JP3409602B2 - Rack and pinion steering system - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rack-and-pinion type steering device, and more particularly to a rack-and-pinion type steering device configured to stably engage a pinion shaft and a rack shaft by using a rack guide.

[0002]

2. Description of the Related Art For example, a steering device (vehicle steering device) used in a vehicle such as an automobile transmits an operating force (rotational force) of a steering wheel to a steering gear box through a steering column, and a steering gear box. In the above, the rotational force of the steering wheel is converted into the linear moving force of the tie rod, and thereby the direction of the tire connected to the tie rod is changed.

As a steering gear box system adopted in this type of vehicle steering system, a rack and pinion system, a ball nut system, a worm sector system, a worm pin system and the like are generally known. Among these various types, in recent years, a rack and pinion type steering gear box, which has a simple structure and a sharp handle, has become mainstream. As the rack and pinion type steering device, for example, an actual Kaihei 3-1
There is one disclosed in Japanese Patent No. 5784.

FIG . 4 is a view showing the vicinity of a meshing portion of a rack and a pinion of a rack and pinion type steering device. The rack-and-pinion type steering device shown in the figure is fixed to a frame of a vehicle. Generally speaking, a housing 51 and a pinion gear 52 are formed and an operation force of a steering wheel (not shown) is transmitted. The pinion shaft 53 and the pinion gear 52
A rack shaft 55 formed with a rack gear 54 that meshes with a predetermined range, and a rack that guides the moving direction of the rack shaft 55 and biases the rack shaft 55 toward the pinion shaft 53 by the elastic force of a rack guide spring 56. It is composed of a guide 57 and the like.

Therefore, when the steering wheel is rotated by the driver, this operating force causes the pinion shaft 5 to move.
3 is rotated, and the pinion gear 52 formed on the pinion shaft 53 is the rack gear 5 formed on the rack shaft 55.
4, the rack shaft 55 moves vertically in the vertical direction with respect to the paper surface in accordance with the rotation direction of the pinion shaft 53. Tires are connected to both sides of the rack shaft 55 via tie rods (not shown), so that the tire connected to the tie rods changes its direction when the rack shaft 55 moves.

On the other hand, the rack guide 57 is provided in the housing 51.
It is mounted in a moving chamber 58 formed in a manner movable in the directions of arrows C1 and C2 in the figure. Further, a rack guide spring 56 is interposed between the rack guide 57 and the spring cap 59 fixed to the housing 51.
The C1 direction end portion of the rack guide 57 in the drawing is engaged with the rack shaft 55, and the C2 direction end portion is connected to the rack guide spring 56.

The rack guide 57 is always elastically biased in the C1 direction by the elastic force of the rack guide spring 56, so that the rack shaft 55 is moved by the rack guide spring 56.
Of the pinion shaft 5 via the rack guide 57 by the elastic force of
3 is pressed and urged. In this way, the rack shaft 55 is pressed and biased by the pinion shaft 53 so that the pinion shaft 53
Is restricted with respect to the rack shaft 55, and the backlash between the pinion gear 52 and the rack gear 54 can be reduced, so that the operating force of the steering wheel can be reliably transmitted to the rack shaft 55.

[0008]

As described above, in the rack and pinion type steering device, the moving chamber 58
The rack guide spring 56 disposed inside the rack guide spring 56 biases the rack guide 57, and the rack shaft 55 is biased toward the pinion shaft 53 via the rack guide 57.

When a strong force (impact) acts on the vehicle due to the vehicle traveling on an irregular road or the like, this impact is transmitted to the rack shaft 55 through the tire and the tie rod connected to the tire. At this time, since the rack guide 57 regulates the displacement of the rack shaft while maintaining the meshing state of the pinion gear 52 and the rack gear 54, when the reverse input is applied as described above, the meshing of the pinion gear 52 and the rack gear 54 is performed. The load due to the reverse input is transmitted to the steering system via the section.

Therefore, the conventional rack-and-pinion type steering device has a problem that it is necessary to increase the rigidity (strength) of the steering system in order to cope with this reverse input. Specifically, it is necessary to maintain the strength of the gear part, main shaft, etc., and it is necessary to have an excessive strength as compared with the strength required in the normal use area, which lowers productivity and raises costs. There was a problem that it would end up.

