JPS6374763A - Drive 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 drive device for a bogie of a railway vehicle.

(Prior art and problems) Conventionally, a general truck has three axles, as shown in Fig. 11.
0 has an axle box 31 at both ends, and a bogie frame 33 is supported by an axle spring 32 (primary suspension spring) provided on the axle box 31.

Further, a secondary suspension device 34 is provided on the bogie frame 33, and the axle box 31 has an axle box chamber 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. Furthermore, in the case of an electric trolley, the trolley frame 33
A driving structure is provided in which a driving electric motor 36 mounted on the top and a driving gear device 37 provided on the axle 30 are connected by a flexible shaft joint 38 for driving.

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 truck 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. Binion 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. 11 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 this elastic body 44 has a structure that rotates together with the axle shaft 41, the deflection of the elastic body 44 is repeated in a circular trajectory with a radius equal to the deflection of the elastic body 44 while the vehicle is traveling. Because the internal stress is repeated for the amount of vibration (and the internal stress for the entire load is repeated), it is extremely easy to get fatigued.

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. It becomes less.

In a generally considered bogie structure, when the primary suspension is provided with sufficient deflection, a flexible shaft joint that allows large deflection is required between the drive motor and the drive gear device.

In addition, this shaft joint transmits a large amount of power, and unless there is a difference in rotational angular velocity between input and output, it will cause vibration and noise. It takes.

In addition to those that have a structure that has constant velocity on its own, known methods include methods that achieve uniform velocity by making the angle between the human shaft center and the center of the shaft joint equal, and the angle between the shaft joint and the output shaft. (Practical Mechanical Handbook, 5th edition, published by the Japan Society of Mechanical Engineers,
(See pages 361 to 363).

Furthermore, elastic deformation of a flexible shaft joint is accompanied by displacement due to sliding or rolling during each rotation, and in order to extend its life, it is desirable to use the shaft joint in a state where the amount of deflection is small.

(Purpose) The present invention aims to solve the problem that due to the deflection of the spring of the primary suspension which has sufficient buffering capacity, the uniformity of the conventional drive is lost, vibration and noise are generated, and the flexible shaft joint for power transmission is This solution solves the problem of shortened lifespan due to the displacement that occurs with each rotation, and although the overall structure of the trolley is simple, there is little vibration and noise, and the lifespan of the flexible shaft joint for power transmission is extended. The purpose of this invention is to provide a driving device for the following.

(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 applied to the axle between the two axles of an axle having wheels on the left and right sides. The primary suspension member provided therewith is pivotally connected to an intermediate member mainly consisting of a driving electric motor disposed between two axles so as to be rotatable in the vertical direction, and a spring for the primary suspension is disposed between the intermediate member and the intermediate member. The intermediate member supports the car body load through the car body support spring, which is the secondary suspension, to reduce the number of components of the entire bogie, and the primary suspension member and the intermediate member At least one of the pivot points of the member has a joint structure that allows displacement in the rolling direction of the vehicle body to accommodate irregularities in the plane of the track, and at least one of the primary suspension members is equipped with a drive gear device, and the primary The driving gear system and the driving electric motor are connected by a flexible shaft joint for power transmission at a location that almost coincides with the pivot point of the suspension member and the intermediate member, thereby maintaining constant speed of the drive even when the primary suspension spring is deflected. keep,
In addition, the displacement of the joint is reduced.

(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. Corresponding to the fact that both end faces of the spring are non-parallel, it is curved with one circular arc radius, and the radius of curvature is large as a curve that takes the angle formed by both end faces of the spring, resulting in the most natural curved state. .

Further, as the primary suspension member is displaced, the flexible shaft joint provided between the drive gear device and the intermediate member expands and contracts, thereby ensuring good power transmission to the axle.

(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 equipped with a main bearing 3 that supports the load applied to the axle 2.

Reference numeral 5 denotes a driving electric motor 1 disposed between the two axles 2.
2 as the main member, and the above-mentioned primary suspension members 4 are arranged before and after the intermediate member 5, at least one of which is connected to the axle 2.
Figure 3 (A
) or (B), the arm 9 is attached to the pivot point 5a, 6b having the joint shown in FIG. It is installed through.

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

Furthermore, the primary suspension member 4 is equipped with a drive gear device 13,
The driving gear device 13 and the driving electric motor 12 are shown in FIGS. 4 and 5.
They are connected by a flexible shaft joint as shown in the figure.

In reality, there are irregularities in the plane of the track, and it is necessary for the bogie running on the irregularities to have a corresponding structure so that each wheel 1 does not separate from the rail despite the irregularities.

