Car door leaf latch opening and closing mechanism

Abstract

The present invention relates to a mechanism for assisting in opening and closing a latch (10), comprising an electric actuator (16) for controlling the opening and closing of the latch (12). The electric actuator (16) is associated with a reducer (161) having a drive means (18). The drive means (18) is configured to perform a displacement stroke including a first stroke portion for opening the latch (12) and a second stroke portion for closing the latch (12). The reducer (161) has a first reduction ratio at the first stroke portion and a second reduction ratio at the second stroke portion, the first reduction ratio being different from the second reduction ratio and preferably smaller than the second reduction ratio.

Description

Technical Field

[0001] The present invention relates to the field of latches for automotive door leaves, and particularly to the field of latches for vehicle openings such as tailgates, trunks, or side doors of automobiles.

Background Art

[0002] An automotive door leaf is movable between an open position and a closed position of the door leaf. This door leaf generally includes a latch that is movable between its open position and its closed position. When the latch is in the closed position, the door leaf can be blocked in this closed position. Alternatively, when the latch is in the open position, the lock of the door leaf is released so that the door leaf can move from the closed position to the open position. With this latch, the closed position of the door leaf can also be locked and unlocked. Locking means prohibiting the opening and closing of the door. Generally, the locking / unlocking of the latch is mechanically performed by the user inserting a mechanical key, or electrically performed by a microcontroller that controls the latch via a "clip" of the key or the like. In this case, for example, the memory of the microcontroller stores the locked state.

[0003] More specifically, the transition of the door leaf from the open position to the closed position includes the following steps. - A step of moving the door leaf toward the vehicle frame, and - A step of closing the latch by which the door leaf is fixed to the frame. Furthermore, the transition of the door leaf from the closed position to the open position includes the following steps. - A step of opening the latch by which the door leaf is removed from the frame, and - A step of separating the door leaf from the vehicle frame. An electrical mechanism for opening and closing the latch is attached to the latch so that the user can remotely control the opening and closing of the latch. The mechanism assisting in the opening and closing of the latch will also be mentioned. A latch typically includes a bolt and a pawl. The bolt is configured to move, for example, by pivoting around a striker fixed to the car's frame. The pawl is configured to allow or restrict the movement of the bolt, for example, by the operation of a door leaf handle. The bolt is movable in one direction to securely close the latch and can move in the opposite direction to release the latch. [Overview of the project] [Problems that the invention aims to solve]

[0004] The mechanism that assists in opening and closing the latch generally includes an electric actuator, which is configured to allow or prohibit the movement of a bolt to enable the latch to close, and to allow or prohibit the movement of a claw to enable the latch to open. More specifically, known electric actuators comprise a first electric actuator specifically for opening a latch, configured to electrically actuate a claw, and a second electric actuator specifically for closing the latch, configured to electrically actuate a bolt. Thus, these latch opening and closing assist mechanisms are large and have complex kinematics.

[0005] A known solution involves manufacturing an auxiliary mechanism for opening and closing the latch, which has a single electric actuator that performs both the function of opening and closing the latch. However, the power required to open the latch is different from the power required to close it. In practice, high torque is required when closing, and a fast speed is required when opening. To increase the torque, a reduction gear is placed in the electric actuator, which is called a geared motor. Thus, these known solutions have the disadvantage of being speed-limited.

[0006] The object of the present invention is to propose a mechanism for assisting the opening and closing of a door leaf latch that can overcome all or part of the drawbacks of the aforementioned prior art. [Means for solving the problem]

[0007] The mechanism for assisting the opening and closing of a door leaf latch according to the present invention comprises an electric actuator configured to control the opening and closing of the latch, The electric actuator is associated with a reduction gear, This gearbox includes a drive mechanism configured to perform a displacement stroke including a first stroke portion for opening the latch and a second stroke portion for closing the latch. The reduction gear has a first reduction ratio in the first stroke portion and a second reduction ratio in the second stroke portion. The first reduction ratio is different from the second reduction ratio. In other words, the opening and closing assist mechanism of the present invention comprises a reduction gear having a first reduction ratio when the electric actuator controls the opening of the latch and a second reduction ratio when the electric actuator controls the closing of the latch, wherein the first reduction ratio is different from the second reduction ratio. The reduction ratio should be understood as the ratio of the speed of the output operation of the reduction gear to the speed of the input operation of the actuator. Therefore, the opening and closing assist mechanism according to the present invention minimizes bulk. Furthermore, the availability of the latch opening and closing function is improved, and the kinematics become immediately available. In fact, the kinematics for operating the latch opening and closing chain are the same; only the gearbox differs.

[0008] According to another feature of the present invention, the opening and closing assisting mechanism includes one or more of the following features, individually or in all possible combinations: According to one feature of the present invention, when the drive means performs a first stroke portion, the reduction gear is configured to generate a first torque, and when the drive means performs a second stroke portion, the reduction gear is configured to generate a second torque, the second torque being greater than the first torque. The ratio of the first torque to the second torque is between 3 and 5. The ratio of the first torque to the second torque is 4.

[0009] According to one feature of the present invention, when the drive means executes a first stroke portion, the reduction gear is configured to generate a first speed, and when the drive means executes a second stroke portion, the reduction gear is configured to generate a second speed, wherein the first speed is faster than the second speed. The ratio of the first speed to the second speed is inversely proportional to the ratio of the first torque to the second torque. The ratio of the second speed to the first speed can be set between 3 and 5. The ratio of the second speed to the first speed is 4. According to one feature of the present invention, the first stroke portion is executed in a first displacement direction, and the second stroke portion is executed in a second displacement direction opposite to the first displacement direction. Alternatively, the first stroke portion and the second stroke portion are executed in the same displacement direction. According to one feature of the present invention, the first reduction ratio is smaller than the second reduction ratio. Therefore, high torque is provided for the closing function and high speed is provided for the opening function.

