JPS6374765A - Suspension system for truck - Google Patents

Abstract

(57) [Abstract] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] (Industrial application field) The present invention relates to a suspension system for a bogie of a railway vehicle.

(Prior Art and Problems) Conventionally, as shown in FIG. 10, a general suspension system for a bogie has an axle box 31 at both ends of an axle 300, and an axle spring 32 ( The bogie frame 33 is supported by a primary suspension spring.

Further, a secondary suspension device 34 is provided on the bogie frame 33, and the axle box 31 is attached to the axle box guard 3 with respect to the bogie frame 33.
It is supported by an axle box support device such as No. 5 so as to restrict movement in the front, rear, left and right directions.

As described above, since the truck is composed of many parts, it is desirable to simplify the entire truck by reducing the number of component parts from the viewpoint of manufacturing and maintenance.

For this purpose, a trolley as shown in, for example, Japanese Patent Laid-Open No. 60-45259 has been proposed.

That is, as shown in FIG.
5. It is supported via a bearing 46, and also supports all the load from the secondary suspension system 43.

The driving force from the motor 42 is transmitted through the gear coupling 47. Pinion 48. Hollow shaft 45 via large gear 49
and is further transmitted to the axle shaft 41 via the elastic body 44.

Therefore, by supporting the gear box 40 on the axle 41 and arranging the secondary suspension device 43 on the exterior body of the motor 42,
The axle box 31 and truck frame 33 in FIG. 10 are omitted, simplifying the entire structure.

However, the elastic body 44, such as rubber, provided between the gear box 40 and the axle 41 is the shaft spring 32 which becomes the primary suspension spring in FIG.
However, since the elastic body 44 has a structure that rotates together with the axle 41, the deflection of the elastic body 44 is repeated in a circular trajectory with the radius of the deflection of the elastic body 44 as a radius, and the axle spring 32 Rather than repeating internal stress due to vibrations such as
Since it is subjected to repeated internal stress equal to the full load, it is subject to conditions that make it extremely susceptible to fatigue.

Therefore, in order to create an elastic body with sufficient fatigue resistance within a limited space, it is necessary to reduce deflection and reduce the repeated stress value, and the elasticity as a primary suspension is insufficient and the cushioning effect is insufficient. The problem is that there are fewer of them.

(Objective) The present invention provides a suspension system for a bogie that has sufficient buffering capacity as a primary suspension while simplifying the overall structure of the bogie.

(Means for Solving the Problems) In order to solve the above problems and achieve the object, the present invention provides a main bearing that supports the load on the axle between both wheels of an axle having left and right wheels. A primary suspension member having a structure is pivotally connected to an intermediate member disposed between two axles so as to be vertically displaceable, and a spring for the primary suspension is provided between the primary suspension member and the intermediate member. The suspension has sufficient buffering capacity, and the intermediate member supports the car body load via a secondary suspension, such as a car body support spring, reducing the number of components of the entire bogie. Also, the primary suspension part and the intermediate member are pivotally connected. The joint structure allows at least one of the points to be displaced in the rolling direction of the axle to accommodate irregularities in the plane of the track.

(Function) When the primary suspension member is displaced using the pivot point that allows rolling displacement with the intermediate member as a fulcrum, the spring provided between the primary suspension member and the intermediate member is compressed, but the compressed state is as follows. In response to the fact that both end faces of the spring are non-parallel, the spring is curved with a single arc radius, and as a curve that takes the angle formed by both end faces of the spring, the radius of curvature is large, resulting in the most natural curved state. .

(Example) Embodiments of the present invention will be described with reference to the drawings.

FIG. 1 shows a basic embodiment of the invention, in which:
An axle 2 having wheels 1 on the left and right sides is housed in a primary suspension member 4 having a main bearing 3 that supports the load applied to the axle 2.

