JP6875901B2 - Tension balancer - Google Patents

Description

The present invention relates to a tension balancer that keeps the tension applied to an overhead wire of an electric railway constant.

Since the overhead wire of an electric railway is affected by slack and tension due to expansion and contraction due to temperature changes and inclination of the support that has changed over time, a tension balancer that has the function of keeping the tension applied to the overhead wire constant by a coil spring is used. Has been done.
Further, a tension balancer using a spiral spring instead of a coil spring has been proposed (see, for example, Patent Document 1).
The tension balancer of Patent Document 1 is housed in a case, and has a spiral spring having an outer peripheral end attached to the case, a central axis connected to the inner peripheral end of the spiral spring, and both ends of the central axis. It is configured to include a fixed involute groove wheel and a cable or the like, one end of which is wound around the involute groove wheel and the other end of which is connected to an overhead wire.

Then, when the temperature rises and the overhead wire expands, a spiral spring is wound and a tension balancer operates so as to wind the cable around the involute groove wheel to correct the expansion amount of the overhead wire.
In addition, when the temperature drops and the overhead wire contracts, the spiral spring loosens and the tension balancer operates so as to send the cable out of the involute groove wheel to correct the contraction amount of the overhead wire.
In this way, the tension balancer operates so as to adjust the length of the cable by the torque generated by winding and loosening the spiral spring, so that the tension applied to the overhead wire is kept constant.

Patent No. 5006410

However, in the case of the tension balancer of Patent Document 1, the cable may be worn while the cable is repeatedly wound and sent out, and if the wear progresses, the cable may be broken. Therefore, regular maintenance is performed. It had to be done, and the complexity of its management could be a problem.

An object of the present invention is to provide a tension balancer having excellent durability.

In order to achieve the above object, the present invention
It is a tension balancer for keeping the tension applied to the overhead wire constant.
The case body fixed to the support structure and
A spiral spring that is housed inside the case and whose outer peripheral end is locked inside the case.
The central axis connected to the inner peripheral end of the spiral spring and
A rotating lever connected to the end of the central shaft,
A groove cam member having a groove formed to guide a moving body that abuts on the rotating lever and moves.
A tension transmission member provided with a connecting member having one end connected to the moving body and an overhead wire connected to the other end.
With
When the overhead wire expands, the central axis rotates in the direction in which the spiral spring loosens, and the rotating lever rotates in the direction in which the moving body approaches the support structure side.
When the overhead wire contracts, the central axis rotates in the direction in which the spiral spring is wound, and the rotating lever is configured to rotate in a direction away from the supporting structure. did.

In this tension balancer, when the overhead wire expands, the rotation lever rotates in the direction of bringing the moving body (for example, a cam follower) to which the tension transmission member to which the overhead wire is connected is connected to the support structure side, and the overhead wire is rotated. When contracted, the rotation lever is configured to rotate in a direction that moves the moving body (for example, a cam follower) to which the tension transmission member to which the overhead wire is connected is connected from the support structure.
It goes without saying that the tension balancer having such a configuration can maintain a constant tension applied to the overhead wire, and as in the case of the tension balancer cable of the prior art (Patent Document 1), wear progresses and the tension balancer breaks. Since it is not provided with a member that can be used as a tension balancer, it can be suitably used as a tension balancer having excellent durability.
That is, if the tension balancer has excellent durability, it is not necessary to perform frequent inspections and maintenance, and the burden on the maintenance manager can be reduced.

When the tension balancer keeps the tension applied to the overhead wire constant, it means that the overhead wire tension is not only held at a predetermined value (specified value) but also the overhead wire tension is maintained within a predetermined range (specified range). It shall also include.
That is, the tension balancer has a function of holding the overhead wire so as to apply a substantially constant tension.

Also, preferably
Both ends of the central axis project horizontally from the side surface of the case body.
The rotating lever, the moving body, and the groove cam member are provided on both sides of the case body, respectively.
Both ends of the moving body are exposed on both sides of the groove cam member through the groove.
The tension transmitting members are paired with each other so as to sandwich the groove cam member so as to be connected to both ends of the moving body.
By doing so, the tension applied to the overhead wire acts on the tension balancer in the direction along the extending direction of the overhead wire via the tension transmission member, so that the tension balancer operates satisfactorily.

