Transmission mechanism and related grab ship unloader

Abstract

The utility model relates to a transmission mechanism. The transmission mechanism comprises a first input shaft and a second input shaft, the gear shifting mechanism comprises a spline sliding sleeve, a spline shaft and an inner hole spline gear, the spline shaft is supported by a first bearing and is in transmission connection with the first input shaft, an outer spline is arranged outside the spline sliding sleeve, an inner spline is arranged in an inner hole, and the spline sliding sleeve is in axial moving fit with an outer spline of the spline shaft through the inner spline; the spline gear is rotatably sleeved on the spline shaft by a second bearing through a gear inner hole; a gear hole internal spline is integrally arranged on one side, close to the spline sliding sleeve, in the gear inner hole of the spline gear; and a gear mechanism with which the spline gear engages with the toothed member. The spline sliding sleeve moves into or out of the gear inner hole, the spline gear is movably connected with or separated from the spline shaft, and therefore the gear shifting mechanism is selectively in transmission connection with the first input shaft and the gear mechanism. The utility model further relates to the grab ship unloader comprising the transmission mechanism. By means of the gear shifting mechanism, structural compactness and efficient connection or disconnection are achieved, and the rigidity of the gear shifting mechanism is improved.

Description

Technical Field

[0001] This application generally relates to a transmission mechanism, and further relates to related grab unloaders that include such a transmission mechanism. Background Technology

[0002] Transmission mechanisms, especially planetary differential gearboxes, particularly those used in grab bucket ship unloaders, typically include a shifting mechanism to connect and disengage the trolley traveling stage from the hoisting / closing stage. This shifting mechanism is, for example, a sliding spline shifting mechanism. During shifting, a shifting wrench, via a shift fork, moves a spline sleeve axially along the spline shaft, engaging or disengaging the outer spline of the sleeve with the inner spline of the internal spline shifting gear, thus connecting or disengaging the gear from the spline shaft. This internal spline gear usually consists of a spline sleeve and an outer gear, connected by bolts. For this two-piece internal spline gear, during planetary differential gearbox operation, the connecting bolts often break due to shear forces, leading to shifting mechanism failure. Furthermore, this transmission mechanism is relatively space-consuming and not compact.

[0003] In addition, the inner ring of the spline shift gear in this conventional shift mechanism is equipped with two bearings. In the prior art, the bearing clearance is not adapted during installation, which leads to a decrease in the stiffness of the gear in the shift mechanism and causes vibration and noise in the shift structure during operation, and may even cause the gear to fail due to impact.

[0004] In addition, the sun gear shaft structure commonly used in planetary differential gear trains is a split type, namely a floating sun gear. The sun gear is connected to the drive shaft through a spline. This structure often leads to failure of the planetary differential gear train due to wear or breakage of the internal and external splines.

[0005] Therefore, a transmission mechanism is desired that can achieve a compact structure, efficiently connect or disconnect the shifting mechanism, and solve the problem of poor rigidity of the shifting mechanism. Utility Model Content

[0006] According to one aspect of this application, this application relates to a transmission mechanism comprising: a first input shaft configured to input power; and a shifting mechanism comprising a splined sleeve, a splined shaft, and an internal splined gear, wherein the splined shaft is supported by a first bearing and the first input shaft is drively connected to the splined shaft to drive the splined shaft to rotate; the splined sleeve has an external spline on its outer ring and an internal spline in its inner hole; the splined sleeve is axially movable but non-rotatably engaged with an external spline on the splined shaft via the internal spline; and the internal splined gear is rotatably fitted via a second bearing. On the splined shaft; an internal splined gear integrally formed with an internal spline in the gear bore near the splined sleeve; and a gear mechanism, wherein the internal splined gear has external teeth on its outer periphery to engage with the toothed components of the gear mechanism, wherein the splined sleeve moves into the gear bore to move the internal splined gear and the splined shaft; wherein the splined sleeve moves out of the gear bore to move the internal splined gear and the splined shaft apart; and wherein a shifting mechanism is connected between the first input shaft and the gear mechanism to selectively drive the first input shaft and the gear mechanism.

