Patent ID: 12240135

DETAILED DESCRIPTION OF THE INVENTION

Except as otherwise noted, the articles “a,” “an,” and “the” mean “one or more.” Referring toFIG.1, an embodiment of a shaving razor10is shown. The shaving razor can have a handle12and a blade cartridge unit15which can releasably attach to the handle12and can contain one or more blades17. The description herein relates primarily to the handle12, and features associated with the handle12that facilitate pivoting of the blade cartridge unit15relative to the handle12, and provision of skin benefit delivery components to the skin of a user of the razor10.

In the illustrated embodiments the skin benefit delivery components extend from handle12through an opening in the cartridge unit15and 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 inFIG.1can deliver a fluid to the skin of the user. As shown inFIG.2which shows the underside of the razor depicted inFIG.1, a portion of the handle12can extend through blade cartridge unit15and be exposed as face80. Face80can 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 inFIG.2and in more detail inFIG.3in which the blade cartridge unit15has been removed, face80is a surface of a pivoting head22and can have openings78through which a fluid can be dispensed for skin benefit during and after shaving. Pivoting head22can pivot about a pivot axis, referred to herein as a pivot axis or a first axis of rotation26with respect to handle12, as well as a secondary axis of rotation27that is generally perpendicular to the first axis of rotation26. Fluid flow from the reservoir in handle12can be achieved by pressing the skin benefit actuator14, which can be a depressible button, and which presses on a fluid reservoir inside handle12to urge fluid flow toward and through the pivoting head22, as described more fully below. The reservoir may be of any type. One example is described in co-owned, co-pending U.S. patent application Ser. No. 15/499,307, which is hereby incorporated herein by reference.

In like manner,FIG.4shows another embodiment of a shaving razor that can have a handle12and a blade cartridge unit15which can releasably attach to the handle12and can contain one or more blades17. In the embodiment ofFIG.4, the pivoting head22can comprise a heat delivery element which can deliver a heat benefit to the skin or a heat skin benefit. As with the razor shown inFIG.1, pivoting head22can pivot about the first axis of rotation26with respect to handle12, as well as a secondary axis of rotation27that is generally perpendicular to the first axis of rotation26. As shown inFIG.5which shows the underside of the razor depicted inFIG.4, a portion of the handle12can extend through blade cartridge unit15and be exposed as heating surface82, discussed more fully below. As shown inFIG.5and in more detail inFIG.6in which the blade cartridge unit15has been removed, heating surface82is a surface of a pivoting head22and can be heated to deliver a heat skin benefit during or after shaving. Heating can be achieved by pressing the skin benefit actuator14, which can be a depressible button, and which closes a powered circuit inside handle12to a flexible circuit to the pivoting head22, as described more fully below. The handle12may 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, which is hereby incorporated herein by reference.

Referring now toFIG.7, 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 razor10providing a fluid skin benefit can also be incorporated into a razor10providing 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 inFIG.7, the handle12can comprise a main body16that can include a main frame18and a secondary frame20. The main body16including its component main frame18and secondary frame20members can comprise a durable material such as metal, cast metal, plastic, impact-resistant plastic, and composite materials. The main frame18can be made of metal and can provide a significant portion of the structural integrity of the handle. In an embodiment the main frame18is comprised of zinc. In an embodiment the main frame18is comprised of die cast zinc. The secondary frame20can be made of a plastic material and can overlie most of the main frame18and provide for a significant portion of the size and comfort of the handle12.

Continuing to refer toFIG.7, a pivoting head22can be connected to the main body16by one or more arms24. Pivoting head22can pivot about the first axis of rotation26that is defined by the connection of the pivoting head22to pins30disposed at distal portions58of arms24, as described more fully below. As discussed above, blade cartridge unit15attaches to the pivoting head22such that the blade cartridge unit15can pivot on handle12to provide more skin contact area on the skin of a user during shaving.

The pivoting head22can have a shape beneficially conducive to both attaching to the blade cartridge unit15and facilitating the delivery of a skin benefit from the handle12to and through the blade cartridge unit15attached to the handle12.

The shape of the pivoting head22can 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 inFIG.8and shows a shape having a relatively wide upper face (or opening)32, a relatively narrow lower face34, two long major faces36, and two end faces38that are generally trapezoidal-shaped.

The description “trapezoidal prism” is used herein as the best description for the overall visual appearance of the pivoting head22, but the description does not imply any particular geometric or dimensional requirements beyond what is described herein. That is, the pivoting head22, including the cover member40, need not have complete edges or surfaces. Further, edges need not be unbroken and straight, and sides need not be unbroken and flat.

Pivoting head22and 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/m2can 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 toFIG.9, embodiments of the disclosure in which a fluid skin benefit can be delivered via the pivoting head22are described.FIGS.9-13shows a pivoting head in side profile in which corresponding faces32,34,36, and38of the trapezoidal prism shape inFIG.8are shown, the trapezoidal prism shape schematically representing the general shape impression of the pivoting head22.FIG.9shows a portion of pivoting head22that includes a cover member40, a base member42connected to cover member40, and arms24connected handle12and to pivoting head22at pivot axis, i.e., first axis of rotation26. A fluid skin benefit can be delivered via a benefit delivery member in the form of a fluid benefit delivery member76operatively coupled to base member42to permit fluid flow from the fluid delivery member into the pivoting head22. Thus, fluid benefit delivery member76can include a flexible plastic benefit pivot delivery connection, such as a flexible silicone plastic tube, operatively coupled to a fluid reservoir in the handle12and to base member42such that upon depressing the skin benefit actuator14on handle12, a fluid, including a lubricating lotion, can be transmitted from inside handle12through pivoting head22, and out of openings78on face80as shown inFIG.10.

The materials chosen for fluid benefit delivery member76can 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 member76can 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 member76can 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 member42which can be a different material, including a relatively harder plastic. However, fluid benefit delivery member76can also be formed separately and joined to base member42. 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 member76can 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 member76can include materials having a hardness of about10on a Shore A durometer scale and about60on a Shore A durometer scale. The materials for any benefit delivery member, such as the fluid benefit delivery member76or heat delivery member96can be below60A, including values below50A.

In an embodiment, materials for the fluid benefit delivery member76can 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 mm4to about 40 mm4.

