JPH10266661A - Steering lock device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve strength and productivity by forming a lock pin to be engaged with a steering shaft as a dimensionally specified rectangular cross section, and molding it by a press. SOLUTION: A lock mechanism slidingly moves a lock pin 39 held in a housing of a steering lock device by a slider, and switches the pin 39 to a lock condition of preventing rotation of a shaft 17 by engaging with an engaging recessed part 38 of the steering shaft 17 and a lock release condition of making the shaft 17 rotatable by releasing engagement. Next, the pin 39 is formed in a plate shape by press molding, and a cross section is formed in an equilateral quadrangular shape, and when a length of the side running in the axial direction of the shaft 17 is denoted by H mm and a length of the side orthogonal to this is denoted by B mm and a diameter of the shaft 17 is denoted by D mm, (H>=16) is realized, and 6>=B>= 13050/(D.H)}<1/2> is realized. Therefore, the lock pin can be easily manufactured, and a strength limit of the lock mechanism can be improved by balancing flexural strength of the lock pin and strength of a lock pin fitting part of the housing.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a steering column pipe having a housing having a guide projection fitted into a fitting hole of the steering column pipe. The present invention relates to a steering lock device configured such that a lock mechanism having a lock pin formed in a square shape can switch between engagement and disengagement of a lock pin with an engagement recess according to rotation of a rotor.

[0002]

2. Description of the Related Art Conventionally, such a steering lock device is already known, for example, from Japanese Utility Model Publication No. 3-27891.

[0003]

By the way, a bending load is applied to the lock pin of the lock mechanism by the turning torque of the steering shaft while the lock pin is engaged with the engagement recess. Therefore, in the above conventional one,
When the length of the first side along the axial direction of the steering shaft in the cross-sectional shape of the lock pin is H, and the length of the second side orthogonal to the first side is B, ｛Z = (1/6)・ H ・
The length B is set relatively large so that the section modulus Z of the lock pin expressed as B ^{2 2} is increased to increase the bending strength of the lock pin, for example, 1 ≧ B
The lengths B and H are set so that /H≧0.5.

However, if the bending strength of the lock pin is set to be excessive, the strength of the contact portion between the guide projection and the fitting hole provided in the steering column pipe for fitting the guide projection is increased. In order to improve the strength limit of the lock mechanism, the deformation will occur at the guide protrusion and the fitting contact part of the fitting hole before the deformation of the lock pin. It is necessary to balance the bending strength of the lock pin with the strength of the fitting contact portion of the guide projection and the fitting hole.

The present invention has been made in view of such circumstances, and balances the bending strength of a lock pin with the strength of a fitting contact portion of a guide projection and a fitting hole to limit the strength of a lock mechanism. It is an object of the present invention to provide a steering lock device that can be improved.

[0006]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a steering shaft provided with an engagement recess on an outer surface, and a steering shaft corresponding to the engagement recess along the axial direction of the steering shaft. A steering column pipe having a fitting hole at a position and surrounding the steering shaft, a housing attached to the steering column pipe having a guide projection fitted into the fitting hole, and inserted into the housing;
A cylinder body to be fixed, a rotor inserted into the cylinder body so as to be capable of rotating operation by an inserted key, and a engaging recess formed in a sliding hole opened at a tip of the guide projection and provided in a housing. And a lock pin that is slidably fitted so as to be able to be engaged with the engagement recess, and is configured to be able to switch between engagement and disengagement of the lock pin with the engagement recess in accordance with rotation of the rotor. The lock pin is formed so as to have a square cross-sectional shape including a first side along the axial direction of the steering shaft and a second side orthogonal to the first side. In the steering lock device, when the length of the first side of the lock pin is Hmm, the length of the second side of the lock pin is Bmm, and the diameter of the steering shaft is Dmm, H ≧ 166 ≧ B ≧ ｛13050 / ( · H)} ^1/2 wherein a length B which satisfies, with a H, the lock pin is characterized in that it is press-molded.

According to such a configuration, the stress at the fitting contact portion of the guide projection and the fitting hole decreases as H increases, but by satisfying H ≧ 16, the stress is reduced. It is possible to converge almost to the lower limit level, and 6 ≧
By satisfying B, it is possible to press-mold the lock pin. Further, by satisfying B ≧ {13050 / (DH)} ^1/2 , the lock pin can be provided with a necessary and sufficient bending strength. it can.

[0008]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiments of the present invention will be described below based on one embodiment of the present invention shown in the accompanying drawings.

