WO2004074613A1

WO2004074613A1 - Three dimensional hinge system for véhicle door

Info

Publication number: WO2004074613A1
Application number: PCT/CN2004/000094
Authority: WO
Inventors: Zhide Feng
Original assignee: Feng, Shuzhen
Priority date: 2003-02-05
Filing date: 2004-02-04
Publication date: 2004-09-02

Abstract

A linkage for the vehicle door and the body frame provides a simple and stable three dimensional hinge system for the vehicle door which occupies less space and adapts to all kinds of vehicle. This invention includes a body frame and a door, which is hinged to the doorframe of the body frame. The invention also includes a main connecting lever that comprises a first end that connects to the doorframe and a second end that connects to the inside of the door, a sub connecting lever that comprises a first end that connects to the body frame and a second end that connects to the door.

Description

Technical field of automobile door three-dimensional hinge system

The present invention relates to the field of automobile door and vehicle body connection mechanism fields, and more particularly to a three-dimensional hinge system for automobile doors. technical background

The automotive industry has been trying its best to solve the inconvenience caused to users during the opening and closing of car doors. Most of the existing technologies use a single-axis hinge system or a four-link mechanism with a short link. The former is called the inner door hinge in the automotive industry. After the door is opened, a part of the front edge or the rear edge enters the body contour. The latter are mostly hinges for the door, and after the door is opened, no part enters the body contour. When a car using the above door hinges is parked in a parking lot where other cars are parked next to it and the door needs to be opened, an accident of the car door colliding with another car often occurs. In addition, when the doors are opened, the lateral extension of these doors from the body of the car also causes inconvenience for the occupants to get in and out of the car.

U.S. patents using a uniaxial hinge in the prior art include US6247744 by Josto Design Company, Townsend et al., And US2003097731 by Nania Adrian, USA. The movement of the door where these mechanisms are installed is only a simple rotation. Art preclude the use of a short link four-bar linkage including the US General Motors Company Siladke et al US5491875, Toyota Motor Corporation Shiraishi Dai ichi et al US4700984, American Daimler Chrysler company Presley Willian T installation of US6647592 ₀ The movements of the doors of these mechanisms when the door is opened and closed are mainly rotation, and also a small amount of translation. The purpose of this small amount of translation is mainly so that no part of the vehicle door enters into the contour of the vehicle body after the door is opened. When the doors of the above two mechanisms are opened, the doors basically open laterally about the rotation axis, occupying a lot of space.

US2003093878 (JP20010355519) proposed by Hara et al., Another Japanese company, Fuji Heavy Industry, uses a four-link mechanism with a long rotating link. The mechanical characteristics of the link include: a). Two rotating links (in US2003093878) The part numbers (3) and (4)) must be different in length; b). The two rotating links (3) and (4) can only be placed between the inner side of the body body (1) and the door (2) C). The main link (3) of the two rotating links must have a collision avoidance (10A, 10B) to prevent the door from colliding with the main body (1) when the door is fully opened; . The movements of the doors installed with these mechanisms when the door is opened and closed are still dominated by rotation, and at the same time a certain translation is made. When the door is fully opened, the door still has a large lateral extension, and the mechanism is complicated, which affects the overall mechanism stability and is difficult to install.

At present, the rear doors of many vans use a door sliding mechanism to slide the door along three fixed guide rails provided on the body, and the door is close to the body when the door is opened. 美国 US 'patents using this technology include Germany ’s Grossbach et al. ’S

1 Replacement page (Article ² δ) US3605338, US4152872 by Japanese company Nissan Tanizaki et al., And US6550848 by Kleemann of Porsche Aktiengesellschaft, Germany. The main disadvantage of the door sliding mechanism is that there needs to be enough space on the body of the vehicle to install three fixed guide rails. The three guide rails, especially the guide rails placed on the outside of the vehicle body and the lubricant filled in it, affect the aesthetics of the car. Large vibration and noise problems, and its manufacturing cost is high. This technology has not been applied to small vehicles such as cars, nor has it been applied to the front door of any car.

The door of the passenger side of some buses also uses a four-link mechanism with two long and substantially equal turning links.-This mechanism makes the movement of the door basically dominated by translation. The door is placed after it is fully opened. Next to the door opening, it is close to the car body. However, because the four rotating shafts of the two rotating links are all arranged vertically on the car body floor, in order to maintain the stability of the four-link mechanism when it is just opened, the fixed rotating shafts of the auxiliary links in the two rotating links need to enter The distance between the sides of the body is large. Therefore, all buses applying this technology place the fixed shaft of the auxiliary link on the underside of the car body floor. At the same time, the main link of the two rotating links also occupies Large body space.

Summary of the Invention

The purpose of the present invention is to overcome the shortcomings in the prior art, and to provide a three-dimensional hinge system for a car door that is simple and stable in structure, takes up little space when opening a door, and is suitable for various types of cars (especially small cars). This system can also be used to connect the general door and door frame structure or the container and lid.

First discuss the principle of the invention:

The present invention mainly adopts the structural principle of the three-dimensional four-link mechanism in the machine to achieve the purpose of the invention. As shown in FIG. ΊΌ-1, the four-link mechanism in question consists of a fixed link 1 (representing the body body 1), and an opposite lever. 2 (representing door 2), the main link 3 and the auxiliary link 4, the fixed link 1 and the main link 3 are connected by a first shaft 311; the main link 3 and the opposite rod 2 are connected by a second shaft 321; fixed The connecting rod 1 and the auxiliary link 4 are connected by a third shaft 411; the auxiliary link 4 and the opposing rod 2 are connected by a fourth shaft 421. We also assume that the above four axes are parallel to each other.