[0010] In one embodiment of the present invention, the reduction gear includes a first lever arm whose displacement is controlled by the driving means when the driving means executes the first stroke portion, and a second lever arm whose displacement is controlled by the driving means when the driving means executes the second stroke portion. According to another feature of the present invention, the second lever arm is shorter than the first lever arm. Therefore, the reduction ratio of the first lever arm is smaller, generating the displacement velocity. Instead, the second lever arm can generate torque. According to one feature of the present invention, the driving means is a wheel. According to one feature of the present invention, the reduction gear includes a transmission means that is driven by the driving means and configured to drive the first and second lever arms. The driving means may be a wheel whose rotation is the displacement stroke. The transmission means may be a wheel whose rotation is the displacement stroke. The second lever arm can be positioned on the transmission means such that the transmission means has an axis of rotation that coincides with the second axis of rotation of the second lever arm. Thus, the kinematics of the auxiliary mechanism can be simplified, and its kinematics can be applied to supplying different forces between the closing and opening of the latch.

[0011] According to one feature of the present invention, the transmission means comprises a pin arranged in the axial direction of the transmission means, and the first lever arm comprises a gate configured to be driven by the pin when the drive means performs the first stroke portion. According to one feature of the present invention, the transmission means is a wheel that forms a gear assembly with the driving means. According to one feature of the present invention, the pin is configured to pass from the first side of the gate to the second side of the gate when the drive means executes the first stroke portion. Thus, the pin is configured to pass from the first side of the gate to the second side of the gate after driving the first lever arm to enable the opening of the latch.

[0012] According to one feature of the present invention, the pin is configured to pass from the second side of the gate to the first side of the gate when the drive means executes the third stroke portion. In this way, when the drive means executes the first stroke portion, the pin is again ready to drive the first lever arm through the gate. Next, we will discuss the reset of the opening and closing mechanism. This reset is performed automatically, thus avoiding further operation using switches or the like. This can occur at any time during the opening and closing cycle of the latch. According to one feature of the present invention, the latch includes a bolt and a pawl that are movable between an open position and a closed position of the latch. The first lever arm is configured to drive the pawl at the open position of the latch, and the second lever arm is configured to drive the bolt at the closed position of the latch.

[0013] In another embodiment of the present invention, the speed reducer includes a planetary gear train. According to this embodiment, the speed reducer includes an output shaft whose displacement is controlled by the drive means when the drive means executes the first stroke portion. When the drive means executes the second stroke portion, the first stroke portion corresponds to a displacement in a first displacement direction, and the second stroke portion corresponds to a displacement in a second displacement direction opposite to the first displacement direction. According to one feature of the present invention, the latch includes a bolt and a pawl that are movable between an open position and a closed position of the latch. The output shaft is configured to drive the bolt to the closed position of the latch when the drive means operates, a second stroke portion, and when the drive means executes the first stroke portion, the output shaft is configured to drive the pawl to the open position of the latch. The output shaft corresponds to one lever arm.

[0014] According to one feature of the present invention, the planetary gear train includes a first stage such as a planetary carrier and a second stage such as a satellite gear. When the driving means executes the second stroke portion, the output shaft is displaced and controlled by the driving means via the second stage in order to generate the second torque for closing the latch. Therefore, the second stage is a transmission means that is driven by the driving means and drives the output shaft when the driving means executes the second stroke portion. The first stroke portion can be executed in a first rotational direction, and the second stroke portion can be executed in a second rotational direction opposite to the first rotational direction. The first torque and the second torque may be the first torque and the second torque generated, for example, by the output shaft by the planetary gear train. According to one feature of the present invention, in order to generate the first speed that enables the latch to be opened, the first stage is configured to be locked when the driving means executes the second stroke portion, and the second stage is configured to be locked when the driving means executes the first stroke portion.

[0015] The planetary gear train may include one such first stage. For example, it can include one such planetary carrier and one such second stage, for example, one such planetary gear. In the first stage, one rotation axis, for example, a first rotation axis can be provided. The rotation of the first stage around the first rotation axis is allowed in the first rotational direction around the first rotation axis and is blocked in a second rotational direction opposite to the first rotational direction around the first rotation axis. The second stage has a rotation axis, for example, a second rotation axis, and the rotation of the second stage is allowed in the first rotational direction around the second rotation axis and is blocked in a second rotational direction around the second rotation axis opposite to the first rotational direction around the second rotation axis. Therefore, it is possible to simplify the kinematics of the auxiliary mechanism, and this kinematics is applied to the supply of the different forces between the closing and the opening of the latch.

[0016] The first rotational direction around the first rotation axis and the first rotational direction around the second rotation axis can be the same rotational direction. The second rotational direction around the first rotation axis and the second rotational direction around the second rotation axis can be the same rotational direction. Thus, the kinematics of the auxiliary mechanism can be further simplified, and this kinematics can be applied to the supply of the different forces between the closing and opening of the latch.

