WO2015043545A1

WO2015043545A1 - Point machine

Info

Publication number: WO2015043545A1
Application number: PCT/CN2014/087976
Authority: WO
Inventors: 杨超; 韩锐
Original assignee: 西门子信号有限公司; 杨超; 韩锐
Priority date: 2013-09-30
Filing date: 2014-09-30
Publication date: 2015-04-02
Also published as: CN104512437A; CN104512437B

Abstract

A point machine (100) comprises a motion rod component (110), and further comprises a planet gear mechanism (120), where the planet gear mechanism (120) comprises a large gear (122) having an outer toothed ring (1221) and an inner toothed ring (1222), a planet gear (124) is engaged with the inner toothed ring (1222), a shaft of the planet gear (124) is fixedly connected to an end of a swing arm (126), the other end of the swing arm (126) is pivotally connected to a driving shaft (128), and the driving shaft (128) is connected to the motion rod component (110). By means of a gear mechanism, a bearing capability of the point machine (100) is increased, the entire circumference of the gear mechanism is a kinematic pair, so that local wear is reduced, the service life of the point machine (100) is extended, harmful impact on the point machine (100) during start and stop is reduced, and a mature gear transmission technology is adopted to reduce a processing cost.

Description

Switch machine

Technical field

The invention relates to a railway control device, in particular to a switch machine.

Background technique

The switch machine is the actuator of the ballast control system for switching, locking the position of the ballast rail or the core rail, and indicating and supervising the position and state of the ballast tip rail or the core rail in the interlocking zone.

At present, the transmission mode of the electric switch machine is mainly driven by a ball screw, as shown in Fig. 1. In the switch 10 shown in Fig. 1, the circular motion outputted by the motor 12 is converted into a linear motion by the ball screw mechanism 14 for driving the action lever 16 of the switch to change from the first extreme position to the second extreme position or On the contrary, the conversion of the switch is realized. After years of use and improvement of the ball screw transmission scheme, the technology has matured.

Summary of the invention

For the ball screw drive shown in Figure 1, the ball and the lead screw are always in contact with each other during the operation of the ball screw. The inventors of the present invention have found through research that during the movement of the ball, the speed of movement of each contact point on the circular arc line is different, so that there is a large amount of relative between the ball and the lead screw in addition to pure rolling. slide. Such sliding causes the switch machine to withstand the wear of the sliding friction, in particular the wear of the balls, in addition to the rolling friction during repeated operation. The wear of the balls is also a cause of the difficulty in finding the overall life of the ball screw.

To this end, the present invention proposes a new type of switch machine that does not use a conventional ball screw structure. In turn, the planetary gear structure is introduced into the switch machine.

According to an embodiment of the present invention, a switch machine according to the present invention includes an action lever and a planetary gear mechanism. The planetary gear mechanism includes a large gear and a planetary gear, the large gear has an outer ring gear and an inner ring gear, the planetary gear meshes with the inner ring gear, and the shaft of the planetary gear is fixedly connected with one end of a swing arm. The other end of the swing arm is pivotally connected to a drive shaft, and the drive shaft reciprocates linearly under the driving of the planetary gears to drive the action lever. Preferably, a motor is coupled to the outer ring gear of the large gear and drives the large ring gear to rotate. More preferably, the planetary gear mechanism is disposed above the action lever. Further, optionally, the drive shaft may be directly connected to the action bar and drive the action bar to move, or the drive shaft is coupled by a gear mechanism and drives the action bar to move.

According to one embodiment of the invention, a switch machine of the present invention includes a motor, an action rod assembly and a planetary gear mechanism. The planetary gear mechanism further includes: a large gear having an outer ring gear and an inner ring gear, the outer ring gear being rotated by the motor; a planetary gear meshing with the inner ring gear serving as a sun gear a planetary shaft of the planetary gear is coupled to the large gear and is driven by the large gear; a swing arm has one end fixedly coupled to the planetary shaft of the planetary gear, and the other end and a drive shaft Pivotally, the drive shaft drives the action rod assembly; wherein the planetary gear mechanism is designed to cause the drive shaft to reciprocate linearly.

