JP2021161818A - Rail head reprofiling device - Google Patents

Abstract

To provide a rail head reprofiling device capable of reprofiling a rail head with high accuracy.SOLUTION: A head of a rail 20 is corrected with a grindstone 70 by traveling a drive carriage 30 and a driven carriage 60 on the rail 20, with the grindstone 70 provided on the driven carriage 60 and rotated to be brought into contact with the head of the rail 20. The driven carriage 60 comprises: a shaft case 80 that rotatably supports the grindstone 70; a tilting mechanism that supports the shaft case 80 on the driven carriage 60 in such a manner that the grindstone 70 and a rotating shaft 73 can tilt in the longitudinal direction of the driven carriage 60. The driven carriage 60 further includes: a pressing cylinder 90 that presses the cutting surface of the grindstone 70 against the head of the rail 20; and pressing cylinders 91, 92 that press the shaft case 80 in such a manner that the rotating shaft 73 is tilted forward in the traveling direction of the driven carriage 60.SELECTED DRAWING: Figure 2

Description

The present invention relates to a rail head rectifying device for rectifying a rail head of a railway.

As the rail head correction device, the device described in Patent Document 1 is known. The rail head rectifying device described in the same document has a trolley running on the rail and a rotary grindstone provided on the trolley. In this rail head rectifying device, when the bogie is viewed in the vehicle width direction, the rotation axis of the grindstone extends perpendicular to the traveling surface of the bogie. Then, when the head of the rail is corrected, the dolly is run and the grindstone is rotated to come into contact with the head of the rail. As a result, the surface of the rail head is cut by the grindstone, and uneven wear (wavy wear, etc.) of the rail head is corrected.

JP-A-2017-57680

In the rail head rectifying device, when the bogie travels on the rail, the front wheels of the trolley pass through the rail before rectification. Therefore, depending on the wear condition of the rail head, the front wheels of the bogie may move up and down unnecessarily according to the surface shape of the rail head, so that the posture of the bogie may be unnecessarily tilted in the front-rear direction. In this case, the rotating shaft of the grindstone is unnecessarily tilted with respect to the rail together with the bogie, which is one of the factors that reduce the accuracy of the rail head being ground by the grindstone.

The present invention has been made in view of such circumstances, and an object of the present invention is to provide a rail head rectifying device capable of rectifying a rail head with high accuracy.

The rail head rectifying device for solving the above problems includes a trolley having a structure capable of traveling on the rail and a rotary grinder provided on the trolley so that the rotation axis extends in the vertical direction of the trolley. In a rail head rectifying device, the rail head rectifying device comprises A rotary support portion that rotatably supports the grindstone, a tilt support portion that supports the rotary support portion on the trolley in a manner in which the grindstone and the rotary shaft can tilt in the front-rear direction of the trolley, and the grindstone. A grindstone pressing portion that presses against the rail side and presses the cutting surface of the grindstone against the head of the rail, and a forward press that presses the rotary support portion in a manner that tilts the rotating shaft forward in the traveling direction of the trolley. It has a part and.

According to the above configuration, when the rail head is corrected, the cutting surface of the grindstone is pressed against the rail head in a state where the rotation axis of the grindstone can be tilted in the front-rear direction. Therefore, even if the posture of the bogie is unnecessarily tilted in the front-rear direction due to uneven wear of the rail head, the cutting surface of the grindstone and the surface of the rail head are maintained in a aligned state. , The axis of rotation of the grindstone will tilt in the front-back direction. As a result, the cutting surface of the grindstone can be moved following the surface of the rail head, so that the rail head can be sharpened with high accuracy by the grindstone.

In the above configuration, when the trolley is run to correct the rail head, the frictional force generated at the contact portion between the rail head and the grindstone causes the trolley to move behind the grindstone, the rotating shaft, and the rotating support portion in the traveling direction. A force that pushes to the side (backward pushing pressure) comes to act. According to the above configuration, when the bogie is driven to correct the rail head, the rotation axis of the grindstone is tilted forward in the traveling direction of the bogie, in other words, it is rotated in the direction of moving the grindstone forward in the traveling direction. The support portion will be pressed. Thereby, at least a part of the rear pressing force can be offset by the force (forward pressing force) that presses the rotation support portion (grindstone and the rotation shaft) forward in the traveling direction by the front pressing portion. Therefore, it is possible to prevent the rotation axis from tilting to the rear side in the traveling direction due to the rearward pressing force, so that the rail head can be sharpened with high accuracy by the grindstone.

In the rail head rectifying device, it is preferable to have a rear pressing portion that presses the rotation supporting portion in a direction in which the rotating shaft is tilted rearward in the traveling direction of the bogie.
According to the above configuration, when the bogie is moved forward, one of the pair of pressing portions can be used as the front pressing portion to correct the rail head with a grindstone. Moreover, when the bogie is driven backward, the other of the pair of pressing portions can be used as the front pressing portion to correct the rail head with a grindstone. As described above, according to the above configuration, it is possible to correct the rail head with a grindstone with high accuracy in response to the bidirectional traveling of the bogie.

In the rail head correction device, the higher the traveling speed of the bogie, the greater the pressing force for pressing the rotation support portion in the direction of tilting the rotation shaft forward in the traveling direction of the bogie. It is preferable to have a setting unit that determines the pressing force by the front pressing portion and the pressing force by the rear pressing portion.

The higher the traveling speed of the bogie, the greater the frictional force generated at the contact portion between the rail head and the grindstone, so that the rearward pressing force acting on the grindstone, the rotating shaft, and the rotating support portion also increases. According to the above configuration, the forward pressing force (specifically, the resultant force of the pressing force by the front pressing portion and the pressing force by the rear pressing portion) for canceling such a rear pressing force is applied as the traveling speed of the bogie is higher. Can be made larger. As a result, the rearward pressing force can be suitably canceled by the forward pressing force, so that the rotation axis together with the grindstone can be preferably suppressed from tilting backward in the traveling direction due to the backward pressing force.

