WO2013167708A1

WO2013167708A1 - Balanced hinge device with brake

Info

Publication number: WO2013167708A1
Application number: PCT/EP2013/059680
Authority: WO
Inventors: Eros Gherardi
Original assignee: C.M.I. Cerniere Meccaniche Industriali S.R.L.
Priority date: 2012-05-09
Filing date: 2013-05-08
Publication date: 2013-11-14
Also published as: US9364132B2; EP2847404A1; US20150107053A1; PL2847404T3; ITBO20120257A1; EP2847404B1; EP2847404B8

Abstract

A balanced hinge device with brake comprises a first connecting means (3) assigned to be fixed to a structure or frame and connected via at least a kinematic means (8) to a second connecting means (5) assigned to be fixed to a door or a shutter. Said device (1) comprises at least a friction means (9) fixed to at least one among first connecting means (3), second connecting means (5) and kinematic means (8), each friction means (9) slidably contacts, at least at a predetermined rotation arc of one of the connecting means (3, 5) with respect to the other, with a portion of at least one among first connecting means (3), second connecting means (5) and kinematic means (8) and with at least a contact means (11).

Description

Balanced hinge device with brake

Technical Field

The present invention relates to the field of hinges and refers to a balanced hinge device with brake particularly suitable for appliances such as dishwashers and in general for doors and shutters having horizontal rotation axis for craft and industrial equipment, electrical apparatus, furniture and furnishings.

Background Art

There are known hinges for doors or shutters having lower horizontal rotation axis, equipped with elastic elements and friction elements assigned respectively to balance the door weight and to allow the slowing down and/or the stopping and levelling off in one or more positions of said door.

One disadvantage of some of these known hinges consists in that the braking action exerted by the friction elements acts throughout all the hinge rotation arc slowing down the door in every position preventing or making difficult to obtain some functionalities.

Another disadvantage of some known hinges consists in that the friction elements are very complex and bulky.

Further disadvantage of some of such known hinges consists in that the forces transmitted by the several elements and organs of the hinge are very high and exercise very intense stress so requiring to use oversized, very robust and high accuracy machined materials resulting very expensive, extremely overweighed and oversized, they cause significant wear and excessive sensitivity to accidental liquids presence, detergents or oils due to the excessive friction reduction due to such materials.

Another disadvantage consists in that these known hinges generally do not allow a final closure free stroke having sufficient force to achieve the closing lock of the door by the respective lock.

Disclosure of Invention

An object of the present invention is to propose a balanced hinge device with a brake suitable to exert a braking action in one or more predetermined sectors of the rotation arc of the hinge and to reduce or eliminate the braking action in the other sectors.

Another object is to provide a compact device reliable and long lasting that it is feasible to easily obtain braked rotation sectors and not depending on the needs and desired functions.

A further object is to provide a balanced hinge device with brake suitable to balance the door weight and that it is light, cheap, small and reliable.

Another object is to provide a device suitable to keep the door locked in one or more ranges of angular positions of the same.

A further object is to provide a device able to keep the door elastically locked in one or more angular positions.

Another object is to provide a device allowing the door to have a free final closure stroke with a force sufficient to cause the door lock closing.

A further object is to provide a device whose actuation and friction characteristics can be easily modified and/or set-up during the production stage by substituting one or two parts.

Brief Description of Drawings

The characteristics of the invention are highlighted in the following with particular reference to the accompanying drawings in which the orientations are related to a condition wherein the device is fixed joined to the apparatus not shown:

figure 1 shows a schematic side view of the balanced hinge device with brake object of the present invention in a close condition;
figure 2 shows a partial enlarged view and the device of figure 1 wherein some elements are represented in transparency to show the underlying elements;
figure 3 shows a section view along the plane III-III of figure 2;
figure 4 shows a schematic, partial, enlarged and in transparency of the device of figure 1 in a condition of partial opening;
figures 5 and 6 show section views respectively according to the planes V-V and VI-VI of figure 4;
figure 7 illustrates the device of figure 4 in a full open condition;
figure 8 shows a section view along the plane VIII-VIII of figure 7;
figure 9 shows an isometric view of the device of figure 1 in partial closure condition;
figure 10 shows an exploded view of figure 9 wherein some elements are only partially illustrated.

