Automatic speed changing winch

Abstract

The invention provides an automatic speed changing winch which can achieve automatic clutch and automatic speed changing according to different loads. The winch can automatically achieve combination and separation of the roller and the gear mechanism through the contact clutch, the gear mechanism can automatically select different transmission ratios according to different loads on the roller, the transmission ratio is small and the rotating speed is high when the loads are low, and the transmission ratio is large and the bearing capacity is high when the loads are high. According to the automatic speed changing winch, the functions can be completely achieved in a mechanical mode, and the functions can also be achieved in a mode of combining a mechanical structure and electromagnetic control.

Description

Technical Field

[0001] The present invention relates to the field of transmission or traction devices, and specifically to a winch with automatic speed change, having the functions of independent clutch and automatic speed change. Background Art

[0002] A winch can wind a rope around a drum under power drive to achieve pulling or lifting of heavy objects. According to different power sources, it can be divided into manual winches, electric winches, hydraulic winches, pneumatic winches, etc. The application scenarios of winches are very extensive. Most winches do not have a speed change function, and for the few winches with a speed change function, the speed change effect can only be achieved through manual operation or remote control operation, which is relatively inconvenient to use. And due to the usually large transmission ratio of winches, the speed is very slow and the efficiency is low when releasing the rope through the power device. Summary of the Invention

[0003] The purpose of the present invention is to at least partially overcome the defects of the prior art and provide an automatically variable speed winch that can automatically adjust the size of the transmission ratio according to different working conditions, using a small transmission ratio under low load and a large transmission ratio under high load.

[0004] The purpose of the present invention is also to provide a winch with an independent clutch. When actively pulling and releasing the rope, the drum is separated to freely control the pulling speed, while when winding the rope, the drum is combined, and when lowering the rope under load, the drum is combined, effectively improving the working efficiency.

[0005] To achieve the above purpose or one of the purposes, the technical solution of the present invention is as follows: An automatically variable speed winch, characterized in that: the winch includes a speed change unit, a fixing member, a friction clutch, a friction clutch control mechanism, and a clutch device; the speed change unit includes a speed change input element and a speed change output element; the friction clutch is arranged in the speed change unit and is configured to be able to make the speed change input element and the speed change output element of the speed change unit have the same or different rotational speeds; the friction clutch control mechanism is configured to be able to separate the friction clutch when exceeding a given load, and when below this given load, the friction clutch is combined; the clutch device is arranged between the speed change unit and the fixing member of the winch and is configured to be able to achieve the combination and separation between the component parts of the speed change unit and the fixing member.

[0006] According to a preferred embodiment of the present invention, it further includes a power transmission unit and a contact clutch; the power transmission unit includes a power input member and a power output member; the contact clutch is arranged in the power transmission unit and connects the power input member and the power output member of the power transmission unit; the contact clutch is configured to be able to separate the power output member from the power input member, and when the power input member rotates actively, the power output member can be combined with the power input member; the power transmission unit includes the connection between the actuating element and the speed-changing input element of the speed-changing unit, the connection between the speed-changing output element of the speed-changing unit and the speed-changing input element of the next-stage speed-changing unit, and the connection between the speed-changing output element of the speed-changing unit and the drum of the winch. Specifically, the power transmission unit refers to the connection of power elements in the winch except the speed-changing unit, including the connection between the actuating member and the speed-changing input element of the first-stage speed-changing unit, the connection between the speed-changing output element of the first-stage speed-changing unit and the speed-changing input element of the second-stage speed-changing unit, the connection between the speed-changing output element of the second-stage speed-changing unit and the speed-changing input element of the third-stage speed-changing unit, etc., that is, the connection between the speed-changing output element of the upper-stage speed-changing unit and the speed-changing input element of the lower-stage speed-changing unit, and the connection between the speed-changing output element of the last-stage speed-changing unit and the drum.

[0007] According to a preferred embodiment of the present invention, the speed-changing unit is a planetary gear mechanism, including a sun gear, a ring gear, and a planet carrier; the speed-changing input element is the sun gear, and the speed-changing output element is the planet carrier or the ring gear.

[0008] Specifically, a friction clutch is arranged in the planetary gear mechanism and connects the sun gear and the planet carrier, or connects the planet carrier and the ring gear, or connects the sun gear and the ring gear.