Under normal circumstances, when the relative rod (door 2) is displaced relative to the fixed link (body body), there are both translation and rotation. However, the application of the present invention to automobiles is mainly based on translation, allowing a small amount of rotation.

The mutual positions of the above four links are as follows:

a. As shown in Figure 10-1, when the third axis 411 coincides with the extension line of the first axis 311, at the same time, the main plane of the fixed link is defined by the midpoint between the first axis axis line and the third axis axis line The distance La from the midpoint of the axis of the second axis is also very short. At this time, the movement of the mechanism is equal to the three-dimensional triangle composed of the opposite rod 2, the main link 3 and the auxiliary link 4 around the first axis 311 (the third axis 411 ), That is, the relative lever 2 (representing the door 2) also rotates around the first axis 311 (third axis 411), thus losing the significance of the four-link mechanism, which does not comply with the application of the present invention to automobiles. The main starting point is panning. In this case, a plan view viewed along the axis of the first axis 311 is shown in FIG. 10-2. b. As shown in Figure 11-1, on the basis that the above four axes are kept parallel, the three-dimensional spatial position of the midpoint of the axis of the four axes does not change, and the ends of the axis of the four axes are backward / downward (that is, along the The X coordinate value increases / Z coordinate decreases / Y coordinate does not change). The direction is tilted forward by an angle α. The distance between the extension of the first axis 311 and the center point of the third axis 411 is changed from zero to , Then this mechanism becomes a four-link mechanism in the complete sense (that is, the length of the four links is not zero). If you keep the other constant, the larger the absolute value of α within a certain range (-45 degrees to 45 degrees), the larger 1 ^ will be, and the more stable the mechanism will be. Making the first shaft 311 and the third shaft 411 generate such an inclination angle can make it from scratch, and it can also make it small to large, thus making the mechanism more stable. A two-dimensional view of the situation along the axis of the first axis 311 is shown in Figure 11-2. For example, if the center point of the four-axis axis does not move and the upper end is tilted forward / downward, the same effect can be produced. Generally, it is recommended that the upper end of the above-mentioned axis line be inclined forward / downward when the front door is installed behind the A-pillar, and the upper-end of the above-mentioned axis line is installed forward / downward when the rear door is installed in front of the C-pillar. Negative tilt. On the contrary, the door is prone to interfere with the ground or shoulder when the door is opened.

c As shown in Figure 12-1, in the state of the b case above, the three-dimensional coordinates of the center point of the four-axis axis line are unchanged, and then the upper end is moved inward / downward, that is, the X coordinate is unchanged / Z The coordinate value decreases / Y coordinate is tilted by an angle γ in the direction of increasing (for the left door) or decreasing (for the right door). The two-dimensional view of the situation along the axis of the first axis 311 is shown in Figure 12-2. Based on the distance between the extension of the first axis 311 and the midpoint of the third axis 411 axis, The vertical distance between the main plane of the fixed link defined by the midpoint of the first axis 311 axis line and the third axis 11 axis center line and the second axis 321 axis line center point is changed from a distance close to zero to a larger L ₂ , the following analysis of the structure of the reason for this setting.

From case a 'to case b, that is, only the inclination angle otr at the upper end of the axis of the first axis 311 makes the mechanism a four-link mechanism on the complete meaning one', but because each link is not a rigid body, each axis and each connection There is also a gap in the connection of the levers. In this way, when the mechanism is in some positions, such as when the door 2 has just been opened, the main plane of the main link defined by the midpoint of the first axis axis line and the second axis axis line and the first axis The main plane of the fixed link defined by the midpoint of the axis of the axis and the axis of the third axis is nearly coincident, and the stability of the mechanism may still have major problems.

In order to analyze the stability of the mechanism at this time, first of all, except for the auxiliary link, the other links and axes are ideal rigid bodies, and there is no gap between all the parts. In addition to the fixed link 1, the other one is fixed. One degree of freedom of a part can make the mechanism a static structure in the dynamic sense. If the other fixed part is the main link 3, the sub-system consisting of the main link 3 and the fixed link 1 can be replaced by an imaginary rigid fifth link 5 to make the mechanism dynamic. Static structure. At this time, the above system has a triangular structure composed of a fifth link 5 (a completely fixed rigid body), an opposite rod 2 (a rigid body fixed at one end), and a secondary link (a non-rigid body fixed at one end). In the dynamic sense, it stands still, but in the sense of material mechanics, it will produce a small displacement caused by the elastic deformation of the auxiliary link 4, and accordingly, a slight rotation about the second axis 321 will be generated relative to the rod 2. The auxiliary link 4 A length change and a slight rotation around the third axis 411 are generated. The following further analyzes the situation of the triangular structure composed of the fifth link 5, the counter link 2, and the auxiliary link 4. The following are the main planes of the opposite rods defined by the midpoint of the second axis 321 axis line and the fourth axis 421 axis center line and the secondary connection defined by the third axis 411 axis line and the fourth axis 421 axis center line Analyze the angle β between the major planes of the rods when the β i (case cl) is increased to a relatively large β ₂ (case c2), which is close to zero.

