unit <NUM> can pivot on handle <NUM> to provide more skin contact area on the skin of a user during shaving.

The pivoting head <NUM> can have a shape beneficially conducive to both attaching to the blade cartridge unit <NUM> and facilitating the delivery of a skin benefit from the handle <NUM> to and through the blade cartridge unit <NUM> attached to the handle <NUM>.

The shape of the pivoting head <NUM> 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 <FIG> and shows a shape having a relatively wide upper face (or opening) <NUM>, a relatively narrow lower face <NUM>, two long major faces <NUM>, and two end faces <NUM> that are generally trapezoidal-shaped.

The description "trapezoidal prism" is used herein as the best description for the overall visual appearance of the pivoting head <NUM>, but the description does not imply any particular geometric or dimensional requirements beyond what is described herein. That is, the pivoting head <NUM>, including the cover member <NUM>, 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 <NUM> 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 <NUM> kJ/m<NUM> (as measured by ISO <NUM>/<NUM>). The thermoplastic resin can have a relatively high tensile modulus above <NUM> MPa as measured using ISO <NUM>-<NUM> /<NUM>-A (<NUM>/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 <NUM> kJ/m<NUM> (as measured by ISO <NUM>/<NUM>), including with values equal to or greater than <NUM> kJ/m<NUM>, and including values greater than <NUM> kJ/m<NUM> can be utilized. Further, it is contemplated that the thermoplastic material is relatively stiff having a tensile modulus above <NUM> MPa as measured using ISO <NUM>-<NUM> /<NUM>-A (<NUM>/min). Examples include HOSTAFORM® XT20 and HOSTAFORM® S9363.

Referring now to <FIG>, embodiments of the disclosure in which a fluid skin benefit can be delivered via the pivoting head <NUM> are described. <FIG> shows a pivoting head in side profile in which corresponding faces <NUM>, <NUM>, <NUM>, and <NUM> of the trapezoidal prism shape in <FIG> are shown, the trapezoidal prism shape schematically representing the general shape impression of the pivoting head <NUM>. <FIG> shows a portion of pivoting head <NUM> that includes a cover member <NUM>, a base member <NUM> connected to cover member <NUM>, and arms <NUM> connected handle <NUM> and to pivoting head <NUM> at pivot axis, i.e., first axis of rotation <NUM>. A fluid skin benefit can be delivered via a benefit delivery member in the form of a fluid benefit delivery member <NUM> operatively coupled to base member <NUM> to permit fluid flow from the fluid delivery member into the pivoting head <NUM>. Thus, fluid benefit delivery member <NUM> can include a flexible plastic benefit pivot delivery connection, such as a flexible silicone plastic tube, operatively coupled to a fluid reservoir in the handle <NUM> and to base member <NUM> such that upon depressing the skin benefit actuator <NUM> on handle <NUM>, a fluid, including a lubricating lotion, can be transmitted from inside handle <NUM> through pivoting head <NUM>, and out of openings <NUM> on face <NUM> as shown in <FIG>.

The materials chosen for fluid benefit delivery member <NUM> 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 <NUM> 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 <NUM> 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 <NUM> which can be a different material, including a relatively harder plastic. However, fluid benefit delivery member <NUM> can also be formed separately and joined to base member <NUM>. 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 <NUM> can include creep resistant materials having an increase in tensile strain of less than about <NUM>% from an initial tensile strain when measured using ISO <NUM> carried out at <NUM> hours at <NUM> Fahrenheit (<NUM>).

In an embodiment, materials for the fluid benefit delivery member <NUM> can include materials having a hardness of about <NUM> on a Shore A durometer scale and about <NUM> on a Shore A durometer scale. The materials for any benefit delivery member, such as the fluid benefit delivery member <NUM> or heat delivery member <NUM> can be below 60A, including values below 50A.

In an embodiment, materials for the fluid benefit delivery member <NUM> can include elastomers having compression sets less than about <NUM>% as measured by ASTM D-<NUM>.

In an embodiment, benefit delivery member has a moment of inertia from about <NUM><NUM> to about <NUM><NUM>.

Other materials suitable for fluid benefit delivery member <NUM> 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 <NUM> (corresponding to the end faces <NUM> of the schematic shape shown in <FIG>) of the pivoting head <NUM> can have a limit member <NUM> that limits the extent of rotation of pivoting head <NUM> about first axis of rotation <NUM>. In an embodiment, limit members <NUM> limit rotation by providing a surface of the pivoting head <NUM> that can come into contact with arms <NUM> to stop rotation. For example, in an embodiment, the limit members can include first and second surfaces <NUM>, <NUM> that can come into contacting relationship with arms <NUM> to stop rotation of the pivoting head about first axis of rotation <NUM>. In an embodiment, surfaces <NUM>, <NUM> can be diverging surfaces that diverge relative to each other from a closest position near the pivoting axis <NUM> a distance substantially the extent of the portion of pivoting head <NUM> corresponding to the short dimension of the major faces <NUM> of the trapezoidal prism shape. As can be understood from <FIG>, the first diverging surface <NUM> can limit movement of the pivoting head to a first position and the second diverging surface <NUM> can limit the movement of the pivoting head to a second position. Pivoting of the pivoting head <NUM> is thus limited by the interaction of the diverging surfaces and the arms <NUM>. First and second diverging surfaces <NUM>, <NUM>, can be flat, partially flat, or have non-flat portions, with the only requirement being that a portion of the diverging surfaces contact arm <NUM> to limit rotation as desired. As shown in <FIG>, for example, first diverging surface <NUM> of limit member <NUM> can be substantially flat and can be disposed in contacting
relationship adjacent arm <NUM> to limit the pivoting head <NUM> from further pivoting in a counterclockwise direction (as viewed in <FIG>).

As can be understood from the description herein, the included angle <NUM> between the diverging surfaces (e.g., an angle of divergence) for the angularly diverging surfaces <NUM> and <NUM> can determine the angular rotation of pivoting head <NUM> about first axis of rotation <NUM>. In an embodiment, the angle of divergence for the angularly diverging surfaces <NUM> and <NUM> can be up to <NUM> degrees or more. As can be understood, therefore, in an embodiment, pivoting head <NUM> can rotate from a first position at <NUM> degrees to a second position at about <NUM> degrees relative to the first position, and any position therebetween. At all positions a spring member <NUM> can apply a biasing force at a location corresponding to a main bar portion axis <NUM>, as described more fully below, to urge pivoting head <NUM> toward the first, at rest, position. The position shown in <FIG>, can be considered a rest position, as this is the position of the pivoting head <NUM> when no biasing force is applied against spring member <NUM> (shown in <FIG>) to rotate the pivoting head clockwise (as viewed in <FIG>). The rest position of the pivoting head can be at any angle within the included angle <NUM>.

