WO2019110188A1

WO2019110188A1 - Lock for a motor vehicle door and/or lid with return springs

Info

Publication number: WO2019110188A1
Application number: PCT/EP2018/078783
Authority: WO
Inventors: Marco Scocco
Original assignee: Cebi Italy S.P.A.
Priority date: 2017-12-07
Filing date: 2018-10-19
Publication date: 2019-06-13

Abstract

A lock (100) for a motor vehicle door and/or lid comprises: a catch (1) intended to engage a striker fixed to the body of the vehicle, a pawl (2) that acts on the catch (1) to lock the catch; an actuation lever (6) intended to actuate the pawl (2) and the catch (1), an actuator (3) that moves said actuation lever (6) by means of a transmission (T) comprising: a first gear (4), an intermediate gear (8), a second gear (9) and a connection lever (5) connected to the second gear (9) and to the actuation lever (6). A first return spring (85) is disposed between the box of the lock and the intermediate gear (8), and a second return spring (95) is disposed between the box of the lock and the second gear (9).

Description

LOCK FOR A MOTOR VEHICLE DOOR AND/OR LID WITH RETURN

SPRINGS

The present patent application for industrial invention relates to a lock for motor vehicle door and/or lid, in particular for the trunk of a motor vehicle.

Various types of locks for motor vehicle doors and/or lids are known on the market. Said locks comprise a catch that engages a“U”- shaped striker fixed to the body of the vehicle.

The catch is actuated by an electrical motor by means of a transmission with gears and levers. A stop lever, which is normally known as“pawl”, engages the catch in order to lock the catch in closing position In such a type of locks, if the motor is blocked, the catch is blocked in closing position by the pawl and the lock cannot be opened.

In order to remedy such a drawback, locks with two motors are known: a big motor to actuate the gears and the levers that are used to actuate the catch, and a small motor to actuate the pawl. Obviously, such locks are cumbersome and expensive because they are provided with two motors. Moreover, if the big motor is locked, also the catch is locked. In fact, the actuation of the small motor releases the pawl, but not the catch, which remains locked. Several systems are known to release the catch by disconnecting the transmission or by disconnecting the levers.

Such a drawback is partially solved by locks provided with only one motor with epicycloidal reduction gear and with an emergency release system that provides for manually actuating a lever that is translated to unlock the epicycloidal reduction gear of the motor and permit the rotation of the catch in the opening position. However, such an emergency release system is complicated and cumbersome because of the presence of several lever mechanisms. Moreover, such an emergency release system is difficult to be actuated by the user, who needs to disengage the pawl from the catch and then actuate the catch.

Moreover, locks are known, which are provided with an emergency opening device with a first lever that is removably fastened to the actuation lever, and a second lever that cooperates with the first lever and actuates the pawl to release the pawl from the locking position wherein it locks the catch. In view of the above, the emergency opening device not only opens the lock, but also uncouples the electrical motor. However, for a correct operation of said lock, it is necessary to provide an electrical engine that is capable of inverting the direction of rotation. The control of such a type of electrical motor by means of the electronic control unit (ECU) of the vehicle is complicated because it is necessary to control the position of the gear connected to the engine by means of position detection means, such an additional lever or a microswitch.

Furthermore, in the locks of the prior art, the direction of rotation of the motor must be inverted at every opening and closing cycle of the lock in order to reset the gears to the initial position. Such an inversion of the direction of rotation considerably complicates the control of the engine by the ECU.

The purpose of the present invention is to eliminate the drawbacks of the prior art by providing a lock for a vehicle door and/or lid that is reliable and easy to release when the motor of the lock if blocked, avoiding the use of a complicated mechanism for emergency opening.

Another purpose of the present invention is to disclose such a lock for a vehicle door and/or lid that has a limited number of parts, is not cumbersome and is easy to make, assemble and control.

These purposes are achieved according to the invention with the characteristics of the independent claim 1.

Advantageous embodiments of the invention appear from the dependent claims.

The lock for a motor vehicle door and/or lid according to the invention comprises: - a catch hinged to a box of the lock, around a pivoting axis, said catch comprising a slot intended to engage a striker fixed to the body of the vehicle,

- a pawl hinged to the box of the lock around a pivoting axis and acting on said catch to lock the catch in closing position;

- an actuation lever intended to actuate said pawl and said catch, and

- an actuator that moves said actuation lever by means of a transmission.