According to the present invention, the rail head can be corrected with high accuracy.

The plan view of the rail head rectifying device of one Embodiment. Side view of the rail head rectifying device. The block diagram which shows the drive device of the drive carriage. The block diagram which shows the air pressure supply circuit. (A) and (b) Explanatory drawing which shows the adjustment mode of the tilt angle in the vehicle width direction of a tilt block. Explanatory drawing which shows the tilting mode in the front-rear direction of a shaft case. A flowchart showing an execution procedure of the work of correcting the rail head. (A) and (b) Schematic diagram showing the map structure of the calculation map used for setting the output pressure of the electropneumatic regulator. The schematic which shows the state of the rail head rectifying device before the contact of a grindstone. The schematic which shows the state of the rail head rectifying device at the time of contact of a grindstone. The schematic diagram which shows the state of the rail head rectifying device at the time of rectifying a rail head.

Hereinafter, an embodiment of the rail head rectifying device will be described.
As shown in FIGS. 1 and 2, the rail head correction device of the present embodiment includes a drive bogie 30 for running the device on the rail 20 and a grindstone for correcting the head of the rail 20. It has a spindle bogie 60. The drive carriage 30 and the spindle carriage 60 are connected via a connection mechanism 31. The rail head rectifying device is used in a state where the drive carriage 30 and the spindle trolley 60 are connected by the connecting mechanism 31 when the head of the rail 20 is rectified. On the other hand, when the rail head rectifying device is transported, the drive carriage 30 and the spindle carriage 60 are disconnected by the connection mechanism 31. As a result, the drive carriage 30 and the spindle carriage 60 can be divided and transported separately.

The drive carriage 30 has a frame 32 having a rectangular outer shape and wheels 33 attached to the frame 32. Two wheels 33 are provided on one rail 20 in a manner in which two wheels 33 are mounted on the frame 32, two at each of the left and right ends in the vehicle width direction of the frame 32, for a total of four wheels 33.

A manual lever type brake device 34 is attached to the drive carriage 30. When the brake device 34 is turned on, a friction piece (not shown) is pressed against the wheel 33 to regulate the rotation of the wheel 33. When the brake device 34 is turned off, the friction piece is separated from the wheel 33 to allow the wheel 33 to rotate.

As shown in FIGS. 1 to 3, a generator 35 is mounted on the frame 32. The generator 35 has a built-in internal combustion engine as a power source, and is started by a manual operation. The drive carriage 30 is provided with an electric motor 36 (specifically, a servomotor) for driving the carriage. The output shaft of the electric motor 36 is connected to one of the wheels 33 via a speed reducer 37, an air clutch 38, and a gear mechanism 39.

A control panel unit 40 is provided on the frame 32. The control panel unit 40 has a control device 41 (FIG. 3) mainly composed of a microcomputer and a motor drive device 42 (specifically, a servo amplifier) for driving an electric motor 36. .. Further, a touch panel type operation panel 43 is attached to the control panel unit 40, and various operation switches such as a start power switch 44, an operation preparation on switch 45, and an operation preparation off switch 46 are attached. A pendant switch 47 is attached to the control panel unit 40. The pendant switch 47 includes an on / off switch 471 that switches between valid / invalid operation by the switch 47, a changeover switch 472 that switches between traveling for moving the drive carriage 30 and traveling for correcting the rail head, and driving. It has a forward switch 473 for forward traveling of the bogie 30 and a reverse switch 474 for reverse traveling. The operation panel 43 and various operation switches 44 to 46, 471 to 474 are connected to the control device 41, and the output signal of the operation panel 43 and the detection signals of the various operation switches 44 to 46, 471 to 474 are connected to the control device 41. It has been captured.

The control device 41 performs various calculations based on the output signals of the operation panel 43 and the detection signals of various operation switches, and based on the calculation results, the operation control of the motor drive device 42 (electric motor 36), and eventually the drive. The traveling control of the trolley 30 is executed.

A compressor 50 is mounted on the frame 32. As shown in FIG. 4, the compressor 50 includes an internal combustion engine 51 as a power source, a pressure pump 52 driven by the internal combustion engine 51, an air tank 53 for storing high-pressure air generated by the pressure pump 52, and the like. doing. The compressor 50 is of a type that is started by a manual operation.

In the present embodiment, the generated pressure (air pressure) of the compressor 50 is supplied to various actuators of the spindle bogie 60 and used for operating the grindstone 70. Control (air pressure supply control) for supplying air pressure to various actuators of the spindle bogie 60 is also executed by the control device 41. In the present embodiment, the control device 41 corresponds to the control unit. The air pressure supply circuit for supplying air pressure to various actuators of the spindle bogie 60 and the execution mode of air pressure supply control will be described in detail later.

As shown in FIGS. 1 and 2, the spindle carriage 60 has a frame 61 having a rectangular outer shape and three wheels 62 attached to the frame 61. Two wheels 62 are attached to one end (lower part of FIG. 1) of the frame 61 in the vehicle width direction so as to ride on one of the pair of rails 20. Further, an arm 63 extending in the vehicle width direction is projected from the other end (upper side of FIG. 1) of the frame 61 in the vehicle width direction, and an arm 63 extending in the vehicle width direction is projected from the other end of the pair of rails 20 at the tip of the arm 63. One wheel 62 is attached in a riding mode. The spindle trolley 60 can travel on the rail 20 by three wheels 62.