Referring to <FIG>, pivoting head <NUM> is shown connected to the main frame <NUM> of the main body <NUM> by arms <NUM>, referred to individually as first arm 24A and second arm 24B. The nomenclature of "A" and "B" is used herein to denote individual pairs of elements. Fluid benefit delivery member <NUM> extends from main body <NUM> and connects to base member <NUM>, which is joined to cover member <NUM> to provide for controlled fluid transport from a reservoir inside handle <NUM> to one or more openings <NUM> on the face <NUM> of pivoting head <NUM>. As discussed above, face <NUM> can extend through an opening on an attached blade cartridge unit <NUM> such that face <NUM> can be disposed very near, or even on, the skin of a user when razor <NUM> is used for shaving. Fluid flow can be provided, for example, by pressure applied to a flexible fluid reservoir inside handle <NUM>. Pressure can be applied, for example, by the user pressing on a skin benefit actuator <NUM> on handle <NUM>.

As shown in <FIG> and <FIG>, in an embodiment, a proximal portion <NUM> of arms <NUM> can be connected to the main frame <NUM> at a mounting location <NUM>. Arms <NUM> can be made of metal and the main frame can be made of metal such that a relatively strong connection can be facilitated by the fixation of metal arms on a metal main frame. Proximal portion <NUM> of arm <NUM> can define an opening <NUM> (shown in more detail in <FIG>) in arm <NUM> which can engage a protuberance <NUM> on main frame <NUM> for connection to main body <NUM> of handle <NUM>. Arms <NUM> likewise have a distal portion <NUM> which can engage a bearing recess <NUM> in pivoting head <NUM> (described more fully below) for connecting the pivoting head <NUM> to the main body <NUM> of handle <NUM>. Thus, as shown in <FIG> and <FIG>, in an embodiment, a first arm 24A can have a first proximal portion 52A that can define an opening 54A that can connect to a first protuberance 56A at a first location 60A on main frame <NUM>, and a second arm 24B can have a second proximal portion 52B that can define an opening 54B that can connect to a second protuberance 56B at a second location 60B on main frame <NUM>. Likewise, a first arm 24A can have a first distal portion 58A that can connect to a first bearing recess in pivoting head <NUM>, and a second arm 24B can have a second distal portion 58B that can connect to a second bearing recess in pivoting head <NUM>.

Referring now to <FIG>, certain components of an embodiment of the pivoting head <NUM> are shown in more detail. Pivoting head <NUM> can have mating portions that when connected together form a spring-loaded compartment <NUM> therebetween, the compartment facilitating the delivery of a skin benefit to a user during shaving. For example, as discussed above, pivoting head <NUM> can have a cover member <NUM>, a base member <NUM> connected to cover member <NUM>, and arms <NUM> connecting the pivoting head <NUM> to main body <NUM>.

As shown in <FIG> and <FIG>, which show assembly views of certain components of one embodiment of a pivoting head <NUM> from different angles, arms <NUM> can have pins <NUM> disposed at distal portions <NUM> thereof. In an embodiment, cylindrical pins <NUM> can be welded to distal portions <NUM> of arms <NUM>. Each pin <NUM> can be operatively disposed in a bearing recess <NUM> on pivoting head <NUM>. The bearing recess <NUM> can be a cylindrical opening on cover member <NUM> having an inside diameter slightly greater than the outside diameter of pins <NUM>, such that cover member <NUM>, and therefore pivoting head <NUM>, can freely pivot upon the first axis of rotation <NUM>. A spring member <NUM> is partially disposed between the mating faces of the cover member <NUM> and base member <NUM> and acts to bias the pivoting head <NUM> in relation to arms <NUM> into the first position as shown in <FIG>, in which first diverging surface <NUM> of limit member <NUM> rests in contacting relationship with arm <NUM>.

Spring member <NUM> 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 <NUM> comprises torsion springs, and can have at least one coil spring <NUM>. In an
embodiment, two coil springs 68A and 68B are coupled together in a spaced relationship by a main bar portion <NUM> as shown in <FIG>. In an embodiment, coil springs <NUM> can each define a longitudinal coil axis <NUM>. In an embodiment, the axis of rotation, which can be called a pivot axis or a first pivot axis, can be parallel to and offset from one of the longitudinal coil axes.

Additionally, spring member <NUM> can be can be made of plastic, impact-resistant plastic, metal, and composite materials. In an embodiment, the spring member <NUM> 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 <NUM>, 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 <NUM> can be made of <NUM> Series or <NUM> Series stainless steel at spring temper per ASTM A313. In an embodiment, spring member <NUM> can be comprised of stainless steel wire (e.g., <NUM> stainless steel wire) having an ultimate tensile strength metal greater than <NUM> MPa or an engineering yield stress between about <NUM> MPa and about <NUM> MPa.

First arm 24A and second arm 24B can each be generally flat members having generally parallel planar opposite sides. Arms <NUM> can define an imaginary plane <NUM>, as shown in <FIG>, and the imaginary plane 66A of arm 24A can be coplanar with the imaginary plane 66B of arm 24B. Pins <NUM> can each have an imaginary longitudinal pin axis <NUM> disposed centrally in relation to each pin, and imaginary longitudinal pin axis 68A of pin 30A on arm 24A can be coaxial with longitudinal pin axis 68B of pin 30B on arm 24B, as indicated in <FIG>.

Arms <NUM> can have various shapes and features beneficially adapted to the pivoting head <NUM>. Additionally, arms can be made of plastic, impact-resistant plastic, metal, and composite materials. In an embodiment, arms <NUM> can be comprised of metal. Arms <NUM> and can be made of a <NUM> or <NUM> Series stainless steel having an engineering yield stress measured by ASTM standard E8 greater than about <NUM> MPa, and preferably greater than <NUM> MPa and a tensile strength again measured by ASTM standard E8 greater than <NUM> MPa.

As shown in <FIG>, arms <NUM> can be sized and shaped appropriately to the size of the pivoting head <NUM> and handle <NUM> to which pivoting head <NUM> is attached. In example
embodiments shown in <FIG> and <FIG>, arm <NUM> can be considered in plan view having an arm length, Al, of from about <NUM> to about <NUM>, and can be about <NUM>. In an embodiment arm <NUM> can have an arm width, Aw, of from about <NUM> to about <NUM>, and can be about <NUM>. In the embodiments shown in <FIG> and <FIG>, arm <NUM> can be a substantially uniform thickness plate having an arm thickness, At, of from about <NUM> to about <NUM>, and can be about <NUM>. In an embodiment, arm <NUM> can be substantially flat in side profile, as shown in <FIG>. In an embodiment, arm <NUM> can have at least one bend as shown in side profile in <FIG>. As shown, a pin <NUM> can be integral with arm <NUM>, or attached, such as by welding, to arm <NUM> such that a portion 30C of pin <NUM> extends laterally to engage the bearing recess <NUM> of the pivoting head <NUM>. Pin <NUM> can be a circular cross section cylindrical shape having a length of from about <NUM> to about <NUM> and can be about <NUM>. Pin <NUM> can have a largest cross-sectional dimension, such as a diameter, of from about <NUM> to about <NUM>, and can be about <NUM>. Perimeter of holes in arm can be from about <NUM> to about <NUM> and can be about <NUM>. To ensure product integrity during accidental drops and to prevent excessive deflection during use, along the length of the arm, the arms have a minimum cross-sectional moment of inertia multiplied by the elastic modulus of the arm material greater than <NUM> N-cm<NUM>. In an embodiment, this minimum cross-sectional moment of inertia multiplied by the elastic modulus of the arm material can be about <NUM> N-cm<NUM> to about <NUM> N-cm<NUM>.