The transmission comprises:

- a first gear driven into rotation by said actuator,

- a second gear moved by the first gear, and

- a connection lever connected to the second gear and to the actuation lever.

The lock also comprises:

- first spring means arranged in such a way to be loaded when the actuator is actuated in an opening travel of the lock, and unloaded when the opening travel ends, in order to reset the gears to an initial position, and

- second spring means arranged in such a way to be loaded when the actuator is actuated in a closing travel of the lock, and unloaded when the closing travel ends, in order to reset the gears to an initial position.

Additional features of the invention will appear manifest from the detailed description below, which refers to merely a illustrative, not limiting embodiment, as illustrated in the attached figures, wherein:

Figs. 1 and 1 A are two perspective views, taken from different angles, which show the lock of the invention in opening position;

Figs. 2 and 2A are two perspective views, taken from different angles, which show the lock of the invention in temporary closing position; Figs. 3 and 3A are two perspective views, taken from different angles, which show the lock of the invention in permanent closing position;

Figs. 4 and 4A are two perspective views, taken from different angles, which show the lock of the invention during the opening step.

With reference to the Figures, the lock of the invention is disclosed, which is generally indicated with reference numeral (100).

With reference to Figs. 1 and 1 A, the lock (100) comprises a catch (1 ) intended to engage a“U”-shaped striker (B). The striker (B) is fixed to the body of the vehicle. Instead, the lock (100) is disposed in a box or a casing fixed to the door and/or lid of the vehicle.

The body (10) of the catch (1 ) is shaped as a plate and is provided with a“U”-shaped slot (1 1 ) intended to engage the striker (B).

A pivoting hole (12) is obtained in the body (10) of the catch for pivoting the catch in the box that contains the lock, around a pivoting axis (Y1 ).

The catch (1 ) comprises an arm (13) that extends in substantially orthogonal direction relative to the direction of the slot (1 1 ). The arm (13) is intended to actuate the catch. The arm (13) ends with a tooth (16) provided with a rounded end.

A locking tooth (14) is disposed in one edge of the slot (11 ). A positioning tooth (15) is disposed on one edge of the body of the catch, outside the slot.

The catch is stressed towards a closing position by a spring.

A stop lever or pawl (2) cooperates with the catch (1 ) to lock the catch in closing position,

The pawl (2) has a rod-shaped body (20). A pivoting hole (21 ) is obtained in one first end of the body (20) in order to pivot the pawl to the box of the lock with a pivoting axis (Y2) parallel to the pivoting axis (Y1 ) of the catch.

An actuation projection (22) protrudes from a second end of the body (20). A stop tooth (23) protrudes from the body (20) in intermediate position between the pivoting hole (21 ) and the actuation projection (22). The stop tooth (23) faces the catch (1 ). A spring (not shown) stresses the pawl (2) towards the catch (1 ).

In Fig. 2, the stop tooth (23) of the pawl is stopped against the positioning tooth (15) of the catch. In Fig.3, the stop tooth (23) of the pawl is stopped against the locking tooth (14) of the catch.

An arm (24) projects from the pawl towards the catch and ends with a follower (25) suitable for cooperating with a cam (17) shaped as an arched projection that projects from the body of the catch (1 ).

An actuation lever (6) actuates the catch (1 ) and the pawl. The actuation lever (6) is actuated by means of an actuator (3) and a transmission (T). The transmission (T) comprises a first gear (4), an intermediate gear (8), a second gear (9) and a connection lever (5). The actuator (3) comprises a geared motor (30) with an output shaft (31 ) whereon a worm screw (32) that engages the first gear (4) is mounted.

The first gear (4) comprises a toothed wheel provided with a first toothing (40) suitable for engaging with the worm screw (32). The first gear (4) has an axis of rotation (X1 ) that is inclined relative to the pivoting axes (Y1 , Y2) of the catch and the pawl. Said inclination can be approximately 120°.

The first gear (4) is a double-toothed gear and comprises a second toothing (42) splined on the rotational shaft of the first gear. The axis of rotation of the second toothing (42) of the first gear coincides with the axis of rotation (X1 ) of the first gear. The second toothing (42) of the first gear has a radius of the pitch circle that is lower than the radius of the pitch circle of the first toothing (40) of the first gear. The radius of the pitch circle of the second toothing (42) is lower than half of the radius of the pitch circle of the first toothing (40).

