CN111284380A - Emergency locking follow-up mechanism in rapid acceleration movement process - Google Patents
Emergency locking follow-up mechanism in rapid acceleration movement process Download PDFInfo
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- CN111284380A CN111284380A CN202010132452.0A CN202010132452A CN111284380A CN 111284380 A CN111284380 A CN 111284380A CN 202010132452 A CN202010132452 A CN 202010132452A CN 111284380 A CN111284380 A CN 111284380A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/80—Head-rests
- B60N2/888—Head-rests with arrangements for protecting against abnormal g-forces, e.g. by displacement of the head-rest
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Abstract
The invention relates to an emergency locking follow-up mechanism in a rapid acceleration movement process, wherein two ends of a gear metal plate and a stop metal plate are respectively connected with a base and an lug in a pivoting mode to form a main body of a four-bar mechanism, the main body is provided with a locking position between an initial position and an unlocking position, the emergency locking follow-up mechanism comprises a gravity lock which is rotatably installed on one side of the base, and the gravity lock is connected with the stop metal plate through a gravity lock spring piece. According to the invention, through the design of the gravity lock, when the acceleration of the gravity lock is smaller than the critical acceleration, the main body reaches the locking position firstly than the gravity lock; when the acceleration of the gravity lock is larger than the critical acceleration, the gravity lock reaches the locking position before the main body. In addition, the gravity lock can reduce the idle stroke and reach the locking position more quickly by utilizing the omega spring, and provides a homodromous moment action along with the motion direction of the gravity lock, so that the gravity lock can be prevented from rebounding.
Description
Technical Field
The invention relates to the field of automobile seats, in particular to an emergency locking follow-up mechanism in a rapid acceleration motion process.
Background
When the vehicle runs into the rear, the human body falls backwards due to inertia, the pressure of acceleration or deceleration of the vehicle is concentrated on the fragile neck and the head of the human body, and the headrest has a buffering effect on the pressure, so that the human body is protected. In order to allow the headrest to be adjusted back and forth as desired, the headrest is generally equipped with a mechanical movement mechanism for the headrest in both the front and rear directions. In addition, in order to return the headrest to the initial position after the position adjustment, the front-rear two-way headrest mechanical movement mechanism is also equipped with a return mechanism. The reset mechanisms of the front and back two-way headrest mechanical motion mechanisms which are mainstream in the market at present are manual and self-reset. The common manual two-way headrest mechanical movement mechanism has large size and space and the modeling needs to be provided with a button, so that the mechanism is difficult to be applied to headrests with small size and appearance requirements. The self-resetting two-way headrest mechanical movement mechanism is usually a four-bar linkage mechanism, has small space size and does not need button operation, and has exquisite structure and low requirements on the size and the modeling space of the headrest. However, the current self-resetting two-way headrest mechanical movement mechanism still has the following problems: a) in the process of rapid acceleration movement, the unlocking of the two-way self-resetting mechanism is invalid; b) during a high-speed collision, the two-way self-resetting mechanism moves forwards along with the action of inertia force to unlock and then returns to the initial position, and the initial position of the headrest moves backwards relative to the designed position, so that the effective supporting and protecting effect on the head and the neck of a passenger cannot be provided, and the two-way self-resetting mechanism is shown in fig. 1. In addition, in order to withstand the throwing-out of, for example, the backrest frame during a crash with rapid acceleration, the prior art provides emergency locking mechanisms which are of complex design and can only be applied to specific projects, and which are not referenced to four-bar linkages.
Disclosure of Invention
The invention provides an emergency locking follow-up mechanism in an emergency acceleration process, which solves the problem that a mechanical mechanism of a self-resetting front-back two-way headrest in the prior art is unlocked and invalid in the emergency acceleration process, and solves the problem that the headrest cannot restore to an initial position and cannot provide effective supporting and protecting effects for the head and neck of a passenger.
