Motor vehicle locking device

Abstract

The invention relates to a motor vehicle locking device, in particular a motor vehicle lock, preferably a motor vehicle cover lock. The locking device is equipped with locking mechanisms (1, 2) mainly comprising a bolt (1) and a pawl (2). Furthermore, a helical torsion spring (5) is provided for acting on the locking pin (3) which interacts with the locking mechanism (1, 2). According to the invention, the helical torsion spring (5) has a rectangular cross-section.

Description

Technical Field

[0001] The invention relates to a motor vehicle locking device, in particular a motor vehicle lock, preferably a motor vehicle hood lock, which has a locking mechanism mainly comprising a lock tongue / ratchet and a lock pawl / ratchet; and a helical torsion spring for loading a lock pin interacting with the locking mechanism. Background Art

[0002] Motor vehicle locking devices are typically used on or in motor vehicles in order to, for example, lock doors, hatches, hoods, etc. relative to the vehicle body. This mainly involves motor vehicle locks, in particular motor vehicle hood locks, which are used, for example, in hoods or tailgates. On the one hand, there is the problem that the hood rattles due to the movement of the vehicle or the effects of wind, since the locking pin, which is caught by the locking tongue in the locked state of the locking mechanism, moves relative to the locking tongue within the entry opening of the locking tongue. On the other hand, it is important that such hoods open intactly.

[0003] For this purpose, the following measures are usually taken in practice, that is, the locking mechanism, which is located in its locked position or main locking position, is opened by means of a handle or an electric motor. Now, the front cover needs to be transferred to the so-called disengaged position and at least partially opened by means of a helical torsion spring. For this purpose, the helical torsion spring acts on the locking pin. In the disengaged position, the user can grasp and unscrew the front cover through the gap thus created between the motor vehicle body and the front cover. The prerequisite for this is a sufficiently large opening torque on the front cover and provided by the relevant helical torsion spring.

[0004] It must be taken into account that the front hood is loaded with additional weight, for example due to snow or ice lying on it, which may prevent the assuming the disengaged position. Accordingly, a high opening torque is typically required. This high opening torque is provided in the prior art, for example according to DE 10 2006 002 338 A1, by a force accumulator, which moves the front hood into its raised position or disengaged position. The force accumulator can be a plurality of leaf springs. This results in a lengthy construction and a complex and expensive design.

[0005] In the prior art of this type according to DE 10 2009 021 613 A1, a damping device is provided, which has at least one spring element received in a housing or a lock housing. In a variant embodiment, the spring element can be a helical torsion spring. Here, the helical torsion spring acts on two tongs elements that can move relative to each other and are received movably in the lock housing. The locking pin is preloaded by the tongs elements in a force-loaded manner. In general, this should prevent the locking pin from rattling in the locked position of the locking mechanism.

[0006] The prior art has proven itself in principle, but on the one hand uses a lengthy and complex design and on the other hand is limited with respect to the opening torque provided by the helical torsion spring. The present invention is intended to remedy this in general. Summary of the invention

[0007] The object of the present invention is to further develop such a motor vehicle locking device in such a way that an increased opening torque is provided compared to the prior art while taking into account a compact and cost-effective design.

[0008] In order to solve this technical problem, a motor vehicle locking device of this type is characterized within the scope of the invention in that the helical torsion spring has a rectangular cross section. A variant is particularly preferred in which the helical torsion spring has a square cross section.

[0009] Within the scope of the invention, the helical torsion spring is used primarily and unchanged for indirectly or directly loading the locking pin. The helical torsion spring has a winding section and two legs adjoining the winding section or extending from the winding section. Compared to the prior art according to DE 10 2009 021 613 A1, the helical torsion spring according to the invention does not have a circular cross section, but a rectangular cross section, in particular a square cross section. That is, the spring wire used for the forming process of the helical torsion spring is not provided with a circular cross section according to the invention, but with a rectangular cross section or a square cross section. This achieves two major advantages over the prior art.

[0010] Firstly, the opening torque provided by the helical torsion spring with a rectangular or square cross section and loading the locking pin is greater than the opening torque of the helical torsion spring of the same construction with a circular cross section. In practice, within the scope of the invention, an opening torque between 3 Nm and 6 Nm is provided. Preferably, the opening torque is between about 4 Nm and 5 Nm. This opening torque typically corresponds to an opening force acting on the locking pin, which is usually above 60 N, in particular greater than 80 N, preferably 100 N, or more. As a result, the front cover can still be reliably opened when, for example, snow or ice is on the front cover.

[0011] In addition to the increased opening moment or opening force on the locking pin compared to the prior art, the required helical torsion spring has the further advantage that the opening moment between the pre-locking position and the main locking position of the locking mechanism is not subject to large fluctuations or drops. In practice, the opening moment applied by the helical torsion spring between the pre-locking position and the main locking position of the locking mechanism differs by a maximum of about 30%. Preferably, it even differs by only a maximum of 25%. That is, the opening moment of the helical torsion spring in the pre-locking position and the opening moment of the helical torsion spring in the main locking position differ by a maximum of 30% or 25%.