Other materials suitable for fluid benefit delivery member76can 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 ends44(corresponding to the end faces38of the schematic shape shown inFIG.8) of the pivoting head22can have a limit member46that limits the extent of rotation of pivoting head22about first axis of rotation26. In an embodiment, limit members46limit rotation by providing a surface of the pivoting head22that can come into contact with arms24to stop rotation. For example, in an embodiment, the limit members can include first and second surfaces48,50that can come into contacting relationship with arms24to stop rotation of the pivoting head about first axis of rotation26. In an embodiment, surfaces48,50can be diverging surfaces that diverge relative to each other from a closest position near the pivoting axis26a distance substantially the extent of the portion of pivoting head22corresponding to the short dimension of the major faces36of the trapezoidal prism shape. As can be understood fromFIG.9, the first diverging surface48can limit movement of the pivoting head to a first position and the second diverging surface50can limit the movement of the pivoting head to a second position. Pivoting of the pivoting head22is thus limited by the interaction of the diverging surfaces and the arms24. First and second diverging surfaces48,50, can be flat, partially flat, or have non-flat portions, with the only requirement being that a portion of the diverging surfaces contact arm24to limit rotation as desired. As shown inFIG.9, for example, first diverging surface48of limit member46can be substantially flat and can be disposed in contacting relationship adjacent arm24to limit the pivoting head22from further pivoting in a counter-clockwise direction (as viewed inFIG.9).

As can be understood from the description herein, the included angle43between the diverging surfaces (e.g., an angle of divergence) for the angularly diverging surfaces48and50can determine the angular rotation of pivoting head22about first axis of rotation26. In an embodiment, the angle of divergence for the angularly diverging surfaces48and50can be up to 50 degrees or more. As can be understood, therefore, in an embodiment, pivoting head22can 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 member64can apply a biasing force at a location corresponding to a main bar portion axis86, as described more fully below, to urge pivoting head22toward the first, at rest, position. The position shown inFIG.9, can be considered a rest position, as this is the position of the pivoting head22when no biasing force is applied against spring member64(shown inFIG.13) to rotate the pivoting head clockwise (as viewed inFIG.9). The rest position of the pivoting head can be at any angle within the included angle43.

Referring toFIG.10, pivoting head22is shown connected to the main frame18of the main body16by arms24, referred to individually as first arm24A and second arm24B. The nomenclature of “A” and “B” is used herein to denote individual pairs of elements. Fluid benefit delivery member76extends from main body16and connects to base member42, which is joined to cover member40to provide for controlled fluid transport from a reservoir inside handle12to one or more openings78on the face80of pivoting head22. As discussed above, face80can extend through an opening on an attached blade cartridge unit15such that face80can be disposed very near, or even on, the skin of a user when razor10is used for shaving. Fluid flow can be provided, for example, by pressure applied to a flexible fluid reservoir inside handle12. Pressure can be applied, for example, by the user pressing on a skin benefit actuator14on handle12.

As shown inFIGS.10and11, in an embodiment, a proximal portion52of arms24can be connected to the main frame18at a mounting location60. Arms24can 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 portion52of arm24can define an opening54(shown in more detail inFIG.12) in arm24which can engage a protuberance56on main frame18for connection to main body16of handle12. Arms24likewise have a distal portion58which can engage a bearing recess62in pivoting head22(described more fully below) for connecting the pivoting head22to the main body16of handle12. Thus, as shown inFIGS.11and12, in an embodiment, a first arm24A can have a first proximal portion52A that can define an opening54A that can connect to a first protuberance56A at a first location60A on main frame18, and a second arm24B can have a second proximal portion52B that can define an opening54B that can connect to a second protuberance56B at a second location60B on main frame18. Likewise, a first arm24A can have a first distal portion58A that can connect to a first bearing recess in pivoting head22, and a second arm24B can have a second distal portion58B that can connect to a second bearing recess in pivoting head22.

Referring now toFIG.13, certain components of an embodiment of the pivoting head22are shown in more detail. Pivoting head22can have mating portions that when connected together form a spring-loaded compartment84therebetween, the compartment facilitating the delivery of a skin benefit to a user during shaving. For example, as discussed above, pivoting head22can have a cover member40, a base member42connected to cover member40, and arms24connecting the pivoting head22to main body16.

As shown inFIGS.13and14, which show assembly views of certain components of one embodiment of a pivoting head22from different angles, arms24can have pins30disposed at distal portions58thereof. In an embodiment, cylindrical pins30can be welded to distal portions58of arms24. Each pin30can be operatively disposed in a bearing recess62on pivoting head22. The bearing recess62can be a cylindrical opening on cover member40having an inside diameter slightly greater than the outside diameter of pins30, such that cover member40, and therefore pivoting head22, can freely pivot upon the first axis of rotation26. A spring member64is partially disposed between the mating faces of the cover member40and base member42and acts to bias the pivoting head22in relation to arms24into the first position as shown inFIG.4, in which first diverging surface48of limit member46rests in contacting relationship with arm24.

Spring member64can 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 member64comprises torsion springs, and can have at least one coil spring68. In an embodiment, two coil springs68A and68B are coupled together in a spaced relationship by a main bar portion70as shown inFIG.14. In an embodiment, coil springs68can each define a longitudinal coil axis74. 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 member64can be can be made of plastic, impact-resistant plastic, metal, and composite materials. In an embodiment, the spring member64can 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 member64, 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 member64can be made of 200 Series or 300 Series stainless steel at spring temper per ASTM A313. In an embodiment, spring member64can 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 arm24A and second arm24B can each be generally flat members having generally parallel planar opposite sides. Arms24can define an imaginary plane66, as shown inFIG.9, and the imaginary plane66A of arm24A can be coplanar with the imaginary plane66B of arm24B. Pins30can each have an imaginary longitudinal pin axis67disposed centrally in relation to each pin, and imaginary longitudinal pin axis67A of pin30A on arm24A can be coaxial with longitudinal pin axis67B of pin30B on arm24B, as indicated inFIG.14.