FIGS. 1 to 9 show an embodiment of the present invention. FIG. 1 is a longitudinal sectional side view of a steering lock device, FIG. 2 is an enlarged sectional view taken along line 2-2 of FIG. 1, and FIG. 2 of 3
FIG. 4 is an enlarged sectional view taken along line 4-4 of FIG. 2, and FIG.
FIG. 6 is a simplified diagram corresponding to FIG. 3 for explaining the relationship between stress and dimensions, FIG. 6 is a diagram showing a stress ratio according to the size of a lock pin along the axial direction of the steering shaft, and FIG. FIG. 8 is a view showing a stress ratio of the guide protrusion according to a distance from the center of the lock pin to a side surface of the fitting hole in a plane perpendicular to the plane. FIG. 8 shows the center of the lock pin in a plane perpendicular to the axis of the steering shaft. FIG. 9 is a diagram in which the distance from the fitting to the side surface of the fitting hole is determined according to the diameter of the steering column pipe.
FIG. 9 is a diagram viewed from a direction along line 9-9 in FIG. 3.

Referring first to FIG. 1, this steering lock device comprises a housing 11, a cylinder body 12 inserted and fixed to the housing 11, and a key 1 inserted therein.
And a rotor 14 inserted into the cylinder body 12 so as to be rotatable by the rotor 3 and engaged with the rotor 14 so as not to be able to rotate relative thereto, and coaxially disposed behind the rotor 14 to be rotatable with respect to the housing 11. Joint 15 supported by
A lock state in which the rotation of the steering shaft 17 (see FIGS. 2 and 3) is prevented and an unlocked state in which the rotation of the steering shaft 17 is enabled can be switched according to the rotation of the rotor 14 and the joint 15. Lock mechanism 1
6 is provided.

Referring to FIGS. 2 and 3, the steering shaft 17 is coaxially surrounded by a fixed steering column pipe 18.
A mounting surface 19 having a circular cross section and in contact with the outer periphery of the housing 8 is provided on a mounting portion 11 a integral with the housing 11. A column holder 21 having a mounting surface 20 having an arc-shaped cross section in contact with the outer periphery of the steering column pipe 18 on a side opposite to the mounting surface 19 is fastened to the mounting portion 11a by a pair of bolts 22,22. That is, the housing 11 is attached to the steering column pipe 18.

Referring again to FIG. 1, the cylinder body 12 is inserted into the front half of a housing hole 23 provided in the housing 11, and a resilient engagement member 24 mounted on the outer periphery of the cylinder body 12. Is resiliently engaged with an engagement groove 25 provided on the inner surface of the storage hole 23 so that the cylinder body 1
The axial movement in the second storage hole 23 is prevented.

The rotor 14 has a key hole 26 having an open front end.
, And is inserted into the cylinder hole 27 of the cylinder body 12 so as to be rotatable and movable within a limited range along the axial direction. In addition, grooves 2 extending along the axial direction of the cylinder hole 27 are provided at a plurality of locations spaced circumferentially on the inner surface of the cylinder hole 27.
Are provided, and a plurality of tumblers 29 urged in a direction to engage with the grooves 28 are provided on the rotor 14.
Attached to. Thus, each tumbler 29...
When the key 13 is not inserted into the key hole 26, the rotor 13 is engaged with the groove 28 to prevent the rotation of the rotor 14.
Slide to a position that allows the rotation of.

At the front end of the rotor 14, the key 13 is inserted into the rotor 14 and the key 1 from the rotor 14 is inserted.
The key slider 30 is mounted so as to be able to slide in a direction along one diameter line of the rotor 14 in accordance with the extraction of the key 3. One end of the key slider 30 is in contact with a front end of an operation lever 32 supported on the housing 11 via a support shaft 31. Between the operation lever 32 and the housing 11, a front end of the operation lever 32 is provided. A spring 33 that exerts a spring force in the direction of pressing the key slider 30 is provided. When the key 13 is removed from the key hole 26 and the rotor 14 is at the LOCK position, the key slider 3
0 is pressed to a position where the other end protrudes from the outer surface of the rotor 14, and the key hole 26 and the key slider 3
When the key 13 is inserted into the key slider 0, as shown in FIG. 1, the key slider 30 is brought up to a position where both end surfaces thereof are flush with the outer surface of the rotor 14 against the resilient force applied from the operating lever 32. The key slider 30 will move,
When the rotor 14 rotates in this state, one end of the operating lever 32 comes into sliding contact with the outer surface of the rotor 14. In addition, a key detection switch 35 that detects operation in accordance with the operation of the operation lever 32 is attached to the housing 11 to detect insertion of the key 13 into the rotor 14.