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

The dashed line indicates that there is an uneven plane of 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 is directed 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 6a and 6b but also in the rolling direction.

FIG. 3(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. 3(B) shows an example of a general ball joint instead of FIG. 3(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.

Next, an embodiment of the flexible shaft joint for power transmission as well as the effect of the primary suspension will be described with reference to FIGS. 4 and 5.

FIG. 4(A) is a side view showing the primary suspension member 4, the intermediate member 5, and the power transmission shaft joint, in which a flexible shaft joint 50 ( (corresponding to the reference numeral 14 in FIG.
This shows the state in which the input and output axes are aligned and in a straight line.

The bending points 5Qa and 50b of the shaft joint 50 are arranged at positions equidistant by β/2 from the perpendicular Z-Z from the pivot point 6a.

50c is a spline, which allows the shaft joint 50 itself to expand and contract in response to changes in the relative position between the primary suspension member 4 and the intermediate member 5.

Reference numeral 51 denotes two prongs fitted to the human power shaft of the drive gear device 13, and 52 refers to two prongs fitted to the output shaft of the drive electric motor 12.

FIG. 4(B) is a side view showing the state when the primary suspension member 4 is deflected δ1 from the state shown in FIG. 4 (A), the solid line shows a state in which the primary suspension member 4 draws an arc of radius r around the pivot point 6a with the intermediate member 5 from the broken line state and has been raised by a deflection δ1. .

The spring 7 is compressed by a deflection δ2 from the length hl to h2, and the magnitude of the deflection δ1 and 62 is close to 1:1 in the figure. By arranging a coil spring or rubber spring having almost the same load and spring constant as the axial spring 32,
It can be used as a primary suspension similar to a normal bogie and has sufficient buffering capacity, and due to the structure of the bogie, such a spring 7
Sufficient space can be provided to place the

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 the solid line state of FIG. 4(B), the shaft coupling 50 has a bending point 50a,
It is bent at two points 50b and a refraction point 50a.

50b can be bent at the location where each cross axis exists.

In the state shown in FIG. 4(A), the position of the shaft joint 50 is at the bending point 50a.
, 50b are each I! Since they are placed at an equal distance of /2,
When the solid line state shown in FIG. 4(B) is reached, the shaft joint 50 slides on the spline 50C, and the distance between the bending points 50a and 50b becomes shorter.

At this time, if a perpendicular line z'-z' is drawn from the pivot point 6a to the center line of the shaft joint 50, the bending point 50a of the shaft joint 50,
50b are located at the same position of β'/2, and each refraction is symmetrical with a refraction angle α6. α has the same value.

This is explained in the 36th edition of "Mechanical Practical Handbook" published by the Japan Society of Mechanical Engineers.
As shown on pages 1 to 363, since the input and output refraction angles are equal, the rotational angular velocities of the input and output shafts are equal, that is, the conditions for constant velocity drive are met.

Furthermore, the fact that the refraction angles are equal means that the angle α formed by the intermediate member 5 and the primary suspension member 4 is shared between two parts in the form α6 = α, = α/2, and the refraction angle at one location is minimized. It will be stopped at.

In this example, the spring 7 is horizontal in the solid state, and the pivot point 6
The spring length is arranged so that the center of the spring is on the perpendicular line Z-Z from a.

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

In such an arrangement, when the spring 7 is bent from the length hl to h2 and compressed by δ2, the perpendicular z'-z' from the pivot point 6a to the axis x-X of the spring 7 and both ends of the spring 7 are h2
As shown by /2, it coincides with the center of the spring length h2.

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.

5(A) and 5(B) show other embodiments, and FIG. 5(A) shows a flexible shaft joint called a gear-shaped shaft coupling that utilizes the meshing of an internal gear and an external gear. A shaft coupling 53 (corresponding to the reference numeral 14 in FIG. 1) is shown, and the shaft coupling 53 connects the drive electric motor 12, which is a component of the intermediate member 5, and the drive gear device 13 provided in the primary suspension member 4, and generates power. This shows the state in which the input and output shafts of the shaft joint are aligned and in a straight line.

The bending points 53a, 53b of the shaft joint 53 are arranged at positions equidistant β/2 from the perpendicular Z-Z from the pivot point 6a.

Reference numeral 53C denotes an internal gear which is connected to the external gear 54 fitted to the input shaft of the drive gear device 13 and the output shaft of the drive motor 12 in response to changes in the relative position between the primary suspension member 4 and the intermediate member 5. The structure is such that the meshing position of the external gear 55 that is fitted to the shaft changes.