According to the switch machine proposed by the above embodiment of the present invention, since the original ball screw structure is replaced by the planetary gear mechanism, the service life problem caused by the repeated wear of the balls is no longer present. Moreover, the service life of the gear is correspondingly longer than that of the ball screw. Furthermore, in the embodiment of the present invention, the machining accuracy of the gear can be in accordance with the conventional precision, whereby the machining cost of the gear is also lower than that of the ball screw, thereby reducing the manufacturing cost of the entire switch machine. It is particularly important that the planetary gear mechanism drives the linear motion of the drive shaft to not immediately act and stop immediately. In the embodiment of the present invention, since the planetary gear mechanism is used, the driving shaft drives the action lever to undergo a process of gradual acceleration-constant speed-gradual deceleration during the movement from the first extreme position to the second extreme position, thereby avoiding the process. A situation in which the ends of the motion section are subjected to a force impact. In other words, the power output has no impact, which increases the force from the other side. The life of the part increases the life of the entire switch and reduces energy consumption.

Preferably, the ring gear is supported on the bull gear by a bearing in a rotatable manner relative to the large gear. This design makes the entire planetary gear mechanism compact and more suitable for small size requirements.

More preferably, the drive shaft is directly coupled to the action bar in the action bar assembly and drives the action bar to move. Optionally, the action bar assembly includes: a transmission gear pivotally coupled to the drive shaft; a drive rack engaged with the transmission gear; a drive gear pivotally coupled to the drive shaft, and Rotating synchronously with the transmission gear; a drive rack engaged with the drive gear and coupled to the actuating lever. This design can be easily adapted to the requirements of different strokes of the action bar. The modular design of the action rod assembly allows the stroke of the action rod to be changed with only a few components changed, thus adapting to the requirements of different application environments.

In addition, the planetary gear mechanism used in the embodiment of the present invention supports the non-directional operation of the motor. That is to say, in the case where the motor does not change the direction of rotation, the reciprocating linear motion of the action lever can be achieved. Of course, the solution proposed by the present invention can also output a linear motion in the first direction when the motor rotates forward, and a linear motion in the opposite direction to the first direction when the motor is reversed.

In addition, the gear mechanism is used to improve the bearing capacity of the switch machine, and the gear mechanism is all circular motion, thereby reducing local wear and prolonging the overall service life of the switch machine. At the same time, the planetary gear mechanism reduces the harmful impact of the switch when starting and stopping, and uses mature gear transmission technology to reduce the processing cost.

DRAWINGS

Figure 1 is a schematic view of a conventional switch machine.

2 is a top plan view of a switch machine in accordance with one embodiment of the present invention.

Figure 3 is a perspective view of a planetary gear mechanism employed in a switch machine in accordance with one embodiment of the present invention.

4 is a top plan view of the planetary gear mechanism and the transmission gear mechanism illustrated in FIG. 3.

Reference numeral

10 turn machine 12 motor 14 ball screw mechanism 16 action bar

100-turn machine 101 housing 110 action rod assembly 120 planetary gear unit

122 large gear 1221 outer ring gear 122 inner ring gear 124 planetary gear

1241 planetary shaft 126 swing arm 128 drive shaft 140 motor

112 drive gear 114 drive gear

detailed description

The invention is described below in conjunction with the preferred embodiments of the invention. Many specific details are set forth in the description below. However, those skilled in the art will appreciate that the present invention may be practiced without some or all of these details. In some cases, well-known techniques are not described to avoid unnecessary confusion.

2 shows a schematic view of a switch 100 in accordance with an embodiment of the present invention. An action rod assembly 110 is mounted in the outer casing 101 of the switch 100 for pushing the ballast from one extreme position to the other to achieve a ballast action. A planetary gear mechanism 120 is mounted above the action lever assembly 110. The detecting lever 130 is mounted on one side of the actuating lever 110 for indicating and monitoring whether the switch machine is in place. The planetary gear mechanism 120 can be coupled to the motor 140 via, for example, a gear reducer (not shown). Those skilled in the art will be able to know how to connect the motor and gear mechanism through the reducer based on their own knowledge. Driven by the motor 140, the planetary gear mechanism 120 converts the rotational motion (circumferential motion) output by the motor 140 into a linear motion for driving the motion lever assembly to perform a corresponding reciprocating linear motion.