Pivot points 6a and 6b are arranged at the front and rear of the intermediate member 5 disposed between the two axles 2, and at least one of the pivot points 6a and 6b can be used to control displacement of the vehicle body in the rolling direction. The joints shown in FIG. 4(A) or 4(B) are used so as to allow the above-mentioned primary suspension members 4 to be attached via arms 10 so as to be vertically displaceable, and the springs 7 of the primary suspension are It is attached via arm 9.

Further, the intermediate member 5 is provided with a vehicle body support spring 8 which is a secondary suspension.

As shown in FIG. 2, the spring 7 is horizontal in the normal state (shown by the solid line), and the perpendicular Z from the pivot point 6a
- It is arranged so that the center of the spring length hl is on Z.

That is, both end surfaces of the spring 7 have the same radius of /2.

In such an arrangement, the primary suspension member 4 moves from the solid line state to the intermediate member 5 in an arc of radius r around the pivot point 6a, and rises by a deflection δ1 (shown as a broken line), and the spring 7 has a length hl.
When compressed by the deflection δ2 at h2, the perpendicular line z'-z' from the pivot point 6a to the axis X-X of the spring 7 and both ends of the spring 7 are the same as the spring length h2, as shown by h2/2. coincides with the center.

This means that the spring 7 is compressed and its end surfaces are non-parallel, so it is curved with one circular arc radius R, and the curvature takes the angle β formed by the both end surfaces of the spring 7. It has the advantage of having the largest radius of curvature of any curve, and being the least unreasonable and natural curve.

The magnitude of the deflections δ1 and δ2 is 1:1 in the figure.
As for the spring 7, an axle spring 32 such as a coil spring or a rubber spring, which is usually placed on the axle box 31 of a truck shown in FIG. 10, is used.
By arranging springs 7 with approximately the same load and spring constant, it is possible to obtain sufficient shock absorbing capacity as a primary suspension similar to that of a normal bogie, and the structure of the bogie does not require such a spring 7. Sufficient space can be provided for placement.

Note that although the above description has been made assuming that the primary suspension member 4 is raised relative to the intermediate member 5, this is a relative matter;
Since the next suspension member 4 is supported by the rail via the axle 2, this actually means that the intermediate member 5 is lowered relative to the rail by a deflection δ1.

In addition, actual tracks have surface irregularities, and the bogie running on them needs to have a corresponding structure so that each wheel 1 does not separate from the rail despite the irregularities.

FIG. 3 is a schematic diagram of the same, where the solid line indicates a state where there is no irregularity in the plane of the track, and the axle 2 with wheels 1 at both ends is horizontal.
There is no relative displacement in the rolling direction between the two axles 2,
Each primary suspension member 4 supporting the axle 2 is also horizontal.

The dashed line indicates that there is an uneven plane on the track and each wheel 1 is in contact with the rail, the primary suspension member 4 relatively nearer rotates in the direction of arrow A, and the wheel 1 on the left faces upward in the direction of arrow B. To,
The right wheels 1 are respectively displaced downward in the direction of arrow C.

Therefore, as described above, it is clear that a structure is required that allows at least one of the primary suspension members 4 to be displaced not only in the vertical direction at the pivot points 5a and 5b but also in the rolling direction.

FIG. 4(A) is an exploded perspective view of one embodiment, in which a rod 60 formed at the tip of the arm 10 of the primary suspension member 4 is inserted into a round hole of a cross 61 to prevent displacement in the rolling direction. A nut 62 is screwed in to allow and prevent axial escape.

Cylindrical pin portions 61a protruding from both sides of the cross body 61 are fitted into round holes of the two brackets 63, allowing the primary suspension member 4 to be displaced in the vertical direction.

By adopting such a structure, a joint that allows the primary suspension member 4 to be displaced in the vertical direction and in the rolling direction can be obtained.

