High-power anti-reverse gearbox and winching machine

Abstract

The utility model discloses a high-power anti-inversion gearbox, and aims to solve the technical problems of low power, large size and insufficient safety of the gearbox of the conventional winching machine. The gearbox comprises a box body, an end cover installed on one side of the box body, a cover plate installed on the upper portion of the box body, a vent hole formed in the cover plate, an oil pointer installed on the lower portion of the box body, a handle installed on the cover plate and a gear train assembly installed in the box body. The gear train assembly comprises six shafts and a one-way bearing installed at the input end of the gearbox, the gearbox is formed by refitting a tractor gearbox, the original relative position of each transmission shaft and the gear meshing position are changed, the size of the gearbox is reduced, and the speed ratio is increased by increasing the number of change gears of the last two stages of the output end. The one-way bearing is installed at the input end of the gearbox to prevent the output shaft from rotating reversely. Compared with a traditional winching machine gearbox, the equipment is more suitable for different working conditions, and the size is reduced.

Description

TECHNICAL FIELD

[0001] The utility model relates to a kind of big power anti-reverse gearbox. BACKGROUND

[0002] Among the existing winch in market, the specifications and models of the gearbox used are numerous, but there are very few that can reach a traction speed of 6 m / min while the pulling force reaches 8-10 tons. Some small-specification winches can reach a speed of 6 m / min when the maximum pulling force reaches 5 tons, but when the pulling force reaches 8-10 tons, the speed can only reach 3-4 m / min. To cover up the problem of insufficient load power of these small-specification gearboxes, some manufacturers force to increase the engine power under the original design structure framework, regardless of the design strength of the main force components such as gearbox, outer frame body and center support body, so that they work under overload and are forced to reach the technical indicators. This will lead to frequent product failure and rapid reduction of service life.

[0003] The inventor knows a winch gearbox that can rotate forward and backward (patent document number CN106704557A), which separates or disconnects the clutch inner disc and the clutch outer disc by pulling the clutch shaft handle, and makes the first gear mesh with the second gear or the tenth gear by pulling the gearshift handle left and right, so that the gearbox can realize the forward and backward rotation of the driving shaft through the additional transmission shaft.

[0004] However, the inventor of the present application found at least the following technical problems in the process of implementing the technical solutions in the embodiments of the present application: First, the gear ratio of the gearbox is too small, causing the output shaft to output power at a high speed but with small torque, which is not suitable for high-power power devices. Second, the device lacks an effective anti-reverse mechanism, which makes it difficult to ensure the safety of personnel and equipment when the power device suddenly stalls.

[0005] The information disclosed in this BACKGROUND section is only for the purpose of enhancing the understanding of the background of the present disclosure and should not be treated as acknowledging that this information is prior art known to those of ordinary skill in the art. SUMMARY

[0006] In view of at least one of the above technical problems, the present disclosure provides a high-power anti-reverse gearbox that compresses the space volume and increases the number of gearshift positions by changing the relative positions of the transmission shafts and the gearshift engagement positions of the original gearbox. The number of gearshift positions is increased by increasing the number of gearshift gears in the last two stages to increase the gear ratio, so that it can adapt to different working conditions. The anti-reverse device is simplified by using a one-way bearing to access the input end of the gearbox.

[0007] To achieve the above object, in one aspect of the present disclosure, a high-power anti-reverse gearbox is provided, which comprises a gearbox body and a multi-stage gear train assembly installed in the gearbox body. The gear ratio of the gearbox is increased by increasing the number of gear wheels of the two-stage gear train near the final output end. The shaft train in the multi-stage gear train assembly is arranged compactly along a U, S, L, V-shaped or similar line. A one-way bearing is installed at the input end of the gearbox.

[0008] In some embodiments of the present disclosure, the multi-stage gear train assembly comprises an A shaft, a B shaft, a C shaft, a D shaft, an E shaft and an F shaft which are sequentially drivingly connected.