[0017] The present invention also, - The aforementioned mechanism assists in opening and closing, - A latch comprising a bolt and a claw that are movable between the open position and the closed position of the latch, The drive means is configured to drive the bolt to the closed position of the latch when the drive means executes the second stroke portion. The drive means is configured to drive the claw to the open position of the latch when the drive means performs the first stroke portion. The present invention further relates to a door leaf and an automobile, including the aforementioned latch. Other features and advantages of the present invention will become apparent upon reading the following description and examining the accompanying drawings. [Brief explanation of the drawing]

[0018] [Figure 1] This is a partial schematic diagram, viewed from the first side, of a mechanism that assists in opening and closing the latch of a door leaf according to the first embodiment of the present invention. [Figure 2] This is a schematic diagram of a part of the opening and closing assist mechanism shown in Figure 1, viewed from above. [Figure 3] Figure 1 is a schematic partial view of a part of the opening and closing assist mechanism, seen from the second side opposite to the first side, illustrating the operation of opening the latch. [Figure 4] Figure 3 is a schematic diagram of the opening and closing assist mechanism, showing the continuation of the latch opening operation. [Figure 5]Figure 4 is a schematic perspective view of the opening / closing assist mechanism, showing the continuation of the latch opening operation. [Figure 6] Figure 3 is a schematic diagram of a part of the opening and closing assist mechanism, showing the step of opening the latch. [Figure 7] Figure 1 is a schematic partial view of a part of the opening and closing assist mechanism, seen from the second side opposite to the first side, illustrating the operation of closing the latch. [Figure 8] Figure 7 is a schematic diagram of the opening and closing assist mechanism, showing the continuation of the latch closing operation. [Figure 9] Figure 8 is a schematic diagram of the opening and closing assist mechanism, showing the continuation of the latch closing operation. [Figure 10] Figure 3 is a schematic diagram showing a part of the opening / closing assist mechanism, illustrating the reset operation of the opening / closing assist mechanism that enables the transition of the latch from the closed position to the open position. [Figure 11] This is a schematic diagram showing the door leaf latch opening and closing assist mechanism in the closed position according to a second embodiment of the present invention. [Figure 12] This is a schematic diagram showing the door leaf opening and closing assist mechanism according to the second embodiment of the present invention in the open position. [Figure 13] This is a schematic diagram showing the blocking means in the second embodiment. [Figure 14] This is a schematic diagram of a door leaf equipped with a latch, including an auxiliary mechanism for opening and closing the latch according to the present invention, in this case a tailgate. [Modes for carrying out the invention]

[0019] Figures 1 to 10 show an opening and closing assist mechanism 10 for a latch 12 for an automobile door leaf 100 (see Figure 14), according to a first embodiment of the present invention. The latch 12 (partially shown) is incorporated into, for example, a housing 14, partially shown in Figure 1. The latch 12 is movable between a closed position (Figure 6) and an open position (Figure 8). When the latch 12 is in the closed position, it blocks the door leaf 100 in the closed position. Alternatively, when the latch 12 is in the open position, it releases the door leaf 100, allowing it to move from the closed position to the open position. The latch 12 may be an electrical latch. The latch 12 includes a bolt 121 and a claw 122 that are movable between the closed position of the latch (see Figure 6) and the open position of the latch (see Figure 8).

[0020] Furthermore, the opening / closing assist mechanism 10 includes an electric actuator 16 that controls the opening and closing of the latch 12. The actuator 16 is associated with a reduction gear 161, which includes a drive means 18 configured to perform a single displacement stroke, comprising a first stroke portion for opening the latch and a second stroke portion for closing the latch. The opening / closing assist mechanism 10 includes an electric actuator 16 and a reduction gear 161. The gearbox 161 has a first reduction ratio for opening the latch 12, i.e., in the first stroke portion, and a second reduction ratio for closing the latch 12, i.e., in the second stroke portion. The second reduction ratio is different from the first reduction ratio. The reduction gear 161 has a first reduction ratio when the electric actuator 16 controls the opening of the latch 12, and a second reduction ratio when the electric actuator 16 controls the closing of the latch 12. The actuator 16 is configured to control the drive means 18. In the illustrated embodiment, the actuator 16 is an electric actuator and is rotatable via the drive means 18 to control the opening and closing of the latch.

[0021] In variations not shown, the actuator may, for example, be capable of translational movement. This is referred to as a linear actuator. The opening / closing assist mechanism 10 has the function of assisting in the opening and closing of the latch 12, and the user can remotely control the opening and closing of the latch 12.

[0022] The driving means 18 may be a wheel whose rotation constitutes a displacement stroke. The first stroke portion and the second stroke portion of the drive mechanism 18 can be oriented in the same direction of movement (Figures 3 to 9). In modified examples not shown, the first stroke portion of the driving means 18 can be directed in the first displacement direction, and the second stroke portion can be directed in the second displacement direction opposite to the first displacement direction. It is advantageous for the first reduction ratio to be smaller than the second reduction ratio. This allows the torque applied to close the latch to be greater than the torque applied to open the latch, while the speed applied to open the latch to be faster than the speed applied to close the latch.

[0023] The reduction gear 161 includes at least one lever arm whose displacement is controlled by the drive means 18 as the drive means 18 performs a first stroke portion and / or a second stroke portion. This at least one lever arm can be configured to control the opening and closing of a latch. The reduction gear 161 includes a first lever arm 162 whose displacement is controlled by the drive means 18 when the drive means 18 performs a first stroke portion. Thus, when the actuator 16 controls the opening of the latch, the displacement of the first lever arm 162 is controlled. The reduction gear 161 includes a second lever arm 164 whose displacement is controlled by the drive means 18 when the drive means 18 executes a second stroke portion. Thus, when the actuator 16 controls the closing of the latch, the displacement of the second lever arm 164 is controlled. These lever arms 162 and 164 allow for a change in the reduction ratio, thereby changing the speed and torque at the output of the reducer 161.