Arms24can have various shapes and features beneficially adapted to the pivoting head22. Additionally, arms can be made of plastic, impact-resistant plastic, metal, and composite materials. In an embodiment, arms24can be comprised of metal. Arms24and 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 inFIGS.15-20, arms24can be sized and shaped appropriately to the size of the pivoting head22and handle12to which pivoting head22is attached. In example embodiments shown inFIGS.15and16, arm24can be considered in plan view having an arm length, Al, of from about 10 mm to about 25 mm, and can be about 17 mm. In an embodiment arm24can have an arm width, Aw, of from about 5 mm to about 20 mm, and can be about 10 mm. In the embodiments shown inFIGS.15and16, arm24can be a substantially uniform thickness plate having an arm thickness, At, of from about 0.5 mm to about 4 mm, and can be about 1 mm. In an embodiment, arm24can be substantially flat in side profile, as shown inFIGS.15A and15B. In an embodiment, arm24can have at least one bend as shown in side profile inFIGS.15B and15C. As shown, a pin30can be integral with arm24, or attached, such as by welding, to arm24such that a portion30C of pin30extends laterally to engage the bearing recess62of the pivoting head22. Pin30can be a circular cross section cylindrical shape having a length of from about 2 mm to about 15 mm and can be about 4 mm. Pin30can have a largest cross-sectional dimension, such as a diameter, of from about 0.6 mm to about 2.5 mm, and can be about 1.0 mm. Perimeter of holes in arm can be from about 5 mm to about 25 mm and can be about 10 mm. 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 65 N-cm2. In an embodiment, this minimum cross-sectional moment of inertia multiplied by the elastic modulus of the arm material can be about 400 N-cm2to about 20000 N-cm2.

As shown inFIGS.15and16, arm24can have portions at a proximal portion52defining an opening54. Openings can be used to engage and attach arms24to the main body16. For example, arm24shown inFIG.15corresponds to arm24shown inFIGS.10and11, in which opening54engages a protuberance56on main frame18of main body16.

FIGS.17-20show alternative embodiments of arms24. As shown inFIGS.17B and19B, arms24can have a variable thickness At, and can have a thicker portion generally central to arm24and thinner portions near the ends of arm24. Such a configuration can permit optimization of strength and weight of arms24.FIGS.18and20show alternative connection embodiments in which a hook member on the proximal portion52of arm24can engage a mating portion of main body16.

Pivoting head22can be rotated about first axis of rotation26by a biasing force applied to the pivoting head to rotate the pivoting head22about the first axis of rotation26to a second position such that second diverging surface50rests in contacting relationship with arm24. Upon removal of the biasing force, spring member64can act to rotate pivoting head back to the first position. In an embodiment, pivoting head22can be rotated about the first axis of rotation26, 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 rotation26of less than about 30 N-mm at an angle of rotation of about 50 degrees. In an embodiment, pivoting head22can be rotated about the first axis of rotation26, 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 rotation26of between about 2 N-mm and about 12 N-mm.

In an embodiment in which a fluid benefit delivery member76is coupled to the base member42of pivoting head22, the fluid benefit delivery member76being 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 rotation26. In an embodiment, the restorative, biasing torque about the first axis of rotation26can be about less than about 10 N-mm and can be about 6 N-mm with about 4.5 N-mm contributed by spring member64and about 1.5 N-mm contributed by the fluid benefit delivery member76. 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 member76or a heat delivery member96can 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 inFIG.21, spring member64can be a torsion spring and can include a first coil spring69A and a second coil spring69B coupled by a main bar portion70. A leg extension72can extend from each coil spring69a sufficient length to operatively engage arms24to provide the biasing force necessary to cause pivoting head22to be urged toward the first, rest, position. When the pivoting head is biased to rotate about the first axis of rotation26away from the first, rest, position, spring member64applies a resisting, restorative force to urge the pivoting head back to the first position. Coil springs69A and69B can each define a longitudinal coil axis74. Longitudinal coil axis74A of first coil spring68A can be coaxial with longitudinal coil axis74B of second coil axis68B. One or both of longitudinal axes74can be substantially parallel to and offset from the first axis of rotation26, which can be referred to as a pivot axis. Spring member64can be made of metal, including steel, and can be stainless steel having an engineering yield stress greater than about 600 MPa. In the illustrated embodiments, coil springs69are operatively disposed on each end of pivoting head22and a portion of the main bar portion70resides between the cover member40and base member42to 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 rotation26, the longitudinal coil axes74, and the main bar portion axis86. Specifically, as depicted inFIG.9, the first axis of rotation26can be parallel to and offset from both of the longitudinal coil axes74A,74B, and can, as well, be parallel to and offset from the main bar portion axis86. In an embodiment, the first axis of rotation26can be parallel to and offset from both of the longitudinal coil axes74A,74B a distance of from about 1 mm to about 5 mm. In an embodiment, the first axis of rotation26can be parallel to and offset from both of the longitudinal coil axes74A,74B a distance of about 2 mm.

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.

FIGS.22-24illustrate an embodiment of a base member42having at least one channel87disposed on a face thereof. In an embodiment, base member42includes a channel87for housing a portion of spring member64. The embodiment illustrated inFIGS.22-24includes a fluid benefit delivery member76, but with respect to the channel87the base member42need not be coupled to the fluid benefit delivery member76, but could, instead, house components related to a heating surface82, as described in more detail below. Base member42can be molded plastic, and channel87can be a molded channel. Likewise, fluid deliver member76can be molded flexible plastic and can be molded integrally with base member42. Channel87can have a size and shape conformed to receive the main bar portion70of spring member64, as shown inFIGS.21-24.FIG.22shows spring member64prior to being inserted into channel87;FIG.23shows spring member64placed into channel87with first and second coil springs68A and68B disposed at an exterior portion of base member42. As shown inFIG.18, cover member40, also made of molded plastic and made to have mating surfaces with base member42can be joined by translating onto and connecting to the base member in the direction indicated by arrows inFIG.24.

Once cover member40is in mating relationship with base member42, cover member and base member can be joined, such as by adhesive, press fit, or welding. In an embodiment, as shown inFIGS.25and26, staking pins89can be driven into openings90in a cold press fit as shown inFIGS.25and26to cause the base member42and cover member40to remain in operatively stable mating relationship. In an embodiment that includes a fluid delivery member for a fluid skin benefit, once the base member42and cover member40are securely mated, a compartment84is defined between the parts, which compartment84has a volume into which fluid can flow from the handle12and from which fluid can flow to openings90on the skin interfacing face80of pivoting head22.