[0007] Optionally, the gear mechanism is configured as a planetary gear structure including a sun gear shaft structure disposed in a planet carrier, wherein the sun gear in the sun gear shaft structure is integrally formed with the drive shaft of the planetary gear structure.

[0008] Optionally, the number of second bearings is two, and the inner rings of the two second bearings respectively contact and abut against the two ends of the bushing sleeve fitted on the spline shaft.

[0009] Optionally, the internal spline gear includes a radially inwardly projecting shoulder on the side of the gear bore opposite to the spline sleeve, such that the outer rings of two second bearings are respectively supported on both sides of the shoulder in the axial direction.

[0010] Optionally, the drive shaft is provided with a keyway configured to support an input gear that receives power from the second input shaft.

[0011] Optionally, the drive shaft is provided with a shoulder portion of the bearing configured to limit the support of the drive shaft.

[0012] Optionally, the gear mechanism is configured to include at least two planetary gear structures arranged in parallel, wherein each planetary gear structure includes a gear ring, wherein at least one gear ring is configured to engage the outer teeth of an internal spline gear on its outer side and engage the outer side of a corresponding gear ring of an adjacent planetary gear structure; and the at least one gear ring engages the planetary gear of the corresponding planetary gear structure on its inner side.

[0013] Optionally, each of the at least two planetary gears includes an input gear and these input gears are configured to engage the same second input shaft, which is configured to be connected to a second power source and the first input shaft is configured to be connected to a first power source.

[0014] Optionally, the transmission mechanism also includes a housing, wherein the splined shaft and the drive shaft are supported on the housing of the transmission mechanism via corresponding bearings.

[0015] This application also relates to a grab unloader that includes the transmission mechanism described above.

[0016] This application provides a transmission mechanism that achieves a compact structure, efficient connection or disengagement of the shifting mechanism, and solves the problem of poor rigidity in the shifting mechanism. Furthermore, through combinations of various other preferred embodiments, the problem of low spline connection strength of the sun gear is further addressed, improving the reliability and economy of the gearbox and simplifying maintenance. Moreover, also through combinations of various other preferred embodiments, the problem of difficulty in adjusting the output shaft rotation angle during installation, commissioning, and maintenance of the planetary differential gearbox is also solved. Attached Figure Description

[0017] Figure 1 A schematic diagram of a transmission mechanism according to an embodiment of this application is shown. Detailed Implementation

[0018] The details shown herein are merely examples for illustrative discussion of the disclosed embodiments and to provide an easily understood description of the principles and concepts. No further detail is intended to be shown in this regard, except for the purpose of providing a basic understanding and enabling those skilled in the art to clearly see how the disclosed transmission mechanism can be implemented in practice, in conjunction with the accompanying drawings.

[0019] Figure 1 A schematic diagram of a transmission mechanism 1 according to an embodiment of this application is shown. Figure 1 As shown, in an embodiment of this application, the transmission mechanism 1 includes a first input shaft 10, which is configured to input power. Optionally, the first input shaft 10 is configured to be connected to a first power source (not shown). The first power source may be, for example, various types of engines, such as electric motors, gas turbines, etc. The second power source (not shown) discussed later may also be, for example, various types of engines, such as electric motors, gas turbines, etc.