Also, preferably
The groove extends in a direction closer to the support structure than the central axis and in a direction away from the support structure, and is inclined so as to be vertically separated from the central axis as the distance from the support structure increases. To present.
This will allow the tension balancer to work better.
Specifically, a tension balancer that uses a spiral spring instead of the conventional coil spring is used, and the torque of the spiral spring is applied to the overhead wire by utilizing the property that the spiral spring is wound and the rotational torque acts when the central axis is rotated. This tension balancer operates better because it is converted into tension, the tension fluctuation rate is lowered, and the overhead wire tension is kept constant.

Also, preferably
The groove is formed in a shape that satisfies the condition that F in the following formula (1) becomes constant according to the spring characteristics of the spiral spring.
F = T / (L · cosθ) ・ ・ ・ (1)
Here, F [N] is the tension in the horizontal direction applied to the overhead wire, T [Nm] is the rotational torque of the spiral spring, L [m] is the distance between the central axis and the moving body, and θ is vertical. It is the rotation angle of the rotating lever with which the moving body is in contact with reference to the rotating lever in the direction.
By doing so, the tension balancer operates with high accuracy.
Specifically, a tension balancer that uses a spiral spring instead of the conventional coil spring is used, and the torque of the spiral spring is applied to the overhead wire by utilizing the property that the spiral spring is wound and the rotational torque acts when the central axis is rotated. This tension balancer operates with high accuracy because it has a structure that converts it into tension, lowers the tension fluctuation rate, and keeps the overhead wire tension constant.

Also, preferably
The groove extends in a direction closer to the support structure and away from the support structure than the central axis, and has an arc shape with the central axis as the axis.
This will allow the tension balancer to work better.
Specifically, a tension balancer that uses a spiral spring instead of the conventional coil spring is used, and the torque of the spiral spring is applied to the overhead wire by utilizing the property that the spiral spring is wound and the rotational torque acts when the central axis is rotated. This tension balancer operates better because it is converted into tension, the tension fluctuation rate is lowered, and the overhead wire tension is kept constant.

Also, preferably
The groove is formed in a shape that satisfies the condition that F in the following formula (10) becomes constant according to the spring characteristics of the spiral spring.
F = (T · cos θ) / L ・ ・ ・ (10)
Here, F [N] is the tension in the horizontal direction applied to the overhead wire, T [Nm] is the rotational torque of the spiral spring, L [m] is the distance between the central axis and the moving body, and θ is vertical. It is the rotation angle of the rotating lever with which the moving body is in contact with reference to the rotating lever in the direction.
By doing so, the tension balancer operates with high accuracy.
Specifically, a tension balancer that uses a spiral spring instead of the conventional coil spring is used, and the torque of the spiral spring is applied to the overhead wire by utilizing the property that the spiral spring is wound and the rotational torque acts when the central axis is rotated. This tension balancer operates with high accuracy because it has a structure that converts it into tension, lowers the tension fluctuation rate, and keeps the overhead wire tension constant.

According to the present invention, a tension balancer having excellent durability can be obtained.

It is a perspective view which shows the tension balancer of Embodiment 1. FIG. It is a top view (a) and a side view (b) which show the tension balancer of Embodiment 1. It is explanatory drawing which shows the spiral spring of the tension balancer of this embodiment. It is explanatory drawing which shows the operation of the tension balancer of Embodiment 1. FIG. It is explanatory drawing which shows the operation of the tension balancer of Embodiment 1. FIG. It is explanatory drawing about the moment of the tension balancer of Embodiment 1. It is a perspective view which shows the tension balancer of Embodiment 2. It is a top view (a) and a side view (b) which show the tension balancer of Embodiment 2. It is explanatory drawing which shows the operation of the tension balancer of Embodiment 2. It is explanatory drawing which shows the operation of the tension balancer of Embodiment 2. It is explanatory drawing about the moment of the tension balancer of Embodiment 2.

Hereinafter, embodiments of the tension balancer according to the present invention will be described in detail with reference to the drawings. However, although the embodiments described below are provided with various technically preferable limitations for carrying out the present invention, the scope of the present invention is not limited to the following embodiments and illustrated examples.