Fluid containment in compartment84can be achieved by a sealing relationship between cover member40and base member42.FIG.27Ashows the mating surface of a cover member40andFIG.27Bshows the first mating surface88of a base member42. In the embodiment shown inFIGS.27A-B, sealing can be achieved by the first mating face88of cover member40that, when operatively connected to base member42can mate in a juxtaposed, contacting relationship with a second mating face90of base member42. A gasket member92can extend outwardly from first mating face88and can sealingly fit in a corresponding gasket groove94on base member42.

An embodiment of a pivoting head22can be assembled onto handle12in a manner illustrated inFIGS.28-33. As shown inFIG.28, pins30of arms24can be inserted into bearing recess62of cover member40by translating in the direction of the arrow ofFIG.28, which direction aligns with the longitudinal pin axis67(as shown inFIG.14) and first axis of rotation26. As shown inFIG.28, spring member64is disposed in operative relationship between cover member40and base member42. Once pin30is inserted into bearing recess62, as shown inFIG.29, pin30and arm24can freely rotate in bearing recess62. Arms24can be held in place in any suitable manner while they are slid in the direction of the arrows inFIG.30, which shows before (A) and after (B) depictions of the arm securement in slots103of main body16. Once in place, as shown inFIG.31, openings54of arms24can be exposed through a corresponding access opening106in main body16. As shown inFIG.32, one or more extensions107on or in slot103can provide for an interference fit to hold arms in place for the next step.

Referring now toFIG.33, there is shown certain handle12elements being assembled to secure pivoting head22to handle12. An embodiment of main frame18is shown translating in the direction of the arrows inFIG.33from a first position (A) to join secondary frame20(B). Main frame18can be joined to secondary frame20by adhesive applied at adhesive grooves120on secondary frame20which can mate with corresponding adhesive bosses on main frame18. Main frame18can be disposed on a portion of secondary frame20in a mating relationship such that protuberances56are inserted through access openings106of main body16and openings54of arms24. Protuberances56can provide positive metal-to-metal coupling of arms24to handle12. In an embodiment adhesive can be applied at the connection of protuberances56and openings54to provide for additional securement of arms (and, therefore, pivoting head12) to main frame18(and, therefore, handle12).

Referring now toFIGS.34-36, an embodiment of a pivoting head having a heat delivery member96for delivering heat as a skin benefit is described. Pivoting head22for delivering heat can have components common to those described above for delivering fluid, such as one or more arms24, one or more spring members64, a cover member40and a base member42, and these common components can be configured as described above, or in a similar manner However, the pivoting head22for delivering a heat benefit can also have a heat delivery member96comprised of heat delivery components, including a flexible conductive strip98for conducting electricity from a first proximal portion98A operatively attached in handle12to a second distal portion98B operatively disposed in pivoting head22and delivering heat to the skin at a heating surface82.

FIG.35shows an embodiment of a pivoting head22for a razor delivering a heat skin benefit. The pivoting head can include a cover member40connected to a base member42and a spring member64partially disposed between the cover member40and the base member42. The pivoting head22shown inFIG.35can include components shown in the assembly view ofFIG.36. As shown inFIG.36, in an embodiment spring member64as described above can be disposed between the cover member40and the base member42, substantially as described above. Other components can be disposed on the outside of cover member40and can be attached in a layered relationship having sizes that correspond to the narrow lower face of the cover member40.

As shown inFIG.36, the heat delivery member96may include a face plate102for delivering heat to or proximal to the skin's surface during a shaving stroke for an improved shaving experience. In certain embodiments, the face plate102may have an outer skin contacting heating surface82comprising a relatively hard coating (that is harder than the material of the face plate102), such as titanium nitride to improve durability and scratch resistance of the face plate102. Similarly, if the face plate102is manufactured from aluminum, the face plate102may 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 surface82of the face plate102. The heat delivery element96may be in electrical communication with a portion of the handle12. As will be described in greater detail below, the heat delivery element16may be mounted to the pivoting head22and in communication with the power source (not shown).

Continuing to refer toFIG.36, one possible embodiment of the heat delivery element96is shown that may be incorporated into the shaving razor10ofFIG.4. The face plate102may be as thin as possible, but stable mechanically. For example, the face plate102may have a wall thickness of about 100 micrometers to about 200 micrometers. The face plate102may comprise a material having a thermal conductivity of about 10 to 30 W/mK, such as steel. The face plate102can be manufactured from a thin piece of steel that results in the face plate102having a low thermal conductivity thus helping minimize heat loss through a perimeter wall110and maximizes heat flow towards the skin interfacing surface80. Although a thinner piece of steel is preferred for the above reasons, the face plate102may be constructed from a thicker piece of aluminum having a thermal conductivity ranging from about 160 to 200 W/mK. The heat delivery element96may include a heater (not shown), e.g., a resistive heat element portion of flexible conductive strip98, that is in electrical contact with a micro-controller and a power source (not shown), e.g. a rechargeable battery, positioned within the handle12.

The heat delivery member96may include the face plate102, the flexible conductive strip98heater, a heat dispersion layer100, a compressible thermal insulation layer99, and a portion of cover member40. The face plate102may have a recessed inner surface122opposite the skin application surface82configured to receive the heater98, the heat dispersion layer100and the compressible thermal insulation layer99. The perimeter wall110may define the inner surface122. The perimeter wall110may have one or more tabs108extending from the perimeter wall110, transverse to and away from the inner surface122. For example,FIG.36illustrates four extending from the perimeter wall110.

The heat dispersion layer100may be positioned on and in direct contact with the inner surface122of the face plate102. The heat dispersion layer100may have a lower surface124directly contacting the inner surface122of the face plate102and an upper surface126(opposite lower surface37) directly contacting the heater98. The heat dispersion layer100can be defined as a layer of material having a high thermal conductivity and can be compressible. For example, the heat dispersion layer100may comprise graphite foil. Potential advantages of the heat dispersion layer100include improving lateral heat flow (spreading the heat delivery from the heater98across the inner surface122of the face plate102, which is transferred to the skin application surface82) resulting in more even heat distribution and minimization of hot and cold spots. The heat dispersion layer100may have an anisotropic coefficient of thermal conductivity in the plane parallel to the face plate102of about 200 to about 1700 W/mK (preferably 400 to 700 W/mK) and vertical to the face plate102of 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 layer100allows the heat dispersion layer100adapt to non-uniform surfaces of the inner surface122of the face plate102and non-uniform surfaces of the heater98, thus providing better contact and heat transfer. The compressibility of the heat dispersion layer100also minimizes stray particulates from pushing into the heater98(because the heat dispersion layer100may be softer than the heater), thus preventing damage to the heater98. In certain embodiments, the heat dispersion layer100may comprise a graphite foil that is compressed by about 20% to about 50% of its original thickness. For example, the heat dispersion layer100may have a compressed thickness of about 50 micrometers to about 300 micrometers more preferably 80 to 200 micrometers.