The intermediate gear (8) is hinged to the box of the lock with an axis of rotation (X2) that is parallel to the axis of rotation (X1 ) of the first gear (4). The intermediate gear (8) has a first toothing (80) that engages the second toothing (42) of the first gear. The intermediate gear (8) is a double-toothed gear and comprises a second toothing (82) splined on the rotational shaft of the intermediate gear. The axis of rotation of the second toothing (82) of the intermediate gear coincides with the axis of rotation (X2) of the intermediate gear. The second toothing (82) of the intermediate gear has a radius of the pitch circle that is lower than the radius of the pitch circle of the first toothing (80) of the intermediate gear. The radius of the pitch circle of the second toothing (82) is lower than half of the radius of the pitch circle of the first toothing (80) of the intermediate gear. The radius of the pitch circle of the first toothing (80) of the intermediate gear is higher than the radius of the pitch circle of the first toothing (40) of the first gear.

The second gear (9) is hinged to the box of the lock with an axis of rotation (X3) that is parallel to the axis of rotation (X1 ) of the first gear (4). The second gear (9) has a toothing (90) that extends for an arch of circle of approximately 90°-120°. The toothing (90) of the second gear engages the second toothing (82) of the intermediate gear (8).

In view of the above, the second gear (9) is moved in the same direction as the first gear (4). Instead, the intermediate gear (8) is moved in a different direction compared to the first and the second gear.

The radius of the pitch circle of the toothing (90) of the second gear is higher than the radius of the pitch circle of the first toothing (80) of the intermediate gear.

A pivoting tab (91 ) projects from one side of the second gear, in peripheral position relative to the axis of rotation (X3) of the second gear. The pivoting tab (91 ) is hinged at one first end of the connection lever (5) with a pivoting axis (X4) that is parallel to the axes of rotation (X1 , X2, X3) of the three gears.

The connection lever (5) is a straight rod provided with a first fork (50) at a first end, and with a second fork (51 ) at a second end. The first fork (50) of the connection lever is hinged with the pivoting tab (91 ) of the second gear. The actuation lever (6) has a body (60) provided with a first end with a pivoting pin (61 ) and a second end with an actuation tooth (62). The pivoting pin (61 ) is used to hinge the actuation lever to the box of the lock with a pivoting axis (X5) that is parallel to the axes of rotation (X1 , X2, X3) of the three gears. The actuation tooth (62) faces the pawl (2) and the catch (1 ) in order to actuate the pawl and the catch. In particular, the actuation tooth (62) is disposed between the arm (13) of the catch and the actuation projection (22) of the pawl. The actuation tooth (62) of the actuation lever is suitable for being stopped against the arm (13) of the catch, in order to move the catch against the actuation projection (22) of the pawl in order to move the pawl.

The body (60) of the actuation lever is arched with concavity that faces the second gear (9).

A pivoting tab (63) centrally protrudes from the body (60) of the actuation lever in order to be pivoted in the second fork (51 ) of the connection lever, with a pivoting axis (X6) parallel to the axes of rotation (X1 ) of the three gears and inclined relative to the pivoting axis (Y1 ) of the catch.

A first return spring (85) is mounted in the intermediate gear (8). The first return spring (85) is a helical spring disposed around the axis of rotation (X2) of the intermediate gear (8). The first return spring (95) has a first end (86) that is fixed to the box of the lock, and a second end (87) that faces a rib (84) of the intermediate gear that protrudes radially from the center of the intermediate gear.

A second return spring (95) is mounted in the second gear (9). The second return spring (95) is a helical spring disposed around the axis (X3) of the second gear. The second return spring (95) has a first end (96) that is fixed to the box of the lock, and a second end (97) that faces an edge (94) of the intermediate gear that protrudes radially from the center of the intermediate gear.

Although three gears (4, 8, 9) are shown in the figures, the intermediate gear (8) is optional and can be omitted. In fact, the intermediate gear (8) has been added to improve the transmission ratio of the gear train. In this case, the first return spring (85) can directly actuate the second gear (9) in such a way to push the second gear in opposite direction relative to the pushing direction of the second return spring (95).

Although the figures show two separate return springs (85, 86), a single return spring can be provided and fixed to the box, having two ends that cooperate with the second gear (9) in such a way to push the second gear in a first direction at the end of the opening travel and to push the second gear in a second direction opposite to the first direction at the end of the closing travel.

Following is a description of the operation of the lock (100).

With reference to Figs.1 and 1A, initially the lock is in an open position, wherein the catch (1 ) does not engage the striker. The first return spring (85) is loaded and the second return spring (95) is unloaded.