Overhead lines of electric railways (for example, trolley lines) expand and contract due to fluctuations in temperature and sunshine, heat generated by the flowing load current, and the like.
If the overhead wire is loose, the current collecting condition of the current collector may deteriorate, and if a high tension is applied to the overhead wire, the wire may be broken. Therefore, tension is used to maintain the tension of the overhead wire at a constant value. A balancer is used.

(Embodiment 1)
As shown in FIGS. 1, 2 (a), (b), and 3, the tension balancer 100 of the first embodiment is housed in a case body 10 fixed to a support structure 1 such as a support column and a case body 10. A spiral spring 20 in which the outer peripheral end 21 is locked in the case body 10 and a central axis 30 connected to the inner peripheral end 22 of the spiral spring 20 and whose both ends project from the case body. A rotating lever 40 connected to both ends of the central shaft 30, a groove cam member 60 having a groove 61 for guiding the cam follower 50 as a moving body that moves in contact with the rotating lever 40, and a cam follower. A tension transmission member 70 or the like is provided with a connecting member 80 having one end 71 connected to 50 and an overhead wire connected to the other end 72.
The rotary lever 40, the cam follower 50, and the groove cam member 60 are provided in pairs on both sides of the case body 10.

The case body 10 is a substantially cylindrical case in which the spiral spring 20 is housed.
The case body 10 is fixed to the support structure 1 by the attachment 90.

The mounting device 90 includes an arm metal fitting 91 that supports the case body 10, a vertical member 92 to which the arm metal fitting 91 is attached, a horizontal member 93 that is fixed to the upper and lower ends of the vertical member 92, and a horizontal member. It is provided with a U-bolt 94 and a nut for fixing the material 93 to the support structure 1.
The arm metal fitting 91 is attached to the vertical member 92 so that the position and orientation of the case body 10 with respect to the support structure 1 can be adjusted.

As shown in FIG. 3, the spiral spring 20 is a so-called spring, and is a member that can be used as a drive source by the restoring force that the wound spiral tries to return to its original state.
The spiral spring 20 is an urging force that rotates the central shaft 30 by a restoring force that causes the wound spiral to return to its original state, and tilts the rotary lever 40 connected to the central shaft 30 toward the support structure 1. have.

Both ends of the central shaft 30 are attached so as to protrude horizontally from the side surface of the case body 10, and are pivotally supported by the case body 10.
The base of the rotary lever 40 is axially attached to the end of the central shaft 30.

The rotary lever 40 is urged by a spiral spring 20 so as to abut the cam follower 50 that moves along the groove 61 of the groove cam member 60, and rotates so as to follow the movement of the cam follower 50.
Further, a stopper 41 for restricting further movement of the cam follower 50 is provided at the tip of the rotary lever 40.

The groove cam member 60 is a plate-shaped member perpendicular to the central axis 30, and a groove 61 for guiding the cam follower 50 is formed.
As shown in FIG. 2B, the groove 61 of the groove cam member 60 is formed above the position corresponding to the central axis 30 of the groove cam member 60, and the support structure 1 is formed above the central axis 30. It extends in the direction closer to the support structure 1 and in the direction away from the support structure 1, and is inclined so as to be vertically separated from the central axis 30 as the distance from the support structure 1 increases.
The details of the shape of the groove 61 will be described later.

Further, both ends of the cam follower 50 movably attached to the groove cam member 60 along the groove 61 are exposed on both sides of the groove cam member 60 through the groove 61.
The groove cam member 60 is fixed to the arm fitting 91 of the attachment 90 by a predetermined fixture.

The tension transmission member 70 is, for example, a rod member such as a thin steel rod, one end portion 71 thereof is connected to a cam follower 50, and the other end portion 72 is connected to a connecting member 80.
Specifically, the tension transmission members 70 are paired so as to sandwich the groove cam member 60, and one end portions 71 of the pair of tension transmission members 70 are connected to both ends of the cam follower 50, respectively, and a pair of tension transmission members 70 are connected to both ends of the cam follower 50. The other end 72 of the tension transmission member 70 is connected to the connecting member 80.
The pair of left and right connecting members 80 are connected by a large connecting member 81, and an overhead wire is connected to the large connecting member 81.
A pair of left and right connecting members 80 to which one end 71 of the pair of tension transmitting members 70 is connected to both ends of the cam follower 50 and the other end 72 of the pair of tension transmitting members 70 are connected to the connecting member 81. Since they are connected, the tension applied to the overhead wire acts on the tension balancer 100 in the direction along the extending direction of the overhead wire via the tension transmission member 70, and the tension balancer 100 operates satisfactorily.