The present invention has been made in view of the above points, and by providing a biasing means that functions in a normal use region and an auxiliary biasing means that functions when a reaction force is input, the steering system is operated by reverse input. An object of the present invention is to provide a rack-and-pinion type steering device in which a load is prevented from being transmitted.

[0012]

The above-mentioned problems can be solved by taking the following measures. In the invention according to claim 1, a rack and pinion type comprising a rack guide that is biased by the biasing means to bias the rack shaft slidably in the housing toward the pinion shaft direction in the housing. the steering apparatus, wherein
A rack guide for guiding the rack guide is provided in the housing.
Guide hole and a guide having a larger diameter than the rack guide hole
A hole is provided, the urging means and the auxiliary urging means are arranged in series between the rack guide and the urging means supporting member provided in the housing, and a set load of the auxiliary urging means is provided. Is set larger than the set load of the biasing means ,
A biasing means is provided between the rack guide and the auxiliary biasing means.
And the auxiliary biasing means disposed between the rack guides.
Step portion formed between the guide hole and the large-diameter guide hole
And the urging means supporting member .

According to a second aspect of the invention, in the rack-and-pinion type steering device according to the first aspect, the auxiliary urging means can be moved in the same direction as the moving direction of the rack guide. And is disposed between the contact member and the urging means supporting member, and the contact member is disposed at a predetermined distance from the rack guide, and the contact member is disposed in the pinion axial direction. It is characterized in that it is configured to include an elastic member for urging toward.

The above means operate as follows. According to the invention of claim 1, the rack guide is biased by the biasing means to bias the rack shaft slidably in the housing toward the pinion shaft direction. Also, the bias provided on the rack guide and housing
A biasing means and an auxiliary biasing means are connected in series between the means supporting member.
And the set load of the auxiliary biasing means is applied to the biasing means.
It is set larger than the set load.

Therefore, in a normal state in which the reverse input does not act from the steered wheel side, the rack shaft is pressed toward the pinion shaft direction by the rack guide urged by the urging means having a small set load, and thus the rack shaft and A good meshing state with the pinion shaft can be maintained.

On the other hand, when a reverse input is applied from the steered wheel side, the load due to the reverse input causes the rack guide to move toward the biasing member support member. At this time, first, the biasing means having a small set load receives the load due to the reverse input, but when the load due to the reverse input is larger than the set load of the biasing means, the biasing means alone cannot absorb the load.

In the conventional rack-and-pinion type steering device, only this urging means is provided. Therefore, when a load larger than the set load of the urging means is applied, the urging means becomes rigid. The load is transmitted to the steering system due to the reverse input, so that it is necessary to improve the strength of the steering system.

In the invention according to this claim, however, in addition to the urging means, the auxiliary urging means having a set load larger than the set load of the urging means is provided in series. Even after the load absorption limit state is reached, the rack guide can be displaced by the operation of the auxiliary biasing means.

Therefore, it becomes possible to reduce the rigidity at the time of reverse input, and it is possible to prevent the load due to reverse input from being absorbed by the auxiliary urging means and being transmitted to the steering system. In this way, the load of the reverse input can be prevented from being transmitted to the steering system, so that the strength of the steering system can be reduced.

According to the second aspect of the invention, the auxiliary urging means is composed of the contact member and the elastic member. The contact member is configured to be movable in the same direction as the moving direction of the rack guide, and is arranged at a predetermined distance from the rack guide. Further, the elastic member is arranged between the contact member and the biasing means support member, and biases the contact member in the pinion axis direction.

Therefore, when a reverse input is applied from the steered wheel side, the rack guide is displaced and abuts the abutting member, and the rack guide is displaced against the biasing force of the elastic member.
As a result, the rigidity at the meshing position of the rack shaft and the pinion shaft is reduced, and the load due to the reverse input is absorbed by the deformation of the elastic member. As a result, the load acting on the steering system can be reduced, and therefore the load due to the reverse input can be transmitted to the steering system without increasing the set load of the biasing means that functions in the normal state. Can be reliably prevented.

[0022]

BEST MODE FOR CARRYING OUT THE INVENTION Next, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a rack and pinion type steering device 30 (hereinafter, referred to as a first embodiment of the present invention).
2 is a sectional view showing a steering device), and FIG. 2 is a vehicle steering device 1 to which a steering device 30 is applied.
Is shown. First, a schematic configuration of the vehicle steering system 1 will be described with reference to FIG.

