HANDLE FOR DOORS OR WINDOWS

Technical field

This invention relates to a handle for doors or windows.

More specifically, the handle according to the invention may be applied on doors or windows made from profiles made of metal, PVC or the like, wood- PVC or the like.

Background art

There are two types of "standard" handles currently available on the market: the lever operated cremone handle and the so-called "martellina" handle, which are associated with a wing of the movable sash of the door or window.

The cremone handle comprises a handle or grip, a body handle (prismatic in shape) for containing a kinematic unit designed for converting the rotational movement of the grip (control) into a translational movement for a connecting element protruding from the body handle on the side opposite the one engaged by the grip (usually one or a pair of fins).

The connecting element, with the handle assembled on the sash, couples with a system for transmitting the movement (usually rods housed in suitable channels of the sash and striker for coupling with the protruding element) to drive the opening and closing of the movable sash of the door or window by movement of pins or bosses relative to contact elements positioned on a fixed frame of the door or window.

It should be noted that the kinematic unit housed in the prismatic body comprises a gear wheel connected to the central shaft of the grip. The gear wheel is meshed on one or more racks equipped with one or more corresponding transversal fins, which connect inside with the above- mentioned rods.

The gear wheel for moving the fins rotates about an axis of rotation coinciding with the axis of rotation of the grip.

Cremone type handles are known from patent documents EP446.566, EP1.387.030 EP1.593.799, all in the name of the same Applicant.

The "martellina" handle model is used as an alternative to the cremone handle, especially where there are particular decorative or dimensional requirements (for example, change in colour of accessories, reduced dimensions on doors or windows).

The "martellina" handle, unlike the cremone handle, has a separate structure between the control grip and the kinematic unit designed to convert the rotational movement of the grip (control) into a translational movement: this solution is used to be able to change, in a fast and economic manner, merely the grip according to the chromatic - decorative requirements of the room in which the door or window is installed. Prior art solutions of "martellina" handle are shown in patent documents EP1.748.127 and WO 2008/081236 in the name of the same Applicant.

In this solution, in practice, the kinematic unit (usually called the operating device) can be housed inside the tubular chambers of the profile forming the movable sash of the door or window, whilst only the grip is applied to the outside of the wing of the profile.

It should be noted that the grip of the "martellina" handle has a reduced handle body and a protruding connecting element (usually a shaft with a square cross-section) coaxial to the axis of rotation of the handle to which the kinematic unit is mechanically coupled.

The square shaft couples in a seat made on a toothed rotor housed inside a box-shaped body forming the frame of the device. It should be noted that the rotor and the square shaft are coupled in a zone inside the tubular section of the profile of the sash, that is, these elements are located at a different height (beneath the channel for housing the operating rods of the sash).

The rotor is meshed at least with one rack (if it is a one-way translational movement), positioned coplanar with the channel, and at the ends of which there are pins for connection with the operating rods.

Some prior art solutions of the kinematic unit or devices are illustrated in patent documents DE4409419, DE4409420, EP1.619.326, EP1.621.707 again in the name of the same Applicant.

Now, these two handle models each have merits and defects of a technical - structural type and in terms of decorative appearance.

The cremone handle has an external kinematic unit which makes it possible to reduce to a minimum the machining inside the profile, it does not affect the tubularity of the profile and it allows a substantially direct connection between connecting element and operating rods with extremely reduced dimensions.

However, the cremone handle has large external dimensions and needs extensive machining on the wing of the profile. Moreover, the cremone handle is unlikely to be chosen if the environment in which it is mounted can or must provide for more or less frequent changing of accessories due to requirements of a chromatic nature.

The "martellina" handle has a lower cost relative to the cremone handle and a minimum external space: this makes the "martellina" handle a optimum choice for frequent changes of a chromatic type. In addition, the assembly of the "martellina" handle requires few machining operations on the outer wing of the profile of the sash.

On the other hand, the "martellina" handle is subject to the presence of the kinematic unit inside the tubular chamber which creates a large internal space and requires invasive and complex machining in the tubular chamber to compensate for the presence of the kinematic unit inside the sash.

In addition, there is also the high cost of the internal kinematic unit which consists of a large number of components.

Disclosure of the invention

The aim of this invention is to provide a handle for doors or windows which overcomes the above-mentioned drawbacks of the prior art. More specifically, the aim of this invention is to provide a handle for doors or windows which can combine minimal machining necessary for assembly on the sash with extremely reduced housing dimensions both for the grip and for the kinematic movement components.

A further aim of this invention is to provide a handle for doors and windows which is technically reliable and precise, compact in terms of its functional components and, at the same time, with a high level decorative appearance.

These aims are fully achieved by the handle for doors and windows according to the invention as characterised in the appended claims.

More specifically, the handle for doors or windows, which have a movable sash, comprises a grip having a gripping portion and a base portion or neck facing, in use, a part of the outer profile or wing of the movable sash. The grip can rotate about a first axis.

The handle also comprises a shaft protruding from the grip and passing, in use, through the outer wing of the movable sash to be coupled (again, in use) to a kinematic unit located close to a longitudinal channel inside the profile of the sash in which at least one control rod slides, connected to the kinematic unit designed to convert the rotational movement of the grip into a translational movement of the rod, in both directions.

According to the invention, the handle has the kinematic unit comprising a pair of gear wheels, placed side by side and having a seat positioned, in use, coaxial with each other and engaged simultaneously by the shaft.

Also according to the invention, the handle comprises at least one rack having two separate meshing tracks placed side by side and engaged by a corresponding gear wheel.

Again according to the invention, the rack is formed on a rod-shaped body positioned, in use, parallel to a free upper surface of the channel and provided with means for coupling with the at least one control rod.