The invention provides an emergency locking follow-up mechanism in a rapid acceleration movement process, which comprises a base, a gear metal plate, a stop metal plate and an lug, wherein two ends of the gear metal plate are respectively and pivotally connected to the base and the lug, and two ends of the stop metal plate are also respectively and pivotally connected to the base and the lug, so that a main body of a four-bar linkage mechanism is formed, the main body rotates between an initial position and an unlocking position, the main body is also provided with a locking position between the initial position and the unlocking position, the emergency locking follow-up mechanism further comprises a gravity lock which is rotatably arranged on one side of the base, and the gravity lock is connected with the stop metal plate through a gravity lock reed; when the acceleration of the gravity lock is smaller than the critical acceleration, the gravity lock does not take effect, the main body reaches a locking position before the gravity lock, and the main body pushes the side surface of the gravity lock to reach an unlocking position through the locking position; when the acceleration of the gravity lock is larger than the critical acceleration, the gravity lock takes effect, the gravity lock reaches the locking position before the main body, and the main body is limited by the gravity lock to stay at the locking position.
The body deflection angle displacement W1Time t of1Deflection angle displacement W of the gravity lock2Time t of2The ratio of the components is as follows:
in the formula, K1Subject acceleration, α1Is a horizontal included angle, R, of the main body movement direction1Is the radius of motion of the center of gravity of the main body part, K2Acceleration for gravity locks, α2Is a horizontal included angle R of the movement direction of the gravity lock2Is the gravity lock gravity center movement radius.
The base through first pivot with the bottom of gear panel beating links to each other, through the second pivot with the bottom of ending the position panel beating links to each other, the top of gear panel beating through the third pivot with the auricle links to each other, the top of ending the position panel beating through the fourth pivot with the auricle links to each other, and a torsion spring passes through first pivot is rotationally installed the inboard of base, then urgent locking servo mechanism's equilibrium equation is:
in the formula, FTorsion springIs the pretightening force of the torsion spring, and is more than or equal to ma, m is the mass of the headrest, a is the acceleration of the headrest, α is the included angle between the direction of the operating force and the connecting line between the third rotating shaft and the first rotating shaft, L is the distance between the center of the fourth rotating shaft and the center of the second rotating shaft, L2The distance from the action direction of the torsion spring to the center of the first rotating shaft.
The equilibrium equation of the subject is:
in the formula, K1Is the acceleration of the subject; l is1Is the distance from the center of gravity of the main body to the center of the first rotating shaft, m1Mass of the main body, α3Is the angle between the torsional spring action direction and the vertical direction, FTorsion springIs the pretightening force of the torsion spring.
The balance equation of the gravity lock is as follows:
in the formula, FOmegaIs the pre-tightening force m of gravity lock omega spring2As mass of gravity lock, K2For acceleration of gravity lock, L3Is the distance L from the center of the first rotating shaft to the direction of the inertial force borne by the gravity lock4Is the distance from the centre of the first axis of rotation to the direction of action of the gravity lock omega spring 15.
The top of gravity lock is equipped with a convex platform, forms into the locking face, and the area S of this locking face is:
in the formula, FPunching machineExternal force, σ, applied to the locking surface1To an impact stress less than the yield stress of the material of the locking face, FaFor locking the external force applied to the follower during movement in an emergency, LaFor locking the vertical distance L from the force-bearing point of the follower to the second rotary shaft in case of emergencyPunching machineThe vertical distance from the second rotating shaft to the force bearing direction of the locking surface.
Mass m of the gravity lock2And the position of the center of gravity is determined by:
m2gLG＝M＝Fomega×L4，
Wherein g is the acceleration of gravity, LGIs a gravity force arm, M is a torque force arm of a gravity lock omega spring, FOmegaL4 is the distance from the first pivot to the first mounting hole for the force of gravity locking omega spring 15.
The torque arm M of the gravity lock omega spring is as follows:
M＝Fomega×L4＝FInertial force 2×L3，F3＝m2×g×K2，
In the formula, FInertial force 2Is the inertial force of gravity lock, L3Is the arm of inertia force of the gravity lock, m2As mass of gravity lock, K2Is the acceleration of the gravity lock.
And an extended swing arm is arranged on the side surface of the gravity lock and used for limiting the movement range of the gravity lock.