In addition, FIG. 4(B) shows an example of a general ball joint instead of FIG. 4(A), in which both ends of a shaft having a spherical surface 90 are fitted and fixed into the round holes of the bracket 63, and the primary The arm 10 of the suspension member 4 is provided with a bearing 91 having the spherical surface 90, and the primary suspension member 4
The displacement in the vertical direction and the displacement in the rolling direction are performed by the cooperative action of the spherical surface 90 and the bearing 91.

FIG. 5 shows an embodiment in the case of an electric trolley, with FIG. 5(A) showing a plan view and FIG. 5(B) showing a side view.

That is, the primary suspension member 4 incorporates a driving gear and a main bearing, and the axle 2 is located inside the primary suspension member 4 between the wheels 1 and is not shown.

For the intermediate member 5 mainly composed of a driving electric motor,
The primary suspension member 4 is connected to the ball joints 70a, 7 at the pivot points 5a, 5b.
0b, and the axle 2 can be relatively rolled.

The two springs 71 have a space between them on the left and right sides and are arranged inclined in a "V" shape, and have a shock absorbing function as a primary suspension as well as a rigidity that allows displacement in the rolling direction. 4 to the intermediate member 5 at a right angle in plan view.

The driving electric motor and the driving gear device are connected by a flexible shaft joint 14, typically a gear-shaped shaft joint, to transmit power.

In this example, the center of the flexible shaft joint 14 is located a distance F lower than the center of the axle 2 (see FIG. 5(B)). This is a case where a hypoid gear is used as the drive gear device, and the offset of the pinion appears as eccentricity of the above-mentioned interval F.

A pair of arms 11 are provided on the intermediate member 5 mainly composed of a driving electric motor, and a vehicle body support spring 8 for secondary suspension is attached to the arms 11.

A brake disc 72 that rotates together with the wheel l is provided, and a brake caliper 73 that acts to sandwich the brake disc 72 to apply a brake is attached to the primary suspension member 4.

FIG. 6 shows an embodiment in which only one axle is driven by a drive motor, and in the plan view of FIG. The intermediate member 5 and the primary suspension member 74 are connected at two pivot points 75, and the intermediate member 5 and the primary suspension member 74 maintain a right angle in a plane and are not allowed to be displaced in the rolling direction.

Further, the driving electric motor and the driving gear device are connected by a flexible shaft joint 14 arranged on a line connecting the two pivot points 75, and one axle 2, that is, the wheel 1, is driven from the driving electric motor.

The other primary suspension member 4 is connected to the intermediate member 5 at a pivot point 6 by a ball joint, and further between the pivot point 77 by the ball joint and a bearing 78 such as a large ball bearing on the primary suspension member 4. are connected by an arm 79.

The shape of the arm 79 is shown in FIG. 6(B).

As described above, the primary suspension member 4 is allowed to be displaced in the rolling direction with respect to the intermediate member 5, and
Since the distance to the center of is equal to the length of arm 79,
The axle 2 maintains a right angle in a plane.

FIG. 7 shows a plan view of an embodiment in which the primary suspension members, i.e. the axles, are rigidly maintained at right angles to the intermediate member, the two primary suspension members 4 being connected to the intermediate member 5 and spherically at pivot points 6a, 6b. Connected by a joint, and pivot points 77a, 7 by a ball joint
7b and a bearing 78 such as a large ball bearing on the primary suspension member 4 are connected by an arm 79.

Therefore, the two primary suspension members 4 are allowed to be displaced in the rolling direction relative to the intermediate member 5, and since the distance from the pivot points 6a, 5b to the center of the axle 2 is equal to the length of the arm 79, the axle 2 maintains a right angle in a plane, and as a result, the two axles 2 remain parallel.

Since both the primary suspension member 4 and the arm 79 are highly rigid members, the parallelism of the two axles 2 is maintained with high rigidity.

In the embodiment shown in FIGS. 1 and 5, the spring 7 serving as the primary suspension provided between the primary suspension member 4 and the intermediate member 5 is arranged horizontally, but it is also arranged in an inclined state in the design. This is possible, and an example thereof is shown in FIG.