Best Mode for Carrying Out the Invention

With reference to figures 1 to 10, numeral 1 indicates the balanced hinge device with brake, object of the present invention and comprising a first connecting means 3, preferably made of cut and moulded metal sheet and being mainly flat shaped, assigned to be fixed to a structure or frame such as a dishwasher or another type of apparatus. One end of the first connecting means 3 which in the device operating condition is placed inferiorly in relation to the latter, is pivotally connected via a second pin 4 of the hinge to a second connecting means 5, also preferably made of cut and moulded metal sheet and being mostly flat shaped, assigned to be fixed to a door or shutter of the dishwasher or other apparatus.

Such connecting means 3, 5 are also mechanically connected to compensating elastic means 7 by kinematic means 8 transmitting to said connecting means 3, 5 a mutual approaching elastic force. The elastic means 7 are connected to the first connecting means 3, in particular they are protruding and they are arranged at one end of the first connecting means 3 opposite to the second pin 4, and therefore in the operating condition protrude upward.

This elastic force produced by the elastic means 7, in the operating condition is assigned to balance the gravitational force acting on the door, opposing to the latter.

Such kinematic means 8 comprise a rack means 10 constrained to slide itself parallel by sliding means 20 and a pinion means 12 axially constrained to rotate about a respective first rotation pin 14 fixed to the first connecting means 3.

The rack means 10 and the pinion means 12 bear corresponding toothed sectors respectively rectilinear and disposed along a circumference arc, mutually engaging transforming the reciprocating circular motion of the pinion means 12 in reciprocating linear motion of the rack means 10.

Said sliding means 20 comprise at least one guide having a “U” shaped concave section, alternatively, comprise an elongated slot formed through the thickness in the rack means 10 and having elongated sides parallel to the longitudinal axis of the rack means 10 itself and also include a slider, for example in anti-friction plastic material shaped as a soap bar, fixed to the first connecting means 3, in both cases, the rack means 10 can slide itself parallel without jamming.

The rack means 10 is resiliently pressed by the elastic means 7 which transmits the elastic force to the pinion means 12.

The kinematic means 8 comprise also an arm means 16 whose ends are connected through respective third 17 and fourth 18 connecting pins respectively to the pinion means 12 and the second connecting means 5.

So the elastic force of the elastic means 7 is transmitted through the arm means 16 by the pinion means 12 to the second connecting means 5 pulling the latter towards the first connecting means 3.

The first rotation pin 14 of the pinion means 12 is fixed to the first connecting means 3.

The first 3 and second 5 connecting means, the rack means 10, the pinion means 12 and the arm means 16 lie approximately on respective parallel geometric planes.

The geometric axes of the first 14, second 4, third 17 and fourth 18 pins are perpendicular to said geometric plans.

The distance between the geometric axes of first 14 and third 17 pins is approximately equal to or greater than the engaging radius of the pinion means 12 teeth.

The toothed sector of the pinion means 12 subtends an angle between about 90° and about 180°; the linear development of this toothed sector of the pinion means 12 has a length approximately equal to the length of the corresponding toothed sector of the rack means 10.

The distance between the axes of the second 4 and fourth 18 pins is between half and twice, preferably approximately equal, the distance between the axes of the first 14 and third 17 pins. Preferably, and as shown in the figures, said

pins

4, 14, 17, 18 are placed at the vertices of a deformable parallelogram geometric quadrilateral.

The rack means 10 is elastically pressed by the elastic means 7 via a rod means 22.

The elastic means 7 are a helical spring and whose ends are compressed between a contact 23 of the first connecting means 3, for example cup shaped, and a contact 24 of the rod means 22 having a thin elongated portion connecting the respective contacts 24, consisting of an enlarged head, to its connection to the rack means 10 through the axial slot of said helical spring.

In full open condition two lower portions of the first 3 and second 5 connecting means contact each other blocking any further rotation that can increase the angle between these connecting means.

To stiffen and reinforce the device in the full open condition, the arm means 16 is provided with a first contact means 34, for example consisting of a its side shoulder, in the full open condition, assigned to contact a second contact means 35, consisting for example in a projecting and folded side flap of the first connecting means 3.