The swing arm is at time t2Angle W of position2Comprises the following steps:
in the formula, C2For angular acceleration of gravity lock, K2Acceleration for gravity locks, α2Is a horizontal included angle R of the movement direction of the gravity lock2Is the gravity lock gravity center movement radius.
And a counterweight structure is arranged below the gravity lock.
A first mounting hole is formed in the swing arm of the gravity lock, and a second mounting hole is formed in the stop metal plate.
The gravity lock reed is a gravity lock omega spring.
According to the gravity lock, the locking position is arranged between the initial position and the unlocking position, the gravity lock is arranged on one side of the base, and the locking surface, the counterweight structure, the swing arm and the gravity lock omega spring of the gravity lock are designed, so that when the acceleration of the gravity lock is larger than the critical acceleration, the gravity lock reaches the locking position before the main body, the main body is limited by the gravity lock and stays at the locking position, and the locking state of the two-way self-resetting mechanism is maintained. In addition, the gravity lock can reduce the idle stroke and reach the locking position more quickly by utilizing the omega spring, and provides a homodromous moment action along with the motion direction of the gravity lock, so that the gravity lock can be prevented from rebounding.
Drawings
FIG. 1 is a schematic view of a prior art two-way self-resetting mechanism showing a change in position of a headrest during rapid acceleration movement;
FIG. 2 is a schematic structural view of an emergency lock-up follower according to the present invention;
FIG. 3 is an exploded view of the emergency lock follower in accordance with the present invention;
FIG. 4 is a schematic diagram of the movement of the emergency lock follower in accordance with the present invention;
fig. 5 is a schematic diagram of the movement of the emergency locking follower in the event of a gravity lock being activated according to the invention;
fig. 6 is a schematic diagram of the movement of the gravity lock in the emergency lock follower mechanism when not in effect according to the present invention;
FIG. 7 is a schematic diagram of the structure of the gravity lock in the emergency lock servo mechanism according to the invention;
FIG. 8 is a schematic view of the connection between the gravity lock and the stop plate in the emergency locking servo mechanism according to the present invention;
FIG. 9 is a force analysis diagram of the emergency locking servo mechanism under the action of an external force;
FIG. 10 is a force analysis graph of a gravity lock under impact force;
FIG. 11 is a schematic illustration of calculating the gravity lock swing arm angular position;
FIG. 12 is a schematic view of a gravity lock and a detent sheet metal lock;
FIG. 13 is a schematic view of the forward most point of the stop plate contacting the side of the gravity lock;
FIG. 14 is a schematic illustration of determining the mass and center of gravity position of a gravity lock;
FIG. 15 is an analysis of the force applied by the torsion spring;
FIG. 16 is a force analysis graph of the emergency locking follower when in motion;
FIG. 17 is a force analysis graph of the gravity lock during movement;
FIG. 18 is a schematic illustration of calculating a body portion swing arm angular position;
fig. 19(a) is a schematic diagram of the gravity lock entering an active position in the presence of an omega spring, and fig. 19(b) is a schematic diagram of the gravity lock entering an active position in the absence of an omega spring;
fig. 20 is a schematic diagram of the two-way follow-up hold of the emergency lock-up follow-up mechanism according to the present invention.
Detailed Description
The preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
As shown in fig. 2 and 3, the emergency locking following mechanism of the present invention includes a base 1, a gear metal plate 2, a stop metal plate 3 and an ear plate 8, wherein the base 1 is fixed on a headrest rod (not shown), the ear plate 8 is fixed on a headrest housing (not shown), two ends of the gear metal plate 2 are respectively pivotally connected to the base 1 and the ear plate 8, two ends of the stop metal plate 3 are also respectively pivotally connected to the base 1 and the ear plate 8, so as to form a four-bar linkage mechanism, and when an external force acts on the headrest housing, the ear plate 8 drives the gear metal plate 2 and the stop metal plate 3 to rotate relative to the base 1 (i.e., the headrest rod). Specifically, base 1 links to each other through first pivot 10 and gear panel beating 2's bottom, and base 1 links to each other through second pivot 9 and the bottom of ending a position panel beating 3, and the top of gear panel beating 2 links to each other with the auricle 8 of two symmetries through third pivot 11, and the top of ending a position panel beating 3 links to each other with auricle 8 through fourth pivot 12.