The heater98may be positioned between two compressible layers. For example, the heater98may be positioned between the heat dispersion layer100and the compressible thermal insulation layer99. The two compressible layers may facilitate clamping the heater98in place without damaging the heater98, thus improving securement and assembly of the heat delivery element96. The compressible thermal insulation layer99may help direct the heat flow toward the face plate102and away from the cover member40. Accordingly, less heat is wasted, and more heat may be able to reach the skin during shaving. The compressible thermal insulation layer99may 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 layer38may comprise an open cell or closed cellular compressible foam. The compressible thermal insulation layer99may be compressed 20-50% from its original thickness. For example, the compressible thermal insulation layer99may have a compressed thickness of about 400 μm to about 800 μm.

The cover member40may be mounted on top of the compressible thermal insulation layer99and secured to the face plate102. Accordingly, the heater98, the heat dispersion layer100and the compressible thermal insulation layer99may be pressed together between the face plate102and the cover member40and assembled as described more fully below. The heat dispersion layer100, the heater98, and the compressible thermal insulation layer99may fit snugly within the perimeter wall110. 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 element96. 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 layer99may fit snugly within the perimeter wall110.

Thus, in an embodiment, the first layer in contacting relationship with cover member40can be a compressible thermal insulation layer99such as a foam member. A portion of the heater in the form of a flexible conductive strip98can be sandwiched between a foam thermal insulation layer99and a graphite foil strip heat dispersion layer100. The layers of foam thermal insulation layer99, flexible conductive strip98and graphite foil strip can be connected in layered, contacting relationship to the narrow lower face of the cover member40by a faceplate102. Faceplate102can have a smooth outer surface that corresponds to heating surface82, and tabs108that can be used to connect the heat delivery components to the pivoting head22.

Assembling a pivoting head for delivering a heat skin benefit can be described with reference toFIGS.37-49. Referring to the assembly view ofFIG.37, a graphite foil strip heat dispersion layer100can be placed onto a trough104of faceplate102, such as onto the recessed inner surface122of faceplate102. In a next step, as shown in the assembly view ofFIG.38, distal portion98B of flexible conductive strip98can be shaped and fit into the trough104of faceplate102. Next, as shown in the assembly view ofFIG.39, a compressible thermal insulation layer99member can be placed into trough104of faceplate102. As with the other members placed in trough104, foam thermal insulation layer99can be sized and shaped accordingly to fit in trough104. Next, as shown inFIG.40, cover member40can be placed on top of the other layered components in and faceplate102.

Once cover member40is placed on top of the layered members in an on trough104, faceplate102can be secured to the cover member40via tabs108as shown in the assembly view ofFIG.41A-D. As shown, one or more tabs108, including a pair of tabs labeled1and2inFIG.41A and3and4inFIG.41B, can be folded into receiving openings111on cover member40, as shown in the cross-sectional perspective assembly view ofFIG.41C and41D. As described with respect toFIG.42, spring member64as described above, can be placed in cover member40and seated in corresponding form-fitting recesses, including a channel87, of cover member40. Finally, base member42can be connected to cover member in a sequence described with respect to the assembly view ofFIG.43A-F. As shown inFIG.43A-C, one or more first latching members112on base member42can be placed into and hooked into one or more first latch receiving portions114of cover member40, and, as shown inFIG.43C-F, base member42can be rotated and pressed onto cover member40such that one or more second latching members116can be snapped into cooperating second latch receiving portions118.

Once base member40is securely snapped into place on cover member42, the illustrated embodiment of pivoting head22is ready to be coupled to handle12. As shown inFIGS.44and45arms24can be inserted in the direction of the arrows into the bearing recess62of cover member40by sliding pins30into the bearing recesses62, as described above. As shown inFIG.46, arms24can then be inserted in the direction of arrows into slots103of main body16. As shown in the cut away perspective view ofFIG.47, a slot103is shown having disposed therein the proximal portion of arm24as well as a leg extension72of spring member64. Once arms24are in place into slots103and in place as shown inFIG.48, portions of main body16can be cold stamped in the direction of the arrows to secure arms24to main body16of handle12. As shown in the partial cut away perspective view ofFIG.49, portions of the main body16corresponding to openings54of arms24can be permanently plastically deformed by pressing into the openings54. This operation, known as cold stamping or cold staking, permits secure coupling of arms24, and therefore, pivoting head22, to main body16(and, therefore, handle12).

As disclosed above, pivoting head22can be pivoted about a pivot axis, i.e., axis of rotation26under the biasing force of a spring member64. However, other pivot mechanisms can be employed for both the first axis of rotation26and secondary axis of rotation27. In general, pivoting head22can be in pivotal relation to the handle12via, 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 handle12via 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 rotation26allow 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 rotation26may be measured by deflecting the pivot25degrees about the first axis of rotation26and measuring the required torque about this first axis of rotation26to 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 rotation26can 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 rotation27(shown inFIGS.1and4) allow rotational motions ranging from −12.5 degrees to +12.5 degrees. A rotational stiffness for a pivot mechanism about secondary axis of rotation may be measured by deflecting the pivot −5 degrees and +5 degrees about secondary axis of rotation27and 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 10 degrees difference in angular motion. The rotational stiffness associated with pivot mechanisms about secondary axis of rotation27generally range from about 0.8 to about 2.5 N-mm per degree of rotation.

As disclosed above, components of the pivoting head22and the pivoting mechanism that enable rotation about first axis of rotation26for the embodiments were shown in detail. The handle12was connected to the pivoting head22by a pair of arms24, a spring member26, and a benefit pivot delivery connection. In the embodiments disclosed above, the spring member can be comprised of a metal. But the spring member64can also be comprised of a stress-relaxation resistant material such as a metal, polyetheretherketone, or silicone rubber, all of which can prevent the razor10or razor handle12from taking a “set,” or permanently deforming at deflected angle when the razor10or razor handle12is stored improperly due to the stress relaxation of the components that connect the pivoting head22to 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 handle12to the pivoting head22to deliver a skin benefit through the cartridge15to the skin interfacing face80. As discussed below, a fluid benefit delivery member76and a heat delivery member96can be configured so as to facilitate proper pivoting of the pivoting head about first axis of rotation26and secondary axis of rotation27.