Next, the operation of the tension balancer 100 of the first embodiment will be described.

When the overhead wire connected to the connecting member 81 of the tension balancer 100 expands, for example, as shown in FIG. 4, the central shaft 30 rotates in the direction in which the spiral spring 20 loosens, and the tension transmitting member 70 to which the overhead wire is connected is connected. The rotation lever 40 rotates in the direction in which the cam follower 50 connected to the cam follower 50 is brought closer to the support structure 1 side.
That is, the central shaft 30 is rotated by the force that the spiral spring 20 tries to restore so as to take the slack of the expanded overhead wire, the rotation lever 40 is rotated counterclockwise in the figure, and the cam follower 50 is supported by the structure. Move in the direction closer to the 1 side.

Further, when the overhead wire connected to the connecting member 81 of the tension balancer 100 contracts, for example, as shown in FIG. 5, the central shaft 30 rotates in the direction in which the spiral spring 20 is wound, and the tension connecting the overhead wires is formed. The rotation lever 40 rotates in the direction of moving the cam follower 50 to which the transmission member 70 is connected away from the support structure 1.
That is, as the cam follower 50 moves away from the support structure 1 so as to be attracted to the contracted overhead wire, the rotary lever 40 is rotated clockwise in the figure to wind the spiral spring 20. The central axis 30 is rotated.

The tension balancer 100 that operates in this way keeps the tension applied to the overhead wire constant.
Hereinafter, the mechanism by which the tension balancer 100 of the first embodiment keeps the tension applied to the overhead wire constant will be described.

As described above, the groove 61 of the groove cam member 60 is formed above the position corresponding to the central axis 30 of the groove cam member 60, and the direction and support closer to the support structure 1 than the central axis 30. It is formed so as to extend in a direction away from the structure 1 and to exhibit an inclined shape so as to be vertically separated from the central axis 30 as the distance from the support structure 1 increases.
Explaining the shape of the groove 61 in detail, the groove 61 is formed in a shape that satisfies the condition that F of the following formula (1) becomes constant according to the spring characteristics of the spiral spring 20.
F = T / (L · cosθ) ・ ・ ・ (1)
Here, F [N] is the horizontal tension (overhead wire tension) applied to the overhead wire, T [Nm] is the rotational torque (spring torque) of the spiral spring 20, and L [m] is the central axis 30 and the cam follower 50. The distance (arm length) and θ are the rotation angles of the rotation lever 40 with which the cam follower 50 is in contact with the rotation lever 40 in the vertical direction as a reference.

Then, as shown in FIG. 6, when the rotary lever 40 is in the vertical direction (θ = 0 °), the following equation (2) is established from the balance of the moments.
T1 = F1, L1 ... (2)
(T1 = F1, l1 = F1, L1, cos0 °)
That is, the following equation (3) holds.
F1 = T1 / (L1 ・ cos0 °) ・ ・ ・ (3)

Further, when the rotation angle of the rotation lever 40 is θ, the following equations (4) and (5) are established from the balance of moments.
T2 = F2 ・ L2 ・ cosθ ・ ・ ・ (4)
l2 = L2 ・ cosθ ・ ・ ・ (5)
That is, the following equation (6) holds.
F2 = T2 / (L2 ・ cosθ) ・ ・ ・ (6)

L1 and l2 in FIG. 6 are vertical distances (groove vertical height) from the height position of the central axis 30 to the groove 61 where the cam follower 50 is located.
Table I shows the data related to the above formula (1) in the tension balancer 100 of the first embodiment.

In this way, the tension balancer 100 can maintain a constant tension applied to the overhead wire.
The tension balancer 100 of the present embodiment does not have a member such as the cable of the tension balancer of the prior art (Patent Document 1) that is worn and broken, and thus has excellent durability. It can be suitably used as a tension balancer.
That is, the tension balancer 100 of the present embodiment, which has excellent durability, does not require frequent inspections and maintenance, and can reduce the burden on the maintenance manager.