The spindle bogie 60 is equipped with a grindstone 70 for cutting the head of the rail 20 and peripheral devices of the grindstone 70.
The spindle bogie 60 is provided with a drive unit 71 for rotationally driving the grindstone 70. The drive unit 71 has an internal combustion engine 72 as a drive source, and a rotation shaft 73 connecting the output shaft of the internal combustion engine 72 and the grindstone 70. The internal combustion engine 72 is manually started. When the internal combustion engine 72 is operated, the grindstone 70 is rotationally driven together with the rotating shaft 73.

As shown in FIG. 2, the spindle carriage 60 is provided with a shaft case 80 that supports the drive unit 71. The shaft case 80 has a cylindrical shape extending in the vertical direction (vertical direction in FIG. 2) of the spindle carriage 60. A rotating shaft 73 is inserted through the shaft case 80 in such a manner that the internal combustion engine 72 is arranged above the shaft case 80 and the grindstone 70 is arranged below the coaxial case 80. In this embodiment, the shaft case 80 corresponds to the rotation support portion.

An inner case 82 is attached to the lower part inside the shaft case 80. The inner case 82 is arranged so as to be movable in the vertical direction and non-rotatable in the circumferential direction with respect to the shaft case 80. A rotating shaft 73 is inserted inside the inner case 82, and the rotating shaft 73 is rotatably supported via a bearing. A spline bearing 81 is fixed to the upper part of the inner case 82. The inner case 82 is supported inside the shaft case 80 via the spline bearing 81. A rotating shaft 73 is inserted inside the spline bearing 81. The rotating shaft 73 is rotatably supported inside the shaft case 80 via such an inner case 82 and a spline bearing 81. Further, by being guided by the spline bearing 81, the rotating shaft 73 can move in the vertical direction with respect to the shaft case 80 together with the internal combustion engine 72 and the grindstone 70.

As shown in FIGS. 1 and 5, the shaft case 80 is provided so as to be tiltable with respect to the frame 61 of the spindle carriage 60 via a movable base 64, a support block 65, a tilting mechanism 66, and an adjust bolt 67. There is.

The movable base 64 has a rectangular outer shape. The movable base 64 is arranged above the frame 61 so as to extend parallel to the upper surface of the frame 61. The movable base 64 is attached to the frame 61 via the feed screw mechanism 68. As shown in FIGS. 5A and 5B, the feed screw mechanism 68 includes a male screw 681 extending in the vehicle width direction (left-right direction in FIG. 5) and rotatably supported by the frame 61, and a movable base. It has a female screw member 682 fixed to 64 and fitted with the male screw 681. A rotary lever 683 is fixed to one end of the male screw 681. By operating the rotary lever 683 to rotate the male screw 681, the movable base 64 can be moved in the vehicle width direction with respect to the frame 32.

As shown in FIGS. 1 and 5, the support block 65 has a base block 651 fixed to the movable base 64 and a tilt block 652 tiltably supported by the base block 651. The tilt block 652 has an outer square columnar shape extending in the vertical direction. The tilt block 652 can tilt with respect to the base block 651 so that the upper portion swings in the vehicle width direction with the lower portion as a fulcrum.

The tilting mechanism 66 is attached to the upper end of the tilting block 652. The tilting mechanism 66 has a tilting shaft portion 661 extending in the vehicle width direction and a bearing portion 662 that rotatably supports the tilting shaft portion 661. One end of the tilting shaft portion 661 is fixed to the shaft case 80, and the bearing portion 662 is fixed to the upper end of the tilting block 652. The shaft case 80 is arranged on the outer side in the vehicle width direction with respect to the tilt block 652 in a manner extending in the vertical direction. Further, the shaft case 80 is arranged in such a manner that the grindstone 70 arranged below the shaft case 80 is located between the two front and rear wheels 33. As a result, as shown in FIG. 2, the shaft case 80, together with the grindstone 70, is tilted between the two wheels 33 with the tilting shaft portion 661 (see FIG. 1) as the center of tilt, and the shaft case 60 is in the front-rear direction (left and right in FIG. 2). It is possible to tilt in the direction). In the present embodiment, the support block 65 and the tilting mechanism 66 correspond to the tilting support portion.

A protective sheet 69 is attached to the frame 61 of the spindle carriage 60 so as to cover the periphery of the grindstone 70. The protective sheet 69 prevents sparks generated during cutting by the grindstone 70 from scattering to the outside of the apparatus.

As shown in FIGS. 1 and 5, the adjust bolt 67 is composed of one turnbuckle 671 and two male screw members 672 and 673. The first male screw member 672 is connected to the inner side surface of the tilt block 652 in the vehicle width direction. The second male screw member 673 is connected to the upper surface of the movable base 64. A turnbuckle 671 is provided so as to connect these male screw members 672 and 673. As shown in FIGS. 5 (a) and 5 (b), by rotating the turnbuckle 671, the length of the entire adjust bolt 67 can be changed to adjust the tilt angle of the tilt block 652 in the vehicle width direction. It has become.

As shown in FIGS. 1 and 2, the spindle carriage 60 is provided with a pair of pressing cylinders 90 for lowering the grindstone 70 and pressing it against the head of the rail 20. As these pressing cylinders 90, pneumatically operated ones are adopted. One of the pressing cylinders 90 is arranged in a portion corresponding to the front side in the traveling direction (hereinafter, the forward side [right side in FIG. 2]) when the spindle carriage 60 in the shaft case 80 advances, and the other is the spindle carriage in the shaft case 80. It is attached to a portion corresponding to the front side in the traveling direction (hereinafter, the reverse side [left side in FIG. 2]) when the 60 moves backward. Each pressing cylinder 90 is provided so that the rod portion 902 can move in the vertical direction with respect to the cylinder portion 901. The cylinder portion 901 of each pressing cylinder 90 is fixed to the outer surface of the shaft case 80. A flange portion 84 is projected from the outer peripheral surface of the portion of the inner case 82 that is exposed to the outside below the shaft case 80. The tip of the rod portion 902 of each pressing cylinder 90 is fixed to the flange portion 84.