Case cl: The analysis diagram viewed along the axis of the fourth axis is shown in Fig. 12-3. There is only a slight angle β _{1 (1} '

The trajectory of the moving end of the auxiliary link 4 around the third axis 11 axis 0 0 without force is nu-, and the trajectory _Pl - _Pl of the moving end of the relative rod 2 about the second axis 321 axis _ρ1 . The four-axis 421 axis connects the above two movable ends together, so the fourth-axis 421 axis must be on ^-! ^ And _Pl at the same time. Under normal circumstances (when the main plane of the opposite rod and the main plane of the auxiliary link do not coincide) ) They have two intersections. Here we choose only one intersection ρ _π1 below.

When the auxiliary link 4 receives a load along its longitudinal direction -N to reduce its length by elastic compression Δ, the trajectory of the movable end of the auxiliary link 4 becomes- _η , and the axis of the fourth axis 421 must be at-and ₁ - _Pl at the same time. This point is most likely to be _Pη1 . The distance from this point to the point ρ _π1 is equal to r _u , and its magnitude is equal to the displacement of the fourth axis 421 after the auxiliary link receives a longitudinal load -N along its longitudinal load. The magnitude is relatively large, because the trajectory ¾-1¾ is relatively close to the trajectory _Pl - _Pl because the angle is small.

The fourth axis 421 is located at-n ^ B _Pl - _Pl at the same time. Another point is p _nl . The fourth axis 421 must cross the dead point d to reach this point. The distance from this point to the point p _nl is equal to r ₁₂ , Its magnitude is larger than r _u but relatively close, so the fourth axis 421 'crosses the dead point (T may reach this point is also relatively large,' This is also because the β angle is small, causing the trajectory ffi- and trajectory P ~ ϊ The reason is relatively similar. When the angle is zero, that is, the structure is initially at the dead point position, then the fourth axis 421 axis will have a chance to reach ρ _η1 or _Pη1 after the secondary link receives a longitudinal load-Ν. equal.

Case c2: Referring to FIG. 12-4, the angle between the main plane of the opposite rod and the main plane of the auxiliary link is increased to a larger angle β ₂ . A third sub-link 4 about the axis of the shaft 411 in the absence of stress 0 "track is movable end rotatably m _₂ -m _2, about the second axis relative to the shaft 321 axis. Trajectory o _p2 is rotatably movable end p ₂ -p ₂ , because the axis of the fourth axis 421 connects the above two movable ends, the axis of the fourth axis 421 must be on m ₂ -m ₂ and p ₂ -p ₂ at the same time. When the main plane and the main plane of the auxiliary link are not coincident), there are two intersections. Here, only the lower intersection is selected.

When the auxiliary link 4 receives a load along its longitudinal direction -N and its length is elastically compressed to shorten Δ, the trajectory of the movable end of the auxiliary link 4 becomes ¾-¾, and the fourth axis 421 axis must be at-· and p at the same time. ₂ -p _2. This point is most likely to be p _n2 . The distance from this point to the point ρ _π2 is equal to r ₂₁ , and its magnitude is equal to the fourth axis 421. The axis of the secondary link receives a longitudinal load -N The magnitude of this displacement is relatively small because the larger β ₂ angle causes the trajectory m ₂ -m ₂ to be far away from the trajectory p ₂ -p ₂ .

The other axis of the fourth axis 421 is located on both n ₂ -n ₂ and p ₂ -p ₂ at the same time is _Pn2 . The fourth axis 421 must pass the dead point d to reach this point. The distance from this point to the point is equal to r ₂₂ , its magnitude is much larger than r ₂₁ above, so the fourth axis The possibility that 421 crosses the dead point d to reach this point is also relatively small, which is also because the trajectory m ₂ -m ₂ is far from the trajectory P2-P2 due to the larger β ₂ angle.

For example, in the latter two cases, the auxiliary link is subjected to a variation in the range of -N to + N along its longitudinal load at the same time. Then, the variation range of the position of the fourth axis 421 axis in the cl case cannot exceed the radius of r _u The range of variation of the center position of the fourth axis 421 in the case c2 cannot exceed the circle with a radius of r _21. Obviously, the range of variation in the case c2 is less than the range of variation in the cl. In addition, the possibility that the axis of the fourth axis 421 crosses the dead point d is also smaller in the c2 case than in the cl case.

That is to say, the condition c2 is more precise than the condition cl to restrain the opposite rod, that is, the door.

The axis of the first axis is tilted inward at the upper end (that is, the projection of the angle between the axis of the first axis and the X-Z plane on the YZ plane). The angle γ is within a certain range (for example, between -90 degrees and 90 degrees). ) Has a positive correlation with β, that is, β increases with the increase of γ.

The effect from the case a to the case b above is to increase the distance from the first axis axis line or its extension line to the middle point of the third axis axis line, that is, the effective length of the fixed link, and the effect from the case b to the case c It is to increase the vertical distance of the center point of the second axis axis line from the initial state (when the door is closed) to the main plane of the fixed link by 1 ^.

If the axis of the first axis is tilted outward at the upper end, the door will also have a more stable state immediately after it is opened, but this will cause the door to have a downward displacement after it is opened, and it is easy for the door to interfere with the ground or shoulders. .

In summary, for the application of the present invention to automobiles, the axis of the first axis is rearward at the upper end (for a front car mounted on an A-pillar) or forward (for a rear door mounted on a C-pillar). (Speaking of) tilting 'Γ while tilting inward can make the door more stable after being opened.

The present invention mainly achieves its object through the following technical content.