[0020] The transmission mechanism 1 also includes a shifting mechanism 12, which is configured to selectively connect or disconnect the first input shaft 10 from the gear mechanism 14, which will be described later, to facilitate, for example, the installation, commissioning, and maintenance of the entire transmission mechanism. The shifting mechanism 12 includes an internal splined gear 1200, a splined shaft 1202, and a splined sleeve 1204. Figure 1 As shown, the splined shaft 1202 is supported by a first bearing and driven to the first input shaft 10, for example, via a shaft gear fixedly connected to the splined shaft 1202 and a corresponding output gear fixedly connected to the first input shaft, so that it can be driven to rotate. The splined sleeve 1204 has an external spline on its outer ring and an internal spline in its inner hole, wherein the splined sleeve 1204 is axially movable in engagement with the external spline on the splined shaft 1202 via the internal spline. Of course, after engaging with the external spline, the splined sleeve is non-rotatably mounted on the splined shaft. It is conceivable that the external spline is located in a portion of the splined shaft 1202, and the length of this portion along the axial direction of the splined shaft 1202 can be greater than, equal to, or even less than the axial length of the splined sleeve 1204 or the length of the internal spline in the axial direction. Any possible spline shape, construction, or arrangement area is conceivable without departing from the scope of this application.

[0021] In embodiments of this application, the internal spline gear 1200 is rotatably mounted on the spline shaft 1202 via a second bearing 1206. Furthermore, the internal spline gear 1200 has a gear bore through which the spline shaft 1202 can pass, and an internal spline is integrally formed in the gear bore on the side near the spline sleeve 1204. As will be readily understood by those skilled in the art, the second bearing 1206 is also disposed in the gear bore and optionally located inside the gear bore on the side away from the spline sleeve 1204. Regarding the manner of integral assembly, those skilled in the art can conceive of any possible technical processes without departing from the scope of this application.

[0022] Furthermore, the transmission mechanism also includes a gear mechanism 14, wherein the internal spline gear 1200 engages with the toothed component of the gear mechanism 14, for example by means of the external teeth provided on the outer periphery of the internal spline gear. In other words, the internal spline gear 1200 is always engaged with the toothed component in the gear mechanism 14 by means of its external teeth, such that the rotational movement of the toothed component will cause the internal spline gear 1200 to rotate synchronously or vice versa.

[0023] The following describes in detail how the shifting mechanism 12 achieves the connection and disengagement between the gear mechanism 14 and the first input shaft 10: The spline sleeve 1204 moves into the gear's inner bore, causing the inner spline gear 1200 to move and connect with the spline shaft 1202, meaning that the rotational movement of the spline shaft 1202 will drive the inner spline gear 1200 to rotate together; conversely, the spline sleeve 1204 moves out of the gear's inner bore, causing the inner spline gear 1200 to move and disengage from the spline shaft 1202, meaning that the rotational movement of the spline shaft 1202 will not be transmitted to the inner spline gear 1200, thus allowing the spline shaft 1202 and the inner spline gear 1200 to move independently of each other. It should be understood that, optionally, in the embodiments of this application, the movement of the spline sleeve 1204 can be achieved using a shift fork or similar structure (not shown) known to those skilled in the art, and will not be described in detail here. Using the above-described operation method, the shifting mechanism 12 is ultimately connected and disposed between the first input shaft 10 and the gear mechanism 14 as described above, enabling selective transmission between the first input shaft 10 and the gear mechanism 14. "Selective" means that the first input shaft 10 and the gear mechanism 14 can be moved to or disengage as needed. In the embodiments of this application, the spline shaft and the first input shaft are configured to be parallel to each other; however, this is merely exemplary. Those skilled in the art can conceive of any possible orientation methods without departing from the scope of this application.

[0024] It is conceivable that the length of the spline region within the gear bore of the internal spline gear 1200 in the axial direction is equal to, longer than, or shorter than the length of the external spline region of the sleeve in the axial direction. Optionally, the spline sleeve 1204 has a fork engagement portion on its outer surface to engage a fork 1208 (only a portion of the fork is shown here) to further drive the movement of the spline sleeve 1204 on the spline shaft. The fork mechanism, including this fork, is well known to those skilled in the art and will not be described in detail here. Furthermore, with this fork mechanism, the spline sleeve can also be locked in position by locking the fork, for example, by using a fork locking device in the fork mechanism, to prevent axial movement of the spline sleeve.