[0009] In some embodiments of the present disclosure, the A shaft comprises a first transmission shaft, a one-way bearing installed on the side of the first transmission shaft close to the power input, a deep groove ball bearing installed on the other side of the first transmission shaft, and a double-movement gear installed between the one-way bearing and the deep groove ball bearing.

[0010] In some embodiments of the present disclosure, the B shaft comprises a second transmission shaft, two deep groove ball bearings installed on both sides of the second transmission shaft, and three sets of fixed gears installed between the two deep groove ball bearings.

[0011] In some embodiments of the present disclosure, the C shaft comprises a third transmission shaft, two deep groove ball bearings installed on both ends of the third transmission shaft, and a fixed gear and a double-movement gear installed between the two deep groove ball bearings.

[0012] In some embodiments of the present disclosure, the D shaft comprises a fourth transmission shaft, two deep groove ball bearings installed on both ends of the fourth transmission shaft, and a fixed gear and a double-movement gear installed between the two deep groove ball bearings.

[0013] In some embodiments of the present disclosure, the E shaft comprises a fifth transmission shaft, two deep groove ball bearings installed on both ends of the fifth transmission shaft, and a fixed gear and a double-movement gear installed between the two deep groove ball bearings.

[0014] In some embodiments of the present disclosure, the F shaft comprises a sixth transmission shaft, a small deep groove ball bearing installed on the side of the sixth transmission shaft away from the output end, a large deep groove ball bearing installed on the side of the sixth transmission shaft close to the output end, and a fixed gear and a double-movement gear installed between the two bearings.

[0015] In another aspect of the present disclosure, a winch is provided, which comprises the above-mentioned high-power anti-reverse gearbox.

[0016] The one or more technical solutions provided in the embodiments of the present disclosure have at least any of the following technical effects or advantages:

[0017] 1. By increasing the number of variable gears of the last two stages of the output end, the problem of small speed ratio in the prior art is effectively solved, and the purpose of adapting to different working conditions is realized.

[0018] 2. By changing the relative positions of the transmission shafts and the gear engagement positions of the original transmission, the problem of large volume of the transmission in the prior art is effectively solved, and the effect of improving space utilization is achieved.

[0019] 3. The one-way bearing is adopted, which effectively solves the problems of complex structure, high cost and large volume of the anti-reverse mechanism in the prior art, thereby reducing the manufacturing cost and improving the space utilization. BRIEF DESCRIPTION OF DRAWINGS

[0020] Figure 1 It is a schematic diagram of the overall structure of the high-power anti-reverse transmission in one embodiment of the present disclosure.

[0021] Figure 2 It is a schematic diagram of the overall structure of the gear train assembly in one embodiment of the present disclosure.

[0022] Figure 3 It is a schematic diagram of the gear engagement between the A shaft and the B shaft in one embodiment of the present disclosure.

[0023] Figure 4 It is a schematic diagram of the gear engagement between the B shaft and the C shaft in one embodiment of the present disclosure.

[0024] Figure 5 It is a schematic diagram of the gear engagement structure between the B shaft, the C shaft and the D shaft in one embodiment of the present disclosure.

[0025] Figure 6 It is a schematic diagram of the gear engagement between the D shaft and the E shaft in one embodiment of the present disclosure.

[0026] Figure 7 It is a schematic diagram of the gear engagement between the E shaft and the F shaft in one embodiment of the present disclosure.