The vehicle steering system 1 is generally composed of a steering wheel 2, a tilt mechanism 3, a rotation transmission mechanism 13 (each of the above components is referred to as a steering system), and a steering device 30 which is an essential part of the present invention. ing. Also,
In the present embodiment, an example in which power steering is adopted is shown, and 22 in the figure shows a power cylinder constituting the power steering.

The steering wheel 2 is connected to a first steering shaft 5 inserted in the steering column 4 so that the driver can operate the steering wheel 2
When is turned, the first steering shaft 5 also turns together with the steering wheel 2. Since the tilt mechanism 3 is provided in the present embodiment, the height position of the steering wheel 2 can be adjusted by the tilt mechanism 3.

The first steering shaft 5 is connected to the rotation transmission mechanism 13. Rotation transmission mechanism 13
Is configured to include a first hook universal joint 6, a second hook universal joint 7, a steering shaft 11, and the like. The hook universal joints 6 and 7 have the same configuration, and a cross shaft (not shown) is interposed between the hollow shaft 8 on the input side and the hollow shaft 9 on the output side, so that the axial direction of the hollow shaft 8 can be reduced. The hollow shaft 9 extending in a direction different from that of FIG.

On the hollow shaft 8 of the first hook universal joint 6,
The end portion of the first steering shaft 5 is inserted and fixed by tightening a bolt (not shown) or the like. The upper end of the second steering shaft 11 is fixed to the hollow shaft 9 on the output side by the same fixing method. Further, the lower end of the second steering shaft 11 is fixed to the hollow shaft 8 on the input side of the second hook universal joint 7, and the hollow shaft 9 on the output side is a third shaft provided on the steering device 30.
The steering shaft 12 (hereinafter, the third steering shaft is particularly referred to as a pinion shaft) is fixed.

Inside the gear box 20 constituting the steering device 30, the pinion shaft 12, the rack shaft 14,
A rack guide 15, a set load spring 16, a buffer mitigation spring 17 and the like (see FIG. 1) are internally provided (the specific configuration of the gear box 20 will be described later for convenience of description).

Tie rods 33 and 34 are connected to both sides of the rack shaft 14 disposed in the gear box 20, and linearly move in the same direction as the rack shaft 14 moves in the directions of arrows E1 and E2 in the figure. It has a possible structure. Steering wheels (not shown) are connected to the tie rods 33 and 34, so that the tie rods 33 and 34 are connected to the arrow E in the drawing.
The direction of the steered wheels is changed by the movement in the directions E1 and E2, whereby the vehicle can be steered.

In the vehicle steering system 1 having the above-described configuration, when the driver turns the steering wheel 2, the turning operation force is transmitted to the rotation transmission mechanism 13 via the first steering shaft 5 and further rotated. It is transmitted to the gear box 20 of the steering device 30 via the transmission mechanism 13. In the gear box 20, the transmitted rotational operation force is converted into the linear movement force of the rack shaft 14, and the tie rods 33 and 34 move in the directions B1 and B2 in the figure, whereby the steering wheels (not shown) are oriented. Is changed.

Next, the steering device 30 will be described in detail below. FIG. 1 is a main part configuration diagram showing the inside of a gear box 20 that constitutes a steering device 30. The gear box 20 roughly includes the housing 10, the pinion shaft 12, the rack shaft 14, the rack guide 15, the set load spring 16 (biasing means), the buffer relaxation spring 17 (elastic member), and the stopper plate 19 (contact). (Member) and the like. The buffer relaxation spring 17 and the stopper plate 19 cooperate with each other to form the above-mentioned auxiliary urging means.

The housing 10 is fixed at a predetermined position of a frame provided on the vehicle, and a pinion shaft 12 is rotatably supported in the housing 10. The pinion shaft 12 has a pinion gear 18 at its lower end.
Are integrally formed, and the upper end portion of the housing 10
It is configured to project to the upper part of and to be connected to the rotation transmission mechanism 13 described above.

Since the vehicle steering system 1 according to this embodiment employs power steering, the pinion shaft 12
A control valve (not shown) is disposed on the upper part of the control valve. The control valve supplies high-pressure oil supplied from an oil pump to a cylinder right chamber or a right chamber of the power cylinder 22 in accordance with the turning operation direction of the steering wheel 2. It is configured such that it is selectively supplied to the left chamber of the cylinder, thereby assisting the turning operation of the steering wheel 2.