If the support structure 1 such as a support is tilted due to aging, the attachment condition of the arm metal fitting 91 to the vertical member 92 is adjusted, and the case body 10 and the groove cam member 60 are arranged with respect to the support structure 1. It may be adjusted so that the tension balancer 100 is in a predetermined posture.

(Embodiment 2)
Next, the second embodiment of the tension balancer according to the present invention will be described. The same parts as those in the first embodiment are designated by the same reference numerals, and only different parts will be described.

As shown in FIGS. 7 and 8 (a) and 8 (b), the tension balancer 100 of the second embodiment includes a groove cam member 60 different from the tension balancer 100 of the first embodiment described above.
As shown in FIG. 8B, the groove 61 of the groove cam member 60 of the tension balancer 100 of the second embodiment is formed above the position corresponding to the central axis 30 of the groove cam member 60, and is formed at the center thereof. It has an arc shape centered on the shaft 30, and extends in a direction closer to the support structure 1 and a direction away from the support structure 1 than the central shaft 30.
The details of the shape of the groove 61 will be described later.

Next, the operation of the tension balancer 100 of the second embodiment will be described.

When the overhead wire connected to the connecting member 81 of the tension balancer 100 expands, for example, as shown in FIG. 9, the central shaft 30 rotates in the direction in which the spiral spring 20 loosens, and the tension transmitting member 70 to which the overhead wire is connected is connected. The rotation lever 40 rotates in the direction in which the cam follower 50 connected to the cam follower 50 is brought closer to the support structure 1 side.
That is, the central shaft 30 is rotated by the force that the spiral spring 20 tries to restore so as to take the slack of the expanded overhead wire, the rotation lever 40 is rotated counterclockwise in the figure, and the cam follower 50 is supported by the structure. Move in the direction closer to the 1 side.

Further, when the overhead wire connected to the connecting member 81 of the tension balancer 100 contracts, the central shaft 30 rotates in the direction in which the spiral spring 20 is wound, for example, as shown in FIG. The rotation lever 40 rotates in the direction of moving the cam follower 50 to which the transmission member 70 is connected away from the support structure 1.
That is, as the cam follower 50 moves away from the support structure 1 so as to be attracted to the contracted overhead wire, the rotary lever 40 is rotated clockwise in the figure to wind the spiral spring 20. The central axis 30 is rotated.

The tension balancer 100 that operates in this way keeps the tension applied to the overhead wire constant.
Hereinafter, the mechanism by which the tension balancer 100 of the second embodiment keeps the tension applied to the overhead wire constant will be described.

As described above, the groove 61 of the groove cam member 60 is formed above the position corresponding to the central axis 30 of the groove cam member 60, and the direction and support closer to the support structure 1 than the central axis 30. It is formed so as to exhibit an arc shape centered on the central axis 30 while extending in a direction away from the structure 1.
Explaining the shape of the groove 61 in detail, the groove 61 is formed in a shape that satisfies the condition that F of the following formula (10) becomes constant according to the spring characteristics of the spiral spring 20.
F = (T · cos θ) / L ・ ・ ・ (10)
Here, F [N] is the horizontal tension (overhead wire tension) applied to the overhead wire, T [Nm] is the rotational torque (spring torque) of the spiral spring 20, and L [m] is the central axis 30 and the cam follower 50. The distance (arm length) and θ are the rotation angles of the rotation lever 40 with which the cam follower 50 is in contact with the rotation lever 40 in the vertical direction as a reference.

Then, as shown in FIG. 11, when the rotary lever 40 is in the vertical direction (θ = 0 °), the following equation (11) is established from the balance of the moments.
T1 = F1, L1 = (F1 / cos0 °), L1 ... (11)
That is, the following equation (12) holds.
F1 = (T1 ・ cos0 °) / L1 ・ ・ ・ (12)

Further, when the rotation angle of the rotation lever 40 is θ, the following equation (13) is established from the balance of moments.
T2 = (F2 / cosθ) ・ L2 ・ ・ ・ (13)
That is, the following equation (14) holds.
F2 = (T2 ・ cosθ) / L2 ・ ・ ・ (14)

L1 and l2 in FIG. 11 are vertical distances (groove vertical height) from the height position of the central axis 30 to the groove 61 where the cam follower 50 is located.
Table II shows the data related to the above formula (10) in the tension balancer 100 of the second embodiment.