[0012] This can all be attributed to the rectangular or square cross section of the spring wire and thus the helical torsion spring according to the invention. In practice, the helical torsion spring in question is made of steel, in particular spring steel. Here, unrusted spring steel wire with or without a protective layer can be used as the raw material for the spring wire to produce the helical torsion spring according to the invention with a rectangular or square cross section.

[0013] In either case, spring wires with a rectangular or square cross section have a significantly higher bending moment than spring wires with a circular cross section. Due to the higher bending moment, the helical torsion spring used according to the invention can load the locking pin with a significantly higher opening moment after the forming process on its active leg, which indirectly or directly loads the locking pin, than if a spring wire with a circular cross section was used as the starting material. This is a major advantage of the invention.

[0014] Typically, a design is adopted in which the helical torsion spring surrounds the support mandrel with its wrapping section. In this case, provision is usually made for the wrapping section to surround the relevant support mandrel with a gap, so that the two legs extending from the wrapping section can easily enclose different angles with each other. An obtuse angle is usually provided here. That is, the legs adjoining the wrapping section enclose a relevant obtuse angle with each other.

[0015] Here, the obtuse angle between the two legs can have a value greater than 90° to 180°. Preferably, the value used for the obtuse angle here is greater than 120° to 180°, particularly preferably 150° to 180°. Of course, this is only exemplary and not mandatory.

[0016] At values ​​of, for example, 150° to 180°, the associated locking mechanism transitions from its main locking position at approximately 150° to a pre-locking position at approximately 180°. The change in angle between the two legs of the helical torsion spring adjoining the wrap-around section now corresponds to different opening torques applied to the locking pin, which differ from each other by up to 30% as described above. This means that, for example, the opening torque applied to the locking pin by the helical torsion spring according to the invention in the main locking position of the locking mechanism is usually up to 30% greater than the opening torque applied to the locking pin in the pre-locking position. Preferably, the difference between the two positions is even only up to 25%.

[0017] In terms of design, the following design is adopted, that is, the helical torsion spring uses its movable leg to load the ejector rod that loads the locking pin. In contrast, the fixed leg is fixed to the housing. Here, the fixed leg can be locked with the housing. In contrast, the movable leg usually rests on the contact edge of the ejector rod on the bottom side. The contact edge of the ejector rod itself rests on the locking pin.

[0018] In addition, it has been proved to be advantageous that the ejector rod and the pawl are coaxially supported relative to each other in this case. Here, a common support mandrel ensures coaxial support, which is surrounded by the winding section of the helical torsion spring according to the present invention.

[0019] Thus, a motor vehicle locking device is provided which, with a simple structure, provides an increased opening torque for loading the locking pin compared to the prior art. Furthermore, the opening torque acting on the locking pin or the force loading the locking pin in the opening direction is equalized between the main locking position and the pre-locking position of the locking mechanism. Thus, according to the invention, the opening torque or the opening force differs by a maximum of 30% between these two positions.

[0020] In contrast, the prior art here mostly operates with a deviation of the opening moment and thus the opening force acting on the locking pin between the pre-locking position and the main locking position, which may be 50% or more. According to the invention, the extended or disengaged position of the front cover is thus perfectly assumed and the noise characteristics are improved at the same time, since no rattling noises are perceptible either in the main locking position or in the pre-locking position. This is a major advantage of the invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The invention is described in detail below with reference to the accompanying drawings which show only one embodiment; in the drawings:

[0022] Figure 1 A perspective view of a motor vehicle locking device according to the invention is shown, and

[0023] Figure 2A , Figure 2B Different positions of the locking mechanism are shown. DETAILED DESCRIPTION

[0024] The drawings show a motor vehicle locking device, which is preferably designed as a motor vehicle hood lock according to this embodiment. For this purpose, the motor vehicle locking device or the motor vehicle hood lock shown has a locking mechanism 1, 2, which essentially includes a locking tongue 1 and a locking claw 2. In addition, a locking pin 3 can be seen, which interacts with the locking mechanism 1, 2 and, according to the embodiment, adjoins the hood or front hood 4 on the bottom side.

[0025] In this case, the other basic structure also includes a helical torsion spring 5 for loading the locking pin 3 interacting with the locking mechanism 1, 2. According to this embodiment, the helical torsion spring 5 has a rectangular cross section, in particular a square cross section, such as Figure 1 As the enlarged fragment in the figure clearly shows. In fact, the relevant spiral torsion spring 5 is made of a spring wire with a rectangular cross section or a square cross section. Steel, in particular spring steel, is used as the material for the spring wire.

[0026] According to Figure 2A , Figure 2B In the functional position, it can be seen that the opening torque indicated by the arrow is released by the helical torsion spring 5. Applied to the lock pin 3, that is, in the locking mechanism 1, 2 according to Figure 2A in the main locking position and in its associated corresponding Figure 2B in the pre-locked position as shown in the figure.