Preferably, the pair of gear wheels has, in use, the corresponding toothed profile offset relative to each other by an angle so as to determine a diversified and continuous coupling on the corresponding tracks for meshing the rack during the rotation applied by the shaft.

Thanks to this structure, the kinematic unit has a double width pinion which uses twice the teeth distributed along the relative axis of rotation and with a substantially continuous spacing of the teeth of the two wheels (instead of about the axis) to allow a continuity of meshing on the rack.

Preferably, the pair of meshing tracks have a different distribution of the respective teeth along the rod-shaped body and correlated with the offset angle of the corresponding toothed profile of the gear wheel.

In other words, the two tracks formed on the rod-shaped body have their corresponding ends offset, under equal conditions of total extension, as a function of the offset angle of the gear wheels.

In effect, a first translated limit position of the rod-shaped body corresponds with the meshing of a single tooth of one of the gear wheels in the end seat of the corresponding track, and a second translated limit position (opposite the previous one) of the rod-shaped body corresponds with the meshing of a single end tooth of the other of the gear wheels in the seat of the corresponding track.

In short, the double gear wheel allows a regular and continuous translation of the rod-shaped body without sudden jolting of the latter which, in effect, would transform into discontinuous movements of the grip.

This is possible due to the fact that the pair of gear wheels alongside each other provides the characteristics of a gear wheel (or pinion) with a greater number of teeth and with a smaller spacing, that is, with a constant module that guarantees a greater strength of the teeth.

Brief description of drawings

This and other features of the invention will become more apparent from the following detailed description of a preferred, non-limiting example embodiment of it, with reference to the accompanying drawings, in which: - Figure 1 shows a front view of a window comprising the handle according to this invention;

- Figure 2 is a cross-section through line II - II of Figure 1 ;

- Figure 3 shows an exploded perspective front view of the handle for doors and windows according to this invention;

- Figure 4 shows a plan view from above of a detail of Figure 1 ;

- Figure 5 is a cross-section through line V - V of Figure 4;

- Figure 6 shows a front perspective view of a first kinematic component of the handle according to this invention;

- Figure 7 shows a front perspective view of a contact and positioning plate of the handle according to this invention;

- Figure 8 shows a perspective view of a part of a kinematic unit forming part of the handle according to this invention;

Figure 9 is a scaled-up front view of a detail of the kinematic unit of Figure 8;

- Figures 10 and 11 show rear and front perspective views, respectively, of a cartridge which can be housed in the grip of the handle according to this invention;

- Figure 12 shows a front view of the grip and the kinematic unit housed in the neck of the grip;

- Figure 13 shows an exploded perspective view of the sash of a window and a series of steps for assembly on the sash of the components forming the handle according to this invention;

- Figure 4 shows a plan view from above, with some parts in cross section in order to better illustrate others, of a step for positioning a kinematic unit forming part of the handle according to this invention on a channel inside the sash;

- Figure 15 shows a perspective view of a detail of a variant embodiment of the grip forming part of the handle according to this invention.

- Figure 16 shows a perspective view of a further variant embodiment of the cartridge which can be housed in the grip of Figures 10 and 11 ;

- Figure 17 shows a perspective view, with some parts cut away to better illustrate others, of a part of the kinematic unit forming part of the handle according to this invention in a variant embodiment with double rack;

- Figure 18 shows an exploded perspective front view of an alternative embodiment of the handle for doors and windows according to this invention;

- Figures 19 and 20 show the handle of Figure 18 partially assembled and completely assembled in exploded and perspective views, respectively, with some parts cut away to better illustrate others. Detailed description of preferred embodiments of the invention

With reference to the accompanying drawings and with particular reference to Figures 1 to 3, the handle according to this invention, denoted in its entirety by the numeral 1 , is used to control the opening and closing of a door or window 2 (shown by way of non-limiting example as a window in Figure 1).

It should be noted that the door or window 2 comprises a fixed frame 5t and one wing 5 movable relative to the frame 5t thanks to the presence of one or more hinge units (not illustrated) between one or more open configurations (sash and/or tilted for example) and a closed configuration. The movable sash 5 also comprises a perimeter profile comprising an outer wing 4.

The movable sash 5 also has, along the relative inner perimeter, a profile defining a channel 8 for the slidable housing of one or more control rods 9 (or rod segments, illustrated with a dashed line in Figure 13).

The channel 8 and the inner surface of the outer wing 4 are positioned alongside each other to form a sort of right-angled profile on the outermost perimeter end of the movable sash 5.

It should be noted that between the upper, open, surface of the channel 8 and the free end of the wing 4 there is a distance D8 thanks to the profile of the sash 5.

The rod 9 has pins or bosses (not illustrated) protruding from the channel 8 and designed to engage or disengage (by sliding of the rod 9 in both directions) from contact elements which are fastened to the fixed frame 5t to determine the closed configuration of the sash 5 on the frame 5t or the open configuration of the sash 5 relative to the frame 5t.

The handle 1 for doors or windows 2 comprises a grip 3 having a gripping portion 3a and a base portion or neck 3b opposite, in use, the outer wing 4 of the movable sash 5.

The grip 3 can rotate about a first axis X3.

The first axis X3 is at a right angle to the plane in which the outer wing 4 of the sash 5 lies.

The handle 1 comprises a shaft 6 protruding from the grip 3 and passing through the outer wing 4 of the movable sash 5.

The protruding shaft 6 is connected to a kinematic unit 7 located close to the longitudinal channel 8 inside the profile of the sash 5 in which at least one control rod 9 slides.

The kinematic unit 7 is connected to at least one control rod 9 for converting the rotational movement of the grip 3 into a translational movement of the rod 9, in both directions (see Figures 1 to 3 and 13).