The invention is a three-dimensional hinge system for a vehicle door, which is applied to connect a body body and a door in an automobile. The system includes a main link including a first end portion and a second end portion. The first end is generally connected to the body of the vehicle body, and the A-pillar (or rear pillar) belonging to the door frame of the body is connected to the visible part of the body body approximately at the same height as the instrument panel. The second end It is connected with the door inner panel (the inside of the door is lower than the glass window part); a secondary link including a first end and a second end, and the first end of the secondary link is at another position of the body The second end is connected to another position of the door.

The main link and the auxiliary link of the present invention form a four-link mechanism with the vehicle body and the door, and the structure is stable. The body is used as a fixed part under a certain frame of reference, and the door, the main link and the auxiliary link each have One degree of freedom. When the door is opened, because the door is bound by the main link and the auxiliary link, it will be displaced from the body hole of the door hole with the door frame as the boundary, and this displacement is only translation without rotation, or mainly Pan and slightly rotate. Therefore, the maximum distance between the door and the body (ie, the maximum lateral displacement) during the opening of the door is basically not greater than the effective length of the main link (the second end The vertical distance from the centerline of the shaft hole to the centerline of the first end shaft hole or its extension line) and the effective length of the auxiliary link (the centerline of the fourth end shaft hole to the third The vertical distance of the axis line of the end shaft hole or its extension line), this distance is far less than the maximum distance required when an existing outside or inside door is opened. The invention only adds a main link, a sub link and other auxiliary connecting members between the body of the vehicle and the door. The structure is simple, and the added main link and sub link only occupy a small amount of space and can be hidden in the body The gap between the body and the door will not affect the general use of the car.

In order to make the mechanism of the present invention have better stability, the main link of the present invention is hinged to the body of the vehicle body and the door by means of a hinge shaft. The first end of the main link is connected with the first fixed to the door frame through the first shaft. The hinge seat is hinged, and the second end portion is hinged to the second hinge seat fixed to the door inner panel through the second shaft. In order to enhance the structural stability, the main link should generally have a certain height, or the shaft hole of the main link with the first or second shaft at both ends should have a certain length, generally not less than 100 mra. If two or more main links with a smaller height are used instead of the main link with a larger height, the distance between the two farthest links along the axis direction of the first axis shared by them is generally Should be not less than 100 mm.

Since the role of the auxiliary link is mainly to increase a constraint on the door, there are many positions for installing the auxiliary link on the body body. In order to facilitate the vehicle occupants to enter and exit the body through the door hole, the present invention can connect the auxiliary link through the third axis. The first end of the body is connected to the A-pillar (or rear pillar), sill or top of the door frame of the body frame, and the second end of the auxiliary link is connected to the lower and lower edges of the inner panel of the door through the fourth axis. , Or the top of the window frame.

In order to make the mechanism have a better stability, reduce the "A" of the third axis and the auxiliary link when the occupant enters and exits the body of the vehicle. According to the principle of the four-link mechanism described above, the "axis Φ line Or the distance between the extension line and the center point of the third axis, that is, the effective length of the fixed-point link cannot be too short, and the first and third axes can be tilted backward at the upper end (to the front door). On the premise of the above distance, the third shaft is installed on the A-pillar or a place closer to the A-pillar.

In order to reduce the sway of the door when it is just opened, the included angle between the main plane of the auxiliary link and the main plane of the opposite rod (the plane defined by the midpoint between the second axis and the fourth axis) represents the door It should be less than 10 degrees when the door is closed. When the midpoints of the first axis and the third axis are basically kept at the X, y, and z positions in the three-dimensional space, the upper ends of the first and third axes may be tilted inward at the same time. Increase this angle appropriately.

The connection manner of the auxiliary link with the body body and the door may take different forms. The first end portion of the auxiliary link of the present invention may be hinged with a third hinge fixed to the body body through a third axis, or may be ball-type. Or the universal joint of the cross shaft type is connected to the body, and the connection between the second end portion of the auxiliary link and the door can also be handled in the same way. In order to ensure the overall stability of the mechanism and the convenience of manufacturing, the more recommended method is to articulate the main link and the auxiliary link at both ends to connect the body and the door through four shafts. In order to minimize the installation space of the main link and the auxiliary link in the body of the vehicle body and the distance between the door and the body when the door is opened, the present invention may set the second axis and the first axis parallel to each other. Therefore, the preferred solution of the present invention is that the first end portion of the auxiliary link is hinged to the third hinge seat fixed to the vehicle body through the third shaft, and the second end portion is fixed to the fixed body through the fourth shaft. The fourth hinge seat fixed on the door is hinged, and the first, second, third, and fourth axes are parallel to each other, and the main link main plane G and the auxiliary link main plane H are parallel to each other and do not overlap. The length of the main and auxiliary links is generally not less than 1/3 of the lateral width of the door, and at the same time is not greater than 3/4 of the transverse width of the door, and the effective length of the main and auxiliary links is basically equal, and the difference is generally not more than 10%.

In order to save the appearance of the main link and the auxiliary link to occupy the inner body space of the vehicle body, the present invention may provide a groove for receiving the main link and the auxiliary link on the inner panel of the door, a second hinge seat and a fourth hinge seat. They are respectively fixed to the ends of the grooves.

. Another implementation of the present invention is to set the auxiliary link on the top of the body. At this time, the top of the door frame of the car can also be provided with a concave recess, and a baffle extends inward from the top of the door accordingly. Cooperating with the recess, the first end of the auxiliary link is connected to the top of the body through a shaft or a universal joint, and the second end is connected to a baffle on the top of the door through a shaft or a universal joint.