An exemplary structure of the planetary gear mechanism 120 is specifically illustrated in FIGS. In the example of FIG. 3, the planetary gear mechanism 120 includes two sets of symmetrically disposed planetary gear sets. However, in practice, only one set of planetary gear sets may be provided for driving the actuating lever assembly 110. Each planetary gear set includes a bull gear 122 and a planet gear 124. The bull gear 122 has an outer ring gear 1221 and an inner ring gear 1222. Outer ring gear 1221 For example, it is possible to rotate under the drive of the motor 140 (for example by means of a speed reducer). The ring gear 1222 is preferably supported on the bull gear 122 by, for example, a bearing that is rotatable relative to the bull gear 122. Preferably, for example, the ring gear 1222 is concentric with the outer ring gear 1221. In the example of Figures 3, 4, the planet gears 124 mesh with the ring gear 1222, which acts as a sun gear. The shaft of the planetary gear 124 is a planetary shaft 1241. The planetary shaft 1241 is pivotally disposed on the large gear 122 and is rotatable in synchronization with the large gear 122. The planetary shaft 1241 is fixedly coupled to one end of a swing arm 126, and the other end of the swing arm 126 is pivotally coupled to a drive shaft 128. The drive shaft 128 is used to drive the action bar assembly 110.

In the example of FIGS. 3 and 4, the ring gear 1222 constitutes a sun gear in the planetary gear set. The trajectory of the planetary shaft 1241 driven by the large gear 122 constitutes a planet carrier. The planet gears 124 revolve under the drive of the bull gear 122 while rotating under the restriction of the ring gear 1222. Specifically, the outer ring gear 1221 of the large gear 122, for example, is coupled to the motor 140, that is, driven by the motor 140. Those skilled in the art will appreciate that a speed reducer can be provided between the motor 130 and the bull gear 122 as needed. The large gear 122 is rotated by the motor 140 such that the planetary gears 124 pivotally coupled to the large gear 122 revolve accordingly. Driven by the ring gear 1222, the planet gears 124 that mesh with the ring gear 1222 also simultaneously rotate, thereby causing the swing arm 126 to rotate about the planet axis 1241. Thereby, the swing arm 126 simultaneously realizes the revolution and the rotation under the driving of the planetary gears, so that the combined motion effect of the drive shaft connected to the other end thereof is a linear motion.

The planetary gear mechanism 120 is designed such that the drive shaft 128 coupled to the swing arm 126 can reciprocate in a straight line. Specifically, the revolution speed of the planetary gears, the rotational speed of the planetary gears, and the distance from the drive shaft 128 to the planetary shaft are designed such that the drive shaft 128 moves in a straight line. For example, in the example shown in FIGS. 2-4, the number of teeth and the modulus of the inner and outer ring gears of the large gear 122 and the planetary gear 124 are designed such that the drive shaft 128 linearly reciprocates, so that the driving rod assembly 110 is fixed. Linear motion within the range.

Further, when the planetary gear structure is further designed such that the planetary gear 124 (or the planetary shaft) revolves 180 degrees, the planetary gear 124 itself completes 360-degree rotation, whereby the swing arm 126 and the drive shaft 128 The combined motion trajectory at one end of the connection is a linear trajectory. Preferably, the forward rotation of the motor 140 pushes the drive shaft 128 to reciprocate linear motion without the need for motor reversal. Optionally, when the motor 140 rotates forward, the drive shaft 128 is linearly moved in the first direction, and when the motor 140 is reversed, the drive shaft 128 is pushed to move linearly in a direction opposite to the first direction. Thus, the drive shaft 128 (i.e., the forward or reverse movement of the action rod assembly 110) can be conveniently controlled by controlling the forward and reverse rotation of the motor 140.