When the rod portion 902 of each pressing cylinder 90 is pulled in, the grindstone 70 and the rotating shaft 73 move upward together with the inner case 82. As a result, the grindstone 70 is separated from the head of the rail 20. On the other hand, when the rod portion 902 of the pressing cylinder 90 is pushed out, the grindstone 70 and the rotating shaft 73 move downward together with the inner case 82. As a result, the grindstone 70 is pressed against the head of the rail 20. In this embodiment, the pressing cylinder 90 corresponds to the grindstone pressing portion.

The spindle bogie 60 is provided with a pair of pressing cylinders 91 and 92 for pressing the shaft case 80 in the tilting direction centered on the tilting shaft portion 661. As the pressing cylinders 91 and 92, pneumatically operated ones are adopted. As shown in FIGS. 1 and 6, specifically, the surface of the tilt block 652 on the shaft case 80 side has an eaves shape that protrudes toward the shaft case 80 and extends in the front-rear direction (horizontal direction in FIG. 6). The eaves 83 is fixed. Further, a pressing block 85 (FIG. 6) is projected from the surface of the shaft case 80 on the tilting block 652 side. A first pressing cylinder 91 is provided on the reverse side of the eaves 83, and a second pressing cylinder 92 is provided on the forward side. As shown in FIG. 6, in these pressing cylinders 91 and 92, the cylinder portions 911 and 921 are fixed to the eaves portion 83, and the tips of the rod portions 912 and 922 are fixed to the pressing block 85. In the device of the present embodiment, the shaft case 80 is pressed forward by pushing out the rod portion 912 of the first pressing cylinder 91, while the shaft case 80 is pushed out by pushing out the rod portion 922 of the second pressing cylinder 92. It is pressed to the reverse side.

The spindle bogie 60 is provided with a stopper 653 for regulating the tilt of the shaft case 80. Specifically, a locking block 86 is provided so as to project from the surface of the shaft case 80 on the tilting block 652 (see FIG. 1) side. Further, the stopper 653 is located on the surface of the tilting block 652 on the shaft case 80 side at a position where the locking block 86 is sandwiched between the tilting block 652 and at a position where a gap is formed between the tilting block 652 and the locking block 86. Is fixed. In the device of the present embodiment, when the shaft case 80 tilts in the front-rear direction with respect to the tilt shaft portion 661, when the tilt angle of the coaxial case 80 becomes large, the stopper 653 comes into contact with the locking block 86, which causes the stopper 653 to come into contact with the locking block 86. The tilting of the shaft case 80 is regulated.

Hereinafter, an air pressure supply circuit for supplying air pressure to various actuators of the spindle bogie 60 will be described.
As shown in FIG. 4, the air pressure supply circuit of this embodiment has an air pressure combination 100 and a manifold 101. The output unit of the compressor 50 is connected to the manifold 101 via the air conditioning 100. The air conditioning combination 100 includes an air filter, a mist separator, and a regulator. Four solenoid valves 102 to 105 are attached to the manifold 101. All of these solenoid valves 102 to 105 are always closed type. The high-pressure air introduced from the compressor 50 to the manifold 101 is distributed to the solenoid valves 102 to 105 by the branch passage inside the manifold 101.

The solenoid valve 102 is connected to the lock port of each pressing cylinder 90. When the solenoid valve 102 is closed, high-pressure air (pressure signal) is not input to the lock port, and each pressing cylinder 90 is in a locked state in which it does not operate. On the other hand, when the solenoid valve 102 is opened, a pressure signal is input to the lock port, and each pressing cylinder 90 is in an unlockable state in which it can be operated. In the device of the present embodiment, the solenoid valve 102 is opened when the control for correcting the head of the rail 20 by the grindstone 70 (correction control) is executed. As a result, the pressing cylinder 90 is in the unlocked state. On the other hand, when the correction control is not executed, the solenoid valve 102 is closed. As a result, each pressing cylinder 90 is locked in a state where the grindstone 70 is located away from the head of the rail 20.

The solenoid valve 103 is connected to the extrusion chamber of each pressing cylinder 90 via an electropneumatic regulator 1031 and a meter-out control speed controller 1032. By opening the solenoid valve 103 and executing operation control of the electropneumatic regulator 1031, the pressure in the extrusion chamber of each pressing cylinder 90 can be adjusted. In this circuit, meter-out control by the speed controller 1032 realizes quick introduction when air is introduced into the extrusion chamber in order to increase the pressure in the extrusion chamber of each push cylinder 90, while the pressure in the extrusion chamber is increased. When air is discharged from the extrusion chamber in order to reduce the pressure, the discharge rate is limited. A pressure switch 1033 that is turned on when the pressure of the portion becomes equal to or higher than a predetermined operating pressure is connected to a portion between the electropneumatic regulator 1031 and the speed controller 1032. The output signal of the pressure switch 1033 is taken in by the control device 41.

In the air pressure supply circuit of the present embodiment, the portion between the air pressure combination 100 and the manifold 101 is connected to the lead-in chamber of each pressing cylinder 90 via the speed controller 1061 and the precision regulator 1062 of the meter-out control. Therefore, when the compressor 50 is operated, the output pressure of the compressor 50 is reduced to a predetermined pressure by the precision regulator 1062, and then the compressor 50 is introduced into the suction chamber of the pressing cylinder 90. In this circuit, the meter-out control by the speed controller 1061 realizes quick introduction when air is introduced into the suction chamber in order to raise the pressure in the suction chamber of the pressing cylinder 90 to a predetermined pressure, while the rod portion. When air is discharged from the drawing chamber with the extrusion of 902, the discharge rate is limited.