That is, when it is difficult to arrange the spring 7 above the flexible shaft joint 14, the arm 5a is attached to the intermediate member 5.
, and a spring 7 is disposed obliquely between the tip of the arm 5a and the primary suspension member 4. In this embodiment as well, a hypoid gear is provided in the driving gear device as in the embodiment shown in FIG. is used, and its pinion offset F is attached.

FIG. 9 is a perspective view of another embodiment in which the axle can be steered, and the primary suspension member 4 can be pivoted not only vertically but also horizontally with respect to the intermediate member 5, for example, at a pivot point. 5a,
The axle 2 can be steered by using a ball joint for pivoting the axle 5b, and the illustration shows a case where the two axles 2 are non-parallel on a curve and form an angle Φ.

The vehicle body support spring 8, which is a secondary suspension, has a structure in which the upper surface is directly connected to the vehicle body and the lower surface is placed on a bolster 81. With respect to the bolster 81, a portion extending from the intermediate member 5 to the wheel 1 can be horizontally rotated.

(Effects) The present invention prevents the spring of the primary suspension from working insufficiently as in the conventional example, and has sufficient shock absorbing capacity as the primary suspension, while maintaining the axle, the primary suspension member, and the intermediate member. The primary suspension member is rotatable at least in the vertical direction with respect to the intermediate member, and the spring is disposed between the primary suspension member and the intermediate member, and the intermediate member absorbs the load of the vehicle body. This has the effect that the structure of the entire supported carriage becomes extremely simple.

In addition, by equipping the primary suspension member with a drive gear, using the intermediate member as a drive motor, and connecting the drive motor and drive gear with a flexible shaft coupling for power transmission, it is easy to convert the drive gear into an electric trolley. The primary suspension member has a pivot structure that allows the primary suspension member to rotate in the left and right directions at the pivot point in the vertical direction with respect to the intermediate member, making it possible to create a structure that allows steering. It is something that you have.

[Brief explanation of the drawing]

Fig. 1 is a perspective view of a basic embodiment of the present invention, and Fig. 2 is a perspective view of a basic embodiment of the present invention.
Figure 3 is a rolling schematic diagram of the primary suspension member, Figure 4 (A) is an exploded perspective view of one embodiment of the rolling joint, Figure 4 (B) is the rolling joint and other parts. FIG. 5 is a perspective view of an embodiment of the electric trolley, and FIG.
A) is a plan view, FIG. 6(B) is a side view, and FIG. 6(A) is a -
6(B) is a sectional view of the arm; FIG. 7 is a plan view of an embodiment in which the primary suspension member is highly rigid and maintains a right angle; FIG. The figure is a side view of an embodiment in which the springs of the primary suspension are arranged at an angle, Figure 9 is a perspective view of an embodiment in which the axle can be removed, Figure 10 is a perspective view of a conventional example, and Figure 11 is the same. FIG. 2 is a partially sectional plan view of a conventional example. 1...Wheel, 2...Axle, 3...Main bearing, 4...
- Primary suspension member, 5... Intermediate member, 7... Primary suspension spring, 8... Vehicle body support spring. Patent applicant: Kawasaki Heavy Industries, Ltd. (A) Figure 4

Claims (3)

[Claims] (1) The primary suspension member, which is equipped with a main bearing that supports the load on the axle between both wheels of an axle with left and right wheels, can be vertically displaced with respect to the intermediate member placed between the two axles. A spring is provided between the primary suspension member and the intermediate member, and at least one pivot point between the primary suspension member and the intermediate member is structured to allow rolling displacement of the axle. suspension system for trolleys. (2) The suspension system for a bogie according to claim 1, wherein the primary suspension member and the intermediate member are pivoted by a ball joint. (3) The intermediate member is composed of a driving electric motor, and the driving gear device provided in the primary suspension member and the driving electric motor are connected by a flexible shaft joint. The suspension system for the trolley according to item 2.