[0027] In the above figures, 1 is a gear train assembly, 2 is a first shift handle, 3 is a second shift handle, 4 is a direction change handle, 5 is an oil mark, 6 is a vent hole, 7 is an upper cover plate, 8 is an end cover, 9 is a box body, 11 is an A shaft, 12 is a B shaft, 13 is a C shaft, 14 is a D shaft, 15 is an E shaft, 16 is an F shaft, 21 is a swing handle, 22 is a shift fork, 23 is a guide shaft, 111 is a first transmission shaft, 112 is a one-way bearing, 113 is a double moving gear, 114 is a deep groove ball bearing, 121 is a deep groove ball bearing, 122 is a second transmission shaft, 123 is a fixed gear, 124 is a short spacer sleeve, 125 is a fixed gear, 126 is a long spacer sleeve, 127 is a fixed gear, 31 is a swing handle, 32 is a shift fork, 33 is a guide shaft, 131 is a deep groove ball bearing, 132 is a fixed gear, 133 is a spacer sleeve, 134 is a third transmission shaft, 135 is a double moving gear, 41 is a swing handle, 42 is a shift fork, 43 is a guide shaft, 141 is a deep groove ball bearing, 142 is a fourth transmission shaft, 143 is a double moving gear, 144 is a fixed gear, 145 is a spacer sleeve, 151 is a deep groove ball bearing, 152 is a fixed gear, 153 is a fifth transmission shaft, 154 is a fixed gear, 155 is a double hollow gear, 156 is a spacer sleeve, 161 is a small deep groove ball bearing, 162 is a fixed gear, 163 is an end face roller bearing, 164 is a double hollow gear, 165 is a sixth transmission shaft, and 166 is a large deep groove ball bearing. DETAILED DESCRIPTION

[0028] In the description of the present disclosure, it should be understood that the orientation or positional relationship indicated by the terms "upper", "lower", "front", "back", "left", "right", "top", "bottom", "inner", "outer", "vertical", "horizontal" and the like are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present disclosure and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application. The present disclosure refers to "first", "second" and the like, which are used to distinguish the described objects, and do not have any sequential or technical meaning. Unless otherwise specified, the present disclosure refers to "connection", "coupling", which includes direct and indirect connection (coupling).

[0029] In the following examples, the unit modules or sensors and the like devices are all conventional commercially available products unless otherwise specified.

[0030] The embodiment of the present disclosure provides a high-power anti-reverse gearbox, which solves the problems of insufficient power and power mismatch of the winch gearbox in the prior art. Under the original 5-speed transmission system of the tractor gearbox, the relative positions of the transmission shafts of the gearbox and the gear engagement positions are changed, the number of speed change gears of the last two stages of the output end is increased, and the speed ratio is increased, so that the idea of a multi-speed output gearbox with large torque is realized.

[0031] The technical solutions in the embodiments of the present disclosure are to solve the above problems, and the general idea is as follows:

[0032] By installing a one-way bearing at the input end of the gearbox, the input shaft can only rotate in one direction; by changing the relative arrangement position of each transmission shaft of the gearbox from the original L shape to a U shape, the space utilization is improved; by changing the fixed gear on the A shaft to a double-movable gear, the speed gear position is increased; the power is transmitted layer by layer through the gear train assembly of the gearbox, reaches the last two stages, and is increased by adding a set of double-meshing hollow gears on the E shaft and the F shaft, and finally transmitted to the output shaft, thereby completing the power transmission in the gearbox.

[0033] In order to better understand the technical solutions of the present disclosure, the above technical solutions will be described in detail below in combination with the drawings in the specification and specific embodiments. Embodiments

[0034] The present example discloses a high-power anti-reverse gearbox, as shown in Figure 1 , specifically including a box 9 for providing support for all components, an end cover 8 and an upper cover plate 7 are installed on the box by bolts, an oil mark 5 is installed and fixed at the bottom of the rear of the box, which is convenient for observing the change of oil level in the gearbox. The air vent 6 is installed at the position of the rear opening of the upper cover plate 7, which is used to balance the air pressure inside and outside the gearbox. The end cover 8 connects the bearings of the fixed gear train assembly 1 and the guide shafts of the first speed handle 2, the second speed handle 3 and the direction handle 4 through the openings on its surface, to realize the fixation of the built-in components. The gear train assembly can transmit the torque and speed from the input end of the gearbox to the output end, and increase the torque and reduce the speed.