[0009] According to a preferred embodiment of the present invention, the friction clutch control mechanism includes an elastic member A, a combined feature, and a curved surface feature; the combined feature includes a straight line segment with a straight generatrix and / or a curved line segment with a curved generatrix, and the combined feature is configured such that when the elastic member A enters and / or leaves the curved line segment, the elastic member A generates elastic deformation; the curved surface feature is configured to be able to generate an axial force when rotating.

[0010] The friction clutch control mechanism is used to control the engagement and disengagement of the friction clutch. Specifically, when the load on the drum is large, the curved surface feature generates a large axial force, which overcomes the elastic force of the elastic member A through the combined feature, causing the assembly to push the friction clutch to disengage; when the load on the drum is small, the axial force generated by the curved surface feature is not sufficient to overcome the elastic force of the elastic member A, and the friction clutch remains engaged. The elastic member A enables the friction clutch to be fully engaged under small loads, without being affected by the friction clutch control mechanism, avoiding risks such as the axial force always being generated by the curved surface feature, this axial force always being applied to the friction clutch, and the friction clutch slipping and failing to engage reliably under small loads.

[0011] According to a preferred embodiment of the present invention, the clutch device is a one-way clutch or an electromagnetic-controlled locking pin device. The one-way clutch can be a roller ramp one-way clutch, a wedge one-way clutch, a ratchet mechanism, etc. The electromagnetic-controlled locking pin device is a locking pin driven by electromagnetic force. By inserting the locking pin into the component parts of the speed change unit, this component part is fixed, or the locking pin is separated from the component parts, and this component part is free. The component parts of the speed change unit connected to the clutch device can be a gear ring or a planet carrier.

[0012] According to a preferred embodiment of the present invention, the contact clutch includes a control bracket and a locking block; the control bracket is frictionally connected to the fixed part, there is a groove on the control bracket, and the outer end of the locking block passes through the groove and can rotate around the inner end of the locking block; the locking block is configured to be able to contact both the power input member and the power output member when rotated to the first position, and the contact clutch is engaged, and when rotated to the second position, it does not contact the power output member or the power input member, and the contact clutch is disengaged.

[0013] According to a preferred embodiment of the present invention, the friction clutch includes friction plates, a pressure plate, and an elastic member B. The elastic member B presses the pressure plate against the friction plates, and the pressure plate and the friction plates are respectively circumferentially fixedly connected to different components of the speed change unit.

[0014] According to a preferred embodiment of the present invention, the fixed part includes the housing of the winch fixedly installed, and parts directly or indirectly fixedly connected to the housing.

[0015] According to a preferred embodiment of the present invention, the contact clutch includes a locking block and a return spring; the return spring biases the locking block to move inward into the power input element; the locking block is configured to be able to contact both the power input member and the power output member when in the outer position, and the contact clutch is engaged, and when in the inner position, it does not contact the power output member or the power input member, and the contact clutch is disengaged.

[0016] The winch of the present invention has the following advantages: Automatically shift gears according to the load size without manual intervention: The winch of the present invention automatically operates with a small transmission ratio when the load is small, featuring high speed and efficiency. When the load is large, it automatically switches to a large transmission ratio to meet the working requirements. The process of transmission ratio switching is automatically completed without manual intervention.

[0017] Accurately set the switching load without slipping: Through the action of elastic part A in the friction clutch control mechanism, the friction clutch can be fully engaged when the load on the drum is lower than a specific value, and completely disengaged when it exceeds this specific value, preventing the possible slipping phenomenon caused by a force acting on the friction clutch while it is engaged.