On the other hand, the rack shaft 14 is arranged so as to be linearly movable with respect to the housing 10. Specifically, FIG.
Vertical direction (E1, E2 in Fig. 2)
Direction). This rack shaft 1
A rack gear 27 is formed at a predetermined position of No. 4, and the rack gear 27 is configured to mesh with the pinion gear 18 formed on the pinion shaft 12.

Therefore, when the pinion shaft 12 rotates, the rotational force of the pinion shaft 12 is converted into the linear movement force of the rack shaft 14 by the meshing of the pinion gear 18 and the rack gear 27. With respect to the vertical direction, it moves linearly in the vertical direction (directions E1 and E2 in FIG. 2). Further, as described above, the steered wheels (not shown) are connected to both sides of the rack shaft 14 via the tie rods 33 and 34, so that the rack shaft 14 is connected to the tie rods 33 and 34 by linear movement. The steered wheels change direction.

A rack guide 15 is arranged at a position opposite to the position where the rack gear 27 is formed on the rack shaft 14. A curved recess 15a is formed in a portion of the rack guide 15 facing the rack shaft 14, and the rack shaft 14 is slidably engaged in the recess 15a. By thus engaging the rack shaft 14 with the recess 15a formed in the rack guide 15, the displacement of the rack shaft 14 in the directions of arrows B1 and B2 in the drawing (the axial direction of the pinion shaft 12) is restricted.

The rack guide 15 configured as described above is mounted in a rack guide guide hole 21 formed in the housing 10 so as to be movable in the directions of arrows A1 and A2 in the drawing. In addition, the rack guide guide hole 21 of the housing 10
A stopper plate guide hole 23 is formed at a position on the A2 direction side of the formation position of. The diameter dimension of the stopper plate guide hole 23 is set to be larger than the diameter dimension of the rack guide guide hole 21. Therefore, a step portion 24 is formed at the boundary between the rack guide guide hole 21 and the stopper plate guide hole 23. It

The stopper plate 19 has a disk shape and is mounted in the stopper plate guide hole 23 so as to be movable in the directions of arrows A1 and A2 in the drawing.
That is, the stopper plate 19 is configured to be movable in the same direction as the rack guide 15 . In addition, La
A plug 25 (biasing means supporting member) is fixed to an end portion of the stopper plate guide hole 23 in the A2 direction, which is a position separated from the rack guide 15 by a predetermined distance. At this time, the plug 25 is fixed to the end portion of the stopper plate guide hole 23 after mounting the stopper plate 19 and the buffer relaxation spring 17 in the stopper plate guide hole 23.

The buffer cushioning spring 17 is mounted in the stopper plate guide hole 23 in a compressed state.
Therefore, the stopper plate 19 is always biased in the direction A1 in the figure by the elastic restoring force generated by the buffer cushioning spring 17 (the force for biasing the stopper plate 19 in the direction A1 in the figure is set. Load F1). Therefore, in the normal state, the stopper plate 19 is in contact with the step portion 24 by the buffer mitigating spring 17.

However, when a load larger than the set load F1 is applied to the stopper plate 19 in the direction of the arrow A2, the stopper plate 19 is used as the buffer relaxation spring 17
It moves in the direction of arrow A2 in the figure against the elastic force of. At this time, the movable area of the stopper plate 19 is an area (impact mitigation stroke area) indicated by an arrow L1 in the figure.
The normal state here means a state in which a load due to a reverse input, which will be described later, is not applied to the rack shaft 14.

On the other hand, a rack guide clearance L2 is formed between the rack guide 15 and the stopper plate 19, and a set load spring 16 is interposed in the rack guide clearance L2. In this embodiment, a disc spring is used as the set load spring 16, and the end portion in the A1 direction contacts the rack guide 15 and the end portion in the A2 direction contacts the stopper plate 19.

In the normal state, the set load spring 16 elastically biases the rack guide 15 in the pinion axis direction (direction shown by arrow A1 in the figure) (this elastic biasing force is referred to as set load F2). Therefore, the rack shaft 14 is configured to be pressed toward the pinion shaft 12 by the rack guide 15 biased by the set load spring 16.