[0035] Referring to Figures 2-7 , the A shaft is the input shaft, and a one-way bearing is installed at the input end. The A shaft cooperates with the B shaft, and the A shaft can change the gear ratio with the B shaft by pulling the first speed handle connected to the double-movable gear of the A shaft. The B shaft is connected with the C shaft or the D shaft, and the speed is changed by changing the position of the double-movable gear of the C shaft through the second speed handle; the rotation direction of the output is changed by pulling the direction handle to adjust whether the D shaft is connected with the B shaft or the C shaft. The D is connected with the E shaft through the gear, and the E shaft is connected with the F shaft through the gear, thereby transmitting the power to the output shaft of the gearbox.

[0036] In operation, power is first transmitted from outside to the input shaft of the gearbox, i.e. the first transmission shaft 111 of the A shaft 11, to make it rotate, thereby making the double moving gear 113 on the first transmission shaft 111 rotate. The swing handle 21 of the first gear shift handle 2 can be moved to make the shift fork 22 move, thereby controlling the double moving gear 113 to move left and right. When the double moving gear 113 is on the left side, the large gear in the double moving gear 113 engages with the small fixed gear 123 in the B shaft 12, making the small fixed gear 123 in the B shaft 12 rotate at a speed greater than that of the double moving gear 113 of the A shaft 11, which is the high speed gear; when the double moving gear 113 is on the right side, the small gear in the double moving gear 113 engages with the large fixed gear 127 in the B shaft 12, making the large fixed gear 127 in the B shaft 12 rotate at a speed less than that of the double moving gear of the A shaft 11, which is the low speed gear. In summary, by operating the swing handle 21 of the first gear shift handle 2, it can be selected whether the power is transmitted to the B shaft 12 through the high speed path or the low speed path.

[0037] The power reaching the B shaft 12 makes the second transmission shaft 122 and the gear rotate. The swing handle 31 of the second gear shift handle 3 can be moved to make the shift fork 32 move, thereby controlling the double moving gear 135 of the C shaft 13 to move left and right. When the double moving gear 135 is on the left side, the large gear in the double moving gear 135 engages with the small fixed gear 125 in the B shaft 12, making the large gear in the double moving gear 135 of the C shaft 13 rotate at a speed less than that of the small fixed gear 125 in the B shaft 12, which is the low speed gear; when the double moving gear 135 is on the right side, the small gear in the double moving gear 135 engages with the large fixed gear 127 in the B shaft 12, making the small gear in the double moving gear 135 of the C shaft 13 rotate at a speed greater than that of the B shaft 12, which is the high speed gear. In summary, by operating the swing handle 31 of the second gear shift handle 3, it can be selected whether the power is transmitted to the C shaft 13 through the high speed path or the low speed path.

[0038] The swing handle 41 of the direction change handle 4 can be moved to make the shift fork 42 move, thereby controlling the double moving gear 143 of the D shaft 14 to move left and right. When the double moving gear 143 is on the left side, the large gear in the double moving gear 143 engages with the small fixed gear 132 in the C shaft 13, and when the double moving gear 143 is on the right side, the small gear in the double moving gear 143 engages with the fixed gear 123 in the B shaft 12. Because the transmission of power from the B shaft 12 to the D shaft 14 involves one more C shaft 13 in the left path than in the right path, after the power is transmitted to the D shaft 14 through the left path and the right path, the rotation direction of the D shaft 14 is opposite. In summary, by operating the swing handle 41 of the direction change handle 4, it can be selected whether the power is transmitted to the D shaft 14 in the forward direction or the reverse direction.

[0039] The power transmitted to the D shaft 14 is transmitted to the large gear on the double hollow gear 155 of the E shaft 15 through the fixed gear 144. Since it is a double hollow gear, the E shaft 15 is not rotated. The power transmitted to the large gear on the double hollow gear 155 of the E shaft 15 is transmitted to the large gear on the double hollow gear 164 of the F shaft 16 through the small gear of the double hollow gear 155, and then transmitted to the fixed gear 154 fixed to the E shaft 15 through the small gear of the double hollow gear 164 of the F shaft 16. Thus, the power on the D shaft 14 is transmitted to the fifth transmission shaft 153 of the E shaft 15.