As shown in <FIG> and <FIG>, arm <NUM> can have portions at a proximal portion <NUM> defining an opening <NUM>. Openings can be used to engage and attach arms <NUM> to the main body <NUM>. For example, arm <NUM> shown in <FIG> corresponds to arm <NUM> shown in <FIG> and <FIG>, in which opening <NUM> engages a protuberance <NUM> on main frame <NUM> of main body <NUM>.

<FIG> show alternative embodiments of arms <NUM>. As shown in <FIG> and <FIG>, arms <NUM> can have a variable thickness At, and can have a thicker portion generally central to arm <NUM> and thinner portions near the ends of arm <NUM>. Such a configuration can permit optimization of strength and weight of arms <NUM>. <FIG> and <FIG> show alternative connection embodiments in which a hook member on the proximal portion <NUM> of arm <NUM> can engage a mating portion of main body <NUM>.

Pivoting head <NUM> can be rotated about first axis of rotation <NUM> by a biasing force applied to the pivoting head to rotate the pivoting head <NUM> about the first axis of rotation <NUM> to a second
position such that second diverging surface <NUM> rests in contacting relationship with arm <NUM>. Upon removal of the biasing force, spring member <NUM> can act to rotate pivoting head back to the first position. In an embodiment, pivoting head <NUM> can be rotated about the first axis of rotation <NUM>, which can be considered a first pivot axis, from the first position through an angle of rotation of between about <NUM> degrees and about <NUM> degrees and when rotated the pivot spring applies a biasing torque about the first axis of rotation <NUM> of less than about <NUM> N-mm at an angle of rotation of about <NUM> degrees. In an embodiment, pivoting head <NUM> can be rotated about the first axis of rotation <NUM>, which can be considered a first pivot axis, from the first position through an angle of rotation of between about <NUM> degrees and about <NUM> degrees and when rotated the pivot spring applies a biasing torque about the first axis of rotation <NUM> of between about <NUM> N-mm and about <NUM> N-mm.

In an embodiment in which a fluid benefit delivery member <NUM> is coupled to the base member <NUM> of pivoting head <NUM>, the fluid benefit delivery member <NUM> 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 <NUM>% of the restorative, biasing torque about the first axis of rotation <NUM>. In an embodiment, the restorative, biasing torque about the first axis of rotation <NUM> can be about less than about <NUM> N-mm and can be about <NUM> N-mm with about <NUM> N-mm contributed by spring member <NUM> and about <NUM> N-mm contributed by the fluid benefit delivery member <NUM>. 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 <NUM> or a heat delivery member <NUM> 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 <NUM> and can be greater than <NUM>. Torque can be measured according to the Static Torque Stiffness Method described below in the Test Methods section.

As shown in <FIG>, spring member <NUM> can be a torsion spring and can include a first coil spring 69A and a second coil spring 69B coupled by a main bar portion <NUM>. A leg extension
<NUM> can extend from each coil spring <NUM> a sufficient length to operatively engage arms <NUM> to provide the biasing force necessary to cause pivoting head <NUM> to be urged toward the first, rest, position. When the pivoting head is biased to rotate about the first axis of rotation <NUM> away from the first, rest, position, spring member <NUM> applies a resisting, restorative force to urge the pivoting head back to the first position. Coil springs 69A and 69B can each define a longitudinal coil axis <NUM>. Longitudinal coil axis 74A of first coil spring 68A can be coaxial with longitudinal coil axis 74B of second coil axis 68B. One or both of longitudinal axes <NUM> can be substantially parallel to and offset from the first axis of rotation <NUM>, which can be referred to as a pivot axis. Spring member <NUM> can be made of metal, including steel, and can be stainless steel having an engineering yield stress greater than about <NUM> MPa. In the illustrated embodiments, coil springs <NUM> are operatively disposed on each end of pivoting head <NUM> and a portion of the main bar portion <NUM> resides between the cover member <NUM> and base member <NUM> to provide direct engagement to bias the pivoting head toward a rest position. In the illustrated embodiments it can be understood that there are certain relationships defined between the first axis of rotation <NUM>, the longitudinal coil axes <NUM>, and the main bar portion axis <NUM>. Specifically, as depicted in <FIG>, the first axis of rotation <NUM> can be parallel to and offset from both of the longitudinal coil axes 74A, 74B, and can, as well, be parallel to and offset from the main bar portion axis <NUM>. In an embodiment, the first axis of rotation <NUM> can be parallel to and offset from both of the longitudinal coil axes 74A, 74B a distance of from about <NUM> to about <NUM>. In an embodiment, the first axis of rotation <NUM> can be parallel to and offset from both of the longitudinal coil axes 74A, 74B a distance of about <NUM>.

In an embodiment, spring member can be made of materials including amorphous polymers with glass transition temperatures above <NUM> Celsius, metals, elastomers having compression sets less than <NUM>% as measured by ASTM D-<NUM> and combinations thereof.

In an embodiment, spring member comprises creep resistant materials having an increase in tensile strain of less than about <NUM>% from an initial tensile strain when measured using ISO <NUM> carried out at <NUM> hours at <NUM> Fahrenheit (<NUM>).

<FIG> illustrate an embodiment of a base member <NUM> having at least one channel <NUM> disposed on a face thereof. In an embodiment, base member <NUM> includes a channel <NUM> for housing a portion of spring member <NUM>. The embodiment illustrated in <FIG> includes a
fluid benefit delivery member <NUM>, but with respect to the channel <NUM> the base member <NUM> need not be coupled to the fluid benefit delivery member <NUM>, but could, instead, house components related to a heating surface <NUM>, as described in more detail below. Base member <NUM> can be molded plastic, and channel <NUM> can be a molded channel. Likewise, fluid deliver member <NUM> can be molded flexible plastic and can be molded integrally with base member <NUM>. Channel <NUM> can have a size and shape conformed to receive the main bar portion <NUM> of spring member <NUM>, as shown in <FIG>. <FIG> shows spring member <NUM> prior to being inserted into channel <NUM>; <FIG> shows spring member <NUM> placed into channel <NUM> with first and second coil springs 68A and 68B disposed at an exterior portion of base member <NUM>. As shown in <FIG>, cover member <NUM>, also made of molded plastic and made to have mating surfaces with base member <NUM> can be joined by translating onto and connecting to the base member in the direction indicated by arrows in <FIG>.