The emergency locking follow-up mechanism further comprises a ratchet toothed plate 4 which is fixedly connected to the base 1 through a toothed plate omega spring 7. Specifically, the end surface of the ratchet tooth plate 4 facing the shift position metal plate 2 has shift position teeth 41 thereon, which cooperate with the lower edge 21 of the shift position metal plate 2 to set a specific shift position of the four-bar linkage. In addition, the middle part of the ratchet tooth plate 4 is provided with a through hole 42, and the ratchet push rod 13 fixedly arranged on the gear metal plate 2 passes through the through hole 42 to extend so as to match with the wall surface thereof to limit the rotation range of the gear metal plate 2.
The locking and unlocking principle of the four-bar linkage mechanism of the emergency locking follow-up mechanism is shown in fig. 4, when the headrest shell is pushed, the lug 8 connected with the headrest shell drives the gear metal plate 2 and the stop metal plate 3 to turn forwards by 8 degrees to reach a first gear, turn over by 16 degrees to reach a second gear, turn over by 26 degrees to reach a third gear, turn over by 36 degrees to reach a fourth gear, turn over by 47 degrees to reach an unlocking position, and finally return to the initial gear.
The emergency locking follow-up mechanism further comprises a torsion spring 6 which is rotatably arranged on the inner side of the base 1 through a first rotating shaft 10, and two ends of the torsion spring are respectively connected with the base 1 and the gear metal plate 2 so as to generate an acting force opposite to the rotating direction of the gear metal plate 2 when the gear metal plate 2 rotates, so that the torsion spring is used for driving the four-bar mechanism to reset and ensuring that a headrest cannot be thrown out due to inertia force in the emergency braking process.
In addition, the emergency locking follow-up mechanism further comprises a gravity lock 5 which is rotatably arranged on the outer side of the base 1 through a first rotating shaft 10, and the gravity lock 5 is connected with the stop metal plate 3 through a gravity lock omega spring 15. In this embodiment, POM washers 14 are respectively disposed on both sides of the gravity lock 5 to reduce friction loss when the gravity lock is rotated.
As shown in fig. 5, when the gravity lock 5 is effective, the acceleration of the gravity lock is greater than the critical acceleration, the gravity lock 5 reaches the locking position before the main body, the stop metal plate 3 is turned 38 degrees to reach the locking surface of the gravity lock 5, and cannot enter the unlocking position (that is, cannot reach the unlocking position which can be reached by turning 47 degrees of the stop metal plate 3 shown in fig. 4), and the main body is limited by the gravity lock to stay at the locking position, so that the mechanism is locked.
As shown in fig. 6, when the gravity lock 5 is not in effect, the acceleration of the gravity lock is smaller than the critical acceleration, the main body reaches the locking position before the gravity lock 5, the stop metal plate 3 is turned by 42 degrees and contacts with the side surface of the gravity lock, at this time, the stop metal plate 3 pushes the gravity lock to be turned by 5 degrees continuously and enter the unlocking position shown in fig. 4, that is, the main body pushes the side surface of the gravity lock to pass through the locking position and reach the unlocking position, so that the mechanism is unlocked.
The gravity lock 5 is designed as shown in fig. 7 and 8, and a central hole 51 is formed in a middle portion thereof, and the first rotating shaft 10 passes through the central hole 51 as a rotation center of the movement of the gravity lock 5. A raised platform is provided above the gravity lock 5 forming a locking surface 52, below which a counterweight structure 54 is provided, and an extended swing arm 53 is provided at the side of the gravity lock 5. The swing arm 53 is provided with a first mounting hole 55 for inserting one end of the gravity lock omega spring 15, and the other end of the gravity lock omega spring 15 is inserted into the second mounting hole 31 of the stop metal plate 3. Wherein, the design parameters of the gravity lock 5 include: area S of lock surface 52 and swing arm 53 at time t2Angle W of position2Mass m of the gravity lock 5 by means of a counterweight structure 542And the position of the center of gravity and the torque arm M of the gravity lock omega spring 15.