A joint 15 is supported on the housing 11 at the rear side of the rotor 14 so as to be unable to move in the axial direction and to be rotatable around the axis. Is engaged with the rear end portion so as not to rotate relatively. That is, the joint 15
Rotates with the rotor 14. Further, a spring 36 is provided between the joint 15 and the rotor 14, and the rotor 14 is urged forward by the spring force of the spring 36.

An ignition switch 37 is attached to the rear end of the housing 11, and the rear end of the joint 15 is connected to the ignition switch 37.

The locking mechanism 16 engages with an engagement recess 38 provided on the outer periphery of the steering shaft 17 to prevent the steering shaft 17 from rotating.
And a lock release state in which the steering shaft 17 can be rotated by releasing the engagement with the engagement recess 38, and sliding in a direction for switching between the engagement with the engagement recess 38 and the release of the engagement. A lock pin 39 supported by the housing 11 and a slider 40 engaged with and connected to the lock pin 39 and slidably supported by the housing 11.

The mounting recess 11 is provided in the mounting portion 11a of the housing 11 along the axial direction of the steering shaft 17.
And a guide projection 11b projecting from the mounting surface 19 at a position corresponding to the guide projection 11b.
Are fitted in fitting holes 41 provided in the steering column pipe 18. Moreover, the distal end surface of the guide projection 11b is formed in an arc shape in cross section so as to be flush with the inner surface of the steering column pipe 18. The guide projection 11b has a bending strength of the lock pin 39 in the locked state to prevent the steering shaft 17 from being rotated by an excessive force and being unlocked improperly when the lock mechanism 16 is in the locked state. Is to ensure the effective.

The housing 11 has a first sliding hole 42 having one end opened at the tip of the guide projection 11b, and a first sliding hole 42 which is larger than the first sliding hole 42 and is connected to the other end of the first sliding hole 42. 2
A sliding hole 43 is provided so as to form a step 44 between the first and second sliding holes 42, 43, and the other end of the second sliding hole 43 is closed. A spring 46 that exerts a spring force in a direction in which the lock pin 39 is engaged with the engagement concave portion 38 is provided between the cap 45 mounted on the slider 11 and the slider 40.

The lock pin 39 has a square cross section having a first side along the axis of the steering shaft 17 and a second side orthogonal to the first side. The first sliding hole 42 is slidably fitted to the recess 38 so as to be able to engage with the concave portion 38. The slider 40
Is engaged with and connected to the lock pin 39 so that the second sliding hole 43
The slider 40 is slidably fitted to the slider 40.
Is provided with a through hole 47 through which the joint 15 penetrates, and a contact surface 49 capable of contacting a cam 48 provided in the joint 15 is formed on the inner surface of the through hole 47.

The lock pin 39 is, for example, JIS
S45C or the like is formed into a flat plate by press-forming a material made of carbon steel for machine structure, and the rock well hardness of the lock pin 39 is, for example, quenched after press-forming. For example, 40 (HR
C) It is set so as to be above. On the other hand, housing 1
1 is made of, for example, a zinc alloy die-cast or a magnesium alloy die-cast, and the steering column pipe 18 is made of, for example, an iron pipe.

In such a lock mechanism 16, the rotor 1
4 is a position other than the LOCK position, that is, the ACC position;
In the N position and the START position, the lock pin 39 is disengaged from the engagement recess 38 and the steering shaft 1
7, while the rotor 14 is in the LOCK position, the cam is moved by the spring force of the spring 46 so that the lock pin 39 is engaged with the engagement recess 38. 48 will rotate. On the other hand, the movement of the key slider 30 in accordance with the insertion of the key 13 into the key hole 26 of the rotor 14 causes the operating lever 32 to rotate in the direction in which the rear end approaches the lock pin 39. Rotor 1
When the lock mechanism 16 is in the unlocked state in response to the position of the lock lever 4 being set to a position other than the LOCK position, the operation lever 32 is released.
A regulating recess 50 for engaging the rear end of the lock mechanism 16 to maintain the unlocked state of the lock mechanism 16 is provided. That is, even if the rotor 14 is in the LOCK position, the key 13 is pulled out from the key hole 26, so that the lock mechanism 16 is locked unless the operating lever 32 is rotated in a direction to separate the rear end from the restriction recess 50. There is no.