Once cover member <NUM> is in mating relationship with base member <NUM>, cover member and base member can be joined, such as by adhesive, press fit, or welding. In an embodiment, as shown in <FIG>, staking pins <NUM> can be driven into openings <NUM> in a cold press fit as shown in <FIG> to cause the base member <NUM> and cover member <NUM> to remain in operatively stable mating relationship. In an embodiment that includes a fluid delivery member for a fluid skin benefit, once the base member <NUM> and cover member <NUM> are securely mated, a compartment <NUM> is defined between the parts, which compartment <NUM> has a volume into which fluid can flow from the handle <NUM> and from which fluid can flow to openings <NUM> on the skin interfacing face <NUM> of pivoting head <NUM>.

Fluid containment in compartment <NUM> can be achieved by a sealing relationship between cover member <NUM> and base member <NUM>. <FIG> shows the mating surface of a cover member <NUM> and <FIG> shows the first mating surface <NUM> of a base member <NUM>. In the embodiment shown in <FIG>, sealing can be achieved by the first mating face <NUM> of cover member <NUM> that, when operatively connected to base member <NUM> can mate in a juxtaposed, contacting relationship with a second mating face <NUM> of base member <NUM>. A gasket member <NUM> can extend outwardly from first mating face <NUM> and can sealingly fit in a corresponding gasket groove <NUM> on base member <NUM>.

An embodiment of a pivoting head <NUM> can be assembled onto handle <NUM> in a manner illustrated in <FIG>. As shown in <FIG>, pins <NUM> of arms <NUM> can be inserted into bearing recess <NUM> of cover member <NUM> by translating in the direction of the arrow of <FIG>, which direction aligns with the longitudinal pin axis <NUM> (as shown in <FIG>) and first axis of rotation <NUM>. As shown in <FIG>, spring member <NUM> is disposed in operative relationship between cover member <NUM> and base member <NUM>. Once pin <NUM> is inserted into bearing recess <NUM>, as shown in <FIG>, pin <NUM> and arm <NUM> can freely rotate in bearing recess <NUM>. Arms <NUM> can be held in place in any suitable manner while they are slid in the direction of the arrows in <FIG>, which shows before (A) and after (B) depictions of the arm securement in slots <NUM> of main body <NUM>. Once in place, as shown in <FIG>, openings <NUM> of arms <NUM> can be exposed through a corresponding access opening <NUM> in main body <NUM>. As shown in <FIG>, one or more extensions <NUM> on or in slot <NUM> can provide for an interference fit to hold arms in place for the next step.

Referring now to <FIG>, there is shown certain handle <NUM> elements being assembled to secure pivoting head <NUM> to handle <NUM>. An embodiment of main frame <NUM> is shown translating in the direction of the arrows in <FIG> from a first position (A) to join secondary frame <NUM> (B). Main frame <NUM> can be joined to secondary frame <NUM> by adhesive applied at adhesive grooves <NUM> on secondary frame <NUM> which can mate with corresponding adhesive bosses on main frame <NUM>. Main frame <NUM> can be disposed on a portion of secondary frame <NUM> in a mating relationship such that protuberances <NUM> are inserted through access openings <NUM> of main body <NUM> and openings <NUM> of arms <NUM>. Protuberances <NUM> can provide positive metal-to-metal coupling of arms <NUM> to handle <NUM>. In an embodiment adhesive can be applied at the connection of protuberances <NUM> and openings <NUM> to provide for additional securement of arms (and, therefore, pivoting head <NUM>) to main frame <NUM> (and, therefore, handle <NUM>).

Referring now to <FIG>, an embodiment of a pivoting head having a heat delivery member <NUM> for delivering heat as a skin benefit is described. Pivoting head <NUM> for delivering heat can have components common to those described above for delivering fluid, such as one or more arms <NUM>, one or more spring members <NUM>, a cover member <NUM> and a base member <NUM>, and these common components can be configured as described above, or in a similar manner. However, the pivoting head <NUM> for delivering a heat benefit can also have a heat delivery member <NUM> comprised of heat delivery components, including a flexible conductive strip <NUM> for conducting electricity from a first proximal portion 98A operatively attached in handle <NUM> to a second distal
portion 98B operatively disposed in pivoting head <NUM> and delivering heat to the skin at a heating surface <NUM>.

<FIG> shows an embodiment of a pivoting head <NUM> for a razor delivering a heat skin benefit. The pivoting head can include a cover member <NUM> connected to a base member <NUM> and a spring member <NUM> partially disposed between the cover member <NUM> and the base member <NUM>. The pivoting head <NUM> shown in <FIG> can include components shown in the assembly view of <FIG>. As shown in <FIG>, in an embodiment spring member <NUM> as described above can be disposed between the cover member <NUM> and the base member <NUM>, substantially as described above. Other components can be disposed on the outside of cover member <NUM> and can be attached in a layered relationship having sizes that correspond to the narrow lower face of the cover member <NUM>.

As shown in <FIG>, the heat delivery member <NUM> may include a face plate <NUM> for delivering heat to or proximal to the skin's surface during a shaving stroke for an improved shaving experience. In certain embodiments, the face plate <NUM> may have an outer skin contacting heating surface <NUM> comprising a relatively hard coating (that is harder than the material of the face plate <NUM>), such as titanium nitride to improve durability and scratch resistance of the face plate <NUM>. Similarly, if the face plate <NUM> is manufactured from aluminum, the face plate <NUM> may go through an anodizing process. The hard coating of the skin contact surface may also be used to change or enhance the color of the skin application surface <NUM> of the face plate <NUM>. The heat delivery element <NUM> may be in electrical communication with a portion of the handle <NUM>. As will be described in greater detail below, the heat delivery element <NUM> may be mounted to the pivoting head <NUM> and in communication with the power source (not shown).

Continuing to refer to <FIG>, one possible embodiment of the heat delivery element <NUM> is shown that may be incorporated into the shaving razor <NUM> of <FIG>. The face plate <NUM> may be as thin as possible, but stable mechanically. For example, the face plate <NUM> may have a wall thickness of about <NUM> micrometers to about <NUM> micrometers. The face plate <NUM> may comprise a material having a thermal conductivity of about <NUM> to <NUM> W/mK, such as steel. The face plate <NUM> can be manufactured from a thin piece of steel that results in the face plate <NUM> having a low thermal conductivity thus helping minimize heat loss through a perimeter wall <NUM> and maximizes heat flow towards the skin interfacing surface <NUM>. Although a thinner piece of steel is
preferred for the above reasons, the face plate <NUM> may be constructed from a thicker piece of aluminum having a thermal conductivity ranging from about <NUM> to <NUM> W/mK. The heat delivery element <NUM> may include a heater (not shown), e.g., a resistive heat element portion of flexible conductive strip <NUM>, that is in electrical contact with a micro-controller and a power source (not shown), e.g. a rechargeable battery, positioned within the handle <NUM>.