As shown in fig. 9 and 10, the area S of the lock surface 52 is calculated according to the formula (1):
in the formula, FPunching machineExternal force, σ, applied to the locking surface 521To an impact stress less than the yield stress of the material of the locking face, FaFor locking the external force applied to the follower during movement in an emergency, LaFor emergency locking of the vertical distance, L, from the force-bearing point of the follower to the second axis of rotation 9Punching machineThe perpendicular distance from the second rotating shaft 9 to the force bearing direction of the locking surface.
As shown in fig. 11, the swing arm 53 is at time t2Angle W of position2Calculating according to the formula (2):
in the formula, C2For angular acceleration of gravity lock, K2Acceleration for gravity locks, α2Is a horizontal included angle R of the movement direction of the gravity lock2For movement of gravity lock centre of gravityA radius.
With continued reference to fig. 12 and 13, the radius from the foremost point of the stop sheet metal 3 to the second rotating shaft 9 is R2(ii) a The distance from the highest point of the gravity lock 5 to the center of the first rotating shaft 10 is R1The distance from the center of the second rotating shaft 9 to the center of the first rotating shaft 10 is L; the contact point of the gravity lock 5 and the stop metal plate 3 is O1(ii) a The contact point of the foremost point of the stop metal plate 3 and the side edge of the gravity lock 5 is O2. Due to L and R2As is known, from the engagement curve of the movement trajectory, O can be determined1Location. When the stop metal plate 3 is overturned by 47 degrees, the foremost point of the stop metal plate 3 contacts the side edge of the gravity lock 5, so that O can be determined2Location. From O1And O2The positions of two upper and lower gear positions of the swing arm of the gravity lock 5 can be confirmed.
Referring again to fig. 10 and 14, the mass m of the gravity lock 52And the position of the center of gravity is calculated by the formula (3):
m2gLG＝M＝Fomega×L4， (3)
Wherein g is the acceleration of gravity, LGIs a gravity force arm, M is a torque force arm of the gravity lock omega spring 15, FOmegaL4 is the distance from the first pivot to the first mounting hole for the force of gravity locking omega spring 15.
The torque arm M of the gravity lock omega spring 15 is calculated by equation (4):
M＝Fomega×L4＝FInertial force 2×L3，F3＝m2×g×K2, (4)
In the formula, FInertial force 2Is the inertial force of gravity lock, L3Is the arm of inertia force of the gravity lock, m2As mass of gravity lock, K2Is the acceleration of the gravity lock.
As can be seen from the structure of the emergency locking follow-up mechanism and the design parameters of the gravity lock, the critical acceleration of the gravity lock 5 determines whether the gravity lock 5 is effective and how fast the gravity lock 5 is effective, and the torsion spring 6 determines the critical acceleration of the mechanism. The following describes a specific balance equation of the emergency lock-up follow-up mechanism.
As shown in fig. 15, the balance equation of the emergency lock-up follow-up mechanism is shown in equation (5):
in the formula, FTorsion springThe pre-tightening force of the torsion spring 6 is larger than or equal to ma, m is the mass of the headrest, a is the acceleration of the headrest, L is the distance from the center of the fourth rotating shaft to the center of the second rotating shaft, α is the included angle between the direction of the operating force and the connecting line of the third rotating shaft and the first rotating shaft, and L is the included angle between the direction of the operating force and the connecting line of the third rotating shaft2The distance from the action direction of the torsion spring to the center of the first rotating shaft. And (4) when the simulated acceleration exceeds 1.5G, the headrest is unlocked, and the pre-tightening force of the torsion spring is calculated to be more than or equal to 125.4N. And calculating to obtain the torsion spring pretightening force range of 96.4N-191N according to the requirement of 40 +/-20N on the front and rear two-direction operating force. Therefore, the range of the pretightening force value of the torsion spring is about 125.4N-191N.