[0018] Freely pay out the rope or switch to controlled rope payout as needed: When rapid rope payout is required, the contact clutch disengages and the drum can rotate freely, allowing the user to control the rope payout speed at will. When controlled rope payout is needed, the contact clutch engages to achieve controlled rope payout under load. When the actuating device works to wind the rope, the contact clutch engages and the winch winds the rope quickly or slowly according to the load size. Description of the Drawings

[0019] Figure 1 Schematic diagram of the first embodiment of the self - disengaging and automatically variable - speed winch of the present invention; Figure 2 Schematic diagram of the disengaging device, friction clutch and friction clutch control mechanism in the first embodiment; Figure 3 Schematic diagram of the structural installation of the contact clutch in the first embodiment; Figure 4 Axial schematic diagram of the structural principle of the contact clutch in the first embodiment; Figure 5 Schematic diagram of the second embodiment of the disengaging device and friction clutch control mechanism in the present invention; Figure 6 Schematic diagram of the third embodiment of the friction clutch and friction clutch control mechanism in the present invention; Figure 7 Schematic diagram of the fourth embodiment of the friction clutch, friction clutch control mechanism and contact clutch in the present invention; Figure 8 Schematic diagram of the combined features in the friction clutch control mechanism; Figure 9 Schematic diagram of the fifth embodiment of the contact clutch. Detailed Embodiment

[0020] Exemplary embodiments of the present invention will be described in detail below with reference to the accompanying drawings, where like or similar reference numerals denote like or similar elements. Additionally, in the following detailed description, for the sake of explanation, numerous specific details are set forth to provide a thorough understanding of the embodiments of the present disclosure. However, it is obvious that one or more embodiments can be implemented without these specific details. In other instances, well-known structures and devices are illustrated in a schematic manner to simplify the drawings.

[0021] Figures 1-4 Embodiment 1 of a winch with automatic transmission applying the present invention has the function of autonomous clutch. The winch includes an actuating device 700, a transmission and braking assembly 800, a drum assembly 900, an actuating member 001 connected to the actuating device 700 through the transmission and braking assembly 800, a fixedly installed fixing member 400, and a housing 410 fixedly installed with the fixing member 400. The fixing member 400 and the housing 410 contain a gear shifting mechanism, a clutch device, a friction clutch, a friction clutch control mechanism, and a contact clutch, etc. The gear shifting mechanism includes the following shifting units: a first-stage planetary gear mechanism 100, a second-stage planetary gear mechanism 200, and a third-stage planetary gear mechanism 300. The friction clutch 500 is disposed within the second-stage planetary gear mechanism 200. The friction clutch control mechanism is based on the components of the second-stage planetary gear mechanism 200 where the friction clutch 500 is disposed and the adjacent components, and surface features, combined features, and elastic member A are provided on these components to achieve the control of the friction clutch 500. The power transmission unit includes the connection between the actuating member 001 and the shifting unit, the connection between the upper-stage shifting unit and the lower-stage shifting unit, and the connection between the shifting unit and the drum assembly 900, etc., and is divided into a power input member and a power output member according to the power transmission direction. In this embodiment, the contact clutch 600 is disposed in the power transmission unit connecting the third-stage planetary gear mechanism 300 and the drum assembly 900. The planet carrier 330 of the third-stage planetary gear mechanism 300 is the shifting output element of the shifting unit and serves as the power input member in this power transmission unit, and the drum assembly 900 is the power output member in this power transmission unit.

[0022] Figure 2Shown is the structural principle of the clutch device 1000, the friction clutch 500 and the friction clutch control mechanism in the first embodiment. Here, the clutch device 1000 is a roller ramp one-way clutch, including a ramp provided on the housing 410, rollers 1002 installed in the ramp, and a spring 1001 acting on the rollers 1002. The spring 1001 causes the rollers 1002 to tend to move towards the narrow end of the ramp. The ring gear 210 of the second-stage planetary gear mechanism is installed in the housing 410. Due to the action of the spring 1001, the outer surface of the ring gear 210 is always in contact with the rollers 1002. Therefore, the ring gear 210 can only rotate in one direction. A groove is provided on one side of the ring gear 210 and is matched with the friction plate 520. The friction plate 520 is fixedly connected to the ring gear 210 in the circumferential direction, so that the friction plate 520 rotates integrally with the ring gear 210. There are steel sheets on both sides of the friction plate 520, or parts with the same function as the steel sheets, such as the pressure plate 510 and the planet carrier 230. The pressure plate 510 is matched with the planet carrier 230 with a non-circular cross-section or flange feature, so that the pressure plate 510 is fixedly connected to the planet carrier 230 in the circumferential direction and rotates integrally. The spring 530 is installed on the planet carrier 230, and the other end is limited by the end cover 540. There are threaded holes on the pressure plate 510. The spring 530 is compressed by connecting the pressure plate 540 with bolts, and pressure and frictional force are generated between the pressure plate 510 and the friction plate 520 and between the friction plate 520 and the planet carrier 230. The pressure plate 510, the friction plate 520, the planet carrier 230, the spring 530 and the pressure plate 540 form the friction clutch 500, realizing the frictional connection between the ring gear 210 and the planet carrier 230. Since the spring 530 is compressed and deformed, there is pressure and frictional force between the friction plate 520 and the pressure plate 510 and the planet carrier 230, and the ring gear 210 rotates integrally with the planet carrier 230; when the pressure plate 540 is moved to the left to further compress the spring 530, the pressure plate 510 leaves the surface of the friction plate 520, and the friction clutch 500 disengages, and the ring gear 210 and the planet carrier 230 can rotate independently.