The heat delivery member <NUM> may include the face plate <NUM>, the flexible conductive strip <NUM> heater, a heat dispersion layer <NUM>, a compressible thermal insulation layer <NUM>, and a portion of cover member <NUM>. The face plate <NUM> may have a recessed inner surface <NUM> opposite the skin application surface <NUM> configured to receive the heater <NUM>, the heat dispersion layer <NUM> and the compressible thermal insulation layer <NUM>. The perimeter wall <NUM> may define the inner surface <NUM>. The perimeter wall <NUM> may have one or more tabs <NUM> extending from the perimeter wall <NUM>, transverse to and away from the inner surface <NUM>. For example, <FIG> illustrates four extending from the perimeter wall <NUM>.

The heat dispersion layer <NUM> may be positioned on and in direct contact with the inner surface <NUM> of the face plate <NUM>. The heat dispersion layer <NUM> may have a lower surface <NUM> directly contacting the inner surface <NUM> of the face plate <NUM> and an upper surface <NUM> (opposite lower surface <NUM>) directly contacting the heater <NUM>. The heat dispersion layer <NUM> can be defined as a layer of material having a high thermal conductivity and can be compressible. For example, the heat dispersion layer <NUM> may comprise graphite foil. Potential advantages of the heat dispersion layer <NUM> include improving lateral heat flow (spreading the heat delivery from the heater <NUM> across the inner surface <NUM> of the face plate <NUM>, which is transferred to the skin application surface <NUM>) resulting in more even heat distribution and minimization of hot and cold spots. The heat dispersion layer <NUM> may have an anisotropic coefficient of thermal conductivity in the plane parallel to the face plate <NUM> of about <NUM> to about <NUM> W/mK (preferably <NUM> to <NUM> W/mK) and vertical to the face plate <NUM> of about <NUM> to <NUM> W/mK and preferably <NUM> to <NUM> W/mK to facilitate sufficient heat conduction or transfer. In addition, the compressibility of the heat dispersion layer <NUM> allows the heat dispersion layer <NUM> adapt to non-uniform surfaces of the inner surface <NUM> of the face plate <NUM> and non-uniform surfaces of the heater <NUM>, thus providing better contact and heat transfer. The compressibility of the heat dispersion layer <NUM> also minimizes stray particulates from pushing into the heater <NUM> (because the heat dispersion layer <NUM> may be softer than the heater), thus preventing damage to the heater <NUM>. In certain embodiments, the heat dispersion layer <NUM> may comprise a graphite foil that is compressed by about <NUM>% to about <NUM>% of its original thickness. For example, the heat dispersion layer <NUM> may have a compressed thickness of about <NUM> micrometers to about <NUM> micrometers more preferably <NUM> to <NUM> micrometers.

The heater <NUM> may be positioned between two compressible layers. For example, the heater <NUM> may be positioned between the heat dispersion layer <NUM> and the compressible thermal insulation layer <NUM>. The two compressible layers may facilitate clamping the heater <NUM> in place without damaging the heater <NUM>, thus improving securement and assembly of the heat delivery element <NUM>. The compressible thermal insulation layer <NUM> may help direct the heat flow toward the face plate <NUM> and away from the cover member <NUM>. Accordingly, less heat is wasted, and more heat may be able to reach the skin during shaving. The compressible thermal insulation layer <NUM> may have low thermal conductivity, for example, less than <NUM> W/mK and preferably less than <NUM> W/mK. In certain embodiments, the compressible thermal insulation layer <NUM> may comprise an open cell or closed cellular compressible foam. The compressible thermal insulation layer <NUM> may be compressed <NUM>-<NUM>% from its original thickness. For example, the compressible thermal insulation layer <NUM> may have a compressed thickness of about <NUM> to about <NUM>.

The cover member <NUM> may be mounted on top of the compressible thermal insulation layer <NUM> and secured to the face plate <NUM>. Accordingly, the heater <NUM>, the heat dispersion layer <NUM> and the compressible thermal insulation layer <NUM> may be pressed together between the face plate <NUM> and the cover member <NUM> and assembled as described more fully below. The heat dispersion layer <NUM>, the heater <NUM>, and the compressible thermal insulation layer <NUM> may fit snugly within the perimeter wall <NUM>. 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 <NUM>. 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 <NUM> may fit snugly within the perimeter wall <NUM>.

Thus, in an embodiment, the first layer in contacting relationship with cover member <NUM> can be a compressible thermal insulation layer <NUM> such as a foam member. A portion of the heater in the form of a flexible conductive strip <NUM> can be sandwiched between a foam thermal insulation layer <NUM> and a graphite foil strip heat dispersion layer <NUM>. The layers of foam thermal insulation layer <NUM>, flexible conductive strip <NUM> and graphite foil strip can be connected in layered, contacting relationship to the narrow lower face of the cover member <NUM> by a faceplate <NUM>. Faceplate <NUM> can have a smooth outer surface that corresponds to heating surface <NUM>, and tabs <NUM> that can be used to connect the heat delivery components to the pivoting head <NUM>.

Assembling a pivoting head for delivering a heat skin benefit can be described with reference to <FIG>. Referring to the assembly view of <FIG>, a graphite foil strip heat dispersion layer <NUM> can be placed onto a trough <NUM> of faceplate <NUM>, such as onto the recessed inner surface <NUM> of faceplate <NUM>. In a next step, as shown in the assembly view of <FIG>, distal portion 98B of flexible conductive strip <NUM> can be shaped and fit into the trough <NUM> of faceplate <NUM>. Next, as shown in the assembly view of <FIG>, a compressible thermal insulation layer <NUM> member can be placed into trough <NUM> of faceplate <NUM>. As with the other members placed in trough <NUM>, foam thermal insulation layer <NUM> can be sized and shaped accordingly to fit in trough <NUM>. Next, as shown in <FIG>, cover member <NUM> can be placed on top of the other layered components in and faceplate <NUM>.

Once cover member <NUM> is placed on top of the layered members in an on trough <NUM>, faceplate <NUM> can be secured to the cover member <NUM> via tabs <NUM> as shown in the assembly view of <FIG>. As shown, one or more tabs <NUM>, including a pair of tabs labeled <NUM> and <NUM> in <FIG> and <FIG> and <FIG> in <FIG>, can be folded into receiving openings <NUM> on cover member <NUM>, as shown in the cross-sectional perspective assembly view of <FIG>. As described with respect to <FIG>, spring member <NUM> as described above, can be placed in cover member <NUM> and seated in corresponding form-fitting recesses, including a channel <NUM>, of cover member <NUM>. Finally, base member <NUM> can be connected to cover member in a sequence described with respect to the assembly view of <FIG>. As shown in <FIG>, one or more first latching members <NUM> on base member <NUM> can be placed into and hooked into one or more first latch receiving portions <NUM> of cover member <NUM>, and, as shown in <FIG>, base member <NUM> can be rotated and pressed onto cover member <NUM> such that one or more second latching members <NUM> can be snapped into cooperating second latch receiving portions <NUM>.