As shown in fig. 16, the balance equation of the main body portion of the emergency lock follower other than the gravity lock 5 is shown in formula (6):
in the formula, K1Is the acceleration of the body portion; l is1Is the distance from the center of gravity of the main body part to the center of the first rotation axis, m1Mass of the body portion α3Is the angle between the torsional spring action direction and the vertical direction, FTorsion springIs the value calculated for equation (4).
As shown in fig. 17, the equilibrium equation of the gravity lock portion of the emergency lock follower is shown in equation (7):
in the formula, FOmegaIs the pre-tightening force m of the gravity lock omega spring 152As mass of gravity lock, K2For acceleration of gravity lock, L3The distance from the center of the first rotating shaft to the direction of the inertial force borne by the gravity lock (namely the acting arm of the gravity lock); l is4Is in the first rotating shaftThe distance from the center to the action direction of the gravity lock omega spring 15 (namely the action arm of the gravity lock omega spring) when the acceleration K of the main body part1Acceleration K of gravity lock2When the gravity lock 5 starts to move relative to the main body part, the critical acceleration K of the gravity lock can be controlled by designing the omega spring pretightening force of the gravity lock2。
The principle of the gravity lock of the emergency locking follow-up mechanism of the present invention is shown in fig. 11 and 18, and the gravity lock is operated at time t2Angle W of position2Calculated according to equation (2), the body portion is at time t1Is calculated according to equation (8):
in the formula, C1Is the angular acceleration of the main part, K1Acceleration of body part α1Is a horizontal included angle, R, of the main body part moving direction1The radius of motion of the center of gravity of the main body part.
From the equations (2) and (7), the body portion deflection angular displacement W can be derived1Time t of1Angle displacement W of gravity lock2Time t of2Calculating according to the formula (9):
when t is1/t2When the height is larger than 1, the gravity lock has the priority that the main body part enters the action position to play a role in limiting the unlocking of the mechanism.
The action principle of the follow-up stroke compensation structure of the emergency locking follow-up mechanism is shown in fig. 19(a) and (b), when the gravity lock omega spring 15 acts, the gravity lock 5 only needs to be turned upwards by 16 degrees to enter an acting position, and compared with the condition that the middle gravity lock omega spring 15 does not exist, the angular displacement stroke of the gravity lock 5 is shortened by 20 degrees. From equation (2), the reaction time of the gravity lock is reduced 1/3. That is, the use of gravity locks omega springs allows the gravity lock to reach the locking position faster with reduced lost motion.
Taking the four-seat two-way core item as an example, substituting each parameter into the above calculation formula can obtain: mass m of the main body part1Weight lock mass m of (2-0.4) kg2＝0.005763kg；L1＝29.03mm， L2＝18.375mm，L3＝12mm，L4＝6.52mm；FTorsion spring125.42N. By the formula:
and when G is1＝G2When, G1＝G2＝49.6m/s2It can be found that the headrest arrival time C1＝G1*Sin 49.6/R1＝1286.6rad/s2，t10.257 s; gravity lock arrival time C2＝G2*Sin 60.6/R2＝5720.7 rad/s2，t20.0897s, and then t1>t2. It can thus be verified that the gravity lock will reach the active position in preference to the four-bar linkage, thereby ensuring that the mechanism is locked in the crash test.
The mechanical principle of the bidirectional follow-up maintaining structure of the emergency locking follow-up mechanism is shown in fig. 20, the direction of the gravity lock omega spring 15 is always the connecting line of the first mounting hole 55 and the second mounting hole 31, the connecting line of the second mounting hole 31 and the center of the first rotating shaft 10 is a balance line, and when the position of the first mounting hole 55 crosses the balance line, the moment of the omega spring 15 is reversed. When the gravity lock 5 does not cross the balance line during the non-rapid acceleration motion, the torque generated by the torsion spring of the omega spring 15 is always clockwise downward, and the gravity lock 5 is kept at the non-acting position; during rapid acceleration movement, the gravity lock 5 crosses the balance line, and the torque generated by the torsion spring of the omega spring 15 is always anticlockwise and upwards to keep the gravity lock 5 at the acting position. The invention provides a homodromous moment effect along with the movement direction of the gravity lock by utilizing the mechanical property of the omega spring, and can prevent the gravity lock from rebounding.