Referring toFIG.50, a razor10is shown in which the flexible conductive strip98of heat delivery member96bridges a gap between the handle12and the pivoting head onto which is attached a blade cartridge15. As shown inFIG.50, and in more detail inFIG.51, the flexible conductive strip98is longer than the distance to be traversed between the handle12and the pivoting head22, resulting in a loop150of the flexible conductive strip98. This loop150, which can be generally U-shaped or S-shaped, can minimize the effect of the flexible conductive strip98on the biasing torque force required to pivot the pivoting head22about the first axis of rotation26. In general, this loop150of the benefit delivery member contributes to a ratio of biasing torque provided by the sum of the benefit member and the spring member64, and the biasing torque provided by the spring member alone, which torque ration is discussed in more detail below.

In like manner, as depicted inFIG.52, a fluid delivery benefit member, such as a flexible plastic tube, can also have a loop150portion such that excess length of the flexible tube allows for minimizing the effect of the fluid benefit delivery member76on the biasing torque force required to pivot the pivoting head22about the first axis of rotation26. In an embodiment, the installed length of fluid benefit delivery member76, as shown inFIG.53can be from 1 mm to 3 mm less than the free length of the fluid benefit delivery member76. This forced compression contributes to the loop150portion and has been found to aid in further minimizing the effect of the fluid benefit delivery member76on the biasing torque force required to pivot the pivoting head22about the first axis of rotation26.

Additional features found to further minimizing the effect of the fluid benefit delivery member76on the biasing torque force required to pivot the pivoting head22about the first axis of rotation26can be understood with reference toFIGS.53-61. InFIG.53, a portion of handle12at the location where fluid delivery member exits the handle12and begins to traverse the distance to the pivoting head, a fillet radius of curvature152of from between about 1 mm and about 5 mm 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 head22during use.

In a similar manner, as shown inFIG.54, at a portion of handle12at the location where fluid delivery member exits the handle12and begins to traverse the distance to the pivoting head, a chamfer154is provided, as shown. The chamfer can have a chamfer angle of about 5 degrees to about 30 degrees at the proximal end of the handle, and can have a chamfer length of about 3 mm to about 15 mm. Like the radius of curvature152, the chamfer154is 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 head22during use.

The dimensions of a chamfer can be defined as shown in the view ofFIG.54A-C. In view200, a block201is shown with an edge205to be chamfered and a front face206. In view210, block201is shown after edge205has been chamfered creating chamfer202. In view220, chamfer202is shown having a chamfer length204and a chamfer angle203. 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 5 degrees and 30 degrees and chamfer length from 3 mm to 15 mm.

Further, an additional feature found to minimize the effect of the fluid benefit delivery member76on the biasing torque force required to pivot the pivoting head22about the first axis of rotation26can be understood fromFIG.55as a slot156on the handle12at the location of the exit of the fluid benefit delivery member76. In an embodiment, the slot can have a width measured generally parallel to the axis of rotation26of about 3 mm to about 10 mm, and a length measured perpendicular to the width of from about 2 mm to about 15 mm.

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 inFIGS.56-60. For example, as depicted inFIG.56, fluid benefit delivery member76, which can be a flexible molded plastic tube, can be configured such that a distal portion160has a thinner wall diameter than a proximal portion162. As shown inFIG.56, the proximal portion162which can be connected in fluid communication with other components in the handle12(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 portion160which connects to the cover member42of 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 head22about the first axis of rotation26.

InFIG.57, an alternative embodiment of fluid benefit delivery member76is shown in which the tube wall of the fluid benefit delivery member76is 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 member42provide for greater flexibility and less effect on the biasing torque force required to pivot the pivoting head22about the first axis of rotation26.

Alternative embodiments of fluid benefit delivery member76utilizing coil springs to reinforce strength and provide for flexibility are depicted inFIGS.58-60. As depicted inFIG.58, a coil spring164, which can be made of plastic or metal, can configured about the outside of fluid benefit delivery member76. As depicted in the cross-sectional view ofFIG.59, a coil spring164, which can be made of plastic or metal, can configured about the inside of fluid benefit delivery member76. As depicted inFIG.60, a coil spring164, which can be made of plastic or metal, can configured to be molded into the walls of fluid benefit delivery member76.

FIG.61depicts one embodiment of a feature to join fluid deliver member76to the base member42. As shown, a ball and socket joint component166can be present on the base member42. 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 component166.

The joining of the fluid benefit delivery member76to the pivoting head22can be a two-component embodiment, as shown inFIG.62. In a two-component embodiment, the fluid benefit delivery member76can be molded with an integral pivoting head connection member170that can attach to the mating portion of the pivoting head22in any suitable manner, such as snap fit, friction fit, adhesive joining, or the like. In this embodiment, a spring member64(not shown) can be added externally to the pivoting head22to provide for a biasing force on pivoting head.

In an embodiment, the fluid benefit delivery member76and the base member42of the pivoting head22can be overmolded in a two-shot injection mold to form a three-component assembly that can form pivoting head22. In this manner the base member can be a relatively hard material and the fluid benefit delivery member76can be a relatively soft material. A portion of the polymer injection molded for the fluid delivery member forms the gasket member92of the base member42, as described above. Referring toFIG.63, the base member42and fluid benefit delivery member76are shown as they would appear if they were injection molded separately. However, in an embodiment, the fluid benefit delivery member76and the base member42can be overmolded in a two-shot injection mold process to manufacture an integral member as shown inFIG.64, in which the material of the fluid benefit delivery member76extends through base member42and is exposed at the first mating surface88as gasket member92.FIG.65shows another perspective view of the first mating surface88of the cover member42having exposed and extended therefrom a gasket member92which is integral with fluid benefit delivery member76. A two-shot injection molding of the fluid delivery member with the base member42as described is believed to increase the structural integrity of the fluid benefit delivery member76/base member42unit by increasing the force required to remove the base member42from the fluid benefit delivery member76. As described above, the base member can be joined to the third component, i.e., the cover member40, such that their respective first and second mating faces88,90are joined, and gasket member92lodges in and forms a gasket in gasket groove94of cover member40.