By the way, when the lock pin 39 is press-formed, it is inevitable that the burrs 51 are formed on the outer peripheral edge of the lock pin 39 after the press-forming is completed. However, it is desirable to avoid performing the work of removing the burrs 51 since this leads to an increase in the number of work steps. In order to support the lock pin 39 with the burrs 51 slidably in the housing 11, this is shown in FIG. As described above, at the four corners of the first slide hole 42, the escape portions 53, 53,... Thereby, the burrs 51 are connected to the four escape portions 5.
The lock pin 39a can be slidably guided by the first sliding hole 42 by arranging the lock pin 39a in two of 3, 53,.

As described above, since the lock pin 39 is formed by press-forming into a flat plate, the lock pin 3 is formed as compared with the case where the lock pin 39 is formed by cutting.
9 can be formed very easily.

The lock pin 39 needs to have a bending strength to withstand a bending load applied from the steering shaft 17 in the engagement state with the engagement recess 38.
When the bending strength of the housing 9 is set to be excessive,
1 and a guide projection 11b provided on the
b, the strength of the contact portion with the fitting hole 41 provided in the steering column pipe 18 for fitting is relatively lower than the bending strength, and the guide projection 11b is deformed before the lock pin 39 is deformed. In addition, deformation occurs at the fitting contact portion of the fitting hole 41.

Therefore, by balancing the bending strength of the lock pin 39 and the strength of the fitting contact portion of the guide projection 11b and the fitting hole 41, the breaking strength of the lock mechanism 16 can be improved. A method for setting the cross-sectional dimension of the lock pin 39 in order to achieve such strength balance will be described below.

In FIG. 5, the length of the first side along the axial direction of the steering shaft 17 in the cross section of the lock pin 39 is H, and the length of the second side orthogonal to the first side in the cross section is The thickness of the lock pin 39 is B, the diameter of the steering shaft 17 is D, the torque of the steering shaft 17 is T, the edge of the engagement recess 38 from the opening end of the first sliding hole 42 and the contact point P of the lock pin 39. a length of up to ₁ L _L, the length from the contact point P ₁ along the longitudinal direction of the lock pin 39 to the center of the steering shaft 17 L _S, the contact point P
Previously determined from the lock pin 39 in _one load reaction force to the steering shaft 17 and R _1.

Here, the guide projection 11 of the housing 11
b and the stress at the contact portion between the steering column pipe 18 and the fitting hole 41 were calculated by the finite element method using the length H of the lock pin 39 as a parameter, and a result as shown in FIG. 6 was obtained. did it. As is apparent from FIG. 6, the stress decreases as the length H increases, but when H = 16 mm, the stress substantially converges to the lower limit level. As a result, if H ≧ 16 mm,
The stress at the contact portion between the guide protrusion 11b and the fitting hole 41 can be suppressed to a substantially lower limit level, and it is necessary that H ≧ 16 mm.

On the other hand, the bending stress σ acting on the lock pin 39 can be expressed by the following equation (1).

Σ = M / Z (1) where M is a bending moment, Z is a section modulus of the lock pin 39, and M = R ₁ · L _L (2) Z = (H · B ² ) / 6 ... (3). On the other hand, from the balance of the torque in the steering shaft 17, T = L _S · R ₁ (4), and from the equations (2) and (4), M = (L _L / L _S ) · T. (5). Then, by substituting the expressions (3) and (5) into the expression (1), the following expression (6) can be obtained.

Σ = 6 · (L _L / L _S ) · T / (H · B ² ) (6) By the way, when the diameter D of the steering shaft 17 is 29 mm, B = 5 mm and H = 18 mm If the lock pin 3
The present inventor has confirmed by experiments that the necessary and sufficient bending strength can be obtained by the method No. 9 and the bending stress σ _O of the lock pin 39 with respect to an arbitrary load torque at this time is σ _O = 6 · (L _LO / L _SO ) · T / (18.5 ² ) = (1/75) · (L _LO / L _SO ) · T (7)

The arbitrary values of B and H are required to satisfy σ ≦ σ _O , and from the equations (6) and (7), 6 · (L _L / L _S ) · T / (H · B ² ) ≦ (1/75)
(L _LO / L _SO ) · T, that is, H · B ² ≧ 450 · ( _LL / L _LO ) · (L _SO / L _S ) (8)

Here, if L _L is fixedly determined, L _L / L _LO = 1 (9), and L _S is almost proportional to the diameter D of the steering shaft 17, so that L _SO / L _S = 29 / D (10), and this equation (10) and the above equation (9) are
By substituting into the equation (8), H ・ B ² ≧ (450 × 29) / D (11), and B ≧ {13050 / (DH)} ^1/2 (12).