[0023] The planet carrier 230 is connected to the speed change input element of the next speed change unit through a journal, that is, the sun gear 340 of the third-stage planetary gear mechanism. A curved surface feature oblique groove 503 and an annular groove 502 are provided on the journal fixedly connected to the planet carrier 230. An oblique boss 341 matching the oblique groove 503 is provided on the inner hole of the sun gear 340 that is matched with the journal. The sun gear 340 is a spur gear. The elastic member A is an annular open spring 501 and is arranged in the annular groove 502. The natural inner diameter of the open spring 501 is smaller than the diameter of the journal provided with the annular groove 502, that is, when the open spring 501 is installed in the annular groove 502, it cannot be in full contact with the annular groove 502 in the natural state. The inner hole of the sun gear 340 includes a combined feature on the side facing the friction clutch, a straight line segment with a straight bus and a curved line segment with a curved bus, specifically related to Figure 8It is the same as shown. For the large-diameter part of the straight segment, its inner diameter is close to the outer diameter of the opening spring 501 in the natural state; for the small-diameter part of the straight segment, its inner diameter is close to the outer diameter of the opening spring 501 when it is pressed into the annular groove 502. The curve segment is the transition between the large-diameter straight segment and the small-diameter straight segment. According to different specific design requirements, the lengths of the large-diameter straight segment and the small-diameter straight segment can be set as needed until they are cancelled. The curve generatrix of the curve segment can adopt one of a straight line, an arc, a hyperbola, a parabola, etc. or a combination of the above curves.

[0024] Figure 3 and Figure 4 As shown, a contact clutch 600 is provided between the third-stage planetary gear mechanism 300 and the drum assembly 900. The connection between the speed-changing output element planet carrier 330 of the third-stage planetary gear mechanism 300 and the drum assembly 900 is a power transmission unit. The planet carrier 330 is a power input part, and the outer ring 640 fixedly installed with the drum assembly 900 is a power output part. The inner element 610 of the contact clutch 600 is fixedly installed with the planet carrier 330. The control bracket 620 is frictionally installed with the fixed part 400. The outer ring 640 is fixedly installed in the drum 910 of the drum assembly 900. There is a groove 611 containing partial circular holes on the inner element 610. The inner end of the locking block 630 has a cylindrical surface, which is fitted and installed with the partial circular holes of the groove 611. The outer end extends out of the outer surface of the inner element 610 and is inserted into the groove of the control bracket 620. The inner surface of the outer ring 640 has a groove, which matches the extended end of the locking block 630. The part of the control bracket 620 containing the groove feature has an outer diameter smaller than the minimum inner diameter of the outer ring 640 and an inner diameter larger than the outer diameter of the inner element 610. The locking block 630 can rotate around its cylindrical installation end. Figure 4 As shown, it is the second position of the locking block 630, whose outer end is inserted into the groove of the control bracket 620, and the outer surface does not exceed the outer surface of the control bracket 620. The locking block 630 does not contact the power output part 640, and the contact clutch 600 is disengaged. When the locking block 630 rotates clockwise around its cylindrical installation end and its outer end is inserted into the groove of the outer ring 640, it is its first position. At this time, the locking block 630 contacts both the power input part 330 and the power output part 640, and the contact clutch 600 is engaged.