[0024] The first lever arm 162 and the second lever arm 164 are movable. They are driven by the actuator 16 via the drive means 18. The reduction gear 161 includes a transmission means 19 configured to be driven by a drive means 18. This transmission means 19 is configured to drive a first lever arm 162 and a second lever arm 164. More specifically, in a modified example where the drive means 18 is a wheel, the first lever arm 162 is rotatable about a first axis of rotation A, and the second lever arm 164 is rotatable about a second axis of rotation B.

[0025] The transmission means 19 can be a wheel whose rotation is used as a displacement stroke. Although not shown in the diagram, in a modified configuration in which the actuator is capable of translational movement, the first lever arm and the second lever arm are capable of translational movement. The first lever arm 162 is configured to drive the claw 122 to the open position of the latch, and the second lever arm 164 is configured to drive the bolt 121 to the closed position of the latch.

[0026] As shown in Figure 1, the second lever arm 164 is shorter than the first lever arm 162. As a result, the first reduction ratio is lower than the second reduction ratio. In particular, as shown in Figure 2, the reduction gear 161 includes, for example, a first wheel 17 that is rotationally driven by the actuator via the worm screw of the actuator 16, a second wheel 18 that is rotationally driven by the pinion of the first wheel 17, and a third wheel 19 that is driven by the pinion of the second wheel 18. In this embodiment, as described above, the second wheel 18 is the driving means. Furthermore, in this embodiment, as described above, the third wheel 19 is the transmission means.

[0027] The drive means 18 may have a rotation axis that coincides with the rotation axis A of the first lever arm 162. The drive means 18 can be configured to rotate around the rotation axis A in a first rotation direction F1 (see Figures 3 to 9) and in a second rotation direction F2 (see Figure 10) opposite to the first rotation direction F1. As will be seen later, the first rotation direction F1 can correspond to the displacement direction of the drive means 18 for performing the first and second stroke portions. The second rotation direction F2 can correspond to the third stroke portion of the drive means 18, for example, to the reset of the opening / closing assist mechanism 10.

[0028] The drive means 18 can be configured to rotationally drive the first lever arm 162 to control the opening of the latch 12. The drive means 18 can be configured to rotationally drive the second lever arm 164 to control the closing of the latch 12. More specifically, the drive means 18 can be configured to drive the transmission means 19 in order to drive the first lever arm 162 and the second lever arm 164. The transmission means 19 has an axial pin 20 configured to cooperate with the gate 22 of the first lever arm 162. The first lever arm 162 is rotationally driven by the axial pin 20. The drive means 18 is configured to drive the first lever arm 162 via the pin 20 of the transmission means 19. Therefore, the drive means 18 is a means for driving the first lever arm 162. Therefore, the first lever arm 162 may have a gate 22 configured to be driven by the transmission means 19, for example, via a pin 20.

[0029] The gate 22 can be configured to be driven by the pin 20 of the transmission means 19 when the drive means 18 executes the first stroke portion. Therefore, the gate 22 can be configured to be driven by the pin 20 of the transmission means 19 when the electric actuator 16 controls the opening of the latch 12. The second lever arm 164 is positioned on the transmission means 19, for example, such that the axis of rotation of the transmission means 19 coincides with the second axis of rotation B of the second lever arm 164. The second lever arm 164 is rotationally driven by the drive means 18 via the transmission means 19. Therefore, the drive means 18 is the means for driving the second lever arm 164.

[0030] Figures 3 to 6 show the release of the latch by the electric actuator 16. A linear actuator capable of translational movement may be used instead of the electric actuator. More specifically, the actuator 16 is displacement-controlled to rotate the drive means 18 in a first rotational direction F1 about the rotation axis A. The drive means 18 then performs a first stroke to drive the first lever arm 162 from an initial position (Figure 3) to a final position (Figure 5). The first lever arm 162 can control the latch to the open position. More specifically, the first lever arm 162 displaces the claw 122 away from the bolt 121. The bolt 121 is movable so that the latch 12 can move from the closed position to the open position. The displacement of the bolt 121 that allows the latch 12 to pass from the closed position to the open position is achieved, for example, by the effect of a spring, depressurization of the door seal, or motorization of the door leaf. This displaces the door leaf 100 to the open position of the door leaf. The drive means 18 then moves the claw 122 away from the bolt 121 via the rotational motion of the first lever arm 162 driven by the pin 20. The actuator 16 is displaced so that the latch 12 opens, driving the first wheel 17, which in turn drives the second wheel 18, which in turn drives the third wheel 19. The third wheel 19 can rotate the first lever arm 162 via the pin 20. More specifically, pin 20 drives the gate 22 of the first lever arm 162 in order to drive the first lever arm 162.

[0031] Figure 6 shows in more detail the displacement of the pin 20 that drives the gate 22 of the first lever arm 162 in four steps 6a to 6d. The first three steps 6a, 6b, and 6c show that the pin 20 is positioned on the first side of the gate 22 in order to displace the gate 22. While the drive means 18 rotates in a first rotational direction F1 to perform the first stroke portion, the transmission means 19 is driven in a second rotational direction F2. Thus, the pin 20 can displace the gate 22 of the first lever arm 162 in order to drive the claw 122. During these first three steps 6a, 6b, and 6c, the first lever arm 162 moves from its initial position (Figure 3) to its final position (Figure 5). The fourth step 6d indicates that when the drive means 18 completes its first stroke portion, the pin 20 passes from the first side of the gate 22 to the second side of the gate 22. When the pin 20 is on the second side of the gate 22, the first lever arm 162 is released from contact with the pin 20 and returns to its initial position. Thus, as the first lever arm 162 moves the claw 122 away from the bolt 121, the pin 20 passes from the second side of the gate 22 and the first lever arm 162 returns to its initial position.