In this way, the tension balancer 100 can maintain a constant tension applied to the overhead wire.
The tension balancer 100 of the present embodiment does not have a member such as the cable of the tension balancer of the prior art (Patent Document 1) that is worn and broken, and thus has excellent durability. It can be suitably used as a tension balancer.
That is, the tension balancer 100 of the present embodiment, which has excellent durability, does not require frequent inspections and maintenance, and can reduce the burden on the maintenance manager.

If the support structure 1 such as a support is tilted due to aging, the attachment condition of the arm metal fitting 91 to the vertical member 92 is adjusted, and the case body 10 and the groove cam member 60 are arranged with respect to the support structure 1. It may be adjusted so that the tension balancer 100 is in a predetermined posture.

In the above embodiment, the cam follower 50 is used as the moving body, but the present invention is not limited to this, and for example, a guide roller or the like may be used as the moving body.

In addition, it goes without saying that the specific detailed structure and the like can be changed as appropriate.

1 Support structure 10 Case body 20 Swirl spring 21 Outer peripheral end 22 Inner peripheral end 30 Central axis 40 Rotating lever 41 Stopper 50 Cam follower (moving body)
60 Groove cam member 61 Groove 70 Tension transmission member 71 One end 72 Other end 80 Connecting member 90 Mounting device 91 Arm bracket 92 Vertical member 93 Horizontal member 94 U bolt 100 Tension balancer

Claims (6)

It is a tension balancer for keeping the tension applied to the overhead wire constant.
The case body fixed to the support structure and
A spiral spring that is housed inside the case and whose outer peripheral end is locked inside the case.
The central axis connected to the inner peripheral end of the spiral spring and
A rotating lever connected to the end of the central shaft,
A groove cam member having a groove formed to guide a moving body that abuts on the rotating lever and moves.
A tension transmission member provided with a connecting member having one end connected to the moving body and an overhead wire connected to the other end.
With
When the overhead wire expands, the central axis rotates in the direction in which the spiral spring loosens, and the rotating lever rotates in the direction in which the moving body approaches the support structure side.
When the overhead wire contracts, the central axis rotates in the direction in which the spiral spring is wound, and the rotating lever is configured to rotate in a direction away from the supporting structure. A characteristic tension balancer. Both ends of the central axis project horizontally from the side surface of the case body.
The rotating lever, the moving body, and the groove cam member are provided on both sides of the case body, respectively.
Both ends of the moving body are exposed on both sides of the groove cam member through the groove.
The tension balancer according to claim 1, wherein the tension transmitting members form a pair in an arrangement that sandwiches the groove cam member and are connected to both ends of the moving body. The groove extends in a direction closer to the support structure than the central axis and in a direction away from the support structure, and is inclined so as to be vertically separated from the central axis as the distance from the support structure increases. The tension balancer according to claim 1 or 2, wherein the tension balancer is characterized by exhibiting. The tension balancer according to claim 3, wherein the groove is formed in a shape satisfying the condition that F of the following formula (1) becomes constant according to the spring characteristics of the spiral spring.
F = T / (L · cosθ) ・ ・ ・ (1)
Here, F [N] is the tension in the horizontal direction applied to the overhead wire, T [Nm] is the rotational torque of the spiral spring, L [m] is the distance between the central axis and the moving body, and θ is vertical. It is the rotation angle of the rotating lever with which the moving body is in contact with reference to the rotating lever in the direction. The claim is characterized in that the groove extends in a direction closer to the support structure and a direction away from the support structure than the central axis, and has an arc shape with the central axis as the axis. The tension balancer according to 1 or 2. The tension balancer according to claim 5, wherein the groove is formed in a shape satisfying the condition that F of the following formula (10) becomes constant according to the spring characteristics of the spiral spring.
F = (T · cos θ) / L ・ ・ ・ (10)
Here, F [N] is the tension in the horizontal direction applied to the overhead wire, T [Nm] is the rotational torque of the spiral spring, L [m] is the distance between the central axis and the moving body, and θ is vertical. It is the rotation angle of the rotating lever with which the moving body is in contact with reference to the rotating lever in the direction.

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