Moreover, the handle 1 comprises a first annular kinematic component 10, housed inside a seat 11 made in the neck 3b of the grip 3.

The first component 10 has at least one sector 12 with a toothed profile along its circumference.

In light of this, the first component 10 is connected to the neck 3b in such a way as to rotate around the first axis of rotation X3 of the grip 3.

It should be noted that the handle 1 comprises a second kinematic component 13, comprising a toothed profile 14, housed in the seat 11 and meshing (tangentially) in an area of the sector 12 with a toothed profile of the first component 10.

In light of this, the second component 13 is connected to the protruding shaft 6 in such a way as to allow a rotation of the shaft 6 about a second axis X6 parallel to, and different from, the first axis X3. The first and second kinematic components 10 and 13 form a kinematic chain for the passage of the rotational movement from the grip 6 to the protruding shaft 3 rotating about the second axis X6.

This structure allows a different positioning of the protruding shaft 6 relative to the centre of rotation of the grip 3 thus optimising and diversifying the position of the kinematic unit 7 located close to the channel 8.

Preferably, the first annular kinematic component 10 has the sector 2 with a toothed profile formed on its inner surface facing towards the first axis X3. In light of this, the second kinematic component 13 is positioned inside the dimensions defined by the first annular kinematic component 10 and meshed on the sector 12 with an internal toothed profile (see Figures 5 and 6).

Again preferably, the second kinematic component is a gear wheel 13 meshed on the sector 12 with an internal toothed profile of the first kinematic component 10.

More specifically, the second kinematic component 13 is positioned stably in an area of the seat 11 at a fixed radial distance D relative to the first axis of rotation X3 of the first kinematic component 10 and of the grip 3.

In light of this, the second component or gear wheel 13 is associated with the shaft 6 so as to be coaxial with it and in such a way as to rotate, both, in the same direction of rotation as the first component 10 and the grip 3.

In other words, the gear wheel 13 and the protruding shaft 6 rotate about the second axis X6 offset laterally by the distance D from the first axis X3. In light of this, the second component (or gear wheel) 3 and the shaft 6 are positioned coaxially relative to the second axis X6 and positioned radially offset from first axis of rotation X3 (taking as reference the circumference defined by the first kinematic component 10 which is annular in shape and with the centre X3 coinciding with the first axis of rotation X3).

This offset between the two axes X3 X6 makes it possible to position, in use, the portion of shaft 6 passing through the outer wing 4 of the sash 5 near to a stretch of a free upper surface of the channel 8 (see Figure 2). Preferably, the first annular kinematic component 10 has a sector 12 with a toothed profile formed on an arc-shaped surface and for an angle a (equal to approximately 180°).

In light of this, at each end of the toothed arc 12 there is a single cavity 15 and 16 designed to lock the rotation of the second kinematic component 13 in such a way as to define a corresponding end of rotation position of the grip 3 (see Figures 5 and 6).

Alternatively, the first annular kinematic component 10 has a sector 12 with a toothed profile formed on the entire relative inner circumference, that is, for an angle a equal to 360° (see Figure 18).

In order to obtain in the arc of the toothed sector 12 a rotation of the second kinematic component or gear wheel 13 a rotation of the protruding shaft 6 sufficient for the translation of the kinematic unit to change the sash configurations from closed to open (in several positions) the transmission ratio between the two kinematic components is between 1 : 1.8 and 1 :3.

Preferably, the ratio between the two kinematic components is 1 : 2.6.

This ratio makes it possible to obtain in the rotation within the angle a of the grip 3 a rotation of the protruding shaft 6 by a sufficient angle (equal to approximately 480°) to allow a translational movement of the kinematic unit 7 away from and towards the positions necessary for the open and closed configurations of the movable sash 5.

It should be noted that the first component 10 consists of an annular cylinder open at the two ends.

On the inner surface of the ring there is the toothed sector 12, whilst on the outer surface of the ring there are recesses 28 in a predetermined position along the circumference and whose function will be explained in detail below.

On a front surface of the ring there are the teeth 29 angularly spaced from each other and whose function will be explained in detail below.

It should be noted that the above-mentioned protruding shaft 6 comprises a relative first portion defined by the second kinematic component 13 (gear wheel).

The protruding shaft 6 also comprises a second (intermediate) portion 6a with a cylindrical cross section.

The shaft 6 also comprises a third portion 6b (distal to the second component 13) with a polygonal cross section.

The third portion 6b with a polygonal cross section is the part of the shaft 6 configured for coupling with and shaped to match a moving part of the kinematic unit 7.

Preferably, in the embodiment illustrated merely by way of example, the gear wheel 13 and the protruding shaft 6 form a single component.

Preferably, the third portion 6b of the protruding shaft 6 has a hexagonal cross section.

Preferably, the protruding shaft 6 comprises a fourth portion 6c (proximal) and defining a rear extension (with a cylindrical cross section) to the second kinematic component 13 (that is, opposite the second cylindrical portion 6a). Preferably, the gear wheel 13 has a width S13 calculated along the axis X6 which is less than the width S10 of the toothed sector 12 of the first kinematic component 10, calculated along the axis X6.

It should be noted that the neck 3b of the grip 3 has a substantially cylindrical hollow seat 11.

In light of this, the handle 3 comprises means 30, 31 , 35, 38 for the assembly and the positioning of at least the first 10 and the second 13 kinematic component and at least a part of the protruding shaft 6 to form a pre-assembled module or cartridge C which can be stably housed and extracted in / from the seat 11 of the neck 3b of the handle (see Figures 2, 3, 5 and from 0 to 12 and from 18 to 20).