The device 1 comprises a friction means 9 fixed to the pinion means 12 of the kinematic means 8 that sliding contacts, with mutual sliding, the first connecting means 3 and a contact means 11.

A first side portion 13 of the friction means 9, or one of its two main faces, slidably contacts a flat portion of the first connecting means 3 or an element fixed to it, and a second portion 15 of the friction means 9, or its other main face, contacts, at least at a predetermined rotation arc of the device 1, the contact means 11.

The pinion means 12 has a through hollow seat 19 to accommodate, at least partially, the friction means 9 so that the seat 19 wall contacts the perimeter faces of the friction means 9.

The seat 19 consists of a shaped slot formed through the pinion means 12 and the friction means 9 consists of a body approximately plane and shaped in a complementary way to the respective seat 19.

The contact means 11 is approximately shaped as a bridge with ends fixed to the first connecting means 3 with which defines a partial housing for the pinion means 12 and for the friction means 9.

As above described, the first side portion 13 of the friction means 9 and the corresponding surface of the first connecting means 3 are nearly flat while the second portion 15 of the friction means 9 and the face of the contact means 11 facing the pinion means 12 have respective jutting

parts

21, 25 assigned for mutual contact by sliding friction in correspondence of the predetermined rotation arc at which it is necessary that the friction is increased with an intensity depending mainly on the geometric shape and the friction means 9 and the contact means 11 types.

The jutting part 21 of the friction means 9 is nearly flat and it is joined to the other corresponding second portion 15 of the friction means 9 by means of bevelled end terminations.

The jutting part 25 of the contact means 11 is facing towards the friction means 9 and consists, for example, in a moulded transverse rib of the contact means 11 itself.

The seat 19 has an angular extension, with respect to the rotation centre of the pinion means 12, such as the surface of the seat 19 sweeps the entire surface of the face of the contact means 11 that is facing towards the pinion means 12 during the device complete rotation.

The friction means 9 is made of plastic, nylon, Teflon, or similar also reinforced with fibres.

The invention provides that most of the elements of the device are made of cut and moulded sheet metal. The thickness of the rack means 10 and the pinion means 12 can be greater than that of the other elements to ensure a good engagement and wear resistance. In correspondence of the pivoting couplings between the pins and the respective seats, these latter can be equipped with optional bushings.

The operation of the device, starting from a maximum opening condition in which the first 3 and second 5 connecting means are at the maximum mutual angular distance and the elastic means 7 are at maximum compression, provides that the elastic force of these elastic means 7 transmitted by the kinematic means 8 to the second connecting means and to the door, balances the weight of the latter allowing easy manual lifting. The friction between the contact means 11 and the friction 9 depends on the opening angle and their angular trends can be predetermined properly configuring the second portion 15 of the friction means 9 and in particular the

jutting parts

21, 25.

A simple variant of the invention, not figured, provides that the friction means 9 is fixed to the rack means 10 instead of the pinion means 12 and the contact means 11 is overlapped on the rack means 10, or obtained in a side of the sliding means 20.

An advantage of the present invention is to provide a balanced hinge device with a brake suitable to exert a braking action in one or more preset sectors of the rotation arc of the hinge and to reduce or eliminate the braking action in the other sectors.

Other advantage is to provide a compact device reliable and long lasting that it is feasible to easily obtain braked rotation sectors and not depending on the needs and desired functions.

Another advantage is to provide a balanced hinge device with brake suitable to balance the door weight and that it is light, cheap, small and reliable.

Other advantage is to provide a device suitable to keep the door locked in one or more ranges of angular positions of the same.

Further advantage is to provide a device able to keep the door elastically locked in one or more angular positions.

Other advantage is to provide a device allowing the door to have a free final closure stroke with a force sufficient to cause the door lock closing.

Further advantage is to provide a device whose actuation and friction characteristics can be easily modified and/or set-up during the production stage by substituting one or two parts.