Once base member <NUM> is securely snapped into place on cover member <NUM>, the illustrated embodiment of pivoting head <NUM> is ready to be coupled to handle <NUM>. As shown in <FIG> and <FIG> arms <NUM> can be inserted in the direction of the arrows into the bearing recess <NUM> of cover member <NUM> by sliding pins <NUM> into the bearing recesses <NUM>, as described above. As shown in <FIG>, arms <NUM> can then be inserted in the direction of arrows into slots <NUM> of main body <NUM>. As shown in the cut away perspective view of <FIG>, a slot <NUM> is shown having disposed therein the proximal portion of arm <NUM> as well as a leg extension <NUM> of spring member <NUM>. Once arms <NUM> are in place into slots <NUM> and in place as shown in <FIG>, portions of main body <NUM> can be cold stamped in the direction of the arrows to secure arms <NUM> to main body <NUM> of handle <NUM>. As shown in the partial cut away perspective view of <FIG>, portions of the main body <NUM> corresponding to openings <NUM> of arms <NUM> can be permanently plastically deformed by pressing into the openings <NUM>. This operation, known as cold stamping or cold staking, permits secure coupling of arms <NUM>, and therefore, pivoting head <NUM>, to main body <NUM> (and, therefore, handle <NUM>).

As disclosed above, pivoting head <NUM> can be pivoted about a pivot axis, i.e., axis of rotation <NUM> under the biasing force of a spring member <NUM>. However, other pivot mechanisms can be employed for both the first axis of rotation <NUM> and secondary axis of rotation <NUM>. In general, pivoting head <NUM> can be in pivotal relation to the handle <NUM> 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 <NUM> 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 <NUM> to <NUM>. Rolling element bearings can typically have friction of <NUM> to <NUM>. 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 <NUM> allow rotational motions ranging from about <NUM> degrees from the cartridge rest position to about <NUM> degrees. A rotational stiffness for a pivot mechanism about first axis of rotation <NUM> may be measured by deflecting the pivot <NUM> degrees about the first axis of rotation <NUM> and measuring the required torque about this first axis of rotation <NUM> to maintain this position. The torque levels at <NUM> degrees of rotation can be generally less than <NUM> 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 <NUM> can be generally less than <NUM> N-mm per degree of rotation and preferably between <NUM> N-mm per degree of rotation and <NUM> N-m per degree of rotation.

Typically, additional pivot mechanisms about secondary axis of rotation <NUM> (shown in <FIG> and <FIG>) allow rotational motions ranging from -<NUM> degrees to +<NUM> degrees. A rotational stiffness for a pivot mechanism about secondary axis of rotation may be measured by deflecting the pivot -<NUM> degrees and +<NUM> degrees about secondary axis of rotation <NUM> and measuring the required torques about the secondary axis of rotation to maintain this position. The rotational stiffness may be calculated by dividing the absolute value of the difference in these measured torques by the <NUM> degrees difference in angular motion. The rotational stiffness associated with pivot mechanisms about secondary axis of rotation <NUM> generally range from about <NUM> to about <NUM> N-mm per degree of rotation.

As disclosed above, components of the pivoting head <NUM> and the pivoting mechanism that enable rotation about first axis of rotation <NUM> for the embodiments were shown in detail. The handle <NUM> was connected to the pivoting head <NUM> by a pair of arms <NUM>, a spring member <NUM>, and a benefit pivot delivery connection. In the embodiments disclosed above, the spring member can be comprised of a metal. But the spring member <NUM> 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 <NUM> or razor handle <NUM> from taking a "set," or permanently deforming at deflected angle when the razor <NUM> or razor handle <NUM> is stored improperly due to the stress relaxation of the components that connect the pivoting head <NUM> 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 <NUM> to the pivoting head <NUM> to deliver a skin benefit through the cartridge <NUM> to the skin interfacing face <NUM>. As discussed below, a fluid benefit delivery member <NUM> and a heat delivery member <NUM> can be configured so as to facilitate proper pivoting of the pivoting head about first axis of rotation <NUM> and secondary axis of rotation <NUM>.

Referring to <FIG>, a razor <NUM> is shown in which the flexible conductive strip <NUM> of heat delivery member <NUM> bridges a gap between the handle <NUM> and the pivoting head onto which is attached a blade cartridge <NUM>. As shown in <FIG>, and in more detail in <FIG>, the flexible conductive strip <NUM> is longer than the distance to be traversed between the handle <NUM> and the pivoting head <NUM>, resulting in a loop <NUM> of the flexible conductive strip <NUM>. This loop <NUM>, which can be generally U-shaped or S-shaped, can minimize the effect of the flexible conductive strip <NUM> on the biasing torque force required to pivot the pivoting head <NUM> about the first axis of rotation <NUM>. In general, this loop <NUM> of the benefit delivery member contributes to a ratio of biasing torque provided by the sum of the benefit member and the spring member <NUM>, and the biasing torque provided by the spring member alone, which torque ration is discussed in more detail below.

In like manner, as depicted in <FIG>, a fluid delivery benefit member, such as a flexible plastic tube, can also have a loop <NUM> portion such that excess length of the flexible tube allows for minimizing the effect of the fluid benefit delivery member <NUM> on the biasing torque force required to pivot the pivoting head <NUM> about the first axis of rotation <NUM>. In an embodiment, the installed length of fluid benefit delivery member <NUM>, as shown in <FIG> can be from <NUM> to <NUM> less than the free length of the fluid benefit delivery member <NUM>. This forced compression contributes to the loop <NUM> portion and has been found to aid in further minimizing the effect of the fluid benefit delivery member <NUM> on the biasing torque force required to pivot the pivoting head <NUM> about the first axis of rotation <NUM>.

Additional features found to further minimizing the effect of the fluid benefit delivery member <NUM> on the biasing torque force required to pivot the pivoting head <NUM> about the first axis of rotation <NUM> can be understood with reference to <FIG>. In <FIG>, a portion of handle <NUM> at the location where fluid delivery member exits the handle <NUM> and begins to traverse the distance to the pivoting head, a fillet radius of curvature <NUM> of from between about <NUM> and about <NUM> is provided. The radius of curvature can be understood to reduce the stress applied to the surface of the fluid delivery member at the point of bending due to the pivoting of pivoting head <NUM> during use.