The cartridge C comprises means 30, 35 for positioning and housing the above-mentioned components (first and second component and shaft) and removable fixing means 31 , 38 designed to stabilise the cartridge C made in this way and to fix, again in a removable fashion, the cartridge C inside the seat 11. The cartridge C can therefore be extracted and applied again to the handle 3 in order to modify the settings or the components present.

A further advantage of the cartridge C is due to the possibility of replacing the outer handle (for example, for reasons of appearance in the room in which it is mounted) without having to purchase the entire internal kinematic system, but retaining the one already present.

This also enables the manufacturer to make the management of the store more rational and economic.

In light of this, the cartridge C comprises at least a bottom base 30, the first kinematic component 10, the second kinematic component 13, a part of the protruding shaft 6 and a rear closing element 35.

The cartridge C also comprises first joining means 38 (removable) between the bottom base 30 and the front closing element 35 configured to keep together and in position all the components of the cartridge C.

The cartridge C comprises removable attaching means 31 positioned between the bottom base 30 and the bottom of the hollow seat 11 of the neck 3b of the handgrip 3.

In light of this, the cartridge C has the base 30 used for the fixing and the referencing of the cartridge C inside the seat 11. The base 30, which is cylindrical in shape, comprises a central seat 30a for passage of a screw 31 joining the base 30 to the bottom of the seat 1 .

In light of this, the screw 31 has two different operational stretches: a threaded end for fixing the base 30 to the bottom of the seat 11 , whilst the intermediate stretch is configured in the form of a bushing (coupled to the seat 30a of the base 30) to allow the rotation of the grip 3 without interfering with the base 30.

Moreover, the base 30 has a plurality of holes 32 on its bottom for connecting fixing elements 38 (described in more detail below).

It should be noted that the base 30 is equipped with a series of front reference protrusions 34 for the position for mounting the closing element 35 (described in more detail below). The above-mentioned cartridge also comprises the above-mentioned element 35 for closing the components inside the seat 11 of the neck 3b of the grip 3. As mentioned above, the closing element, consisting of a closing body 35 faces, during assembly and in use, the first kinematic component 10.

The closed body 35 has a first cylindrical portion with a diameter substantially equal to the diameter of the seat 11 of the neck 3b for completely engaging the outermost end of the seat 11.

The closing body 35 has a second portion partly cylindrical and with a diameter smaller than that of the first portion.

The cartridge C may comprise a further front component or cap (labelled 35a in Figure 18) which can be associated with the first portion of the closing body 35 to protect the front parts of the closing body 35 in use. The cap 35a is configured with a plurality of openings designed to allow access to the fixing components and the passage of the protruding part of the shaft 6.

This second portion of the closing body 35 engages at least partly, during assembly and in use, the inner space of the first annular kinematic component 10.

In this way, the closing body 35, mounted, is coaxial with the first axis of rotation X3, but fixed relative to the first kinematic component 10.

In light of this, the above-mentioned protrusions 34 of the base 30 are coupled in recesses made on the second portion with the smaller diameter of the body 35 to ensure the correct reciprocal angular position adopted and consequently the position of the toothed sector 12 inside the first kinematic component 10 (thanks also to the outer recesses 28) so as to render the first kinematic component 10 integral with the grip 3.

During assembling this positioning and consequent coupling between first annular component 10 and neck 3b is essential for positioning the arc defined by the toothed sector 12 in a precise position relative to the gear wheel 13 and relative to the gripping portion 3a of the grip 3. A through seat 36 extending along the second axis of rotation X6 of the shaft 6 is made on the second portion.

This seat 36 has a semicircular cradle-shaped cross section for allowing the passage and the support of the shaft 6 (with the possibility of rotating) and for containing the second kinematic component or gear wheel 13.

The portion of the shaft 6 housed in the seat 36 is a part of the second portion 6a with a cylindrical cross-section, whilst the majority of the portion of shaft 6 protruding from the closing body 35 has a hexagonal cross- section.

In light of this, the third portion 6b with a hexagonal cross section, with cartridge C assembled, protrudes completely from the cartridge C, that is, from the closing body 35.

On the closed body 35 there are axial through seats 37 engaged by pins or screws 38 for joining the closed body 35 to the base 30 by engaging the pins or screws 38 in the above-mentioned holes 32 present on the base 30: in this way, all the kinematic components are correctly positioned to form the cartridge to be fitted inside the seat 11.

The closing of the cartridge C by the joining between closing body 35 and base 30 can be performed by screwing if there are screws, or by a combination of screws and nuts.

Alternatively, the closing of the cartridge C by the joining between the closing body 35 and base 30 can be performed by deformation by folding down the ends engaging the seats 32 of the base 30 if simple pins are provided.

The structure of the extractable cartridge C obtained in this way and the division of the shaft 6 into portions allows a kinematic and motion transmission system to be obtained which is extremely safe, precise and adaptable to the various geometrical configurations of the sash 5.

In effect, each portion of the shaft 6 (gear wheel, cylindrical part, polygonal or hexagonal part and rear supporting part) define specific and very precise functions for supporting, guiding and motion transmission. More specifically, the axial extension of the third polygonal (hexagonal) drive portion 6b protruding from the cartridge C combined with a matching seat on the transmission unit 7 (described in more detail below) allows an adaptation flexibility to be obtained in the coupling with the transmission unit 7 in such a way as to avoid adaptations (dimensional variations of the shaft) with variations in the steps of the profiles of the sash on which it is applied. The term "step" means the distance DG between the wing 4 of the sash 5 on which the handle 3 is applied and the position of the channel 8 on which the transmission unit 7 is positioned (see Figure 2). This distance may vary as a function of the type of profile used for making the sash 5.