Claims

Balanced hinge device with brake comprising a first connecting means (3) assigned to be fixed to a structure or frame and connected at least by kinematic means (8) to a second connecting means (5) assigned to be fixed to a door or a shutter and comprising at least a friction means (9); the device (1) comprises also elastic means (7) balancing the door or the shutter weight connected to the kinematic means (8) for transmitting to the connecting means (3, 5) a mutual approaching elastic force generated by said first elastic means (7); the at least one friction means (9) is fixed to a member of the kinematic means (8) and a first side portion (13) of friction means (9) slides onto at least one among the connecting means (3, 5) or an element fixed to one of them, and a second side portion (15) of the friction means (9), at least in correspondence of at least one predetermined rotation arc of the device (1), slides onto an at least one contact means (11); said device (1) being characterized in that the kinematic means (8) includes a rack means (10) elastically actuated by the first elastic means (7) and it includes a pinion means (12) constrained to axially rotate around a respective first pin (14) connected to the second connecting means (5); wherein said rack (10) and pinion (12) means are reciprocally engaged and the pinion means (12) has at least one seat (19) each for a corresponding friction means (9) whose first side portion (13) contacts the first connecting means (3) or an element fixed to it and whose second side portion (15), opposite to the first (13), slides, in correspondence of the at least one predetermined arc, onto the contact means (11) fixed to the first connecting means (3); each seat (19) is a shaped slot obtained in the pinion means (12) and each friction means (9) is a body that is approximately flat and shaped in a complementary way in respect to the respective seat (19); the kinematic means (8) includes moreover a hinge second pin (4) for the mutual revolving connection of the first (3) and second (5) connecting means; the device further includes an arm means (16) whose ends are connected by means of respective third (17) and fourth (18) connecting pins respectively to the pinion means (12) and to the second connecting means (5).
Device according to claim 1 characterized in that the first side portion (13) of the friction means (9) and the corresponding surface of the first connecting means (3) are almost flat; the contact means (11) is approximately bridge shaped, said bridge has ends fixed at the first connecting means (3) with which defines a partial housing for the pinion means (12) and for each friction means (9); the second side portion (15) of the friction means (9) and/or the face of the contact means (11) towards the pinion means (12) have respectively jutting parts (21, 25) assigned to the mutual contact by sliding friction in correspondence with said predetermined rotational arc.
Device according to one of the claims from 1 or 2 characterized in that the jutting part (21) is almost flat and it is joined to the remaining second corresponding portion (15) of the friction means (9) by means of bevelled ends and that the jutting part (25) of the contact means (11) is facing the friction means (9).
Device according to any of the previous claims characterized in that the seat (19) has an angular extension, with respect to the pinion means (12) rotation centre, such as the surface of the seat (19) sweeps the whole surface of the contact means (11) facing towards the pinion means (12) during the device complete rotation.
Device according to any of the previous claims characterized in that the friction means (9) is made of plastic material, nylon, Teflon, or similar, also fibres reinforced.
Device according to any of the previous claims characterized in that the first rotational pin (14) of the pinion means (12) is fixed to the first connecting means (3) laying on a plane parallel to the laying planes of the second connecting means (5), the rack means (10), the pinion means (12) and the arm means (16).
Device according to claim 6 characterized in that the first (14), second (4), third (17) and fourth (18) pins are perpendicular to said laying planes; the distance between the axes of the first (14) and third (17) pins is the same or bigger then the engagement radius of the teeth of the pinion means (12) wherein such teeth are distributed on a sector of the pinion means (12) that subtends an angle ranging between about 90° and about 180°.
Device according to claim 7 c haracterized in that the distance between the axes of the second (4) and fourth (18) pins is between half and double, preferably approximately the same, of the distance between the axes of first (14) and third (17) pins; wherein said pins (14, 4, 17, 18) are placed to the vertices of a quadrilateral preferably a parallelogram.
Device according to claim 8 characterized in that the rack means (10) is constrained to slide along its longitudinal axis by sliding means (20); the sliding means (20) include at least a concave guide having “U” shaped cross-section
Device according to claim 9 characterized in that the rack means (10) is elastically actuated by the first elastic means (7) by means of a tie-rod means (22); the first elastic means (7) are compressed helical spring types with engageable ends in contacts (23, 24) respectively of the first connecting means (3) and of the tie-rod means (22).