[0025] Figure 5 As shown, it is the second embodiment of the clutch device and the friction clutch control mechanism. The difference from the first embodiment is that: The clutch devices are different: In the first embodiment, the clutch device is a one-way clutch. In the second embodiment, the clutch device is a locking pin device controlled by an electromagnetic unit. Specifically, an electromagnetic unit 1010 capable of controlling the locking pin is installed on the housing 410, and a groove 211 matching the locking pin is provided on the gear ring 210. When the electromagnetic unit 1010 controls the locking pin to be in the upper position, the gear ring 210 is separated from the housing 410, and the gear ring 210 can rotate freely. When the electromagnetic unit 1010 controls the locking pin to be inserted into the groove 211 in the lower position, the gear ring 210 is combined with the housing 410, and the gear ring 210 cannot rotate.

[0026] The friction clutch control mechanisms are different: The friction clutch in the second embodiment is the same as that in the first embodiment and is also provided in the second-stage planetary gear mechanism 200. However, the friction clutch control mechanism is slightly different, specifically reflected in the different surface features. In the first embodiment, the surface feature of the friction clutch control mechanism is the installation fit between the journal and the sun gear 340. The sun gear 340 is a spur gear, and an axial force is generated during rotation by the cooperation of the oblique groove 503 and the oblique boss 341. In the second embodiment, the sun gear 340 is a helical gear. Therefore, the groove 503 on the journal and the boss 341 in the inner hole of the sun gear 340 are linear. The axial force generated during the rotation of the helical gear is used to push the sun gear 340 to move, so as to control the friction clutch 500.

[0027] Figure 6 Shown is the third embodiment of the friction clutch and the friction clutch control mechanism. The friction clutch 500 is provided in the first-stage planetary gear mechanism 100 and is connected to the sun gear 140 and the planet carrier 130. The corresponding friction clutch control mechanism is also set based on the components of the first-stage planetary gear mechanism 100 and the adjacent components. The sun gear 140 includes a spline portion 143, a non-circular cross-section portion 144, and a gear portion 145. The friction clutch 500 includes a pressure plate 510, a spring 530, an end cover 540, a friction plate 520, and the left side plate 139 of the planet carrier. The friction plate 520 is in non-circular cross-section fit with the non-circular cross-section portion 144 of the sun gear 140, and is circumferentially fixed and rotates integrally. The pressure plate 510 is in fit with the left side plate 139 of the planet carrier with a flange feature, and is circumferentially fixed and rotates integrally. The end cover 540 is threadedly connected to the pressure plate 510 to compress the spring 530, so as to generate pressure and friction force on both sides of the friction plate 520.

[0028] The actuator 001 is fixedly connected to the inner transmission member 580. The inner transmission member 580 has a bi-directional curved surface feature 503 and an annular groove 502. The opening spring 501 is installed in the annular groove 502, which is the same as in the first embodiment. The outer transmission member 590 is sleeved outside the inner transmission member 580. The inner hole includes a bi-directional curved surface feature 591 that matches the bi-directional curved surface feature 503, a combined feature large-diameter straight segment 595, a combined feature curved segment 593, a combined feature small-diameter straight segment 592, and an internal spline 594 that cooperates with the spline portion 143 of the sun gear 140, as Figure 8 shown.

[0029] Figure 7 Shown is the fourth embodiment of the friction clutch, the friction clutch control mechanism, and the contact clutch. The contact clutch 600 is arranged between the speed-changing output element planet carrier 130 of the first-stage planetary gear mechanism 100 and the speed-changing input element sun gear 240 of the second-stage planetary gear mechanism 200. Using the planet carrier 130 as the power input member and the sun gear 240 as the power output member, the specific structural principle is basically the same as that of the first embodiment and will not be elaborated here. The friction clutch 500 is arranged in the first-stage planetary gear mechanism 100 and connects the sun gear 140 and the ring gear 110. Here, the friction plate 520 is connected to the ring gear 110 and rotates integrally with the ring gear 110. The sun gear 140 includes a spline portion 143, a friction clutch support portion 144, and a gear portion 145. The pressure plate 510, the spring 530, and the end cover 540 are all installed on 144. The specific structural principle is similar to that of the first embodiment and will not be elaborated here. The friction clutch control mechanism is similar to the third embodiment, with the difference being the curved surface features. In the third embodiment, a specially processed bi-directional curved surface feature is used, while in this embodiment, an oblique spline is used to generate an axial force during rotation.