Therefore, this type of structure of the pin 6 offers a series of advantages, given by:

- portions optimised for a specific function: guide inside cartridge (fourth portion 6c), motion pick up (gear wheel 13), positioning and support in the cartridge (second portion 6a), transmission of motion (third portion 6b);

- adaptability of the polygonal portion to the various steps varying only the coupling section with the transmission unit without adversely affecting the correct manoeuvre;

- no problem of managing the position tolerances between the upstream mechanism (kinematic unit) and the downstream mechanism (coupling of hexagonal portion with the transmission unit).

Moreover, the shaft structured in this way and combined with the cartridge

C guides and retains the shaft in all the directions during use.

It should also be noted that the extension S13 of the second kinematic component 13 calculated along the axis X6 below the extension S10 of the first kinematic component 10 increases the possibility of adaptability of the pin 6 to the needs of adjusting the third hexagonal portion 6b.

Advantageously, the closing body 35 has a central through hole 35b for allowing the fixing of the screw 31 located in the base 30 on the bottom of the seat 11 of the grip 3, with the cartridge closed.

The closing body 35 has, in addition and assisting the above-mentioned protrusions 15 and 16 of the toothed arc 12, further means for limiting the rotation of the first kinematic component 10 (see Figure 16) acting between the first kinematic component 10 and the closing body 35.

More specifically, on the bottom of the first annular kinematic component 10 (that is to say, on the bottom of the annular cylinder) there is an enlargement defining an arc-shaped sector 70 equipped, at the ends, with two undercuts.

The arc-shaped sector 70 coincides with the arc-shaped extension of the internal toothed sector 12 of the first component 10.

The base of the second portion with a smaller diameter of the closed body

35 is shaped in such a way as to have an arc-shaped extension or radial lobe (fixed) 71 equipped, at its ends, with two contact or stop surfaces for the corresponding undercuts of the arc-shaped sector 70.

In practice, the rotation, in both directions, of the first kinematic component 10 determines the movement of the arc-shaped sector 70 until contact with one or other of the contact surfaces of the extension 71 which determines or assists the stopping of the stroke of the grip 3b.

In a variant embodiment illustrated in Figures 19 and 20, (wherein the first kinematic component 0 has a crown-shaped inner toothed portion 12, that is, at 360°), the means for limiting the stroke of the handle 3 are made between the bottom base 30 (of the cartridge C) and the bottom of the seat 11 of the neck 3b of the handle 3.

In this variant embodiment, the bottom wall of the base 30 is provided with an arc-shaped sector 300 equipped, at the ends, with two undercuts.

The arc-shaped sector 300 coincides with the maximum stroke, in rotation, which can be performed by the internal toothed sector 12 of the first component 10.

The base of the seat 11 made in the neck 3b of the handle 3 is made (or shaped to match) in such a way as to have an arc-shaped extension 301 equipped, at its ends, with two contact or stop surfaces for the corresponding undercuts of the arc-shaped sector 300. In practice, the rotation, in both directions, of the handgrip 3 determines the movement of the semi-arc 301 until contact with one or other of the contact surfaces of the arc-shaped sector 300 (the base is stationary relative to the handgrip 3) which determines the stopping of the stroke of the handgrip 3b. This handle rotation end of stroke structure allows a very high strength to be obtained avoiding additional components inside the seat and avoiding the touching of the kinematic component(s).

Preferably, the handle also comprises means 24 for referencing and stabilising the positions adopted by the grip 3 during its rotation around the first axis X3.

These referencing and stabilising means 24 are interposed between the outer wing 4 of the sash 5 and the first kinematic component 10.

More specifically, the referencing and stabilising means 24 are positioned inside the cartridge C which encloses the other kinematic movement components.

In light of this, these referencing means 24 are interposed between the kinematic component 10 and the closing body 35 of the cartridge C.

In light of this, the means 24 comprise a further ring 39 positioned between the first kinematic component 10 and the inner surface of the first portion of the closed body 35.

The ring 39 is coupled, therefore, on the surface of the second portion of the closed body 35.

The ring 39 also has a relative annular surface facing and in contact with the front surface (again, annular) of the first component 10 equipped with teeth 29.

The ring 39 has the relative annular surface equipped with a series of recesses 40 alternated with enlargements 41 to allow a stable positioning alternating with an uncoupling of the teeth 29 from the recesses 40 during rotation of the grip 3: this is in order to stabilise, during coupling of the teeth 29 - recesses 40, the correct angular position of the grip 3, corresponding to a closed - open configuration of the movable sash 5. To make this type of coupling adaptable, there are elastic means 42 between the ring 39 and the inner surface of the first portion of the closing body 35.

These elastic means 42, acting axially and parallel to the first axis X3, keep in constant contact the ring 39 with the first kinematic component 10 and allow withdrawal of the ring 39 during rotation of the grip 3.

In light of this, the elastic means 42 comprise a plurality of springs 43 (helical) distributed along the circumference of the inner surface of the first portion of the closed body 35.

The closed body 35 has a corresponding plurality of seats for partial housing/contact of the springs 43.

Each spring 43 surrounds or fits to, at its other end, a corresponding guide pin 44 protruding transversely from the annular surface of the ring 39.

Thanks to this type of ring structure with springs, combined with the presence of the removable cartridge C, it is possible to adapt the settings of the positioning system as a function of the type of door or window and the hardware articles used (for example, moved by 0° - 180°, 0° - 90° - 180°, 0°- 45°- 90° etc.).

The choice and the settings of the positioning system occurs simply by inserting in the cartridge C the correct snap-on ring, without varying other components.

The presence of the springs enables a balanced distribution of the opposing force of the 360° snap disk over the entire circumference.