In one example, the drive shaft 128 can directly drive the motion rod motion in the motionstick assembly 110. In another example, the drive shaft 128 is moved by its own rotation and motion to drive the lever assembly, such as by another set of transmission gear mechanisms (shown in Figures 3 and 4). In FIGS. 3 and 4, the transmission gear mechanism includes, for example, a gear set that is driven to rotate by the drive shaft 128, and specifically includes a transmission gear 112 and a drive gear 114 and a transmission rack attached to the transmission gear 112 (not shown). ). The drive gear 114 meshes with a drive rack (not shown) therebelow that is coupled to the action bar and urges the action bar to move. The transmission gear 112 and the drive gear 114 are pivotally connected to the drive shaft 128 and linearly moved by the drive shaft 128. The drive gear 112 meshes with the drive rack above it and rotates under the constraints of the drive rack. The drive gear 112 and the drive gear 114 rotate in synchronism. Thereby, the transmission gear mechanism is capable of amplifying the linear motion of the drive shaft 128 by its translation and rolling. In addition, if the size of the transmission gear 112 is changed, the movement stroke of the drive rack (ie, the action rod) can be easily changed, so that the stroke requirements of different switch machines can be adapted by changing the fewest components.

In the solution of the present invention, there is no local repeated wear, and local excessive wear is avoided to affect the service life. The processing cost of the gear is much lower than that of the ball screw, which reduces the manufacturing cost of the switch. It is especially important that the linear motion of the planetary gear mechanism to drive the drive shaft is not uniform. According to the mechanical principle, the drive shaft drives the drive rod to undergo a process of gradual acceleration-constant speed-gradual deceleration when moving from the retracted position to the extended position, thereby avoiding the situation of force impact at both ends of the motion section.

The invention has been described in detail above with reference to the specific embodiments. However, those skilled in the art will appreciate that there are some modifications and equivalents within the scope of the invention. Therefore, the claims of the present invention should be construed as including all such modifications and equivalents.

Claims

A switch machine includes an action rod assembly (110), wherein the switch machine further includes a planetary gear mechanism (120), wherein the planetary gear mechanism includes a large gear (122) having an outer ring gear ( 1221) and an inner ring gear (1222), the planetary gear (124) meshes with the inner ring gear (1222), and the shaft of the planetary gear (124) is pivotally connected to one end of the swing arm (126), the swing arm The other end of (126) is pivotally coupled to a drive shaft (128) that is coupled to the lever assembly (110).
The switch machine according to claim 1, wherein the motor (130) is coupled to the outer ring gear (1221) and drives the large ring gear (122) to rotate.
The switch machine according to claim 1, wherein said planetary gear mechanism (120) is disposed above said action lever assembly (110).
The switch machine of claim 1 wherein the drive shaft (128) is directly coupled to the action rod assembly (110) and drives the motion rod (110) to move.
The switch machine of claim 1 wherein the drive shaft (128) is coupled by a gear mechanism and drives the motion rod assembly (110) to move.
A switch machine, including:

a motor (140),

a action rod assembly (110),

A planetary gear mechanism (120) comprising:

a large gear (122) having an outer ring gear (1221) and an inner ring gear (1222), the outer ring gear (1221) being driven by the motor (140),

a planetary gear (124) that meshes with the inner ring gear (1222) that acts as a sun gear, the planet shaft of the planetary gear (124) being pivotally coupled to the large gear (122), and at the The gear (122) drives the lower movement,

a swing arm (126) having one end fixedly coupled to the planet shaft of the planetary gear (124), The other end is pivotally connected to a drive shaft (128), and the drive shaft (128) drives the action rod assembly (110);

Wherein, the planetary gear mechanism (120) is designed such that the drive shaft (128) reciprocates linearly.
The switch machine according to claim 6, wherein the ring gear (1222) is supported on the large gear (122) by a bearing so as to be rotatable relative to the large gear.
The switch machine of claim 6, wherein the drive shaft (128) is directly coupled to the action rod in the action rod assembly (110) and drives the motion rod to move.
The switch machine of claim 6 wherein said lever assembly (110) includes a transmission gear mechanism, said transmission gear mechanism comprising:

a transmission gear (112) pivotally connected to the drive shaft (128);

a drive rack engaged with the transmission gear (112);

a driving gear (114) pivotally connected to the driving shaft (128) and rotating synchronously with the transmission gear (112);

A drive rack engages the drive gear (114) and is coupled to the actuating lever.