The actuation tooth (62) of the actuation lever (6) holds the pawl (2) in such a way that the tooth (23) of the pawl (2) does not interfere with the catch (1 ). When the lid and/or door is closed, the catch (1 ) is stopped against the striker. Therefore, the catch (1 ), which is pushed by its spring, rotates towards the closing position in such a way that the striker engages the slot (1 1 ) of the catch, as shown in Figs.2 and 2A. During said movement of the catch, the cam (17) of the catch slides relative to the follower (25) of the pawl.

With reference to Figs. 2 and 2A, the stop tooth (23) of the pawl is stopped against the positioning tooth (15) of the catch. In such a situation, there is provided a first temporary closing of the lock.

For the permanent closing of the lock, the actuator (3) is actuated, making the shaft of the geared motor rotate in a closing direction in such a way as to make the gears (4, 8, 9) rotate in the directions of the arrows (F1 , F2, F3), respectively.

During said movement of the gears (4, 8, 9) in the closing travel, the first return spring (85) is unloaded, favoring the movement of the intermediate gear (8) in the direction of the arrow (F2) and the second return spring (95) is loaded.

The rotation of the second gear (9) in the direction of the arrow (F3) determines a movement of the connection lever (5) in the direction of the arrow (F4). Therefore, the connection lever (5) drags the actuation lever (6) in such a way that the actuation tooth (62) of the actuation lever is moved closer to the arm (13) of the catch, releasing the pawl (2).

With reference to Figs. 3 and 3A, the actuation tooth (62) of the actuation lever is stopped against the arm (13) of the catch, making the catch (1 ) rotate around its pivoting axis (Y1 ) towards a permanent closing position wherein the slot (1 1 ) of the catch engages the striker.

The stop tooth (23) of the pawl slides on the edge of the catch and is stopped against the stop tooth (14) of the catch, locking the catch in permanent closing position. In such a situation the lock cannot be opened.

If the actuator (3) operates properly, the opening of the lock (100) is made by means of the actuator (3), making the shaft (31 ) of the geared motor rotate in opposite direction relative to the closing direction. In view of the above, the gears (4, 8, 9) rotate in the directions of the arrows (P1 , P2, P3), respectively. The actuator (3) is actuated by means of the electronic control unit (ECU) of the vehicle.

During said movement of the gears (4, 8, 9), the first return spring (85) is loaded and the second return spring (95) is unloaded, favoring the movement of the second gear (9) in the direction of the arrow (P3).

The rotation of the second gear (9) in the direction of the arrow

(P3) determines a movement of the connection lever (5) in the direction of the arrow (P4). Therefore, the connection lever (5) drags the actuation lever (6) that rotates around its axis (X5) in such a way that the actuation tooth (62) of the actuation lever is moved farther from the arm (13) of the catch, and is moved closer to the actuation projection (22) of the pawl (2).

With reference to Figs. 4 and 4A, the actuation tooth (62) of the actuation lever is stopped against the actuation projection (22) of the pawl, making the pawl rotate around its axis (Y2), in such a way that the stop tooth (23) of the pawl is disengaged from the locking tooth (14) of the catch, releasing the catch and permitting the opening of the lock.

With reference to Figs. 3 and 3A, if the lock is in closing position and the actuator (3) does not work or is blocked, the pawl (2) can be actuated manually to open the lock. Instead, in the locks of the prior art, an emergency device was necessary to release the pawl in case of a motor failure.

The advantage of the return springs (85, 95) consists in the fact that the catch (1 ) is always free of mechanical constraints, because the transmission (T) is reset to the initial position by the return springs (85, 95) at the end of the closing cycle and at the end of the opening cycle.

The second return spring (95) resets the transmission to the initial position at the end of the closing cycle. The first return spring (85) resets the transmission to the initial position at the end of the opening cycle.

The follower (25) of the pawl and the cam (17) of the catch form a memory system to prevent the return of the pawl (2) if the catch (1 ) has not rotated completely.

The electrical motor of the actuator (3) is powered for a sufficiently long time to guarantee that the drive shaft (31 ) makes a complete travel until a stall position.

It must be considered that in the locks of the prior art, the electrical motor needs to be inverted at every cycle to reset the gears to the initial position. Instead, in the lock (100) of the invention, because of the provision of the return springs (85, 95), the electrical motor of the actuator (3) does not need to be inverted at every cycle to reset the gears to the initial position. In fact, after the closing cycle, the second return spring (95) is loaded and resets the gears to the initial position, without inverting the direction of rotation of the engine. After the opening cycle, the first return spring (85) is loaded and resets the gears to the initial position, without inverting the direction of rotation of the engine. Obviously, in such a case, the management of the electrical motor of the actuator is much simpler because it is not necessary to invert the direction of rotation of the motor to reset the gears to the initial position.