FIG. 5(B) is a partially cross-sectional side view showing the state when the primary suspension member 4 is subjected to a deflection δ from the state shown in FIG. 5(A).
The broken line indicates the input and output shafts of the shaft coupling 53 in FIG. 5 (
The same state as in A) is shown, and the solid line shows a state in which the primary suspension member 4 draws an arc of radius r around the pivot point 6a with the intermediate member 5 from the broken line state and has been raised by a deflection δ1.

The spring 7 is compressed by a deflection δ2 from the length hl to h2, and the magnitude of the deflections δ1 and δ2 is close to 1:1 in the figure. By arranging a coil spring or rubber spring having almost the same load and spring constant as the axial spring 32,
It can be used as a primary suspension similar to a normal bogie and has sufficient buffering capacity, and due to the structure of the bogie, such a spring 7
Sufficient space can be provided to place the

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 the solid line state of FIG. 5(A), the shaft joint 53 has a bending point 53a,
It is bent at two points 53b and a refraction point 53a.

53b is a location where each of the external gears 54 and 55 is present, and since the tips of the teeth of each external gear are rounded, refraction is possible at this position.

In the state shown in FIG. 5(A), the position of the shaft joint 53 is at the bending point 53a.
, 53b are located at an equal distance of l/2, so the fifth
When the state shown by the solid line in Figure (B) is reached, the shaft joint 53 slides with the internal gear 53c, and the interval between the bending points 53a and 53b becomes shorter.

At this time, if a perpendicular line is drawn from the pivot point 6a to the center line of the shaft joint 53, the refraction points 53a and 53b of the shaft joint 53 are located at the same position of β'/2, and each refraction is symmetrical and the refraction angle is α6. α has the same value.

Therefore, the fact that the refraction angles are equal means that the angle α formed by the intermediate member 5 and the primary suspension member 4 is shared between two parts in the form α6 = α, = α/2, and the refraction angle at one location is This means that the amount of sliding of the tooth surfaces of the internal gear 53c and the external gears 54 and 55 is minimized.

This embodiment has almost the same functions as the embodiment shown in FIG. 4 above.

Gear-type shaft couplings are described in the 3rd edition of "Mechanical Practical Handbook" published by the Japan Society of Mechanical Engineers.
It is known from pages 59 to 360, etc., and unlike hook universal joints using cross joints, it has the feature of basically having constant velocity even when used alone because of the meshing of a large number of gears. .

FIG. 6 shows another embodiment, with FIG. 6(A) showing a plan view and FIG. 6(B) showing a side view.

That is, the primary suspension member 4 incorporates a driving gear device 13 and a main bearing 3, and the axle 2 is located inside the primary suspension member 4 between the wheels 1 and is not shown.

The primary suspension member 4 is connected to a ball joint 70a at pivot points 6a and 6b for an intermediate member 5 mainly composed of a driving electric motor 12.
, 70b, so that the axle 2 can rotate vertically and horizontally, and can also roll relatively.

The two springs 71 are spaced apart from each other on the left and right sides, and are arranged to be inclined in an "8" 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 12 and the driving gear device 13 are coupled through a flexible shaft joint 53, typically a gear-shaped shaft joint, to transmit power.

In this embodiment, the center of the flexible joint 53 is located at a distance F lower than the center of the axle 2 (see FIG. 6(B)). This is a case where a hypoid gear is used for the driving gear device 13, 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 12, and a vehicle body support spring 8 for secondary suspension is mounted on the arms 11.

The wheels 1 have brake discs 72 that rotate together, and a brake caliper 73 that acts to sandwich the brake discs 72 to apply a brake is attached to the primary suspension member 4.

FIG. 7 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 configured as There is.

Further, the drive electric motor 12 and the drive gear device 13 are connected to a flexible shaft joint 53 arranged on a line connecting two pivot points 75 on the north side.
and one axle 2, that is, the wheel 1, is driven from the drive electric motor 12.

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. 7(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. 8 shows a side view of an embodiment in which the center of the drive motor is located higher than the center of the wheel.

That is, this is an example in which the center of the drive electric motor 12, which is the main component of the intermediate member 5, is located higher than the center of the wheel 1 by the distance G, and the drive gear device 1 provided in the primary suspension member 4
The input shaft of No. 3 has an angle α. A flexible shaft coupling 53 for power transmission connects the output shaft of the drive motor 12 and the drive gear device 1.
Combine the 30 people axis.

The bending points 53a and 53b of the two flexible shaft joints 530 are located at lengths 1"/2 and 1~/2, respectively, from the perpendicular line z'-z' to the center line of the shaft joint 53 from the pivot 6a, and is refracted at angles α and α.Geometrically, α=α6+
α.