The closed body 35 has at least two further seats 45 (diametrically opposite each other) for coupling with the means 46 for fixing the grip 3 to the movable sash 5 (that is, on the outer wing 4).

Preferably, the fixing means 46 comprise a pair of pins or tie rods 47 which consist of a cylindrical body which can be stably housed in a snap-on fashion in the seats 45 and provided with a base with a larger diameter for retaining, in use, the grip 3 against the outer wing 4 of the sash 5.

Each pin 47 has a free protruding threaded head for fixing the grip 3 to the sash 5.

In light of this, the handle 1 comprises a contact and reference plate 25 for fixing the grip 3 (see also Figure 7).

Moreover, the plate 25 also acts as a reference for the correct positioning of the kinematic unit 7 on the channel 8 (as described in more detail below). The plate 25 has at least one pair of through holes 25a and 25b, one (the 25b) for the passage of the shaft 6 and the other (25a and threaded) for coupling with the means 46 for fixing the grip 3.

Preferably, the plate 25 has a set of three through holes 25a, 25b, 25c wherein the central through hole 25b is engaged by the shaft 6 and the two side holes 25a and 25c (threaded) are used for performing the coupling with the threaded heads of the fixing pins 47.

Moreover, the plate 25 has at least one protruding pin 27 whose function will be explained in more detail below.

Preferably, the plate 25 has a pair of protruding pins 27 positioned at least on sides opposite the central hole 25b for passage of the shaft 6.

This plate 25 is positioned, in use, on the inner surface of the wing 4 of the sash 5, with its holes coaxial with at least two holes (F1 , F2, F3) made on the wing 5 (see also Figure 13).

Preferably, the wing 4 of the sash 5 has three holes F1 , F2, the F3 made one after the other along a shared line or axis and parallel to the longitudinal extension of the wing 4.

As mentioned above, the handle 1 also comprises a kinematic unit 7

(shown partly in Figures 8 and 9).

According to the invention, the kinematic unit 7 comprises a first and a second gear wheel 17, 18, different to each other, placed side by side and in contact with each other and having a seat 19, 20 positioned, in use, coaxial with each other and engaged simultaneously by the protruding shaft

6 (that is, the third protruding portion 6b).

Preferably, the seats 19 and 20 of the gear wheels 17, 18 have a hexagonal cross-section corresponding to the hexagonal cross-section of the protruding shaft 6.

Also according to the invention, the kinematic unit 7 also comprises a rack 21 having two separate meshing tracks 21a, 21 placed side by side and engaged by a corresponding gear wheel 17, 18.

Again according to the invention, the rack 21 is formed on a rod-shaped body 22 positioned, in use, parallel to a free upper surface of the channel 8 and provided with means 23 for coupling with the at least one control rod 9. Each track 21a and 21b of the rack 21 is made by incision on the rod- shaped body 22 (substantially each meshing seat is defined on a cavity and made in the thickness of the rod-shaped body 22) defining corresponding tracks 21a, 21b with recessed meshing seats for the teeth of the first and second gear wheel 17 and 8.

In other words, each track 21a and 21b is obtained with a plurality of hollows 210 different and in succession on the rod-shaped body 22: this defines a rack 21 with an extension not protruding from the basic reference plane P22 of the rod-shaped body 22.

In light of this, each track 21a and 21b is different and separated by a central longitudinal rib 211.

The advantage of rack teeth made with a hollow is the greater strength as they are perimetrically closed in the structure and not as in the "cantilever" racks. In light of this, the presence of a central rib for separation between the tracks generates a strengthening of the teeth in the rack and achieves a safe anchoring of the teeth of the first and second gear wheels: in effect, the overall geometry obtained in this way determines a bilateral anchoring of the teeth (on both sides), having greater strength compared with non- anchored teeth, or teeth only anchored on one side.

In this specific case, the rod-shaped body 22 is positioned, in use, facing a free upper surface of the channel 8.

Preferably, the pair of gear wheels 17, 18 has, in use, the corresponding toothed profile offset relative to each other by an angle β (see Figure 9) so as to determine a diversified and continuous coupling on the corresponding tracks 21a and 21 b for meshing the rack 21 during the rotation applied by the shaft 6.

Basically, the kinematic unit 7 has a double width pinion which uses twice the teeth X6 distributed along the second axis of rotation X6 and with a substantially continuous spacing of the teeth of the two wheels 17 and 18 (instead of about the axis) to allow a continuity of meshing on the rack 21. In light of this, the pair of meshing tracks 21a and 21b have a different distribution of the respective teeth along the rod-shaped body 22 and correlated with the offset angle β of the corresponding toothed profile of the gear wheel 17, 18.

In other words, the two tracks 21a and 21 b formed on the rod-shaped body 22 have their corresponding ends offset, under equal conditions of total extension, as a function of the offset angle of the gear wheels 17 and 18. In effect, a first translated limit position of the rod-shaped body 22 corresponds with the meshing of a single tooth of one of the gear wheels 17 or 18 in the end seat of the corresponding track 21a or 21b, and a second translated limit position (opposite the previous one) of the rod-shaped body 22 corresponds with the meshing of a single end tooth of the other of the gear wheels 18 or 17 in the seat of the corresponding track 21b or 21a. In short, the double gear wheel allows a regular and continuous translation of the rod-shaped body 22 without sudden jolting of the latter which, in effect, would transform into discontinuous movements of the grip 3.

This is possible due to the fact that the pair of gear wheels alongside each other provides the characteristics of a gear wheel (or pinion) with a greater number of teeth and with a smaller spacing, that is, with a constant module that guarantees a greater strength of the teeth.

These mechanical characteristics are distributed along the second axis X6 and with an offset of the teeth of the two wheels 17 and 8.