In practical applications, the present invention can also be installed in a rear door frame mechanism of an automobile, and the mechanism can use a mechanism that is completely consistent with the above mechanism or a mechanism that is symmetrical to the above mechanism. When the door is opened with a symmetrical mechanism, the door is displaced from front to back.

The invention can install an elastic element between the main link, the auxiliary link, the door and the body of the vehicle. When the relative movement occurs between the door and the body, the elastic element stores more energy when it is usually closed. On the contrary, when the door is opened, the energy released by the elastic element can help to reduce the force exerted on the door.

In the present invention, a power driving device can be installed between any two of the main link, the auxiliary link, the door and the body of the vehicle. When the power driving device is activated, it can cause relative movement between the door and the body of the vehicle. The power drive device can be selected with a motor, 'at this time the stator of the motor can be fixed to the body or the door, and a rotor of the motor can be fixed to the' main 'link or the auxiliary link.

Compared with the prior art, the present invention has the following significant improvements and substantial features:

1. The additional lateral space required to fully open the door is far less than the same space required to install internal and external door mechanisms in the prior art;

2. After the vehicle door is fully opened, the present invention provides a larger door opening space than the conventional internal door hinge and external door hinge mechanism in the prior art; '

3. Occupies a small amount of effective internal cavity space of the body, and does not need to install fixed guide rails. It can be installed in various types of cars, especially for cars, sports cars or off-road vehicles and minivans;

4. Simple hinge structure, low cost and good stability;

5. Compared with the door sliding mechanism, the appearance is more beautiful, which meets the aesthetic requirements of the existing automotive industry design;

6. Low vibration and noise, low lubrication requirements and easy maintenance.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic front view of a vehicle door in a closed state according to Embodiment 1 of the present invention; FIG. 2 is a front side view of a vehicle door in an opened state according to Embodiment 1 of the present invention;

3 is a rear side view of a vehicle door in an opened state according to Embodiment 1 of the present invention;

FIG. 4 is a rear view of an opened state of a vehicle door according to Embodiment 1 of the present invention; FIG.

5 is a side view of a vehicle door in an opened state according to Embodiment 1 of the present invention;

Fig. 6 is a front side view of a vehicle door in an opened state according to Embodiment 2 of the present invention

Fig. 7 is a rear side view of a vehicle door in an opened state according to Embodiment 3 of the present invention

FIG. 8 is a schematic structural diagram of a main link in Embodiment 3 of the present invention

FIG. 9-1 is a schematic space diagram of Embodiment 4 of the present invention;

9-2 is a side view of Embodiment 4 of the present invention;

Figure 10-1 is a perspective view of the first position of the four-link mechanism.

Figure 10-2 is a schematic plan view of the first position of the four-link mechanism

Figure 11-1 is a perspective view of the second position of the four-link mechanism

Figure 11-2 is a schematic plan view of the second position of the four-link mechanism

Figure 12-1 is a perspective view of the third position of the four-link mechanism

Figure 12-2 is a schematic plan view of the third position of the four-link mechanism

Figure 12-3 shows the third position of the four-link mechanism. Β is the principle of small angle;

12 "¾ is a schematic view of the principle of the third position of the four-link mechanism with a large angle. Γ Figure 13-1 is a top view of a conventional inner hinge or outer hinge applied to the front and rear doors at the same time; Figure 13-2 shows The invention is applied to the top views of the front and rear doors at the same time.

Related part numbers and concept indexes:

1 Body body (fixed link) 2 Door (or opposite lever)

3 main link 4 auxiliary link

5 Fifth link 6 Roof cover

7 Power drive unit 11 Door frame

12 sill 13 recess on top of door frame

23 Door inner panel 2 Door window frame bezel

25 Door lower edge extension 31 First end of main link

32Main link second end 32A Main link second end upper branch

32B second branch of main link lower end 41 first end of auxiliary link

42 secondary link second end 61 recess of roof cover 102 Elastic element 111 A pillar lower side pillar

112 Dashboard 113 Upper C-pillar

241 311 first axis

312 first hinge 321 second shaft

322 second hinge 322 A second hinge (top)

322B second hinge (bottom) 411 third axis

412 Third hinge 421 Fourth axis

422 Fourth hinge

A-pillar definition of the front pillar

C-pillar Rear pillar in a four-door car

The G plane is defined by the midpoint of the first axis axis and the second axis, and is also called the main link main plane. The H plane is defined by the third axis and the fourth axis. The plane is also called the vertical distance between the midpoint of the first axis axis line and the third axis axis line of the main plane of the auxiliary link. It is also called the effective length of the fixed link. Vertical distance of the main plane of the fixed link

N Amount of longitudinal load on the secondary link along its axis

Projection of the angle between the axis of the first axis and the Υ-Z plane on the χ-Z plane

"the projection of the angle between the axis of the γ axis and the X-Z plane on the ΎZ plane

β The included angle between the main plane of the auxiliary link and the main plane of the opposite rod

The X-Υ-Z coordinate system uses the center of the front axle of the car as the origin, the direction pointing to the rear of the car is X forward, the direction to the right of the car is Υ positive, and the direction to the top of the car is ζ positive.

X-Z plane Car symmetry center plane

detailed description

The following further describes the present invention in detail with reference to the drawings-in this specification, the coordinate system of the related parts of the invention is defined according to the three-dimensional coordinates commonly used in the automotive industry, that is, the center of the front axis of the car is used as the origin and the backward direction is positive The X direction (long), the right direction is the positive Υ direction (width or horizontal), and the upward direction is the positive ζ direction (height).