[0027] The specific design of the helical torsion spring 5 with a rectangular or square cross section according to the invention ensures that, in accordance with Figure 2A The relevant opening torque in the main locking position Corresponding to Figure 2B The opening torque of the pre-locking position shown in the figure differs from each other by 30% at most in value. Here, the opening torque provided by the helical torsion spring 5 A value between 3 Nm and 6 Nm, preferably between 4 Nm and 5 Nm, can be provided. A force is thus generated which acts on the locking pin 3 in the opening direction, which can typically be greater than 50 N, even 100 N or more.

[0028] In terms of structure, it can be seen that the helical torsion spring 5 surrounds the support mandrel 6 with its winding section 5a. In this case, a gap is formed between the winding section 5a in question and the support mandrel 6. In this way, the two legs 5b and 5c extending from the winding section 5a can enclose different angles α with respect to each other, for example, according to Figure 2A and Figure 2B As can be seen in the diagram.

[0029] Here, the angle α enclosed by the two legs 5b, 5c is an obtuse angle according to this embodiment, which can have a value of 90° to 180°. In fact, it can be seen that in the case corresponding to Figure 2A The angle α in the main locking position shown in FIG. 1 is approximately 150°, while the angle α corresponding to Figure 2B The illustrated pre-locking position in corresponds to an angle α of approximately 180°.

[0030] Here, not only the following structural design is adopted, namely, the helical torsion spring 5 surrounds the relevant supporting mandrel 6 with its winding section 5a. Moreover, the helical torsion spring 5 additionally ensures with its movable leg 5b that the ejector rod 7, which is in contact with the locking pin 3 and is additionally provided, is loaded. For this purpose, according to this embodiment, the movable leg 5b of the helical torsion spring 5 that is in contact and moves together with the ejector rod 7, contacts the contact edge 7a of the ejector rod 7 at the bottom side, and the locking pin 3 itself moves with its arc-shaped portion to contact the contact edge. By contacting the locking pin 3 with the contact edge 7a of the ejector rod 7, it itself is loaded along the corresponding contact edge with the aid of the helical torsion spring 5 according to the invention. Figure 1The opening direction of the arrow in FIG. 1 is applied, which ensures that the locking pin 3 cannot perform relative movement inside the entry opening of the locking tongue 1 and therefore no rattling noise occurs.

[0031] This applies not only to Figure 2B pre-locking position, but also for the corresponding Figure 2A . This is also ensured by the fact that the forces exerted by the spring 5 on the locking pin 3 in the pre-locking position and in the main locking position differ from each other by only 30% at most, as already described at the beginning. As a result, in both locking positions, it can be expected that the locking pin 3 is held with its arc-shaped portion inside the entry opening of the locking tongue 1 without rattling.

[0032] List of reference numerals:

[0033] 1 Lock tongue

[0034] 2 Locking claws

[0035] 1.2 Locking mechanism

[0036] 3 Locking pin

[0037] 4 Hood or front cover

[0038] 5 Helical torsion spring

[0039] 5a Winding section

[0040] 5b Leg Movement

[0041] 5c Fixed Leg

[0042] 5b, 5c Legs

[0043] 6 Supporting mandrel

[0044] 7 Ejector rod

[0045] 7a Attach to edge

[0046] Opening torque

[0047] α angle

Claims

1. A motor vehicle locking device, in particular a motor vehicle lock, preferably a motor vehicle hood lock, comprising: a locking mechanism (1, 2) mainly comprising a locking tongue (1) and a locking claw (2); a helical torsion spring (5) for loading a locking pin (3) interacting with the locking mechanism (1, 2), It is characterized in that The helical torsion spring (5) has a rectangular cross section.

2. The device according to claim 1, characterized in that The helical torsion spring (5) has a square cross section.

3. The device according to claim 1 or 2, characterized in that The opening torque applied by the helical torsion spring (5) between the pre-locking position and the main locking position of the locking mechanism (1, 2) The difference is about 30% at most.

4. The device according to any one of claims 1 to 3, characterized in that The helical torsion spring (5) generates an opening torque of between 3 Nm and 6 Nm, preferably between approximately 4 Nm and 5 Nm.

5. The device according to any one of claims 1 to 4, characterized in that The helical torsion spring (5) surrounds the support mandrel (6) with its winding section (5a).

6. The device according to any one of claims 1 to 5, characterized in that The spiral torsion spring (5) uses its movable leg (5b) to load the ejector rod (7) of the loading lock pin (3), while the fixed leg (5c) is fixed on the housing (8).

7. The device according to any one of claims 1 to 6, characterized in that The winding section (5a) surrounds the support mandrel (6) with some play.

8. The device according to any one of claims 1 to 7, characterized in that The legs (5b, 5c) adjoining the wrap-around section (5a) enclose an obtuse angle (α) with one another.

9. The device according to claim 8, characterized in that The value of the obtuse angle (α) is greater than 90° to 180°, preferably 120° to 180°.

10. The device according to any one of claims 1 to 9, characterized in that The helical torsion spring (5) is made of steel, in particular spring steel.

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