In an embodiment, the fluid flow path of the pivoting head22can be configured to provide for relatively unobstructed, smooth, continuous fluid flow from the fluid benefit delivery member76to openings78in face80of pivoting head22, which can be a skin interfacing face. As shown inFIGS.66A and66B, which depict partial cross-sectional views of a pivoting head22having joined thereto a fluid benefit delivery member76that enters at a location having an area approximating the cross-sectional area of the fluid benefit delivery member76tube, a flow distributor171which 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 member76. By beginning fluid deflection and distribution almost immediately upon entry to the compartment84, it has been unexpectedly found that fluid flow is enhanced, and blockage or clogging of openings, including openings78, is minimized or eliminated. In an embodiment the fluid flow distributor171is located about 0.5 mm to about 2 mm from a junction of the connection of the fluid benefit delivery member76to the pivoting head22. In an embodiment, the fluid reservoir in the pivoting head22can have a small cross section closer to the connection of the fluid benefit delivery member76to the pivoting head22.

In general, the internal fluid conduit associated with fluid benefit delivery member76can 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 member76can 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 member76.

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 strip98of heat delivery member96and fluid benefit delivery member76, can be comprised of materials that stress relax, it can be advantageous if the rotational stiffness of the pivoting head22is greater than twice, or more preferably greater than5times, the rotational stiffness of the pivoting head22with the benefit delivery member removed. The rotational stiffness of the pivoting head22without 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 head22and the handle12. 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 head22. This latter configuration greatly reduces the probability and conditions under which the razor10or razor handle12can 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 rotation26, for example) of the pivot mechanism and torques versus angles of rotation between sections are measured. Referring toFIG.67, in general, the pivot mechanism400can be understood to rotate a first section401of the test component located on one side of the pivot mechanism relative to a second section402of 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.

InFIGS.68and69, 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 line407for measurements408of torque versus rotation angle over the middle 50%404of the full range405of angular motion of the pivot mechanism400unless 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 section401, which can rotate, and the second section402, which is held fixed, constant.

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 inFIG.70, the instant center of rotation C of a pivot mechanism undergoing a planar rotation can be determined by tracing the path, PATH1and PATH2, of two points, P1, and P2, on the rotating first section401. As an illustration,FIG.7shows Section401at3positions401a,401b,and401c,and it calculates the instant center of rotation C at position401b.At this angle of rotation, two lines, T1and T2, can be drawn tangent to PATH1and PATH2respectively. Two additional lines, R1and R2, can be drawn perpendicular to T1and T2respectively. The instant center can be located at the intersection of R1and 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 0.25 mm2.

Step 2: Clamp the test component in appropriate test fixture with torque sensor centered on axis of rotation

As shown inFIG.71, an appropriate test measurement system420can 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 base421, tester torque cell422, and torque tester rotational member423. Instron's MT1 MicroTorsion tester has a full-scale torque cell of 225 N-mm, with a torque accuracy of +1-0.5%, a torque repeatability of +1-0.5%, and an angle resolution of 0.003 degrees. The tester base421is fixed and attached to a torque cell422while the tester rotational member423rotates about an axis of rotation, TT. The fixed second section402is fastened to the torque cell side422of the tester using a first clamping mechanism424. The rotating first section401is fastened to the tester rotational member423using a second clamping mechanism425. 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 section401of 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 (424and425) 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.

Step4. 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:

a. a main body;

b. a first substantially flat metal arm having a first proximal portion and a first distal end, the first proximal portion being rigidly coupled to the main body at a first location;

c. a second arm having a second proximal portion and a second distal end, the second proximal portion being rigidly coupled to the main body at a second location; and

d. the first and second distal ends being in spaced relationship and having pivotally coupled therebetween a pivoting head.

B. The handle of paragraph A, wherein the handle weighs between 60 grams and 100 grams.

C. The handle of paragraph A or B, wherein the first distal end and second distal end each comprise a pin member welded thereto.

D. The handle of any of paragraphs A-C, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin member and the second pin member reside in a coaxial relationship.
E. The handle of any of paragraphs A-D, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin operatively engages a first receiving opening in the pivoting head and the second pin operatively engages a second receiving opening in the pivoting head.
F. The handle of any of paragraphs A-E, wherein the first and second arms are each rigidly coupled to the main body by a securement selected from the group consisting of welding, staking, cold heading, adhesive bonding, snap-fit, and frictional engagement.
G. The handle of any of paragraphs A-F, wherein the first and second arms each comprise metal plates, each metal plate defining a plate plane, and wherein the first arm plate plane is generally co-planar with the second arm plate plane.
H. The handle of any of paragraphs A-G, wherein the main body comprises a material selected from the group consisting of metal, cast metal, plastic, impact-resistant plastic, and composite.
I. A handle, the handle comprising:

a. a main body;

b. a first metal arm having a first proximal portion and a first distal end, the first proximal portion being slidably interlocked at a first location of the main body;

c. a second metal arm having a second proximal and a second distal end, the second proximal portion being slidably interlocked at a second location of the main; and

d. the first and second distal ends being in opposed relationship and having pivotally coupled therebetween a pivoting head, the pivoting head having a trapezoidal prism-like shape.

J. The handle of paragraph I, wherein the handle weighs between 60 grams and 100 grams.

K. The handle of paragraph I or J, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin member and the second pin member reside in a coaxial relationship.
L. The handle of any of paragraphs I-K, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin operatively engages a first receiving opening in the pivoting head and the second pin operatively engages a second receiving opening in the pivoting head.
M. The handle of any of paragraphs I-L, wherein the first and second arms each comprise metal plates, each metal plate defining a plate plane, and wherein the first arm plate plane is generally co-planar with the second arm plate plane.
N. The handle of any of paragraphs I-M, wherein the main body comprises a material selected from the group consisting of metal, cast metal, plastic, impact-resistant plastic, and composite.
O. The handle of any of paragraphs I-N, wherein the main body comprises zinc.
P. A handle, the handle comprising:

a. a main body;

b. a first discrete metal arm having a first proximal portion and a first distal end, the first proximal portion being rigidly coupled to the main body at a first protuberance on the main frame;

c. a second discrete metal arm having a second proximal and a second distal end, the second proximal portion being rigidly coupled to the main body at a second protuberance on the main frame; and

d. the first and second distal ends being in opposed relationship and having pivotally coupled therebetween a pivoting head, the pivoting head having a trapezoidal prism-like shape.