[0030] Figure 9 Shown is the fifth embodiment of the contact clutch. The contact clutch 600 is arranged between the speed-changing output element planet carrier 330 of the third-stage planetary gear mechanism 300 and the drum assembly 900. Using the planet carrier 330 as the power input member and the outer ring 640 fixedly connected to the drum assembly 900 as the power output member. The inner element 610 of the contact clutch 600 is fixedly installed with the planet carrier 330. The inner element 610 has a wedge-shaped groove 611 for installing a wedge-shaped lock block 630 with a cylindrical outer surface. On the surfaces of the inner element 610 and the wedge-shaped lock block 630 facing the drum assembly 900, an annular groove is also provided for installing an annular return spring 650.

[0031] The following describes the working process of the winch with self-clutching and automatic speed-changing functions according to the first embodiment of the present invention in combination with the combined features in the attached Figures 1-4 and attached Figure 8 drawings: The actuating device 700 drives the actuating member 001 to rotate through the transmission and braking assembly 800. The actuating member 001 is in transmission connection with the sun gear 140 in the first-stage planetary gear mechanism 100, driving the sun gear 140 to rotate. The speed is changed through the first speed-changing unit and transmitted to the second speed-changing unit: in the second-stage planetary gear mechanism 200, the friction clutch 500 is in frictional connection with the planet carrier 230 and the ring gear 210. A one-way clutch 1000 is arranged between the ring gear 210 and the housing 410. The sun gear 340 of the third-stage planetary gear mechanism 300 is in transmission connection with the planet carrier 230 through a curved surface feature - an inclined groove 503 / an inclined boss 341. There is an annular groove 502 on the connecting journal, and an opening spring 501 is installed thereon. The inner hole on the side of the sun gear 340 facing the opening spring 501 includes combined features, such as Figure 8 as shown. The opening spring 501 is located at the large end position of the curve segment 593. There is a small gap or no pressure contact between the left end face of the sun gear 340 and the end cover 540 of the friction clutch 500. The connection between the speed-changing output element planet carrier 330 of the third-stage planetary gear mechanism 300 and the drum assembly 900 is a power transmission unit, and a contact clutch 600 is installed. The control bracket 620 is in frictional connection with the fixing member 400. The locking block 630 is hinged to the inner element 610 at its inner cylindrical end, and its outer end extends beyond the outer surface of the inner element 610 and is inserted into the groove of the control bracket 620. The outer ring 640 is fixedly installed in the drum 910, and there is a groove in its inner ring. The protruding end of the locking block 630 can be inserted into this groove when the locking block 630 rotates to the first position. The ring gears 110 of the first-stage planetary gear mechanism 100 and the ring gears 310 of the third-stage planetary gear mechanism 300 are respectively fixedly connected to the housing 410 and the fixing member 400.

[0032] When it is necessary to separate the drum assembly 900, if the locking block 630 is not in the second position, the actuating device 700 reverses, driving the inner element 610 to rotate clockwise ( Figure 4 viewing direction), driving the inner end of the locking block 630 to rotate clockwise together. The outer ring 640 fixedly connected to the drum assembly 900 remains stationary. Due to the frictional force between the control bracket 620 and the fixing member 400, the control bracket 620 tends to be stationary, and the outer end of the locking block 630 inserted into the groove also tends to be stationary. Therefore, the locking block 630 rotates inwards around its supporting cylindrical end to the second position. At this time, the outer end of the locking block 630 is stuck in the groove of the control bracket 620, and its outer surface does not extend beyond the outer surface of the control bracket 630 and is completely not in contact with the outer ring 640, and the drum 900 can rotate freely.

[0033] When the drum assembly 900 needs to be combined, the actuating device 700 rotates forward, driving the inner element 610 and the inner end of the locking block 630 to rotate counterclockwise together. Since the control bracket 620 tends to remain stationary, the groove of the control bracket 620 causes the protruding end of the locking block 630 to rotate in the opposite direction, that is, the locking block 630 rotates clockwise around its supporting end and opens outward, rotating to the first position. The protruding end of the locking block 630 is inserted into the groove of the outer ring 640. Therefore, the inner element 610 drives the outer ring 640 to rotate together through the locking block 630, that is, the drum assembly 900 is combined with the actuating device.