Numerous variations and modifications can be made to the present embodiment of the invention, which are within the reach of an expert of the field, and in any case fall within the scope of the invention.

Claims

1.Lock (100) for motor vehicle door and/or lid comprising:

- a catch (1 ) hinged to a box of the lock, around a pivoting axis (Y1 ), said catch (1 ) comprising a slot (1 1 ) intended to engage a striker fixed to the body of the vehicle,

- a pawl (2) hinged to the box of the lock around a pivoting axis

(Y2) and acting on said catch (1 ) to lock the catch in closing position,

- an actuation lever (6) intended to actuate said pawl (2) and said catch (1 ), and

- an actuator (3) that moves said actuation lever (6) by means of a transmission (T),

wherein said transmission (T) comprises:

- a first gear (4) driven into rotation by said actuator (3),

- a second gear (9) moved by said first gear, and

- a connection lever (5) connected to the second gear (9) and to the actuation lever (6);

wherein said lock also comprises:

- first spring means (85) arranged in such a way to be loaded when the actuator is actuated in an opening travel of the lock and unloaded when the opening travel ends, in order to reset the first and the second gear to an initial position, and

- second spring means (95) arranged in such a way to be loaded when the actuator is actuated in a closing travel of the lock and unloaded when the closing travel ends, to reset the first and the second gear in an initial position.

2. The lock (100) of claim 1 , wherein said actuation lever (6) is hinged to the box of the lock in a pivoting axis (X5) that is inclined relative to the pivoting axis (Y1 ) of the catch and said first and said second gear (4, 9) are hinged to said box of the lock in axes of rotation (X1 , X3) that are parallel to said pivoting axis (X5) of the actuation lever.

3. The lock (100) of claim 2, wherein said connection lever (5) comprises a first fork (50) and a second fork (52) disposed at the ends of said connection lever and respectively hinged to a pivoting tab (91 ) of said second gear and to a pivoting tab (63) of said actuation lever (6).

4. The lock (100) of any one of the preceding claims, wherein said actuator (3) is a geared motor (30) having an output shaft (31 ) with a worm screw (32) that engages said first gear (4).

5. The lock (100) of any one of the preceding claims, comprising an intermediate gear (8) that engages said first gear (4) and said second gear (9).

6. The lock (100) of claim 5, when depending on claim 4, wherein the first gear (4) is a double-toothed gear comprising a first toothing (40) that engages said worm screw (32) and a second toothing (42) that engages said intermediate gear (8); and

said intermediate gear (8) is a double-toothed gear comprising a first toothing (80) that engages said second toothing (42) of the first gear and a second toothing (82) that engages said second gear (9).

7. The lock (100) of claim 6, wherein

the radius of the pitch circle of the second toothing (42) of the first gear is lower than the radius of the pitch circle of the first toothing (40) of the first gear,

the radius of the pitch circle of the second toothing (82) of the intermediate gear is lower than the radius of the pitch circle of the first toothing (80) of the intermediate gear, the radius of the pitch circle of the first toothing (80) of the intermediate gear is higher than the radius of the pitch circle of the first toothing (40) of the first gear, and the radius of the pitch circle of the toothing (90) of the second gear is higher than the radius of the pitch circle of the first toothing (80) of the intermediate gear.

8. The lock (100) of any one of the preceding claims, wherein - the first spring means (85) consist in a first return spring disposed between said box of the lock and said intermediate gear (8), and - the second spring means (95) consist in a second return spring disposed between said box of the lock and said second gear (9).

9. The lock (100) of claim 8, wherein said first spring means (85) are a helical spring disposed around the axis (X2) of the intermediate gear (8); said helical spring having a first end (86) that is fixed to the box of the lock and a second end (87) that faces a rib (84) of the intermediate gear that protrudes radially from the center of the intermediate gear.

10. The lock (100) of claim 8 or 9, wherein said second spring means (95) are a helical spring disposed around the axis (X3) of the second gear (8); said helical spring having a first end (96) that is fixed to the box of the lock and a second end (97) that faces an edge (94) of the intermediate gear that protrudes radially from the center of the intermediate gear.