Above 1! If they are arranged so that "/2=1"'/2, then α6=α, and α,=α,=α/2.

In this way, it is advisable to make the refraction equal in order to maintain the constant velocity of the shaft joint 53.

In the case of this embodiment, the displacement that occurs per rotation of the shaft joint is larger than in the embodiment shown in FIG. 6, so it is preferable to use a shaft joint that is suitable for large displacements, such as a hook universal joint ( Normally, the maximum bend is 3 degrees or less for gear-shaped shaft joints, and 20 degrees or less for hook universal joints.)

This embodiment is applied when a space for arranging some equipment below the intermediate member 5 is desired.

FIG. 9 shows a side view of an embodiment in which the intermediate member has a driving electric motor and a power transmission gear.

That is, the center of the drive electric motor 12, which is the main component of the intermediate member 5, is located at a higher position than the center of the wheel 1 by the distance G, and 1
A hypoid gear is used for the drive gear device 13 in the next suspension member 4, and the human power shaft is spaced F by the offset of the gear.
is below the center of wheel 1.

Therefore, the center of the drive electric motor 12 and the drive gear device 1
There is a distance of F+G=H from the center of the input shaft of No. 3.

A spur gear 83 attached to the output shaft of the drive motor 12 within the end casing 82 of the drive motor 12;
Further, power is transmitted to the human power shaft of the drive gear device 13 via the flexible shaft joint 53.

In this embodiment, it is kept more horizontal than in the flexible shaft joint 53 shown in FIG. 8.

Therefore, since the usage conditions are good for a shaft coupling, the degree of freedom in selecting the shaft coupling is increased, and as in the embodiment shown in FIG. It is effective when applied in some cases.

FIG. 10 is a perspective view of another embodiment in which the axle can be steered, and the primary suspension member 4 can be rotated not only in the vertical direction but also in the horizontal direction with respect to the intermediate member 5, for example, at a pivot point. 6a
, 5b can be pivoted by using a ball joint to steer the axle 2, and the figure shows a case where the two axles 2 are not parallel to each other on a curved line 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, and the center plate is provided directly above the driving electric motor 12, which is the main component of the intermediate member 5. 80 allows the portion from the intermediate member 5 to the wheel 1 to rotate horizontally with respect to the bolster 81.

In addition, in order to maintain the constant velocity of the shaft joint and to reduce the amount of displacement that occurs each rotation of the shaft joint, it is necessary to position the flexible shaft joint for power transmission horizontally and above the pivot point. It is desirable to arrange them so that they match.

(Effects) The present invention has a simple overall structure of the bogie, has sufficient buffering capacity as a primary suspension, does not lose uniformity of drive even with large displacement of the primary suspension, and therefore reduces vibration and noise. This has the advantage that there is no reduction in the life of the flexible shaft joint.

In addition, by using a pivot structure in which the primary suspension member is movable in the horizontal direction at a pivot point that is movable in the vertical direction relative to the intermediate member, it also has the feature of making it possible to steer the vehicle. .

[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 (Δ) is an exploded perspective view of one embodiment of the rolling joint; Figure 3 (B) is a perspective view of another embodiment of the rolling joint; Figure 4 (A) is a rolling schematic diagram of the suspension member; (B)
Figure 5 is a side view of an embodiment of a flexible shaft joint for power transmission;
A) (B) is a partially sectional side view of another embodiment of the flexible shaft joint, FIG. 6 shows another embodiment of the present invention, FIG. 6 (A) is a plan view, and FIG. is a side view, FIG. 7 (Δ) is a plan view of an embodiment in which only the -axle is driven by a drive motor, and FIG.
) is a sectional view of the arm, FIG. 8 is a side view of an embodiment in which the center of the drive motor is located higher than the center of the axle, and FIG. 9 is a side view of an embodiment in which the drive motor and transmission gear are provided as intermediate members. 10 is a perspective view of an embodiment in which the axle can be steered, FIG. 11 is a perspective view of a conventional example, and FIG. 12 is a partially sectional plan view of the same 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, 12... Drive electric motor, 13... Drive gear device.

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, at least one pivot point between the primary suspension member and the intermediate member is structured to allow rolling displacement of the axle; 1. A drive device for a truck, characterized in that the primary suspension member is provided with a drive gear device, and a flexible shaft joint is provided at a location that substantially coincides with the bending position of the primary suspension member and the intermediate member. (2) The truck driving device according to claim 1, wherein the flexible shaft joint is a hook universal joint or a gear-shaped shaft joint. (3) The bogie drive device according to claim 1 or 2, characterized in that a transmission gear is provided between the drive electric motor and the flexible shaft joint.