[0040] The power on the E shaft 15 is transmitted to the fixed gear 162 of the F shaft 16 through the fixed gear 152, thereby rotating the sixth transmission shaft 165, i.e., the output shaft of the transmission, and completing the power transmission in the transmission.

[0041] When the winch lifts the heavy object upward, if the engine suddenly stops, the heavy object will have a tendency to fall downward due to the loss of lifting force. This tendency will cause the output shaft of the transmission to have a movement tendency opposite to that in the normal operation of the machine. Through a series of transmissions of the gear set of the transmission, this tendency will finally be transmitted to the input shaft of the transmission, i.e., the first transmission shaft 111 of the A shaft 11. This is the input end of the entire speed reduction mechanism, and the torque is the smallest. Therefore, only a one-way bearing 112 is needed to make the input shaft rotate only in the direction of the power transmitted by the power device and not rotate reversely due to the falling tendency of the heavy object.

[0042] Although some preferred embodiments of the present disclosure have been described, those skilled in the art who have the basic inventive concept can make additional changes and modifications to these embodiments. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments and all changes and modifications falling within the scope of the present disclosure.

[0043] Obviously, those skilled in the art can make various modifications and variations to the present disclosure without departing from the spirit and scope of the inventive concept. Thus, if these modifications and variations of the present disclosure fall within the scope of the claims of the present application and their equivalents, the scope of protection of the present disclosure is also intended to include these modifications and variations.

Claims

1. A high power reversing gearbox comprising a housing and a multi-speed gear train assembly mounted within said housing, characterised in that: The speed ratio of the gearbox is adjusted by increasing the number of gear wheels in the two-stage gear train near the final output end; the shaft train in the multi-stage gear train assembly is arranged compactly along a U, S or V-shaped line; the gearbox is provided with an input end for receiving power, and a one-way bearing is installed at the input end.

2. A high power non-reverse transmission as claimed in claim 1, wherein, The multi-stage gear train assembly comprises an A shaft, a B shaft, a C shaft, a D shaft, an E shaft and an F shaft which are sequentially drivingly connected.

3. A high power non-reverse transmission as claimed in claim 2, wherein, The A shaft comprises a first transmission shaft, a one-way bearing is installed at the power input side of the first transmission shaft, a deep groove ball bearing is installed at the other side of the first transmission shaft, and a double-movement gear is installed between the one-way bearing and the deep groove ball bearing.

4. A high power non-reverse transmission as claimed in claim 2, wherein, The B shaft comprises a second transmission shaft, two deep groove ball bearings are installed at the two sides of the second transmission shaft, and three sets of fixed gears are installed between the two deep groove ball bearings.

5. A high power non-reverse transmission as claimed in claim 2 wherein, The C shaft comprises a third transmission shaft, two deep groove ball bearings are installed at the two ends of the third transmission shaft, and a fixed gear and a double-movement gear are installed between the two deep groove ball bearings.

6. A high power non-reverse transmission as claimed in claim 2 wherein, The D shaft comprises a fourth transmission shaft, two deep groove ball bearings are installed at the two ends of the fourth transmission shaft, and a fixed gear and a double-movement gear are installed between the two deep groove ball bearings.

7. A high power non-reverse transmission as claimed in claim 2 wherein, The E shaft comprises a fifth transmission shaft, two deep groove ball bearings are installed at the two ends of the fifth transmission shaft, and a fixed gear and a double-movement gear are installed between the two deep groove ball bearings.

8. A high power non-reverse transmission as claimed in claim 2 wherein, The F shaft comprises a sixth transmission shaft, a small deep groove ball bearing is installed at the side of the sixth transmission shaft away from the output end, a large deep groove ball bearing is installed at the side of the sixth transmission shaft close to the output end, and a fixed gear and a double-movement gear are installed between the two bearings.

9. A winch characterized by: The high-power anti-reverse gearbox of claim 1 is contained.

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