Example 1

As shown in FIGS. 1 and 2, a three-dimensional hinge system for an automobile door according to the present invention can connect the door 2 to a door frame 11 of the body 1 in a hinge shaft form. A portion surrounded by the door frame 11 is opened for passengers to enter and exit. The door opening of the body body 1 cooperates with the door 2 when closed. The dotted lines in the figure are the parts that are not visible in the main view. It can be seen from the figure that the present invention includes:

The main link 3 includes a first end portion 31 and a second end portion 32. The first end portion 31 is similar in height to the lower section 111 and the instrument panel 112 of the A-pillar (front pillar) of the door frame 11. The second end 32 is connected to the upper part of the inner panel 23 of the door 2. As shown in FIG. 3, the height of the connection can be similar to that of the instrument panel 112 (when door 2 is closed), and it is connected to 23 in the length direction. The position can be set at about the middle of the length of door 2;

A secondary link 4, which includes a first end portion 41 and a second end portion 42, the secondary link 4 is located below the main link 3, and the first end portion 41 of the secondary link and The position of the lower section 111 of the A-pillar of the door frame 11 close to the threshold 12, that is, the lower end of the first end 31 of the main link 3 is connected, and the second end 42 is connected to the lower part of the inner panel of the door 2 near the lower edge of the door 2. The effective length of the link 4 is equal to the effective length of the main link 3, as shown in FIG.

With reference to FIG. 2, FIG. 3, FIG. 5, and FIG. 5, the first end portion 31 of the main link 3 in this embodiment is hinged to the first hinge 312 fixed to the lower section 111 of the A-pillar of the door frame 11 through the first shaft 311. The second end portion 32 is hinged to the second hinge 322 fixed to the upper portion 23 of the inner panel of the door 2 through the second shaft 321. The first axis 311 and the second axis 312 are parallel to each other, and the upper end of the first axis 311 is inclined rearward. The angle α between the axis line and the Y-Z plane on the X-Z plane is an acute angle. The upper end of the first axis 311 is inclined inward, and the projection γ between the axis line of the first axis 311 and the X-Z plane on the Y-Z plane is an acute angle.

The first end portion 41 of the auxiliary link 4 is hinged to the third hinge 412 fixed to the lower A-pillar 111 of the door frame 11 through a third shaft 411, and the second end portion 42 is fixed to the inside of the door 2 through a fourth shaft 21 The fourth hinge 422 on the lower part of the board is hinged, and the third axis ³ 1′1, the second axis ³² 1, the third axis 411, and the fourth axis l are parallel to each other. As shown in FIG. ¾, the third axis 311 ;-The main plane G of the main link 3 defined by the second axis 321 and the main plane Η of the auxiliary link 4 defined by the third axis 411 and the fourth axis 421 are parallel to each other and do not overlap.

The vehicle body 1 (equivalent to a fixed link), the door 2 (equivalent to an opposite lever), the main link 3, and the auxiliary link 4 of the present invention constitute a four-link mechanism. When the door is opened, the main link 3 and the auxiliary link The connecting rod 4 rotates around the first shaft 311 and the lower third shaft 411 at the upper part of the lower section 111 of the front pillar (A-pillar) fixed to the door frame 11 because the upper ends of the first shaft 311 and the third shaft 411 are tilted backward α Angle, angle γ inward, so while the main link 3 and the auxiliary link 4 drive the door 2 to move forward, it also accompanies it to produce a first outward, inward displacement, and upward or first upward and then backward Down displacement. The inner panel 23 of the door 2 is provided with a groove 21 and a groove 22 for receiving the main link 3 and the auxiliary link 4, respectively. The third hinge bracket 322 and the fourth hinge bracket 422 are fixed to the groove 21 and the groove 22, respectively. Ends.

Because the door 2 is restrained by the main link 3 and the auxiliary link 4 and only translates with no rotation relative to the body body 1, when the door 2 is opened to occupy the maximum lateral (upward) space, the door 2 and the body body 1 The lateral distance between them is much smaller than the lateral distance when the door of the general outside or inside door structure is opened (mainly turning) to occupy the largest lateral space. The former is approximately equal to half the door length, and the latter is approximately equal to the door length. Therefore, the present invention Ming cars save about one side (left or right) of door opening space equal to half the door length.

When the door 2 is continuously opened, the present invention shows greater advantages. The lateral distance between the door 2 and the body body 1 will be less and less, and it will reach a minimum value when the door 2 is fully opened. Basically, The upper part can be in close contact with the body body 1. At this time, the occupant is basically not restricted by the door 2 when entering or leaving the car, but is only restricted by the door frame 11 itself, thus providing maximum convenience for the occupant to enter and exit the body body 1.

In the above embodiment, the effective length of the main link 3 'and the effective length of the auxiliary link may be slightly different, but the difference between them should generally not be greater than 10%. At this time, the displacement of the door 2 includes two parts of translation and rotation, and translation is the main part with a small amount of rotation. The preferred embodiment described above is based on the case where the door 2 is mounted on the visible part of the A-pillar 111 via the main link 3.