[0025] Optionally, the spline sleeve 1204 has a stop on its outer surface to limit the distance between the spline sleeve 1204 and the gear inner bore. As an example, the stop is configured as a radially outward protrusion from the outer peripheral surface of the spline sleeve 1204, such that when the spline sleeve 1204 is moved into the gear inner bore, the protrusion abuts against the end face of the inner spline gear 1200, preventing the spline sleeve 1204 from moving further into the gear inner bore, thereby avoiding interference with other components such as shift forks. Of course, the stop can take any possible structure capable of limiting the movement distance of the spline sleeve 1204 into the gear inner bore without departing from the scope of this application.

[0026] By utilizing the integral structure of the internal spline and the internal spline gear 1200, the internal spline gear 1200 can be used simultaneously as a spline sleeve that engages with the spline sleeve 1204 in the prior art and as a transmission gear for transmitting power to the spline shaft 1202. Furthermore, it can enhance the overall rigidity and stability of the internal spline gear 1200, avoiding the breakage or damage that may occur due to a separately manufactured spline sleeve connected to the internal spline gear by means of bolts, etc.

[0027] According to an embodiment of this application, the gear mechanism 14 is configured as a planetary gear structure including a sun gear shaft structure 1404 disposed in the planet carrier 1402. Optionally, the gear mechanism 14 may be selected as any differential gear mechanism 14 without departing from the scope of this application. In the case of a planetary gear structure, the sun gear shaft structure 1404 includes a sun gear 1408 and a drive shaft 1406, and the sun gear 1408 in the sun gear shaft structure 1404 is integrally formed with the drive shaft 1406 of the planetary gear structure.

[0028] By machining the sun gear and drive shaft 1406 into a single unit, the diameter of the connection between the sun gear 1408 and drive shaft 1406 can be increased, thereby increasing the rigidity of the entire sun gear shaft structure.

[0029] According to an embodiment of this application, there are two second bearings 1206, and the inner rings of the two second bearings 1206 are respectively fitted abutting against the two ends of the bushing 1210 of the splined shaft 1202. Specifically, the bushing 1210 is disposed between the inner splined gear 1200 and the splined shaft 1202 and between the two second bearings 1206. In this case, the inner rings of the second bearings 1206 can be aligned with the ends of the bushing 1210. Depending on the bearing configuration, especially for adjustable bearings, it is known that the bearing clearance itself can be adjusted by adjusting the position of the bearing inner ring, for example, by changing the relative axial position (relative axial position relative to the bearing outer ring) of the raceway, such as the rollers, in the bearing through the bearing inner ring. In this case, by providing the bushing 1210 as described above, the relative distance (relative axial position) between the inner rings of the two second bearings 1206 can be effectively defined and determined. Therefore, by selecting bushings 1210 of different axial lengths, the bearing clearance of the two second bearings 1206 can be adjusted and limited differently, which helps to support the spline shaft 1202 more stably and ensure motion stability and smoothness.

[0030] According to an embodiment of this application, the internal spline gear 1200 includes a radially inwardly projecting shoulder 1212 on the side opposite to the spline sleeve 1204 within the gear bore. This shoulder is configured to receive the outer rings of two second bearings 1206 on either side of the shoulder 1212 in the axial direction. In other words, the outer ring of one of the second bearings 1206 is disposed within the gear bore from the spline side of the gear bore and is held in position when it abuts against the shoulder 1212. At this location, on the side of the bearing outer ring axially opposite to the shoulder 1212, any suitable retaining member (not shown), such as a retaining ring, can be additionally provided to hold the bearing outer ring against the shoulder 1212. The outer ring of the other of the second bearings 1206 is introduced from the other side of the gear bore until it abuts against the other side of the shoulder 1212 and optionally is also held against the shoulder 1212 by means of any suitable retaining member, such as a retaining ring.