Further, since the lock pin 39 is formed by press forming, and the upper limit of the plate thickness which can be mass-produced by press forming is about 6 mm, the range of the length B finally becomes 6 ≧ B ≧ {13050 / (DH)} ^1/2 It is necessary to set as (13).

Referring again to FIG. 5, when the torque of the steering shaft 17 acts on the lock pin 39 while the lock pin 39 is engaged with the engagement recess 38, the lock pin 3
From 9, a bending load R ₂ acts on the guide protrusion 11 b of the housing 11 at a contact position P ₂ with the opening edge of the first sliding hole 42, and the steering column pipe 18 is fitted along the plate thickness direction. A reaction force R ₃ acts from the contact portion between the hole 41 and the guide projection 11b. For convenience, if the concentrated load at the center position P ₃ of the contact portion is the reaction force R ₃ , the steering shaft 17 Positions P ₂ in a plane perpendicular to the axis of
When the offset amount α of P ₃ increases, local shearing or bending is likely to occur in the guide protrusion 11b, which is disadvantageous in strength. If the offset amount α becomes too small, the thickness of the guide projection 11b becomes thin, which is disadvantageous in strength. Therefore, although be determined properly in accordance with the offset amount α to the diameter D _C of the steering column pipe 18 is required on the holding strength of the guide projection 11b, this time, the steering column a proper value of the offset amount pipe 18 Is automatically set in accordance with the diameter D _C of the laser beam, which contributes to the rationalization of productivity. A method of setting the offset amount α for such a purpose will be described below.

Since the guide projection 11b is to be fitted into a fitting hole 41 provided in the steering column pipe 18 having a circular cross section, the offset amount α is a plane orthogonal to the axis of the steering shaft 17. And changes in accordance with the distance b from the center of the lock pin 39 to the outer surface of the guide projection 11b, that is, the inner surface of the fitting hole 41.
This distance b is equal to the diameter D _{C of the} steering column pipe 18.
The offset amount α can be set to an appropriate value by appropriately setting the offset amount α.

[0037] Here, the diameter D _C is 32mm, 36mm,
Three steering column pipes 18 having a length of 40 mm are prepared, and the distance b is set under the condition of 3 mm <B <10 mm.
When the maximum value of the stress acting on the guide projection 11b when the value was changed was calculated, the result as shown in FIG. 7 could be obtained. According to FIG. 7, the diameter D _C is 32mm
, The stress becomes minimum at b = 6 mm, and the diameter D
_{When C} is 36 mm, the stress is minimized at b = 6.3 mm, and when the diameter D _C is 40 mm, b =
It can be seen that the stress is minimized at 6.7 mm.

[0038] In this way the diameter D _C is 32mm, 36m
3 steering column pipes 1 m and 40 mm
8, the distance b at which the stress of the guide projection 11b is minimized
The horizontal axis diameter D _C of the steering column pipe 18,
Plotting the distance b on the vertical axis and the coordinates on, becomes as shown in FIG. 8, the curve connecting the plotted points, with ^{_{b = 0.0031D C 2 -0.1375D C +}} 7.2 ...... (14) The resulting quadratic curve. That is, if the distance b on the quadratic curve is selected, the guide protrusion 1
Although the stress acting on 1b can be minimized and the strength of the guide projection 11b can be set appropriately, a margin of 0.5 mm is provided on each of the plus side and the minus side. Therefore, the first _{(14), f (D C) = 0.0031D} C 2 -0.1375D C + 7.2 ...... replaced with _{(15), f (D C} ) -0.5 ≦ b ≦ f (D _C ) +0.5 (16) The distance b is set so as to be within a range that satisfies (16).

That is, the bending strength of the lock pin 39 and
In order to balance the strength of the guide protrusion 11b and the fitting contact portion of the fitting hole 41, the length H of the first side of the lock pin 39 along the axial direction of the steering shaft 17, and the circumferential direction of the steering shaft 17 Is set as H ≧ 16 mm 6 ≧ B ≧ {13050 / (DH)} ^1/2 . Therefore, as shown in FIG.
7 is a rectangular shape that is long along the axial direction,
When the diameter D of the steering shaft 17 is 29 mm, for example, H = 18 mm and B = 5 mm. Since the lock pin 39 has such a cross-sectional shape, the bending strength of the lock pin 39 and the guide protrusion are obtained. 11b and the strength of the fitting contact portion of the fitting hole 41 are balanced, and the breaking strength of the lock mechanism 16 can be improved. On the other hand, when the diameter D of the steering shaft 17 is 29 mm as shown in FIG.
m and B = 8 mm, whereas the lock mechanism 16 having the lock pin 39 having the cross-sectional shape of FIG.
% Or more.