Q. The handle of paragraph P, wherein the handle weighs between 60 grams and 100 grams.

R. The handle of paragraph P or Q, wherein the first distal end and second distal end each comprise a pin member welded thereto.

S. The handle of any of paragraphs P-R, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin member and the second pin member reside in a coaxial relationship.
T. The handle of any of paragraphs P-S, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin operatively engages a first receiving opening in the pivoting head and the second pin operatively engages a second receiving opening in the pivoting head.
U. The handle of any of paragraphs P-T, wherein the first and second arms are each rigidly coupled to the main frame by a securement selected from the group consisting of welding, staking, cold heading, adhesive bonding, snap-fit, and frictional engagement.
V. The handle of any of paragraphs P-U, wherein the first and second arms each comprise metal plates, each metal plate defining a plate plane, and wherein the first arm plate plane is generally co-planar with the second arm plate plane.
W. The handle of any of paragraphs P-V, wherein the main frame comprises a material selected from the group consisting of metal, cast metal, plastic, impact-resistant plastic, and composite.
X. The handle of any of paragraphs P-W, wherein the main frame comprises zinc.
Y. A handle, the handle comprising:

a. a main body weighing greater than about 60 grams;

b. a first arm having a first proximal portion and a first distal end, the first proximal portion being rigidly coupled to the main body at a first location;

c. a second arm having a second proximal portion and a second distal end, the second proximal portion being rigidly coupled to the main body at a second location; and

d. the first and second distal ends being in spaced relationship and having pivotally coupled therebetween a pivoting head.

Z. The handle of paragraph Y, wherein the first and second arms comprise metal and the handle weighs between 60 grams and 100 grams.

AA. The handle of paragraph Y or Z, wherein the first distal end and second distal end each comprise a pin member welded thereto.

BB. The handle of any of paragraphs Y-AA, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin member and the second pin member reside in a coaxial relationship.
CC. The handle of any of paragraphs Y-BB, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin operatively engages a first receiving opening in the pivoting head and the second pin operatively engages a second receiving opening in the pivoting head.
DD. The handle of any of paragraphs Y-CC, wherein the first and second arms each comprise a material selected from the group consisting of metal, plastic, and composite.
EE. The handle of any of paragraphs Y-DD, wherein the first and second arms are each rigidly coupled to the main body by a securement selected from the group consisting of welding, staking, cold heading, adhesive bonding, and frictional engagement.
PP. The handle of any of paragraphs Y-EE, wherein the first and second arms each comprise metal plates, each metal plate defining a plate plane, and wherein the first arm plate plane is generally co-planar with the second arm plate plane.
GG. The handle of any of paragraphs Y-FF, wherein the main body comprises a material selected from the group consisting of metal, cast metal, plastic, impact-resistant plastic, and composite.
HH. A handle, the handle comprising:

a. a main body;

b. a first arm having a first proximal portion and a first distal end, the first proximal portion being slidably interlocked at a first location of the main body;

c. a second arm having a second proximal and a second distal end, the second proximal portion being slidably interlocked at a second location of the main; and

d. the first and second distal ends being in spaced relationship and having pivotally coupled therebetween a pivoting head,.

II. The handle of paragraph HH, wherein the first and second arms comprise metal and the handle weighs between 60 grams and 100 grams.

JJ. The handle of paragraph HH or II, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin member and the second pin member reside in a coaxial relationship.
KK. The handle of any of paragraphs HH-JJ, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin operatively engages a first receiving opening in the pivoting head and the second pin operatively engages a second receiving opening in the pivoting head.
LL. The handle of any of paragraphs HH-KK, wherein the first and second arms each comprise a material selected from the group consisting of metal, plastic, and composite.
MM. The handle of any of paragraphs HH-LL, wherein the first and second arms each comprise metal plates, each metal plate defining a plate plane, and wherein the first arm plate plane is generally co-planar with the second arm plate plane.
NN. The handle of any of paragraphs HH-MM, wherein the main body comprises a material selected from the group consisting of metal, cast metal, plastic, impact-resistant plastic, and composite.
OO. The handle of any of paragraphs HH-NN, wherein the main body comprise zinc.
PP. A handle, the handle comprising:

a. a main body weighing greater than about 60 grams;

b. a first arm having a first proximal portion and a first distal end, the first proximal portion being rigidly coupled to the main body at a first protuberance on the main frame;

c. a second arm having a second proximal and a second distal end, the second proximal portion being rigidly coupled to the main body at a second protuberance on the main frame; and

d. the first and second distal ends being in spaced relationship and having pivotally coupled therebetween a pivoting head.

QQ. The handle of paragraph PP, wherein the first and second arms comprise metal and the handle weighs between 60 grams and 100 grams.

RR. The handle of paragraph PP or QQ, wherein the first distal end and second distal end each comprise a pin member welded thereto.

SS. The handle of any of paragraphs PP-RR, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin member and the second pin member reside in a coaxial relationship.
TT. The handle of any of paragraphs PP-RR, wherein the first arm comprises a first cylindrical pin member welded at the first distal end and the second arm comprises a second cylindrical pin member welded to the second distal end, and wherein the first pin operatively engages a first receiving opening in the pivoting head and the second pin operatively engages a second receiving opening in the pivoting head.
UU. The handle of any of paragraphs PP-TT, wherein the first and second arms each comprise a material selected from the group consisting of metal, plastic, and composite.
VV. The handle of any of paragraphs PP-UU, wherein the first and second arms are each rigidly coupled to the main frame by a securement selected from the group consisting of welding, staking, cold heading, adhesive bonding, snap-fit, and frictional engagement.
WW. The handle of any of paragraphs PP-VV, wherein the first and second arms each comprise metal plates, each metal plate defining a plate plane, and wherein the first arm plate plane is generally co-planar with the second arm plate plane.

XX. The handle of any of paragraphs PP-WW, wherein the main frame comprises a material selected from the group consisting of metal, cast metal, plastic, impact-resistant plastic, and composite.

YY. The handle of any of paragraphs PP-XX, wherein the main frame comprises zinc.