The solenoid valve 104 is connected to the extrusion chamber of the first pressing cylinder 91 via an electropneumatic regulator 1041 and a meter-out control speed controller 1042. By opening the solenoid valve 104 and controlling the operation of the electropneumatic regulator 1041, the pressure in the extrusion chamber of the first pressing cylinder 91, and by extension, the shaft case 80 (see FIG. 6) by the first pressing cylinder 91. The pressing force to be pressed toward the forward side can be adjusted. In this circuit, the meter-out control by the speed controller 1042 realizes quick introduction when air is introduced into the extrusion chamber in order to increase the pressure in the extrusion chamber of the first pressing cylinder 91, while the pressure of the extrusion chamber is increased. When air is released from the extrusion chamber in order to reduce the pressure, the release rate is limited.

Further, the solenoid valve 104 is connected to the extrusion chamber of the second pressing cylinder 92 via an electropneumatic regulator 1043 and a meter-out control speed controller 1044. By opening the solenoid valve 104 and controlling the operation of the electropneumatic regulator 1043, the pressure in the extrusion chamber of the second pressing cylinder 92, and by extension, the pushing that presses the shaft case 80 backward by the second pressing cylinder 92. The pressure can be adjusted. In this circuit, the meter-out control by the speed controller 1044 realizes quick introduction when air is introduced into the extrusion chamber in order to increase the pressure in the extrusion chamber of the second pressing cylinder 92, while the extrusion chamber When air is released from the extrusion chamber in order to reduce the pressure, the release rate is limited.

The solenoid valve 105 is connected to the air clutch 38 via a meter-in controlled speed controller 1051. The solenoid valve 105 is closed when the correction control is not executed. At this time, since the high-pressure air is not introduced into the air clutch 38, the air clutch 38 does not operate, and the electric motor 36 and the wheels 33 are not connected to each other. On the other hand, the solenoid valve 105 is opened when the correction control is executed. At this time, high-pressure air is introduced into the air clutch 38 to operate the air clutch 38, and the electric motor 36 and the wheels 33 are connected to each other. As a result, the drive carriage 30 can be driven by the electric motor 36.

In the device of the present embodiment, the relationship between the traveling direction of the drive carriage 30 and the traveling speed at the time of executing the correction control can be arbitrarily set through the operation of the operation panel 43 by the operator. Then, the control device 41 is based on the relationship between the set traveling speed and the traveling direction, the electric motor 36, the electropneumatic regulator 1031 for the pressing cylinder 90, the electropneumatic regulator 1041 for the first pressing cylinder 91, and the second. The execution pattern of the operation control of various control devices such as the electropneumatic regulator 1043 for the pressing cylinder 92 is determined for each traveling direction. After that, when a start operation for starting the execution of the correction control is performed, the control device 41 executes the operation control of various control devices in the above execution pattern in response to the start operation. After that, when a stop operation for stopping the execution of the correction control is performed, the control device 41 stops the operation control of various control devices in a predetermined execution pattern in response to the stop operation.

In the present embodiment, based on the results of various experiments and simulations by the inventor and the like, the traveling speed of the drive bogie 30 that allows the head of the rail 20 to be properly corrected by the grindstone 70 and the traveling speed of the drive bogie 30. The relationship between the traveling direction of the drive bogie 30 and the execution pattern of the operation control of various control devices is required in advance, and the relationship is stored in the control device 41. Based on this relationship and the relationship between the traveling speed of the drive carriage 30 and the traveling direction input by the operator, the control device 41 executes the correction control.

Hereinafter, the execution procedure of the work of correcting the head of the rail 20 will be described with reference to the flowchart shown in FIG.
As shown in FIG. 7, in this operation, first, various power devices of the rail head rectifying device are activated (step S1). Specifically, the internal combustion engine 51, the compressor 50, and the generator 35 of the drive unit 71 are started by the manual operation of the operator. After that, the start power switch 44 of the control panel unit 40 is turned on to start various electric devices (motor drive device 42 and control device 41). Further, after that, the operation preparation on switch 45 is turned on.

The control device 41 determines an execution pattern of operation control of various control devices (electric motor 36, solenoid valves 102 to 105, electropneumatic regulator 1031, 1041, 1043) in accordance with the activation of the rail head correction device (the electric motor 36, the solenoid valves 102 to 105, and the electropneumatic regulator 1031, 1041, 1043). Step S2). Specifically, in the control device 41, the relationship between the traveling direction of the drive carriage 30 and the traveling speed at the time of executing the correction control is set and stored through the operation of the operation panel 43 by the operator. Then, in the work of step S2, the control device 41 performs various calculations based on the above relationship, and the execution pattern of the operation control of the various control devices is determined based on the calculation results. The work of storing the above relationship in the control device 41 is performed at the time of executing the work of correcting the head of the rail 20 (a series of work shown in FIG. 7), and is performed in advance prior to the execution of the work. You can also go to.

In the present embodiment, based on the above relationship, the output pressure of the first electropneumatic regulator 1041 for the first pressing cylinder 91 and the second pressing cylinder are obtained from the calculation maps shown in FIGS. 8 (a) and 8 (b). The output pressure of the second electropneumatic regulator 1043 for 92 is defined. In the present embodiment, based on the results of various experiments and simulations by the inventor and the like, the traveling speed and traveling direction of the drive carriage 30 capable of correcting the head of the rail 20 at an assumed level and each of them. The relationship with the output pressure of the electropneumatic regulators 1041 and 1043 is required in advance. In the present embodiment, such a relationship is stored in the control device 41 as the calculation map. Specifically, as the same relationship, a relationship that satisfies both (Condition A) and (Condition B) below is defined. (Condition A) Both the output pressure of the electropneumatic regulator for the pressing cylinder on the rear side in the traveling direction of the spindle bogie 60 and the output pressure of the electropneumatic regulator for the pressing cylinder on the front side in the traveling direction are higher as the traveling speed is higher. Become a value. (Condition B) The traveling speed of the drive carriage 30 is obtained by subtracting the output pressure of the electropneumatic regulator for the pressing cylinder on the front side in the traveling direction from the output pressure of the electropneumatic regulator for the pressing cylinder on the rear side in the traveling direction of the drive carriage 30. The higher the value, the higher the value.