The above embodiments are merely preferred embodiments of the present invention, which are not intended to limit the scope of the present invention, and various changes may be made in the above embodiments of the present invention. All simple and equivalent changes and modifications made according to the claims and the content of the specification of the present application fall within the scope of the claims of the present patent application. The invention has not been described in detail in order to avoid obscuring the invention.
Claims (13)
1. An emergency locking follow-up mechanism in a rapid acceleration movement process comprises a base, a gear metal plate, a stop metal plate and an lug, wherein two ends of the gear metal plate are respectively and pivotally connected to the base and the lug, and two ends of the stop metal plate are respectively and pivotally connected to the base and the lug, so that a main body of a four-bar linkage mechanism is formed, and the main body rotates between an initial position and an unlocking position; when the acceleration of the gravity lock is smaller than the critical acceleration, the gravity lock does not take effect, the main body reaches a locking position before the gravity lock, and the main body pushes the side surface of the gravity lock to reach an unlocking position through the locking position; when the acceleration of the gravity lock is larger than the critical acceleration, the gravity lock takes effect, the gravity lock reaches the locking position before the main body, and the main body is limited by the gravity lock to stay at the locking position.
2. The emergency lock follower of claim 1 wherein the body yaw angular displacement W1Time t of1Deflection angle displacement W of the gravity lock2Time t of2The ratio of the components is as follows:
in the formula, K1Subject acceleration, α1Is a horizontal included angle, R, of the main body movement direction1Is the radius of motion of the center of gravity of the main body part, K2Acceleration for gravity locks, α2Is a horizontal included angle R of the movement direction of the gravity lock2Is the gravity lock gravity center movement radius.
3. The emergency locking follow-up mechanism according to claim 1, wherein the base is connected to the bottom of the gear metal plate through a first rotating shaft, and is connected to the bottom of the stop metal plate through a second rotating shaft, the top of the gear metal plate is connected to the lug through a third rotating shaft, the top of the stop metal plate is connected to the lug through a fourth rotating shaft, a torsion spring is rotatably mounted on the inner side of the base through the first rotating shaft, and then the balance equation of the emergency locking follow-up mechanism is as follows:
in the formula, FTorsion springIs the pretightening force of the torsion spring, and is more than or equal to ma, m is the mass of the headrest, a is the acceleration of the headrest, α is the included angle between the direction of the operating force and the connecting line between the third rotating shaft and the first rotating shaft, L is the distance between the center of the fourth rotating shaft and the center of the second rotating shaft, L2The distance from the action direction of the torsion spring to the center of the first rotating shaft.
4. The emergency lock-up follower of claim 3, wherein the body's balance equation is:
in the formula, K1Is the acceleration of the subject; l is1Is the distance from the center of gravity of the main body to the center of the first rotating shaft, m1Mass of the main body, α3Is the angle between the torsional spring action direction and the vertical direction, FTorsion springIs the pretightening force of the torsion spring.
5. The emergency locking follower of claim 3 wherein the balance equation for the gravity lock is:
in the formula, FOmegaIs the pre-tightening force m of gravity lock omega spring2As mass of gravity lock, K2For acceleration of gravity lock, L3Is the distance L from the center of the first rotating shaft to the direction of the inertial force borne by the gravity lock4Is the distance from the centre of the first axis of rotation to the direction of action of the gravity lock omega spring 15.
6. The emergency locking servo-mechanism of claim 3, wherein a convex platform is provided above the gravity lock, and is formed as a locking surface, and the area S of the locking surface is:
in the formula, FPunching machineExternal force, σ, applied to the locking surface1To an impact stress less than the yield stress of the material of the locking face, FaFor locking the external force applied to the follower during movement in an emergency, LaFor locking the vertical distance L from the force-bearing point of the follower to the second rotary shaft in case of emergencyPunching machineThe vertical distance from the second rotating shaft to the force bearing direction of the locking surface.