In a similar manner, as shown in <FIG>, at a portion of handle <NUM> at the location where fluid delivery member exits the handle <NUM> and begins to traverse the distance to the pivoting head, a chamfer <NUM> is provided, as shown. The chamfer can have a chamfer angle of about <NUM> degrees to about <NUM> degrees at the proximal end of the handle, and can have a chamfer length of about <NUM> to about <NUM>. Like the radius of curvature <NUM>, the chamfer <NUM> is believed to reduce the stress applied to the surface of the fluid delivery member at the point of bending due to the pivoting of pivoting head <NUM> during use.

The dimensions of a chamfer can be defined as shown in the view of <FIG>. In view <NUM>, a block <NUM> is shown with an edge <NUM> to be chamfered and a front face <NUM>. In view <NUM>, block <NUM> is shown after edge <NUM> has been chamfered creating chamfer <NUM>. In view <NUM>, chamfer <NUM> is shown having a chamfer length <NUM> and a chamfer angle <NUM>. In general, the torque associated with a pivot benefit delivery member can be reduced by cutout in the surrounding structure of the pivoting benefit delivery member that is a chamfer with a chamber angle between about <NUM> degrees and <NUM> degrees and chamfer length from <NUM> to <NUM>.

Further, an additional feature found to minimize the effect of the fluid benefit delivery member <NUM> on the biasing torque force required to pivot the pivoting head <NUM> about the first axis of rotation <NUM> can be understood from <FIG> as a slot <NUM> on the handle <NUM> at the location of the exit of the fluid benefit delivery member <NUM>. In an embodiment, the slot can have a width measured generally parallel to the axis of rotation <NUM> of about <NUM> to about <NUM>, and a length measured perpendicular to the width of from about <NUM> to about <NUM>.

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 <FIG>. For example, as depicted in <FIG>, fluid benefit delivery member <NUM>, which can be a flexible molded plastic tube, can be configured such that a distal portion <NUM> has a thinner wall diameter than a proximal portion <NUM>. As shown in <FIG>, the proximal portion <NUM> which can be connected in fluid communication with other components in the handle <NUM> (not shown), can have a diameter and/or wall thickness that provides for durability and greater physical integrity during manufacture and use. However, the distal portion <NUM> which connects to the cover member <NUM> of the pivoting head, can comprise a relatively smaller diameter or a relatively thinner wall thickness, thereby providing for greater flexibility and less effect on the biasing torque force required to pivot the pivoting head <NUM> about the first axis of rotation <NUM>.

In <FIG>, an alternative embodiment of fluid benefit delivery member <NUM> is shown in which the tube wall of the fluid benefit delivery member <NUM> is ribbed or corrugated. It is believed that such a design, by permitting much of the wall to be relatively thinner, can, when joined to the base member <NUM> provide for greater flexibility and less effect on the biasing torque force required to pivot the pivoting head <NUM> about the first axis of rotation <NUM>.

Alternative embodiments of fluid benefit delivery member <NUM> utilizing coil springs to reinforce strength and provide for flexibility are depicted in <FIG>. As depicted in <FIG>, a coil spring <NUM>, which can be made of plastic or metal, can configured about the outside of fluid benefit delivery member <NUM>. As depicted in the cross-sectional view of <FIG>, a coil spring <NUM>, which can be made of plastic or metal, can configured about the inside of fluid benefit delivery member <NUM>. As depicted in <FIG>, a coil spring <NUM>, which can be made of plastic or metal, can configured to be molded into the walls of fluid benefit delivery member <NUM>.

<FIG> depicts one embodiment of a feature to join fluid deliver member <NUM> to the base member <NUM>. As shown, a ball and socket joint component <NUM> can be present on the base member <NUM>. The distal end of a tubular fluid delivery member can be joined by pressing or gluing onto the receiving end of the ball and socket joint component <NUM>.

The joining of the fluid benefit delivery member <NUM> to the pivoting head <NUM> can be a two-component embodiment, as shown in <FIG>. In a two-component embodiment, the fluid benefit delivery member <NUM> can be molded with an integral pivoting head connection member <NUM> that can attach to the mating portion of the pivoting head <NUM> in any suitable manner, such as snap fit, friction fit, adhesive joining, or the like. In this embodiment, a spring member <NUM> (not shown) can be added externally to the pivoting head <NUM> to provide for a biasing force on pivoting head.

In an embodiment, the fluid benefit delivery member <NUM> and the base member <NUM> of the pivoting head <NUM> can be overmolded in a two-shot injection mold to form a three-component assembly that can form pivoting head <NUM>. In this manner the base member can be a relatively hard material and the fluid benefit delivery member <NUM> can be a relatively soft material. A portion of the polymer injection molded for the fluid delivery member forms the gasket member <NUM> of the base member <NUM>, as described above. Referring to <FIG>, the base member <NUM> and fluid benefit delivery member <NUM> are shown as they would appear if they were injection molded separately. However, in an embodiment, the fluid benefit delivery member <NUM> and the base member <NUM> can be overmolded in a two-shot injection mold process to manufacture an integral member as shown in <FIG>, in which the material of the fluid benefit delivery member <NUM> extends through base member <NUM> and is exposed at the first mating surface <NUM> as gasket member <NUM>. <FIG> shows another perspective view of the first mating surface <NUM> of the cover member <NUM> having exposed and extended therefrom a gasket member <NUM> which is integral with fluid benefit delivery member <NUM>. A two-shot injection molding of the fluid delivery member with the base member <NUM> as described is believed to increase the structural integrity of the fluid benefit delivery member <NUM>/base member <NUM> unit by increasing the force required to remove the base member <NUM> from the fluid benefit delivery member <NUM>. As described above, the base member can be joined to the third component, i.e., the cover member <NUM>, such that their respective first and second mating faces <NUM>, <NUM> are joined, and gasket member <NUM> lodges in and forms a gasket in gasket groove <NUM> of cover member <NUM>.

In an embodiment, the fluid flow path of the pivoting head <NUM> can be configured to provide for relatively unobstructed, smooth, continuous fluid flow from the fluid benefit delivery member <NUM> to openings <NUM> in face <NUM> of pivoting head <NUM>, which can be a skin interfacing face. As shown in <FIG>, which depict partial cross-sectional views of a pivoting head <NUM> having joined thereto a fluid benefit delivery member <NUM> that enters at a location having an area approximating the cross-sectional area of the fluid benefit delivery member <NUM> tube, a flow distributor <NUM> which directs and distributes fluid flow can be present. It is believed that having the flow distributor begin distribution relatively close to the entry point of the tube of the fluid benefit delivery member <NUM>. By beginning fluid deflection and distribution almost immediately upon entry to the compartment <NUM>, it has been unexpectedly found that fluid flow is enhanced, and blockage or clogging of openings, including openings <NUM>, is minimized or eliminated. In an embodiment the fluid flow distributor <NUM> is located about <NUM> to about <NUM> from a junction of the connection of the fluid benefit delivery member <NUM> to the pivoting head <NUM>. In an embodiment, the fluid reservoir in the pivoting head <NUM> can have a small cross section closer to the connection of the fluid benefit delivery member <NUM> to the pivoting head <NUM>.