When other doors are installed on other pillars, such as the rear door is installed on the rear door frame C pillar through the main link, the visible part of the pillar after opening the door is basically consistent with the description in the preferred embodiment, but the front and rear directions are exactly the opposite, and the rear door is opened. Sometimes there is a displacement from front to back. When the present invention is applied to the front and rear doors at the same time, it exhibits greater advantages than ordinary inner-hinging hinges or outer-hinging hinges, as shown in Figure 13-1. The position of the rear doors relative to each other or the relationship between the two adjacent blades of a shutter is opened at this time, and the front and rear doors are opened smoothly at this time; In all these forms, when the door is fully opened (usually rotated by 75 degrees), there is a lateral protrusion close to the length of the door, which greatly affects the occupant's access to the car. As shown in Figure 13-2, when the door of a car to which the present invention is applied is fully opened, the front door is placed in front of the A-pillar, and the rear door is placed behind the ^C'- pillar; ^¾ between the front door and the rear door The distance is approximately equal to the distance between the A-pillar and C-pillar, and the lateral extensions of the front and rear doors are small. So it provides great convenience for passengers to get in and out of the car.

In the present invention, an elastic element 102 is installed between the main link and the body of the vehicle body. When relative movement occurs between the door and the body of the vehicle body, usually when the door is closed, the elastic element stores more energy, which is obtained when the door is opened. The energy released by the elastic elements helps reduce the force exerted to open the door. In the present invention, a power driving device 7 is installed between the vehicle body 1 and the auxiliary link. When the power driving device 7 is activated, a relative movement between the door 2 and the vehicle body 1 can be caused. The power driving device 7 may be an electric motor. At this time, the stator of the electric motor may be fixed to the vehicle body 1, and the rotor of the electric motor may be fixed to the auxiliary link 4, as shown in FIG. 2.

Example 2

As shown in FIG. 6, when applying the present invention, the top of the door frame 11 of the body 1 can be recessed into a recess 13, the side edge of the roof cover 6 is recessed into a recess 61, and the top of the door window frame of the door 2 is A matching baffle 24 is extended, and a fixed glass window 241 can be installed in the baffle 24 to increase the lighting in the vehicle body 1. At this time, the connection positions of the two ends of the main link 1 are not different from those in the first embodiment. (1) The axis line of the first axis 311 and the axis line of the second axis 321 are parallel to the Z axis. Connect The connecting position of the first end portion 41 of the auxiliary link 4 and the body body 1 may be provided at the top of the door frame 11 near the recess 13 or other structural members of the roof cover 6 to connect the second end of the auxiliary link 4 The connecting position of the portion 42 and the door 2 may be correspondingly provided at the above-mentioned baffle 24. The arrangement of placing the auxiliary link 4 on the top of the door window frame is more suitable for automobiles with a high roof cover.

Example 3

As shown in FIG. 7 and FIG. 8, the main link 3 can also be made with two branches at the second end portion 32, and the two branches are denoted as 32A and 32B, respectively. The 322B is hingedly connected to the top of the door window frame and the upper part of the inner panel of door 2. The shape of the upper branch 32A and its vicinity can be matched with the shape of the corresponding part of the A pillar and the top of the door frame 11, that is, the upper branch 32A of the main link 3 in this form can be hidden in the door 11 when the door 2 is closed. Window frame inside. This type of structure is equivalent to increasing the effective length of the second shaft (the mating length of the second shaft and related parts) and increasing the stability of the hinge mechanism. The position connecting the first end portion 41 of the auxiliary link 4 may also be provided on the upper side, the side or the lower side of the sill 12, and the second end portion 42 may also be connected to the lower edge or the lower edge extension 25 of the door 2. The first end portion 41 of the auxiliary link 4 can also be connected to the body 1 by using a universal joint (including a ball or cross shaft type). Similarly, the second end portion 42 of the auxiliary link 4 can also be connected by a universal joint. The form is connected to the door 2.

Example 4

Another form of increasing the stability of the hinge mechanism is the use of two or more main links. As shown in FIG. 9-1, the first main link 3 'is hinged to the upper portion of the C pillar upper portion 113 near the roof cover 6 through the first shaft 311; the second main link 3, Via the 'axis -311,' "the first end 31," of which is articulated to the position of the middle height of-C¾ 113 'Γ the first end 31 of the first shaft 31 and the second main link 3', The first shaft 311 'of the second shaft should share the same axis extension line; the second shaft 32 of its second end 32, and the second shaft 31' of the second main link 3 ', second The shaft 32 has the same axis extension line. The position of the first end 41 of the auxiliary connecting rod 4 can be set on the upper side of the sill 12, and the second end 42 can be connected to the lower edge of the door 2 or the lower edge of the door. The first end portion 41 of the auxiliary link 4 can also be connected to the body 1 by using a universal joint (including a ball or cross shaft type). Similarly, the second end portion 42 of the auxiliary link 4 can also be universally connected. The form of a knot is connected to the door 2.

Figure 9-2 shows a side view of a car when the roof cover 6 is narrowed significantly. The arrangement of the above two main links for this car can make full use of the relatively inclined upper part of the door frame 11 so that When the first shaft 31 (311 ',) maintains a large inclination angle γ, the first end portion 31' of the first main link and the first shaft 31 can be conveniently connected to a side pillar, such as the upper part of the C pillar 113 Near the roof 6. At this time, the projection D of the vertical distance between the center line of the first axis 311 '(31,) and the center point of the third axis 411 on the Υ-Z plane is also large, and its magnitude corresponds positively to γ The relationship, that is, the increase of γ and β caused by the increase of D, thereby ensuring the stability of the mechanism when the door is just opened.