7. The emergency locking follower of claim 3 wherein the mass m of the gravity lock2And the position of the center of gravity is determined by:
m2gLG＝M＝Fomega×L4，
Wherein g is the acceleration of gravity, LGIs a gravity force arm, M is a torque force arm of a gravity lock omega spring, FOmegaL4 is the distance from the first pivot to the first mounting hole for the force of gravity locking omega spring 15.
8. The emergency locking follower of claim 7 wherein the torque arm M of the gravity lock omega spring is:
M＝Fomega×L4＝FInertial force 2×L3，F3＝m2×g×K2，
In the formula, FInertial force 2Is the inertial force of gravity lock, L3Is the arm of inertia force of the gravity lock, m2As mass of gravity lock, K2Is the acceleration of the gravity lock.
9. The emergency lock follower of claim 1 wherein the side of the gravity lock is provided with an extended swing arm to limit the range of motion of the gravity lock.
10. The emergency locking follower of claim 8 wherein the swing arm is at time t2Angle W of position2Comprises the following steps:
in the formula, C2For angular acceleration of gravity lock, K2Acceleration for gravity locks, α2Is a horizontal included angle R of the movement direction of the gravity lock2Is the gravity lock gravity center movement radius.
11. The emergency locking follower of claim 1 wherein a counterweight is positioned below the gravity lock.
12. The emergency locking follow-up mechanism according to claim 10, wherein a first mounting hole is formed in a swing arm of the gravity lock, and a second mounting hole is formed in the stop metal plate.
13. The emergency detent follower of claim 10, wherein said gravity lock spring leaf is a gravity lock omega spring.
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| CN111284380B CN111284380B (en) | 2021-01-29 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114043908A (en) * | 2021-12-15 | 2022-02-15 | 东风汽车集团股份有限公司 | Protection system and protection method for dealing with automobile rear-end collision |
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| CN1774354A (en) * | 2003-04-14 | 2006-05-17 | 株式会社宇宝技术 | Device for moving headrest back and forth |
| CN101204935A (en) * | 2006-12-22 | 2008-06-25 | 凯波有限责任两合公司 | Cushion initiative type headrest |
| CN203255001U (en) * | 2013-05-16 | 2013-10-30 | 岱山县金鑫海绵制品有限公司 | Headrest of seat of automobile |
| CN207360162U (en) * | 2017-10-10 | 2018-05-15 | 宋阳 | A kind of car seat headrest adjusting mechanism |
| KR20190112538A (en) * | 2018-03-26 | 2019-10-07 | 현대자동차주식회사 | Locking Robustness type Sliding Headrest |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1774354A (en) * | 2003-04-14 | 2006-05-17 | 株式会社宇宝技术 | Device for moving headrest back and forth |
| CN101204935A (en) * | 2006-12-22 | 2008-06-25 | 凯波有限责任两合公司 | Cushion initiative type headrest |
| CN203255001U (en) * | 2013-05-16 | 2013-10-30 | 岱山县金鑫海绵制品有限公司 | Headrest of seat of automobile |
| CN207360162U (en) * | 2017-10-10 | 2018-05-15 | 宋阳 | A kind of car seat headrest adjusting mechanism |
| KR20190112538A (en) * | 2018-03-26 | 2019-10-07 | 현대자동차주식회사 | Locking Robustness type Sliding Headrest |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114043908A (en) * | 2021-12-15 | 2022-02-15 | 东风汽车集团股份有限公司 | Protection system and protection method for dealing with automobile rear-end collision |
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| CN111284380B (en) | 2021-01-29 |
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Address after: 201315 No. 669, kang'an Road, Kangqiao Industrial Zone, Pudong New Area, Shanghai Patentee after: Yanfeng international Seat System Co., Ltd Address before: 201315 No. 669, kang'an Road, Kangqiao Industrial Zone, Pudong New Area, Shanghai Patentee before: Yanfeng andotuo seat Co., Ltd |
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