The presence of two different gear wheels with this geometry allows:

- a constructional simplification of each gear wheel.

- the use of a single wheel model both for the first and second gear wheel by means of a simple mutual phase displacement in the assembly.

The rod-shaped body 22 has two ends consisting of a corresponding wall at a right angle relative to the surface of the rack 21. A fin protrudes perpendicularly from each of the walls equipped with at least one pin 23 for coupling with the rod 9 and defining the above-mentioned means for coupling the kinematic unit 7 with the rod 9.

The coupling of the pin(s) 23 with rod(s) 9 can be one-sided or two-sided depending on the type of openings on the door or window.

Figures 3, 8, 9 and 13 show a kinematic unit 7 with one-sided movement, whilst Figure 17 shows a solution of a kinematic unit 7 with two-sided movement.

In the embodiment of the kinematic unit with two-sided movement there is a second rod-shaped body 72 with a second rack similar to the first rack 21. The second rod-shaped body 72 faces, in use, the rod-shaped body 22 and is provided with two meshing tracks 21a and 21 b for the two gear wheels 17 and 18.

These latter, therefore, are interposed between the two rod-shaped bodies

22 and 72, located on opposite sides of the four tracks 21a and 21 b, and meshed simultaneously with the same tracks.

In this specific case of the unit with two-sided movement, each rod-shaped body 22 and 72 has a single pin 23 (one at one end and the other at the opposite end) for coupling with a corresponding rod 9.

The description of the kinematic unit 7 given hereafter is valid for both the kinematic units referred to even if reference is made to the drawings relative to the kinematic unit 7 with one-sided movement.

The kinematic unit 7 also comprises two protection and containment shells

48 and 49 joined together for the rod-shaped body 22 and for the gear wheels 17 and 18.

The two shells 48 and 49 have different shapes.

A first shell 48 forms a side wall facing, in use, the inner surface of the wing 4 (and the contact plate 25) and a bottom wall 26 shaped for the contact/coupling with the channel 8.

The second shell 49 forms the other lateral part and is coupled with the first shell 48.

The box-shaped body formed by the two shells 48 and 49 is closed (as an upper wall) by the rod-shaped body 22 which slidably couples with the two shells 48 and 49 (in the case of two-sided movement unit, the second rod- shaped body 72 forms part of the bottom of the box-shaped body and is partly housed in the channel 8).

Moreover, the two shells 48 and 49 have inner shaping to allow correct housing of the two gear wheels 17 and 18 with the unit mounted and with spaces suitable for their meshing with the rack 21 and the possibility of rotating.

The first shell 48 has a through hole 48a (on its lateral wall) for housing, in use, the protruding shaft 6 in such a way as to allow a coupling with the seats 9 and 20 of the gear wheels 17 and 18.

Also in the lateral wall of the first shell 48 there is at least one cradle 50 with hole passing through the lateral wall for the positioning of the fixing means 46 of the grip. A further reference cradle 51 (again with a through hole in the lateral wall) is formed on the first shell for coupling with the pin 27 of the contact plate 25.

Preferably, the first shell 48 has a lateral wall provided with four cradles 50, 51 for housing the pair of fixing tie rods 47 (means 46) and the pair of pins 27 of the contact plate 25.

On the second shell 49 there are at least corresponding through holes 52 coaxial with the cradles 50 and 51 made on the first shell 48.

In this way, after the positioning and fixing of the kinematic unit 7 on the channel 8 and the coupling of the protruding shaft 6 to the gear wheels 17 and 18, the grip 3 may be fixed to the wing 4 by screwing the tie rods 47 into the holes 25a and 25c of the plate 25 passing through the holes of the second shell 49 and the through cradles 50 or 51 of the first shell 48.

The second shell 49 also has an incorrect operation safety lock device 53 acting on the rod-shaped body 22, in use, to prevent rotations of the grip 3 with the sash 5 positioned in one of the open configurations (see Figures 3, 4, 8 and 13).

The incorrect operation safety lock device 53, by way of non-limiting example, comprises a contact element 54 for fastening the rod-shaped body 22 positioned, in use, perpendicularly to the first axis of rotation X3 of the grip 3.

The contact element 54 is integral with an operating body 55 (perpendicular to the wing 54) slidably connected inside a tubular seat 56 protruding from the second shell 49. The seat 56 protrudes from the second shell 49 perpendicularly to the second shell 49 and parallel to the first axis of rotation X3 of the grip 3.

Spring means 57 (pre- loaded) are interposed, in use, between the operating body 55 and the lateral wall of the first shell 48 to keep, normally, the contact element 54 in contact with the rod-shaped body 22, which is equipped with one or more seats 58 for coupling with the contact element 54: this locks the movement of the rod-shaped body 22.

In other words, the contact element 54 due to effect of the spring means 57 locks the rod-shaped body 22 with the sash 5 open, whilst during closing of the sash 5 (as shown in Figure 4), the contact element 54 is intercepted by a surface of the frame 5t which moves the contact element 54 away from the rod-shaped body 22 (with further compression of the spring means 57) allowing the translation movement.

It should also be noted that the rod-shaped body 22 and the base 26 of the first shell 49 are provided with a pair of holes 60a, 60b (one of which, 60a, is slotted).

More specifically, the holes 60a, 60b of the rod-shaped body 22 have dimensions greater than the holes 60a, 60b of the base 26 of the first shell 49.

The difference in size of the holes is required for locking the kinematic unit 7 on the channel 8, after the positioning of the unit on the pins 27 of the contact plate 25.