Further, the distance b from the center of the lock pin 39 to the outer surface of the guide projection 11b, ie, the inner surface of the fitting hole 41, in a plane perpendicular to the axis of the steering shaft 17 is determined in accordance with the above equation (16). The guide projection 11b
The distance b which can be set to maximize the strength of the guide projection 11b of the stress acting as a minimum, by a uniform depending on the diameter D _C of the steering column pipe 18, regardless of the specifications of the steering lock device, a steering The shape of the fitting hole 41 in the column pipe 18 can be made constant, and the productivity can be rationalized.
At this time, it is desirable that the cross-sectional shape of the guide protrusion 11b be an elliptical shape as shown in FIG.

Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible to do.

Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible to do.

For example, in the above embodiment, the slider 40
Are engaged with and connected to the lock pin 39, but the slider 40 and the lock pin 39 may be integrally formed without a seam.

[0044]

As described above, according to the present invention, the lock pin can be press-molded to facilitate the formation of the lock pin, and the bending strength of the lock pin, the fitting of the guide projection and the fitting hole can be improved. The strength limit of the lock mechanism can be improved by balancing the strength of the mating contact portion.

[Brief description of the drawings]

FIG. 1 is a vertical sectional side view of a steering lock device.

FIG. 2 is an enlarged sectional view taken along line 2-2 of FIG.

FIG. 3 is a sectional view taken along line 3-3 of FIG. 2;

FIG. 4 is an enlarged sectional view taken along line 4-4 of FIG. 2;

FIG. 5 is a simplified diagram corresponding to FIG. 3 for explaining the relationship between stress and dimensions.

FIG. 6 is a diagram showing a stress ratio according to a size of a lock pin along an axial direction of a steering shaft.

FIG. 7 is a diagram showing a stress ratio of the guide projection according to a distance from the center of the lock pin to a side surface of the fitting hole in a plane perpendicular to the axis of the steering shaft.

FIG. 8 is a diagram in which the distance from the center of the lock pin to the side surface of the fitting hole in a plane perpendicular to the axis of the steering shaft is determined according to the diameter of the steering column pipe.

9 is a view as seen from a direction along line 9-9 in FIG. 3;

FIG. 10 is a diagram corresponding to FIG. 9 of the prior art.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 11 ... Housing 11b ... Guide protrusion 12 ... Cylinder 13 ... Key 14 ... Rotor 16 ... Locking mechanism 17 ... Steering shaft 18 ... Steering column pipe 38 ...・ Engaging recess 39 ・ ・ ・ Lock pin 41 ・ ・ ・ Mating hole 42 ・ ・ ・ Sliding hole

Claims (1)

[Claims] 1. A steering shaft (17) having an engagement recess (38) on an outer surface thereof, and the steering shaft (17).
A steering column pipe (18) having a fitting hole (41) at a position corresponding to the engaging recess (38) along the axial direction of the steering column pipe (18) and surrounding the steering shaft (17); ), A housing (11) having a guide projection (11b) fitted to the steering column pipe (18), and a cylinder body (12) inserted and fixed to the housing (11). Key (1
The cylinder body (1) is made rotatable by 3).
2) a rotor (14) to be inserted into the guide projection (11b) and a sliding hole (42) provided in the housing (11) at the tip end of the guide projection (11b) for engagement with the engagement recess (38). Lock pin (39) fitted slidably to enable
And engaging and disengaging the lock pin (39) with the engagement recess (38) with the rotor (14).
Lock mechanism (1) that can be switched in accordance with the rotation of
6), and the lock pin (39) has a square cross-sectional shape including a first side along the axial direction of the steering shaft (17) and a second side orthogonal to the first side. In the steering lock device formed as described above, the length of the first side of the lock pin (39) is Hmm, the length of the second side of the lock pin (39) is Bmm, and the steering shaft (1) is provided.
7) When the diameter of D is D mm, the lock pin (39) having the lengths B and H satisfying H ≧ 166 ≧ B ≧ {13050 / (DH)} ^1/2 A steering lock device characterized by being press-formed.