After that, by driving the drive carriage 30 through the operation of the pendant switch 47 (see FIG. 2), the rail head correction device is moved to a position where the execution of the correction control is started (step S3). Specifically, first, the on / off switch 471 is operated to the "on position" that enables the operation by the pendant switch 47, and the changeover switch 472 is operated to the "running position". Then, the drive carriage 30 is driven through the operation of the forward switch 473 or the reverse switch 474 to move the race head correction device to the start position.

After that, when the operator performs a start operation for starting the execution of the correction control (step S4: YES), the control device 41 executes the correction control (step S5). Here, when the forward switch 473 or the reverse switch 474 is operated while the changeover switch 472 is operated to the "correction position", the control device 41 determines that the start operation has been performed. In the correction control, specifically, as shown in FIG. 9, the driving carriage 30 is started to travel through the operation control of the electric motor 36, and the operation control of the solenoid valve 102 and the operation control of the electropneumatic regulator 1031 are performed. The pressing cylinder 90 is operated through the wheel, and the grindstone 70 is lowered. At this time, the first pressing cylinder 91 and the second pressing cylinder 92 are not operating and are in a state where they can be expanded and contracted substantially freely. In the period until the start operation is performed (step S4: NO), the rail head correction device of the present embodiment is in the standby state without starting the execution of the correction control.

When the execution of the correction control is started in this way, the operation control of the various control devices is continued until the grindstone 70 comes into contact with the head of the rail 20 (step S6: NO). The contact of the grindstone 70 with the head of the rail 20 is determined by the control device 41 because the pressure in the extrusion chamber of the pressing cylinder 90 has increased, specifically, the pressure switch 1033 has been turned on. NS.

Then, as shown in FIG. 10, when the grindstone 70 comes into contact with the head of the rail 20 (step S6: YES), the electropneumatic regulator 1041 for the first pressing cylinder 91 and the electropneumatic regulator 1043 for the second pressing cylinder 92. Are operated at the output pressures determined in the process of step S2, respectively (step S7). Further, the operation control of the electropneumatic regulator 1031 for the pressing cylinder 90 is executed in such a manner that the grindstone 70 is pressed against the head of the rail 20 at a predetermined predetermined pressure (step S8). Then, in this state, the drive carriage 30 and the spindle carriage 60 travel on the rail 20 at a predetermined speed.

In the rail head rectifying device of the present embodiment, when the grindstone 70 comes into contact with the head of the rail 20, both the first pressing cylinder 91 and the second pressing cylinder 92 are in a state of being substantially freely expandable and contractible. There is. As a result, the shaft case 80 and the rotating shaft 73 can be tilted substantially freely in the front-rear direction. Therefore, in such a state, the cutting surface of the grindstone 70 comes into contact with and pressed against the head surface of the rail 20, so that the cutting surface of the grindstone 70 and the head surface of the rail 20 are aligned. The rotating shaft 73 of the grindstone 70 tilts in the front-rear direction. Therefore, the cutting surface of the grindstone 70 and the head surface of the rail 20 are aligned after the contact, regardless of the relative angle between the cutting surface of the grindstone 70 and the head surface of the rail 20 before the contact.

Therefore, even when the posture of the spindle carriage 60 is unnecessarily tilted in the front-rear direction due to uneven wear of the rail 20 head, the cutting surface of the grindstone 70 and the head surface of the rail 20 are aligned. The rotation shaft 73 of the grindstone 70 is automatically tilted in the front-rear direction so as to be in the state. As a result, the cutting surface of the grindstone 70 can be moved following the surface of the head of the rail 20, so that the head of the rail 20 can be sharpened with high accuracy by the grindstone 70.

Here, as shown in FIG. 11, when the spindle carriage 60 is run to correct the head of the rail 20, the frictional force P0 generated at the contact portion between the head of the rail 20 and the cutting surface of the grindstone 70 (FIG. 11). 10), a force (rear pressing force F0) that presses the grindstone 70, the rotating shaft 73, and the shaft case 80 in a manner of tilting the spindle trolley 60 to the rear side in the traveling direction acts.

In the present embodiment, the spindle carriage 60 is pressed against the rear pressing portion (first pressing cylinder 91 in the example shown in FIG. 11) that presses the shaft case 80 rearward in the traveling direction and the front that presses the shaft case 80 forward in the traveling direction. A pressing portion (in the example shown in FIG. 11, a second pressing cylinder 92) is provided. The pressing force F1 by the first pressing cylinder 91 as the rear pressing portion is larger than the pressing pressure F2 by the second pressing cylinder 92 as the front pressing portion.

Therefore, when the spindle carriage 60 is driven to correct the head of the rail 20, the rotary shaft 73 of the grindstone 70 is moved by the resultant force (= F2-F1) of the pressing cylinders 91 and 92. The shaft case 80 is pressed in the direction of tilting forward in the direction, in other words, in the direction of moving the grindstone 70 forward in the traveling direction. As a result, the rearward pressing force F0 can be offset by the forward pressing force (= F2-F1) that presses the shaft case 80 forward in the traveling direction by the resultant force of the pressing cylinders 91 and 92. In other words, when the spindle bogie 60 travels, it is expected that the rear pressing force F0 will act on the shaft case 80, and a front pressing force capable of canceling the rearward pressing force F0 is applied to the shaft case 80 in advance. Can be left. As a result, it is possible to prevent the rotating shaft 73 from tilting backward in the traveling direction due to the rearward pressing force F0, so that the head of the rail 20 can be corrected with high accuracy by the grindstone 70. can.