In general, the internal fluid conduit associated with fluid benefit delivery member <NUM> can have an internal hydraulic diameter from about <NUM> to about <NUM>. In general, the fluid benefit delivery member can have a minimum hydraulic diameter along the exterior of the fluid benefit delivery member from about <NUM> to about <NUM>.

In general, the materials used for the fluid benefit delivery member <NUM> can be elastomers with compression set of about less than <NUM>%, and preferably about less than <NUM>% measured by ASTM D-<NUM>. In an embodiment, silicone elastomer has been found to be suitable for the fluid benefit delivery member <NUM>.

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 <NUM>%, and preferably less than about <NUM>%, from initial tensile strain when measured using ISO <NUM>-<NUM> carried out at <NUM> 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 <NUM> of heat delivery member <NUM> and fluid benefit delivery member <NUM>, can be comprised of materials that stress relax, it can be advantageous if the rotational stiffness of the pivoting head <NUM> is greater than twice, or more preferably greater than <NUM> times, the rotational stiffness of the pivoting head <NUM> with the benefit delivery member removed. The rotational stiffness of the pivoting head <NUM> 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 <NUM> and the handle <NUM>. 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 <NUM>. This latter configuration greatly reduces the probability and conditions under which the razor <NUM> or razor handle <NUM> 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.

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.

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 <NUM>, for example) of the pivot mechanism and torques versus angles of rotation between sections are measured. Referring to <FIG>, in general, the pivot mechanism <NUM> can be understood to rotate a first section <NUM> of the test component located on one side of the pivot mechanism relative to a second section <NUM> of the test component located on the far side of the pivot mechanism about an axis of rotation AA. These first and second sections may include parts of the pivot mechanism.

In <FIG>, some representative measurements of torque stiffness for different mechanisms are shown. From these figures, torque stiffness can be understood to be a measurement of proportionality between measurement of torque and rotation angle. More specifically, torque stiffness, K, is the proportionality constant for the least squares best fit line <NUM> for measurements <NUM> of torque versus rotation angle over the middle <NUM>% <NUM> of the full range <NUM> of angular motion of the pivot mechanism <NUM> unless otherwise specified. An individual torque measurement can be understood to be the measurement of torque and angle while holding the relative angle between the first section <NUM>, which can rotate, and the second section <NUM>, which is held fixed, constant.

The static torque stiffness method consists of (<NUM>) identifying the instant center of rotation over the full angular range of the motion of the pivot mechanisms, (<NUM>) clamping the test component into an appropriate test fixture that has the torque sensor centered about axis of
rotation, (<NUM>) making the individual measurement of torque and rotation, and (<NUM>) calculating the torque stiffness. The environmental testing conditions for the static torque stiffness method comprise of making measurements at a room temperature of <NUM> Celsius and relative humidity of <NUM>% to <NUM>% and using test components that are in a dry, "as-made" condition.

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 <FIG>, the instant center of rotation C of a pivot mechanism undergoing a planar rotation can be determined by tracing the path, PATH1 and PATH2, of two points, P1, and P2, on the rotating first section <NUM>. As an illustration, <FIG> shows Section <NUM> at <NUM> positions 401a, 401b, and 401c, and it calculates the instant center of rotation C at position 401b. At this angle of rotation, two lines, T1 and T2, can be drawn tangent to PATH1 and PATH2 respectively. Two additional lines, R1 and R2, can be drawn perpendicular to T1 and T2 respectively. The instant center can be located at the intersection of R1 and R2. In general, the instant center can be considered fixed for the full range of angular motion of the pivot mechanism if all pivot centers are in a region R, which has an area of <NUM><NUM>.

As shown in FIG. <NUM>, an appropriate test measurement system <NUM> can be configured to make the torque versus angle measurements needed to calculate the torque stiffness. Representative components of a torque tester such as Instron's MT1 MicroTorsion tester are shown as a tester base <NUM>, tester torque cell <NUM>, and torque tester rotational member <NUM>. Instron's MT1 MicroTorsion tester has a full-scale torque cell of <NUM> N-mm, with a torque
accuracy of +/-<NUM>%, a torque repeatability of +/-<NUM>%, and an angle resolution of <NUM> degrees. The tester base <NUM> is fixed and attached to a torque cell <NUM> while the tester rotational member <NUM> rotates about an axis of rotation, TT. The fixed second section <NUM> is fastened to the torque cell side <NUM> of the tester using a first clamping mechanism <NUM>. The rotating first section <NUM> is fastened to the tester rotational member <NUM> using a second clamping mechanism <NUM>. Both clamping mechanisms are designed to allow the pivot to freely rotate through its full range of motion with little to no lateral loading on the pivot mechanism. They are also designed to make the tester axis of rotation, TT, colinear to the pivot mechanism's axis of rotation, AA. For pivot mechanisms whose instant center of rotation changes, multiple clamps should be used to ensure that these axes are colinear.

The angles of rotation measured in accordance with the static torque stiffness method are the angles of deflection of the moving first section <NUM> 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 (<NUM>) the test component is fixed in space, (<NUM>) the first section is free to rotate about its axis of rotation relative to the fixed test component, (<NUM>) 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 (<NUM>) 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.

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 <NUM>% of the total angular range of the pivot mechanism.

For each of the angles, fasten the test component into the appropriate clamps (<NUM> and <NUM>) 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 <NUM> seconds to <NUM> minute at this angle position. Record the torque value. Move the first section back to the zero angle position and wait <NUM> minute. Move to the next angle position at which a measurement is being made. Repeat the foregoing steps until all measurements are made.

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.

Claim 1:
A handle for a razor, the handle (<NUM>) comprising:
• a main body (<NUM>);
• a pivoting head (<NUM>) pivotally coupled with the main body (<NUM>) about a pivot axis, the pivoting head (<NUM>) having a substantially trapezoidal prism shape and comprising a base member (<NUM>) and a cover member (<NUM>) that overlies the base member (<NUM>) in a mating relationship; and
wherein the cover member (<NUM>) comprises a face (<NUM>) defining at least one exterior opening and the pivoting head (<NUM>) comprises an interior compartment in fluid communication with the main body (<NUM>) and the exterior opening, characterized in that the pivoting head (<NUM>) further comprises at least one interior channel, and a pivot spring which is at least partially disposed in the interior channel, the pivot spring comprising a first coil spring (68A, 69A) and a second coil spring (68B, 69B) and a main bar portion (<NUM>) that couples the first (68A, 69A) and second (68B, 69B) coil springs together, wherein the pivot spring is coupled with the pivoting head (<NUM>) and interacts with the main body (<NUM>) to bias the pivoting head (<NUM>) about the pivot axis into a rest position.