Here, paying attention to the arrangement structure of the set load spring 16 and the buffer mitigation spring 17, as shown in FIG. 1, the set load spring 16 and the buffer mitigation spring 17 interpose a stopper plate 19 therebetween. And are connected in series. The set loads of the springs 16 and 17 are set so that the set load F1 of the buffer cushioning spring 17 is larger than the set load F2 of the set load spring 16.

As described above, by setting the set load F1 of the buffer cushioning spring 17 to be larger than the set load F2 of the set load spring 16, the stopper plate 19 is kept in contact with the step portion 24 in the normal state. Therefore, the set load spring 16 biases the rack guide 15 in the A1 direction using the stopper plate 19 as a base.

Next, the operation of the steering device 30 having the above structure will be described. As described above, in the normal state where the load due to the reverse input is not applied to the rack shaft 14, the stopper plate 19 is in contact with the step portion 24, and the set load spring 16 uses the stopper plate 19 as a base. The guide 15 is biased in the A1 direction. For this reason, the rack shaft 14 is moved by the elastic force of the set load spring 16 via the rack guide 15 into the pinion shaft 12.
The rack shaft 12 and the pinion shaft 14 can be maintained in a good meshing state.

On the other hand, when a reverse input is applied from the steered wheel side due to, for example, a collision with a curb, the rack shaft 12 is displaced in the axial direction (E1 and E2 directions in FIG. 2) by the reverse input, and the rack is accordingly moved. The guide 15 is urged to move toward the plug 25 (direction A2). The load due to this reverse input is first received by the set load spring 16 set to a small set load F2, but the load due to the reverse input is the set load F of the set load F16.
When greater than 1, have a can absorb this only in spring set load 16.

Now, assuming a steering device having a structure in which the buffer cushioning spring 17 does not exist (that is, a steering device having a conventional structure), the set load spring 16 has been extended to a flat shape as described above. Then, the set load spring 16 does not function as a spring, and the housing 1
0, the rack shaft 14, the rack guide 15, and the set load spring 16 are rigidized. Therefore,
The load is transmitted to the pinion shaft 12 by the reverse input, so that it is necessary to improve the strength of the steering system including the pinion shaft 12.

[0047] However, the steering apparatus 30 according to this embodiment, in addition to the set load spring 16, the buffer relaxing spring 17 having a large becomes set load F1 that provided than the set load for the spring 16.

FIG. 3 shows the characteristics of the steering device 30 according to this embodiment. FIG. 3 (A) shows the relationship between the combined spring constant of the set load spring 16 and the buffer relaxation spring 17 and the stroke amount of the rack guide 15, and FIG. 3 (B) is applied to the pinion shaft 12. The relationship between the load applied and the stroke amount of the rack guide 15 is shown.

Attention is first directed to FIG. In the figure,
The vertical axis shows the combined spring constant, and the horizontal axis shows the stroke amount of the rack guide 15. Also, set load spring 1
The spring constant of 6 alone is K1, and the spring constant of the buffer cushioning spring 17 alone is K2. As shown in the figure, when the stopper plate 19 is not displaced and only the set load spring 16 is loaded as in the normal state, the combined spring constant is equivalent to the spring constant of the set load spring 16. Yes, so the combined spring constant is K1.

However, when the stroke amount of the rack guide 15 is increased by the load due to the reverse input, the cushion relaxation spring 17 is bent in addition to the set load spring 16 (the stroke amount S1 in the figure is exceeded). Since the set load spring 16 and the buffer relaxation spring 17 are directly connected, the combined spring constant is K1 · K2 / (K1
+ K2). Therefore, it is possible to set the combined spring constant to a low value when the reverse input is applied, and it is possible to reduce the rigidity at the meshing position of the pinion shaft 12 and the rack shaft 13.

Next, paying attention to FIG. 3B, the vertical axis represents the load applied to the pinion shaft 12 and the horizontal axis represents the stroke amount of the rack guide 15. The load F applied to the pinion shaft 12 is expressed as the product of the stroke amount S and the composite spring constant K1 (F = K1.
S). Therefore, in the state where only the set load spring 16 is loaded (the stroke amount is smaller than S1), the load F applied to the pinion shaft 12 is increased by the stroke amount S, as shown in FIG. Increases in proportion to.