In the present embodiment, the calculation map (see FIG. 8) used for setting the output pressure of each electropneumatic regulator 1041, 1043 has a relationship in which the rear pressing force F0 and the front pressing force (F2-F1) are balanced. It has been decided. When the spindle carriage 60 travels (forwards) in the direction opposite to the examples shown in FIGS. 9 to 11, the first pressing cylinder 91 corresponds to a front pressing portion that presses the shaft case 80 forward in the traveling direction. The second pressing cylinder 92 corresponds to a rear pressing portion that presses the shaft case 80 rearward in the traveling direction.

As shown in FIG. 7, while the operation of the forward switch 473 or the reverse switch 474 of the pendant switch 47 by the operator is continued (step S9: NO), the execution of the correction control in the above-described embodiment is continued. Will be done.

Then, when the operation of the forward switch 473 or the reverse switch 474 of the pendant switch 47 by the operator is stopped (step S9: YES), it is assumed that the stop operation for stopping the execution of the correction control is performed, and the rail 20 Control (stop control) for stopping the work of correcting the head is executed (step S10). In this stop control, after raising the grindstone 70 through the operation control of the electropneumatic regulator 1031 for the pressing cylinder 90, the operation of the pressing cylinder 90 is locked through the operation control of the solenoid valve 102. Further, the first pressing cylinder 91 and the second pressing cylinder 92 are brought into a state of being substantially freely extended through the operation control of the electropneumatic regulators 1041 and 1043. Further, the drive carriage 30 is decelerated and stopped through the operation control of the electric motor 36.

In the present embodiment, the series of operations shown in the flowchart of FIG. 7 is performed again after changing the contact angle of the grindstone 70 with respect to the head of the rail 20 through the manual operation of the feed screw mechanism 68 and the adjust bolt 67. , Repeated multiple times. As a result, the head of the rail 20 is sharpened over a wide area.

As described above, according to the present embodiment, the effects described below can be obtained.
(1) On the spindle carriage 60, a rear pressing portion (one of a pair of pressing cylinders 91 and 92) that presses the shaft case 80 rearward in the traveling direction and a front pressing portion (a pair) that presses the shaft case 80 forward in the traveling direction. The other side of the pressing cylinders 91 and 92) is provided. Then, the pressing force F2 by the front pressing portion was made larger than the pressing pressure F1 by the rear pressing portion. As a result, it is possible to prevent the rotating shaft 73 from tilting backward in the traveling direction due to the rearward pressing force F0, so that the head of the rail 20 can be corrected with high accuracy by the grindstone 70. can.

(2) The spindle carriage 60 is provided with a first pressing cylinder 91 for pressing the shaft case 80 to the forward side and a second pressing cylinder 92 for pressing the shaft case 80 to the reverse side. Therefore, when the spindle bogie 60 is advanced, the correction control can be executed by using the first pressing cylinder 91 as the front pressing portion and the second pressing cylinder 92 as the rear pressing portion. Moreover, when the spindle carriage 60 is moved backward, the correction control can be executed by using the second pressing cylinder 92 as the front pressing portion and the first pressing cylinder 91 as the rear pressing portion. As described above, according to the apparatus of the present embodiment, the rail head can be corrected with high accuracy by the grindstone 70 in response to the bidirectional traveling of the spindle bogie 60.

(3) The forward pressing force that presses the shaft case 80 forward in the traveling direction is adjusted by the difference in pressing force of the pressing cylinders 91 and 92. Therefore, the forward pressing force can be finely adjusted as compared with the device for adjusting the forward pressing force using only one of the pair of pressing cylinders 91 and 92. Further, since the shaft case 80 is pressed backward in the traveling direction by the rear pressing portion, the shaft case 80 is unnecessarily tilted forward in the traveling direction even though the shaft case 80 is pressed forward in the traveling direction by the front pressing portion. You will be able to suppress what you do.

(4) An electropneumatic regulator for the first pressing cylinder 91 in such a manner that the higher the traveling speed of the spindle carriage 60, the greater the pressing force for pressing the shaft case 80 in the direction in which the rotating shaft 73 is tilted forward in the traveling direction. The output pressure of 1041 and the output pressure of the electropneumatic regulator 1043 for the second pressing cylinder 92 are determined. As the traveling speed of the spindle bogie 60 increases, the frictional force P0 (see FIG. 10) generated at the contact portion between the grindstone 70 and the head of the rail 20 increases. The rearward pressing force F0 (see FIG. 11) that acts also increases. According to the present embodiment, the forward pressing force (specifically, the resultant force of the pressing force F2 by the front pressing portion and the pressing force F1 by the rear pressing portion) for canceling the rear pressing force F0 is applied to the spindle carriage 60. The higher the running speed, the larger the value. As a result, the rearward pressing force F0 can be suitably offset by the forward pressing force (F2-F1), so that the rearward pressing force F0 preferably tilts the rotary shaft 73 together with the grindstone 70 to the rear side in the traveling direction. It can be suppressed.

The above embodiment can be modified and implemented as follows. The above embodiment and the following modified examples can be implemented in combination with each other within a technically consistent range.

If the above (condition B) is satisfied, the setting mode of the output pressure of the electropneumatic regulator 1041 for the first pressing cylinder 91 and the output pressure of the electropneumatic regulator 1043 for the second pressing cylinder 92 can be arbitrarily changed. be able to. For example, the output pressure of the electropneumatic regulator for the pressing cylinder on the front side in the traveling direction of the spindle carriage 60 is set to a constant pressure regardless of the traveling speed, and the output pressure of the electropneumatic regulator for the pressing cylinder on the rear side in the traveling direction is set to the traveling speed. Each output pressure may be set such that the higher the pressure, the higher the pressure.