[0032] Figures 7 to 9 show the closing of the latch by the electric actuator 16. A linear actuator capable of translational movement may be used instead of the electric actuator. More specifically, the actuator 16 is then displacement-controlled to rotate the drive means 18 in a first rotational direction F1 about the rotation axis A. The drive means 18 then performs a second stroke portion to bring the second lever arm 164 into contact with the bolt 121. The second lever arm 164 can control the latch to the closed position. More specifically, the second lever arm 164 displaces the bolt 121 around the striker 40 so that the latch can be closed. The drive means 18 then displaces the bolt 121 via the rotational motion of the second lever arm 164. As the drive means 18 rotates in the first rotational direction F1 to perform the second stroke portion, the transmission means 19 is driven in a second rotational direction F2 to bring the second lever arm 164 into contact with the bolt 121. The bolt 121 is driven by the second lever arm 164, which allows the latch to be controlled to the closed position. More specifically, the second lever arm 164 displaces the bolt 121 to the closed position. An actuator 16 whose displacement is controlled to allow the latch 12 to close can drive a first wheel 17. This first wheel 17 drives a second wheel 18, which in turn drives a third wheel 19. The third wheel 19 can rotate a second lever arm 164.

[0033] Figure 10 shows four steps 10a to 10d for resetting the opening / closing assist mechanism, which allows the latch 12 to move from the closed end position to the open ready position. These four reset steps 10a to 10d allow the pin 20 to move from the second side of the gate 22 to the first side of the gate 22. For this purpose, the actuator 16 rotates the drive means 18 in a second rotation direction F2 opposite to the first rotation direction F1. The displacement of the drive means 18 in the second rotation direction F2 is the third stroke portion of the drive means 18. While the drive means 18 rotates in the second rotational direction F2 to perform the third stroke portion, the transmission means 19 is driven in the first rotational direction F1. Thus, the pin 20 of the transmission means 19 enters the gate 22 of the first lever arm 162 and then passes from the second side of the gate 22 to the first side of the gate 22. The pin 20 is then ready to drive the gate, thereby driving the first lever arm 162 to the pawl 122 in the open position of the latch.

[0034] This mechanical reset operation is performed automatically. This eliminates the need for additional actions, such as switches, to position the mechanism in an intermediate position between the open and closed positions. Therefore, the driving means 18 is configured to drive the first lever arm 162 and the second lever arm 164. In order for the first lever arm 162 to drive the claw 122 to the open position of the latch, the pin 20 of the transmission means 19 must be positioned on the first side of the gate 22 (Figure 7). The first and second stroke portions are executed along a first rotational direction F1. The second stroke portion is greater than the first stroke portion. In order for the second lever arm 164 to drive the bolt 121 to the closed position, the drive means 18 must perform a displacement in the first rotational direction F1 that is greater than the displacement in the first rotational direction F1. This allows the pawl 122 to be driven to the open position of the latch via the first lever arm 162. In a modified example not shown, the drive means 18 can be configured to drive the first lever arm 162, and to drive the first lever arm 162, it can be rotated around the axis of rotation A in a first rotational direction F1 (called the opening direction). This is to move the latch 12 in a second rotational direction F2, called the opening direction and the closing direction, in order to drive the second lever arm 164 to close the latch 12.

[0035] Figures 11 to 13 show a mechanism 10 for assisting the opening and closing of the latch 12 of the door leaf 100 of an automobile, according to a second embodiment. In this second embodiment, the latch 12 is incorporated into, for example, the housing 14, similar to the first embodiment. Furthermore, the latch 12 is movable between an open position and a closed position. When the latch 12 is in the closed position, it blocks the door leaf 100 in the closed position. Alternatively, when the latch 12 is in the open position, it releases the door leaf 100, allowing it to move from the closed position to the open position. The latch 12 may be an electric latch. The latch 12 includes a bolt 121 and a claw 122 that are movable between the closed position and the open position. In this second embodiment, the opening / closing assist mechanism 10 includes an electric actuator 16 that controls the opening and closing of the latch 12. The actuator 16 is associated with a reduction gear 161 which includes a drive means 38 configured to perform a displacement stroke that includes a first stroke portion for opening the latch and a second stroke portion for closing the latch.

[0036] Similar to the first embodiment, the gearbox 161 has a first reduction ratio for opening the latch 12, i.e., in the first stroke portion, and a second reduction ratio for closing the latch 12, i.e., in the second stroke portion. The second reduction ratio is different from the first reduction ratio. The gearbox 161 has the first reduction ratio when the electric actuator 16 controls the opening of the latch 12, and the second reduction ratio when the electric actuator 16 controls the closing of the latch 12. The actuator 16 is configured to control the drive means 38. It is advantageous that the first reduction ratio is smaller than the second reduction ratio. In this way, high torque is provided for closing the latch and high speed is provided for opening the latch.

[0037] This second embodiment differs from the first embodiment in that the reduction gear 161 includes a planetary gear mechanism 30. This planetary gear train 30 includes a drive means 38, also called a ring gear, and at least a first stage 32 and a second stage 34. The driving means 38 is the first pinion of a planetary gear train 30 whose displacement stroke is rotational. The driving means 38 can be configured to be rotationally driven in a first rotation direction F1 and a second rotation direction F2 opposite to the first rotation direction F1. The first stroke portion of the drive means 38 can be executed in a first rotation direction F1, and the second stroke portion can be executed in a second rotation direction F2 opposite to the first displacement direction F1.