In effect, after the positioning of the kinematic unit 7 screw means (not illustrated) are housed inside the shells 48 and 49 using the seats present on the rod-shaped body 22 and, subsequently, by using the holes of the bottom 26 of the first shell 49 the screw means can connect with the bottom of the channel 8 fixing all the kinematic unit to the movable sash 5.

In the embodiment according to the invention, the grip 3 houses the cartridge with the kinematic components for rotation of the protruding shaft 6 and the means for fixing the sash 5: in effect, this handle 1 has only and exclusively the grip 3, comprising the gripping portion 3a and the neck 3b, on the outside and in view.

Figure 15 illustrates a variant embodiment of the handle 1 described above. In this solution there is also a base unit 59 as an extension of the neck 3b of the grip 3.

There are no differences with regard to the mechanical and positioning aspects of the cartridge containing the kinematic components and the protruding shaft 6.

In this embodiment, the base unit 59 has constraining seats for the fastening means 46 which have a centre-to-centre spacing and a distance from the shaft 6 greater than the embodiment described previously.

In this case, the two holes of the outer wing 4 (F1 , F3) of the sash 5, for passage of the tie rods 47, are made at corresponding distances different to the passage hole F2.

Advantageously, the contact plate 25 and the kinematic unit 7 (in particular the first shell 48) remain structurally the same.

The contact plate 25 is set up, for this solution, with the pins 27 connected on the original holes 25a, 25c closest to the central hole 25b for passage of the protruding shaft 6; the above-mentioned holes 25a, 25c for passage of the tie rods 47 become the outermost ones to the contact plate 25.

The four cradles 50, 51 present on the first shell 48 exchange simply the functions for engaging with the pins 27 and the tie rods 47. This invention also provides a method for assembly of the handle 1 described above.

According to the invention, the assembly method comprises at least the following steps:

- processing the outer wing 4 of the profile of the sash 5 for forming and preparing at least two through holes F1 , F2 for referencing;

- resting the kinematic unit 7 on the upper part of the channel 8 at the area of the wing 4 wherein there are the referencing holes F1 , F2;

- coupling the kinematic unit 7 with at least one control rod 9 provided inside the channel 8;

- inserting the shaft 6 protruding from the grip 3 inside one (F2) of the holes (F1 , F2) of the wing 4 with successive coupling to the kinematic unit 7 in such a way as to position the shaft 6 along a second axis X6 parallel and separate from the first axis X3 of rotation of the grip 3.

Preferably, between the step of preparing the at least two positioning holes (F1 , F2) and the step of resting the kinematic unit 7 there is a step of preparing and positioning a contact and reference plate 25 on the inner side of the wing 4 close to the channel 8.

In light of this, the plate 25 is provided with at least two corresponding holes (25a, 25b) positioned coaxially to the holes (F1 , F2) made on the wing 4. Preferably, the step of resting the kinematic unit 7 on the channel 8 comprises a step of coupling at least one cradle seat 50, 51 present on the kinematic unit 7 on at least one pin 27 protruding from the contact plate 25 for determining the correct position reference of the kinematic unit 7 and retaining it in the position adopted in such a way as to correlate the position of the kinematic unit 7 with the position of entrance of the protruding shaft 6. Preferably, after the step for resting the kinematic unit 7 on the channel there is at least one step for pre-fixing the kinematic unit 7 to the bottom of the channel 8.

This pre-fixing step is obtained by screw means.

Preferably, the step of processing the outer wing 4 of the profile of the sash 5 forms and prepares three through referencing holes F1 , F2, F3.

On the plate 25 there are at least three through holes 25a, 25b, 25c (of which at least two threaded).

Preferably, after the step of inserting the shaft 6 in the hole of the wing 4 and consequent coupling with the kinematic unit 7 there is a step for fixing the grip 3 to the wing 4 using fixing means 46 (connected to two threaded holes of the plate 25).

Preferably, after the step of fixing the grip 3 there can be a step for adjusting the position of the kinematic unit 7 along the channel 8, followed by a step for fixing final of the kinematic unit.

It should be noted that the kinematic unit may also be installed without the simultaneous assembly of the grip unit, allowing the storage and transport of the assembled door or window without running the risk of damaging the grip.

A handle made as described above fully achieves the pre-set aims thanks to the particular architecture of the grip and the subdivision of the kinematic systems needed for operating in a small space.

Overall, there is only a grip or handle on view and, in preparation of the sash, only three holes, that is to say, internal and external parts of the sash do not have any other type of machining.

In other words, the actual machining to install the entire closing system is three simple circular holes to be made on the contact wing of the sash profile (therefore, outside from the tubularity).

The position of the protruding shaft which rotates with the axis of rotation offset towards the outside of the sash relative to the axis of rotation of the handle makes it possible to shift the machining from the tubularity of the profile to the contact wing.

This makes it possible to make these holes with any technology, from a simple drill bit (three circular holes) to punching, and to move the handle laterally with respect to the position of a traditional prior art handle: this reduces the risk of superposing with the glass bead. Thanks to a system for the transfer of motion which is similar to an "epicyclic" reduction gear unit resulting from the two kinematic components, it is possible to obtain, for example, with a rotation of the grip of 180°, a corresponding rotation of the protruding shaft of 480°.

This is thanks to a predetermined transmission ratio obtained from the pair of kinematic components.

The high angle of rotation of the protruding shaft generates a translation of the rod-shaped body sufficient for the strokes necessary for movement of the rods.

The translation of the rack is obtained with a pinion - rack kinematic mechanism comprising the above-mentioned double offset toothing which, under equal conditions of space occupied, allows the doubling of the number of gripping teeth without reducing the size of the teeth and therefore their strength.

This allows the size of the handle unit D8 to be kept inside the distance D8 between the channel 8 and edge of the outer wing 4.