The output pressure of the electropneumatic regulator 1041 for the first pressing cylinder 91 and the output pressure of the electropneumatic regulator 1043 for the second pressing cylinder 92 are set to the traveling speed of the drive carriage 30 set prior to the execution of the correction control. The setting is not limited to the basis, and may be variably set according to the actual traveling speed of the drive carriage 30. Further, as setting parameters used for setting the output pressure of each electropneumatic regulator 1041, 1043, it is possible to use the degree of bending of the rail 20 on the curved road, the tilt angle of the tilt block 652, and the like. In short, the output pressures of the electropneumatic regulators 1041 and 1043 are set so that the rear pressing force F0 caused by the frictional force P0 and the front pressing force, which is the resultant force of the pressing forces of the pressing cylinders 91 and 92, are balanced. I just need to be able to.

-In a device with a single drive carriage 30, the calculation map used to calculate the output pressure of each electropneumatic regulator 1041, 1043 shall be defined as a set of forward relations and reverse relations. You may.

When the spindle bogie 60 is advanced when the correction control is executed, the first pressing cylinder 91 as the front pressing portion is operated to generate the front pressing pressure, and the second pressing cylinder 92 as the rear pressing portion is used. It may be inactive and stretched freely. Further, when the spindle bogie 60 is moved backward when the correction control is executed, the second pressing cylinder 92 as the front pressing portion is operated to generate the front pressing pressure, and the first pressing cylinder 91 as the rear pressing portion is generated. May be inactivated so that it can be freely extended. Even with such a configuration, it is possible to cancel the rear pressing force F0 caused by the frictional force P0 and the front pressing force by the front pressing portion.

-In a device of the type in which the spindle carriage 60 travels in only one direction, one of the pair of pressing cylinders 91 and 92, specifically, the rear pressing portion that presses the shaft case 80 rearward in the traveling direction may be omitted. good.

During the period before the grindstone 70 comes into contact with the head of the rail 20, the output pressure of each electropneumatic regulator 1041, 1043 is pressed by the pressing cylinders 91 and 92 when the grindstone 70 comes into contact with the head of the rail 20. The pressure may be low enough that the pressure does not prevent the shaft case 80 from tilting.

The arrangement mode of the first pressing cylinder 91 and the arrangement mode of the second pressing cylinder 92 can be arbitrarily changed. For example, a flange portion that protrudes toward the forward side is provided at the lower portion of the side surface of the shaft case 80 on the forward side, and a first pressing cylinder that presses the flange portion upward and a second pressing that presses the flange portion downward. A cylinder may be provided. In addition, it is also possible to provide a first pressing cylinder that presses a portion of the shaft case 80 above the tilting shaft portion 661 toward the forward side, and a second pressing cylinder that presses the portion toward the reverse side. With either configuration, the shaft case 80 can be pressed in the direction of tilting forward by the first pressing cylinder, and the shaft case 80 can be pressed in the direction of tilting backward by the second pressing cylinder.

The pressing cylinder 90 and its peripherals, and the pressing cylinders 91 and 92 and their peripherals can be arbitrarily changed. For example, instead of providing the pneumatically operated cylinder and the electropneumatic regulator in combination, it is possible to provide the hydraulically operated cylinder and the hydraulic control valve in combination.

The rail head rectifying device according to the above embodiment does not have a structure (adjustment bolt 67, feed screw mechanism 68, etc.) for changing the contact angle of the grindstone 70 with respect to the head of the rail 20. It can also be applied to a straightening device.

The rail head rectifying device according to the above embodiment can also be applied to a rail head rectifying device having a structure in which the drive carriage 30 and the spindle carriage 60 cannot be separated.
The rail head rectifying device according to the above embodiment can also be applied to a rail head rectifying device of a type in which the grindstone 70 is driven by an electric motor.

20 ... Rail 30 ... Drive carriage 40 ... Control panel section 41 ... Control device 43 ... Operation panel 60 ... Spindle carriage 66 ... Tilt mechanism 70 ... Grinding stone 71 ... Drive section 72 ... Internal combustion engine 73 ... Rotating shaft 80 ... Shaft case 90 ... Pushing Cylinder 91 ... 1st pressing cylinder 92 ... 2nd pressing cylinder 1031 ... Electropneumatic regulator 1041 ... Electropneumatic regulator 1043 ... Electropneumatic regulator

Claims (3)

A bogie having a structure capable of traveling on a rail and a rotary grinder provided on the bogie in a manner in which a rotation axis extends in the vertical direction of the bogie are provided, and the bogie is allowed to travel on the rail and is described as described above. In a rail head rectifying device that rectifies the head of the rail with the grinder by contacting the head of the rail while rotating the grinder.
A rotary support portion that rotatably supports the grindstone,
In a manner in which the grindstone and the rotating shaft can be tilted in the front-rear direction of the carriage, a tilting support portion that supports the rotation support portion on the carriage, and a tilting support portion.
A grindstone pressing portion that presses the grindstone toward the rail side and presses the cutting surface of the grindstone against the head of the rail.
A rail head rectifying device including a front pressing portion that presses the rotation supporting portion in a manner in which the rotating shaft is tilted forward in the traveling direction of the bogie. The rail head rectifying device according to claim 1, further comprising a rear pressing portion that presses the rotation support portion in a direction in which the rotation shaft is tilted rearward in the traveling direction of the carriage. The higher the traveling speed of the trolley, the greater the pressing force for pressing the rotation support portion in the direction in which the rotating shaft is tilted forward in the traveling direction of the trolley. The rail head correction device according to claim 2, further comprising a setting unit for determining a pressing force by the pressing unit.

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