[0038] The planetary gear train 30 includes, for example, an output shaft 31 that forms a lever arm. This output shaft 31 is displacement-controlled by the drive means 38 when the drive means 18 performs a first stroke portion and / or a second stroke portion. The output shaft 31 is displacement-controlled in a first direction when the drive means 38 performs a first stroke portion, and is displacement-controlled in a second direction when the drive means 38 performs a second stroke portion. Thus, the output shaft 31 is displacement-controlled by the drive means 38 when the drive means 38 performs the first stroke portion and when the drive means 38 performs the second stroke portion. Therefore, the drive means 38 is configured to rotationally drive the output shaft 31 in order to control the opening and closing of the latch 12.

[0039] The first stage 32 has a rotation axis C. Rotation of the first stage 32 about this rotation axis C is permitted in a first rotation direction S1, but is blocked in a second rotation direction S2 opposite to the first rotation direction. The second stage 34 has a rotation axis D. Rotation of the second stage 34 about this rotation axis D is permitted in a first rotation direction S1', but is blocked in a second rotation direction S2'. When the drive means 38 executes the second stroke portion in the second rotation direction F2 in response to the latch closing control (Figure 11), rotation of the second stage 34 in the first rotation direction S1' is permitted, and rotation of the first stage 32 in the second rotation direction S2 is prevented.

[0040] When the drive means 38 executes the first stroke portion in the first rotation direction F1 in response to the latch release control (Figure 12), rotation of the first stage 32 in the first rotation direction S1 is permitted, and rotation of the second stage 34 in the second rotation direction S2' is prevented. Here, the first rotation directions S1 and S1' correspond to the same rotation direction, for example, counterclockwise, and the second rotation directions S2 and S2' correspond to the opposite direction, for example, clockwise.

[0041] More specifically, the planetary gear train 30 comprises a planetary carrier and at least one planetary gear supported by this planetary carrier. The first stage 32 corresponds to the planetary carrier, and the second stage 34 corresponds to the planetary gear. Thus, the planetary carrier 32 can be prevented from rotating in a second rotational direction S2 around its axis of rotation C with the help of, for example, a blade brake or a first ratchet wheel 36, and the planetary gear 34 can be prevented from rotating in a second rotational direction S2' around its axis of rotation D with the help of, for example, a blade brake or a second ratchet wheel 36'. Thus, the planetary carrier 32 can be prevented from rotating in a second rotational direction S2 around its axis of rotation C by a first locking means such as a blade brake or a first ratchet wheel 36. Also, the planetary gear 34 can be prevented from rotating in a second rotational direction S2' around its axis of rotation D by a second locking means such as a blade brake or a second ratchet wheel 36'. Furthermore, the planetary gear 34 is rotatable around the rotation axis C of the planetary carrier 32.

[0042] Figure 13 shows a locking mechanism such as a ratchet wheel 36. The reduction gear 161 comprises a planetary gear mechanism 30 and first and second ratchet wheels 36. The planetary gear mechanism 30 includes, for example, a first pinion 38 that is rotationally driven by the actuator 16 via a worm screw of the actuator 16, a first planetary gear 33 and a second planetary gear 34 that are rotationally driven by the first pinion 38, a planetary carrier 32 that is rotationally driven by the first planetary gear 33 and the second planetary gear 34, and a second pinion 37 that is rotationally driven by the second planetary gear 34. As described above, in this embodiment, the first pinion 38 corresponds to the driving means as previously stated, the planetary carrier 32 corresponds to the first stage as previously stated, and the second planetary gear 34 corresponds to the second stage as previously stated.

[0043] When the actuator 16 controls the closing of the latch 12 (Figure 11), the second stage 34 is rotationally driven by the drive means 38 (via the first planetary gear 33) in the first rotational direction S1' around its axis of rotation D, as the drive means 38 executes a second stroke portion in the second rotational direction F2. Furthermore, the second stage 34 is configured to rotate the first stage 32 in the second direction S2 around its axis of rotation C. However, as mentioned above, the first stage 32 is configured to be locked from rotating in the second rotational direction S2 around its axis of rotation C. Therefore, when the actuator 16 controls the closing of the latch 12, the rotation of the first stage 32 is prevented. Next, the second stage 34 drives the output shaft 31 via the second pinion 37 to control the closing of the latch 12. The output shaft 31 can drive a bolt (not shown) to the closed position of the latch 12. Thus, when the actuator 16 controls the closing of the latch 12, the drive means 38 drives the output shaft 31 via the second stage 34.

[0044] When the actuator 16 controls the opening of the latch 12 (Figure 12), the drive means 38 performs a first stroke portion in a first rotation direction F1. In this first rotation direction F1, the drive means 38 is configured to drive the second stage 34 in a second rotation direction S2'. However, as shown above, the second stage 34 is prevented from rotating in the second rotation direction S2' around its axis of rotation D. Since the second stage 34 is prevented from rotating in the second rotation direction S2', it cannot directly drive the second pinion 37. As the drive means 38 executes the first stroke portion, the second stage 34 is prevented from rotating in the second rotation direction S2', so the second stage 34 is rotationally driven in the first rotation direction S1 around the rotation axis C of the first stage 32 via the first stage 32. In this case, the drive means 38, the first stage 32, the second stage 34 and the second pinion 37 rotate together to form a unit that drives an output shaft 31 to control the opening of the latch. This output shaft 31 can be driven to move a pawl (not shown) away from a bolt (not shown), thereby allowing the bolt to move and enabling the latch 12 to open.

[0045] When actuator 16 controls the closing of latch 12, the reduction ratio of the reducer 161 is higher than when actuator 16 controls the opening of latch 12. When the actuator 16 controls the closing of the latch 12, the torque generated by the reduction gear 161 is greater than when the actuator controls the opening of the latch 12. When actuator 16 controls the opening of latch 12, the reduction ratio of the reducer 161 is smaller than when actuator 16 controls the closing of latch 12. When actuator 16 controls the opening of latch 12, the speed generated by the reduction gear is faster than when actuator 16 controls the closing of latch 12. When the actuator 16 controls the closing of the latch 12, a high torque is provided. When the actuator 16 controls the opening of the latch 12, high speed is provided.