Claims

Claim

1. A three-dimensional hinge system for an automobile door, connected between the body (1) and the door (2), characterized in that the system includes at least:

A main link (3), the main link (3) includes a first end portion (31) and a second end portion (32), the first end portion (31) is connected to the body body (1), and the second end The department (32) is connected with the door (2);

A secondary link (4), the secondary link (4) includes a first end portion (41) and a second end portion (42), the first end portion (41) is connected to the body body (1), and the second end portion The section (42) is connected to the door (2).

The three-dimensional hinge system for a vehicle door according to claim 1, characterized in that the first end portion (31) of the main link (3) passes through the first shaft (311) and is connected to the door frame of the vehicle body (1) The first hinge seat (312) on (11) is hinged, and the second end portion (32) is hinged with the second hinge seat (322) inside the door (2) through the second shaft (321).

The three-dimensional hinge system for a vehicle door according to claim 1 or 2, characterized in that the first end portion (41) of the auxiliary link (4) can be connected with the door frame (11) of the body body (1) ) Is connected to the side pillar (111) or the sill (12) or the top of the door frame, and the second end (42) is connected to the corresponding position on the door (2).

The three-dimensional hinge system for a vehicle door according to claim 1 or 2, characterized in that the first end portion (41) of the auxiliary link (4) can be connected with a roof cover of the body body (1) or The body floor is connected, and the second end portion (42) is connected to the corresponding position on the door (2).

The three-dimensional hinge system for a vehicle door according to claim 2, wherein the first axis (311) and the second axis (312) are parallel to each other, and the first axis (311) and the door frame (11) The angle α between the side pillars (111) is an acute angle.

The three-dimensional hinge system for a vehicle door according to claim 2 or 5, characterized in that the first end portion (41) of the auxiliary link (4) is hinged to the body body (1) through a third shaft (411). The third hinge (412) is hinged to the body body (1) through a universal joint, and the second end portion (42) is hinged to the fourth hinge (422) of the door (2) through a fourth shaft (421). It is hinged with the body (1) on or through the universal joint.

7. A three-dimensional hinge system for automobile doors according to claim 2 or 5, characterized in that the first end portion (41) of the auxiliary link (4) is hinged to the body body (1) through a third shaft (411) On the third hinge (412), the second end (42) is hinged on the fourth hinge (422) of the door (2) through the fourth shaft (421), and the first shaft (311), the second The axis (321), the third axis (411), and the fourth axis (421) are parallel to each other, and the main plane G of the main link (3) and the main plane Η of the sub link are parallel to each other and do not overlap.

The three-dimensional hinge system for a vehicle door according to claim 7, characterized in that the angle γ between the first axis (311), the third axis (411) and the plane where the door frame (11) is located is an acute angle.

9. A three-dimensional hinge system for automobile doors according to claim 8, characterized in that the difference between the effective lengths of the main link (3) and the auxiliary link (4) is not more than 10%,

The three-dimensional hinge system for automobile doors according to claim 8, characterized in that the effective length of the main link (3) and the auxiliary link (4) is 1/4 to 3/4 of the width of the door.

11. A three-dimensional hinge system for an automobile door according to claim 8, characterized in that the inside of the door (2) is provided with a groove (21) and a recess respectively accommodating the main link (3) and the auxiliary link (4). The groove (22), the third hinge seat (322) and the fourth hinge seat (422) are fixed to the ends of the groove (21) and the groove (22), respectively.

The three-dimensional hinge system for a vehicle door according to claim 8, characterized in that the first axis (311), the second axis (321), the third axis (411), and the fourth axis (421) Effective length is not less than 100mm.

13. A three-dimensional hinge system for a vehicle door according to claim 8, characterized in that it is between any two of the body (1), the door (2), the main link (3) and the auxiliary link (4) A power drive device (7) or an elastic element (8) is installed.

14. A three-dimensional hinge system for a car door according to claim 2, characterized in that the top of the door frame (11) is recessed inward by a recess (13), and the top of the door (2) extends inwardly by a piece The baffle plate (24) cooperates with the recess (13), the first end portion (41) of the auxiliary link (4) is connected to the top of the body body (1) through a shaft or a universal joint, and the second end portion (42) passes through The shaft or universal joint is connected with the baffle plate (24) on the top of the door (2).

15. A three-dimensional hinge system for a vehicle door according to claim 14, characterized in that a glass window is provided on the baffle (24).

16. A three-dimensional hinge system for a vehicle door according to claim 1, characterized in that the second end portion (32) of the main link (3) includes upper and lower branches (32A) (32B), upper The branch (32A) is connected to the upper part of the window frame of the door (2). The lower branch (32B) is connected to the lower part of the window frame of the door (2).

17. A three-dimensional hinge system for a vehicle door according to claim 1, wherein the main link (3) is also composed of two or more links, each link includes A first end connected to the body (1) and a second end connected to the door (2).

18. A three-dimensional hinge system for a vehicle door according to claim 1, characterized in that the door (2) is a rear door, a first end portion (31) of the main link (3) and a door frame (11) The rear pillar is connected, and the first end portion (41) of the auxiliary link (4) is connected to the body body (1).

19. A three-dimensional hinge system for a car door according to claim 1, wherein the three-dimensional hinge system for a car door is used in a car, a van, an off-road vehicle, a sports car, or a truck.

20. A three-dimensional hinge system for automobile doors according to claim 1, wherein the three-dimensional hinge system for automobile doors is used on a passenger car.