[0031] It is conceivable that the aforementioned bushing 1210, preferably cylindrical, has an axial length that is preferably equal to, greater than, or less than the axial length of the shoulder portion 1212 between its contact positions with the two second bearings 1206. When the bushing 1210 is less than the axial length of the shoulder portion 1212 between its contact positions with the two second bearings 1206, it is conceivable that the bearing inner ring is extended between the shoulder portion 1212 and the splined shaft 1202.

[0032] According to an embodiment of this application, a drive shaft 1406 supports an input gear driven by a second input shaft 1410. As an example and more specifically, the drive shaft 1406 is provided with a engagement portion, such as a keyway or snap-fit, configured to support an input gear 1408 that receives power from the second input shaft 1410. In other words, the drive shaft 1406 has an engagement portion, such as a keyway, near one end to fixately and non-rotatably support the input gear 1408. Therefore, the input gear 1408 is configured to be driveably connected to the second input shaft 1410, enabling power to be transmitted via the second input shaft 1410 to the drive shaft 1406 to drive its movement.

[0033] According to an embodiment of this application, the drive shaft 1406 is further provided with a shoulder portion 1412 configured to limit the bearing supporting the drive shaft 1406. As an example, the drive shaft 1406 has a reduced-diameter shaft portion outside the keyway of the corresponding input gear 1408 (i.e., closer to the corresponding end than the keyway), such that a stepped shoulder portion 1412 is formed at the connection point between the reduced-diameter shaft portion and the body of the drive shaft 1406 (i.e., the larger-diameter shaft portion). With the help of this shoulder portion 1412, the positions of the inner and outer rings of the bearing supporting the drive shaft 1406 can be limited; that is, both the inner and outer rings of the bearing supporting the drive shaft 1406 are positioned to abut against and be held by the end face of the shoulder portion 1412. Also as an example, the shoulder portion can be manufactured as a radially outward protrusion from the outside of the drive shaft 1406 without departing from the scope of this application. Although described herein as having the shoulder located on the drive shaft, the shoulder may also be optionally located within the housing described later, rather than on the drive shaft. In fact, the shoulder can be located in any possible position as long as it ensures the limiting and positioning of the relevant bearing.

[0034] According to an embodiment of this application, the gear mechanism 14 is configured to include at least two planetary gear structures arranged in parallel, preferably two planetary gear structures. In this case, each planetary gear structure includes a ring gear 1414, such that the ring gear 1414 of at least one planetary gear mechanism 14 is configured to engage the external teeth of the internal spline gear 1200 on its outer side and engage the outer side of the corresponding ring gear 1414 of the adjacent planetary gear structure. At this time, the at least one ring gear 1414 is configured to serve as a toothed member of the gear structure to engage the shift mechanism 12. By engaging the outer side of the corresponding ring gear 1414 of the adjacent planetary gear structure, the other planetary gear structure can be indirectly connected to the shift mechanism 12 for transmission. Optionally, the ring gear 1414 can be configured to engage the planetary gear 1416 of the corresponding planetary gear structure on its inner side. Based on the above, it can be understood that the ring gear 1414 includes teeth on both its inner and outer sides for power transmission from the shift mechanism 12 to the planetary gear structure via the ring gear 1414.

[0035] According to embodiments of this application, at least two planetary gear structures each include an input gear 1408, and these input gears 1408 are configured to engage the same second input shaft 1410. In this case, the corresponding input gear 1408 is configured to engage an output gear on the same second input shaft 1410, enabling the drive of at least two planetary gear structures to be achieved using a single second input shaft 1410. Typically, the second input shaft 1410 is configured to connect to a second power source, and the first input shaft 10 is configured to connect to a first power source.

[0036] According to an embodiment of this application, the transmission mechanism further includes a housing 16 and corresponding bearings for the spline shaft 1202 and the drive shaft 1406 are fixed to the housing 16, thereby enabling the spline shaft 1202 and the drive shaft 1406 to be supported on the housing 16 of the transmission mechanism.