[0046] More specifically, Figures 11 and 12 show a planetary gear train that includes the following: That is, the planetary gear train is - A planetary carrier 32 configured such that rotation in a second rotational direction S2 around the rotation axis C is prevented, -A second pinion 37 having one tooth portion Z1, -A second planetary gear 34 is supported by a planetary carrier 32 and configured to prevent rotation in a second rotational direction S2' around its axis of rotation D, and has teeth Z2 connected to teeth Z1 of a second pinion 37, -Supported by a planetary carrier 32, a first planetary gear 33 having one tooth Z2', -A first pinion 38 having a first tooth Z3 and a second tooth Z4 connected to the tooth Z2' of the second planetary gear 34, -It includes a blade brake 36 configured to prevent rotation in a second rotational direction S2 around the rotation axis C of the planetary carrier 32 and rotation in a second rotational direction S2' around the rotation axis D of the second planetary gear 34, respectively. The second tooth Z4 of the first pinion 38 is connected to the worm screw of the actuator 16, which has one tooth Z0.

[0047] Figure 11 shows an actuator 16 that controls the closing of the latch. This actuator rotates the first teeth Z3 and the second teeth Z4 of the first pinion 38. The first teeth Z3 of the first pinion 38 drive the teeth Z2' and Z2 of the first planetary gear 33 and the second planetary gear 34, which are supported by the planetary carrier 32, in a first rotation direction S1'. Furthermore, the first and second planetary gears 33 and 34 are configured to rotate around the rotation axis C of the planetary carrier 32 in a second rotation direction S2 opposite to the first rotation direction S1' of the planetary gear 34 in order to rotate the planetary gear 34. However, the rotation of the planetary carrier 32 in the second rotation direction S2 around its rotation axis C is prevented by the blade brake 36. Therefore, the first and second planetary gears 33 and 34 do not rotate around the rotation axis C of the planetary carrier 32. The teeth Z2 of the second planetary gear 34 drive the teeth Z1 of the second pinion 37, and thus rotate the second pinion 37. The second pinion 37 then drives the output shaft 31 to control the closing of the latch 12. This output shaft 31 can drive a bolt (not shown) in the closed position of the latch.

[0048] Figure 12 shows an actuator 16 that controls the opening of the latch 12. This actuator rotates the first teeth Z3 and the second teeth Z4 of the first pinion 38. The first teeth Z3 of the first pinion 38 drive the teeth Z2' of the first satellite gear 33, attempting to drive the teeth Z2 of the second planetary gear 34 in a second rotation direction S2, opposite to the first rotation direction S1' of the planetary gear 34. However, the second planetary gear 34 is prevented from rotating in the second rotation direction S2' around its axis of rotation D by the blade brake 36. Therefore, the second planetary gear 34 does not rotate around its axis of rotation D and does not drive the teeth Z1 of the second pinion 37. Furthermore, the first planetary gear 33 and the second planetary gear 34 rotate around the rotation axis C of the planetary carrier 32 in the first rotational direction S1 of the planetary carrier 32 in order to rotate the planetary carrier 32. Thus, the first pinion 38, planetary carrier 32, planetary gears 33, 34 and the second pinion 37 rotate together to form a unit that drives the output shaft 31 to control the opening of the latch 12. This output shaft 31 can drive a pawl (not shown) when the latch 12 is in the open position.

[0049] When latch 12 is closed, the reduction ratio is calculated according to the following Willis formula.

number

[0050] Although the present invention has been described with reference to specific embodiments, it is evident that modifications and changes can be made to these examples without departing from the general scope of the invention as defined by the claims. In particular, individual features of the different embodiments illustrated / referenced can be combined in additional embodiments. Accordingly, the description and drawings should be considered illustrative rather than restrictive. [Explanation of Symbols]

[0051] 10. Opening and closing assist mechanism 12 Latch 121 volts 122 Nails 14 Housing 16 Electric Actuators 161 Reducer 162 First Lever Arm 164 Second Lever Arm 17 The first wheel 18. Drive mechanism (second wheel) 19. Means of transmission (third wheel) 20 pins Gate 22 30 Planetary gear train 31 Output shaft 32. Stage 1 (Planetary Carrier) 33 Planetary gears 34. Stage 2 (Planetary Gears) 36 Blade Brake (Ratchet Wheel) 37. Second pinion 38. First pinion (driving means) 40 Striker 100 Door Leaf

Claims

1. An opening / closing assist mechanism (10) that assists in opening and closing the latch (12) of the door leaf (100), The opening and closing assist mechanism includes an electric actuator (16) that controls the opening and closing of the latch (12). The electric actuator (16) is associated with a reduction gear (161) which has a drive means (18) configured to perform a displacement stroke. The displacement stroke includes a first stroke portion for opening the latch (12), a second stroke portion for closing the latch (12), and a third stroke portion corresponding to resetting the opening / closing assist mechanism. The reduction gear (161) has a first reduction ratio in the first stroke portion and a second reduction ratio in the second stroke portion. The first reduction ratio differs from the second reduction ratio, The reduction gear (161) includes a first lever arm (162) whose displacement is controlled by the driving means (18) when the driving means (18) executes the first stroke portion, The drive means (18) is equipped with a second lever arm (164) whose displacement is controlled by the drive means (18) when the drive means (18) executes the second stroke portion. The reduction gear (161) is driven by the driving means (18) and includes a transmission means (19) configured to drive the first lever arm (162) and the second lever arm (164). The transmission means (19) is provided with a pin (20) arranged in the axial direction of the transmission means (19), The first lever arm (162) includes a gate (22) configured to be driven by the pin (20) when the drive means (18) executes the first stroke portion, The pin (20) is configured to pass from the first side of the gate (22) to the second side of the gate (22) when the drive means (18) executes the first stroke portion. The opening and closing assist mechanism is characterized in that the pin (20) is configured to pass from the second side of the gate (22) to the first side of the gate (22) when the driving means (18) executes the third stroke portion.