However, when the rack guide 15 exceeds the stroke amount S1, the combined spring constant becomes low as described above. Therefore, even if the stroke amount S increases, the increase amount of the load F applied to the pinion shaft 12 becomes low. Can be suppressed.
That is, according to the steering device 30 according to the present embodiment,
The load F applied to the pinion shaft 12 at the time of applying a reverse input can be reduced as compared with the conventional characteristic shown by the one-dot chain line in the figure.

Therefore, the pinion shaft 12 at the time of reverse input
The rigidity at the meshing position between the rack shaft 14 and the rack shaft 14 is reduced, and it is possible to prevent the load due to the reverse input from being transmitted to the steering system. In this way, the load of the reverse input can be prevented from being transmitted to the steering system, and thus the strength of the steering system can be reduced. Therefore, it is possible to reliably prevent the load due to the reverse input from being transmitted to the steering system at the time of reverse input without increasing the set load F2 of the set load spring 16 that functions in the normal state. Therefore, it is possible to improve the productivity of the steering system and reduce the cost.

[0054]

[0055]

[0056]

Further, in each of the above-described embodiments, the structure in which two springs are arranged in order to cope with the load due to the reverse input is shown, but the number of springs is not limited to two and it is not limited to three.
It is also possible to adopt a configuration using more than one.

[0058]

As described above, according to the present invention, the following various effects can be realized. According to the first aspect of the invention, in a normal state in which no reverse input is applied from the steered wheel side, the rack shaft is pressed in the pinion axis direction by the rack guide urged by the urging means having a small set load. Therefore, the rack shaft and the pinion shaft can maintain a good meshing state.

Further, when a reverse input is applied from the steered wheel side, the load due to the reverse input is absorbed by the auxiliary biasing means, and the load due to the reverse input can be prevented from being transmitted to the steering system. The strength of the steering system can be reduced. Therefore, it is possible to improve the productivity of the steering system and reduce the cost.

Further, according to the second aspect of the present invention, the rigidity at the meshing position of the rack shaft and the pinion shaft is reduced, and the load due to the reverse input is absorbed by the deformation of the elastic member. It is possible to reliably prevent the load due to the reverse input from being transmitted to the steering system at the time of reverse input without increasing the set load of the biasing means.

[Brief description of drawings]

FIG. 1 is a main part configuration diagram showing an enlarged vicinity of a meshing position between a pinion shaft and a rack shaft of a steering device according to a first embodiment of the present invention.

FIG. 2 is a schematic configuration diagram of a vehicle steering system to which a steering system according to an embodiment of the present invention is applied.

FIG. 3 is a diagram showing characteristics of the steering system according to the first embodiment of the present invention.

FIG. 4 illustrates a conventional pinion shaft of a steering device .
It is sectional drawing which shows the meshing position vicinity with a rack shaft.

[Explanation of symbols]

1 Vehicle steering system 10 housing 12 pinion shaft 14 rack shaft 15 Rack guide 16 Set load spring 17 Buffer buffer spring 18 pinion gear 19 Stopper plate 20 gearbox 21 Rack guide guide hole 23 Stopper plate guide hole 24 Step 25 plugs 27 rack gear 30 Steering device 33,34 Tie rod

Claims (2)

(57) [Claims] 1. By being biased by the biasing means,
The rack shaft is slidable inside the housing
It is equipped with a rack guide that urges in the on-axis direction.
In the rack and pinion type steering device,A rack for guiding the rack guide is provided in the housing.
Rack guide guide hole and a larger diameter than the rack guide guide hole.
With a guide hole, Energizer provided on the rack guide and the housing
The biasing means and the auxiliary biasing means are provided between the step support member and
Arranged in series,The above Set the load of the auxiliary biasing means to the set of the biasing means
Set larger than the load, The biasing means includes the rack guide and the auxiliary biasing means.
Placed between Moreover, the auxiliary biasing means is provided with the rack guide guide hole.
A step portion formed between the large diameter guide hole and
Arranged between the biasing means support member Characterized by
Quand pinion type steering device. 2. The rack-and-pinion type steering device according to claim 1, wherein the auxiliary biasing means is configured to be movable in the same direction as the moving direction of the rack guide, and with respect to the rack guide. And an elastic member disposed between the abutting member and the biasing means supporting member and biasing the abutting member in the pinion axial direction. A rack-and-pinion type steering device characterized by being provided.