[0037] In the embodiments of this application, the transmission mechanism is particularly used in grab bucket unloaders. It is easy to understand that, with the help of the transmission mechanism as described in this application, different working modes of the grab bucket unloader can be realized by operating the shift mechanism 12 in different positions and starting and stopping the first and second power sources, including but not limited to displacement, switching, lifting and so on.

[0038] By combining the various preferred embodiments described above, the problem of difficulty in adjusting the output shaft rotation angle during installation, commissioning, and maintenance of transmission mechanisms such as planetary differential gearboxes can be effectively solved. In other words, by utilizing the structure of the gear ring 1414 (with teeth on both the inner and outer sides), efficient adjustment of the output shaft angle is achieved. For example, angle adjustment can be achieved by simply turning on the first power source, thus enabling angle adjustment.

[0039] Although this application has been described with reference to the accompanying drawings and embodiments, those skilled in the art can conceive of various modifications based on the teachings of this application without departing from the scope of this application.

Claims

1. A transmission mechanism, characterized in that, It includes: The first input shaft is configured to input power; The shifting mechanism includes a splined sleeve, a splined shaft, and an internal splined gear, wherein: The spline shaft is supported by a first bearing and the first input shaft is driven to the spline shaft to drive the spline shaft to rotate; The spline sleeve has an external spline on its outside and an internal spline in its inner hole. The spline sleeve is axially movable and engages with the external spline on the spline shaft via the internal spline. The internal spline gear is rotatably mounted on the spline shaft via a second bearing through the gear's inner bore; the internal spline teeth are integrally formed with an internal spline within the gear's inner bore, near the spline sleeve; and A gear mechanism, wherein the internal splined gear engages with a toothed component of the gear mechanism, wherein the internal splined gear moves into or out of the gear's inner bore via a splined sleeve, and the internal splined gear is kinetically connected to or disengaged from a splined shaft; and The shifting mechanism selectively drives the first input shaft and the gear mechanism.

2. The transmission mechanism according to claim 1, characterized in that, The gear mechanism is constructed as a planetary gear structure including a sun gear shaft structure disposed in a planet carrier, wherein the sun gear in the sun gear shaft structure is integrally formed with the drive shaft of the planetary gear structure.

3. The transmission mechanism according to claim 1, characterized in that, The number of the second bearings is two, and the inner rings of the two second bearings abut against the two ends of the bushing to define the distance between the two bearing inner rings, wherein the bushing is fitted onto the splined shaft.

4. The transmission mechanism according to claim 3, characterized in that, The inner spline gear includes a radially inwardly protruding shoulder on the side opposite to the spline sleeve in the gear's inner bore, such that the outer rings of two second bearings are respectively supported on both sides of the shoulder in the axial direction.

5. The transmission mechanism according to claim 2, characterized in that, The drive shaft is configured to support an input gear driven by a second input shaft.

6. The transmission mechanism according to claim 2, characterized in that, The drive shaft is provided with a shoulder portion of the bearing configured to limit and support the drive shaft.

7. The transmission mechanism according to claim 2, characterized in that, The gear mechanism is configured to include at least two planetary gear structures arranged in parallel, wherein each planetary gear structure includes a gear ring, wherein at least one gear ring is configured to engage the outer teeth of the internal spline gear on its outer side and engage the outer side of the corresponding gear ring of the adjacent planetary gear structure; and wherein the at least one gear ring engages the planetary gear of the corresponding planetary gear structure on its inner side.

8. The transmission mechanism according to claim 7, characterized in that, Each of the at least two planetary gears includes an input gear, and the input gear is configured to engage the same second input shaft, the second input shaft being configured to be connected to a second power source and the first input shaft being configured to be connected to a first power source.

9. The transmission mechanism according to claim 1, characterized in that, The splined shaft and the first input shaft are configured to be oriented parallel to each other.

10. A grab unloader comprising the transmission mechanism described in any one of claims 1-9.

Images