2. In claim 1, When the drive means (18) executes the first stroke portion, the reduction gear (161) is configured to generate a first torque. When the drive means (18) executes the second stroke portion, the reduction gear (161) is configured to generate a second torque. An opening / closing assist mechanism characterized in that the second torque is greater than the first torque.

3. In claim 1, When the drive means (18) executes the first stroke portion, the reduction gear (161) is configured to generate a first speed. An opening / closing assist mechanism characterized in that, when the drive means (18) executes the second stroke portion, the reduction gear (161) is configured to generate a second speed, and the first speed is faster than the second speed.

4. An opening / closing assist mechanism (10) that assists in opening and closing the latch (12) of the door leaf (100), The opening and closing assist mechanism includes an electric actuator (16) that controls the opening and closing of the latch (12). The electric actuator (16) is associated with a reduction gear (161) which has a drive means (38) configured to perform a displacement stroke. The displacement stroke includes a first stroke portion for opening the latch (12) and a second stroke portion for closing the latch (12). The reduction gear (161) has a first reduction ratio in the first stroke portion and a second reduction ratio in the second stroke portion. The first reduction ratio differs from the second reduction ratio, When the drive means (38) executes the first stroke portion, the reduction gear (161) is configured to generate a first torque. When the drive means (38) executes the second stroke portion, the reduction gear (161) is configured to generate a second torque. The second torque is greater than the first torque. The aforementioned reduction gear (161) consists of a planetary gear mechanism (30), The reduction gear is equipped with an output shaft whose displacement is controlled by the drive means, When the drive means (38) executes the first stroke portion, and when the drive means (38) executes the second stroke portion, The first stroke portion corresponds to the displacement of the output shaft in the first displacement direction, and the second stroke portion corresponds to the displacement of the output shaft in the second displacement direction opposite to the first displacement direction. The planetary gear mechanism (30) comprises a first stage (32) of a planetary carrier and a second stage (34) of a planetary gear. An opening / closing assist mechanism characterized in that, when the drive means (38) executes the second stroke portion, the displacement of the output shaft (31) is controlled by the drive means (38) via the second stage (34) to generate the second torque that enables the latch to close.

5. An opening / closing assist mechanism (10) that assists in opening and closing the latch (12) of the door leaf (100), The opening and closing assist mechanism includes an electric actuator (16) that controls the opening and closing of the latch (12). The electric actuator (16) is associated with a reduction gear (161) which has a drive means (38) configured to perform a displacement stroke. The displacement stroke includes a first stroke portion for opening the latch (12) and a second stroke portion for closing the latch (12). The reduction gear (161) has a first reduction ratio in the first stroke portion and a second reduction ratio in the second stroke portion. The first reduction ratio differs from the second reduction ratio, When the drive means (38) executes the first stroke portion, the reduction gear (161) is configured to generate a first speed. When the drive means (38) executes the second stroke portion, the reduction gear (161) is configured to generate a second speed, the first speed being faster than the second speed. The aforementioned reduction gear (161) consists of a planetary gear mechanism (30), The planetary gear mechanism (30) comprises a first stage (32) of a planetary carrier and a second stage (34) of a planetary gear. The first stage (32) is configured to be blocked when the drive means (38) executes the second stroke portion, The opening / closing assist mechanism is characterized in that the second stage (34) is configured to be blocked when the drive means (38) executes the first stroke portion in order to generate the first speed which enables the opening of the latch.

6. An opening / closing assist mechanism (10) that assists in opening and closing the latch (12) of the door leaf (100), The opening and closing assist mechanism includes an electric actuator (16) that controls the opening and closing of the latch (12). The electric actuator (16) is associated with a reduction gear (161) which has a drive means (38) configured to perform a displacement stroke. The reduction gear is equipped with an output shaft whose displacement is controlled by the drive means, The displacement stroke includes a first stroke portion for opening the latch (12) and a second stroke portion for closing the latch (12). The reduction gear (161) has a first reduction ratio in the first stroke portion and a second reduction ratio in the second stroke portion. The first reduction ratio differs from the second reduction ratio, The aforementioned reduction gear (161) consists of a planetary gear mechanism (30), The planetary gear mechanism (30) comprises a first stage (32) of a planetary carrier and a second stage (34) of a planetary gear. When the drive means (38) executes the second stroke portion, the reduction gear (161) is configured to generate a second torque. As the drive means (38) executes the second stroke portion, the displacement of the output shaft (31) is controlled by the drive means (38) via the second stage (34) to generate the second torque that enables the latch to close. The planetary gear mechanism comprises a first stage (32) consisting of planetary carriers and a second stage (34) consisting of planetary gears. The first stage (32) has a first axis of rotation (C) which is permitted to rotate in a first rotation direction (S1) of the first stage, and whose rotation is prevented in a second rotation direction (S2) opposite to the first rotation direction (S1). The opening / closing assist mechanism is characterized in that the second stage has a second rotation axis (D) which is permitted to rotate in a first rotation direction (S1') of the second stage, and whose rotation is prevented in a second rotation direction (S2') opposite to the first rotation direction (S1').

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