[0034] In the working state of the winch, when it is unloaded or the load is small, the actuating device 700 rotates forward to wind the rope. The first-stage planetary gear mechanism 100 operates at normal speed change. Since the friction clutch 500 is engaged in the second-stage planetary gear mechanism 200, the ring gear 210 and the planet carrier 230 rotate at the same speed and rotate integrally with the sun gear 240. The one-way clutch 1000 allows the ring gear 210 to rotate. The sun gear 340 and the planet carrier 230 are connected through a curved surface feature. The opening spring 501 is located at the large end of the curve segment 593 of the combined feature. Since the load is small, the axial force generated by the curved surface feature is small and cannot deform the opening spring 501 into the curve segment 593. Therefore, the sun gear 340 remains stationary in its axial position and the friction clutch 500 is not affected by external forces. The contact clutch 600 is engaged due to the forward rotation of the actuating device 700. The winch operates with the transmission ratio of the first speed change unit superimposed on the transmission ratio of the third speed change unit. The second speed change unit equipped with the friction clutch 500 does not change speed, has a small transmission ratio, a high speed, and high efficiency.

[0035] When the load exceeds a specific value, the axial force generated by the curved surface feature connecting the sun gear 340 and the planet carrier 230 is large. Under the action of this axial force, the opening spring 501 elastically deforms into the curve segment 593, and the sun gear 340 moves to the left to eliminate the gap. When the opening spring 501 enters the small-diameter straight segment, the sun gear 340 presses against the end cover 540, and the axial force acts almost entirely on the end cover 540, compressing the compression spring 530 to separate the friction clutch 500, allowing the ring gear 210 and the planet carrier 230 to rotate at different speeds. At this time, since the planet carrier 230 is a variable-speed output element connecting the load on the drum assembly 900, it has a tendency to remain stationary, thus causing the ring gear 210 to have a reverse rotation tendency. The one-way clutch 1000 prevents the ring gear 210 from rotating in the reverse direction. Therefore, the second-stage planetary gear mechanism 200 transmits power with speed change. The winch superimposes the transmission ratios of the three speed change units and operates at the maximum transmission ratio, with the maximum working torque. Due to the action of the opening spring 501, the friction clutch 500 is not affected by axial force at all when the winch load is lower than the given value, and when the winch load exceeds the given value, it is sufficient to separate the friction clutch 500. Therefore, there will be no phenomenon of slipping of the friction clutch 500 under certain load conditions.

[0036] Figure 5 In the second embodiment shown, the friction clutch 500 is the same as that in the first embodiment. The curved surface features that generate axial force in the friction clutch control mechanism are different, but the working principle is the same. When the axial force generated by the helical gear 340 exceeds a specific value, the compression spring 530 separates the friction clutch 500. The relatively large difference is that the clutch device changes from the one-way clutch in the first embodiment to a pin locking device controlled by electricity. When the load is small, the electromagnetic unit 1010 controls the pin to be in the upper position, and the gear ring 210 can rotate freely. When the load is large, the electromagnetic unit 1010 controls the pin to insert into the groove 211 on the gear ring 210, and the helical gear 340 moves leftward to press against the end cover 540, separating the friction clutch 500, and the second-stage planetary gear mechanism 200 performs variable-speed transmission.

[0037] Figure 6 In the third embodiment shown, the friction clutch 500 connects the sun gear 140 and the planet carrier 130 of the first-stage planetary gear mechanism 100. The curved surface feature 503 of the friction clutch control mechanism can work in both the forward and reverse directions, which is a bidirectional curved surface feature. Figure 7 In the fourth embodiment shown, the friction clutch 500 connects the sun gear 140 and the gear ring 110 of the first-stage planetary gear mechanism 100. The curved surface feature of the friction clutch control mechanism is realized by an inclined spline. In these two embodiments, a clutch device (not shown in the figure) is provided between the gear ring 110 of the first-stage planetary gear mechanism 100 and the housing 410.

[0038] Figure 7 In the fourth embodiment shown, a contact clutch 600 is further provided in the power transmission unit connecting the variable-speed output element of the first variable-speed unit and the variable-speed input element of the second variable-speed unit. The control bracket 620 is in frictional connection with the fixed part 400 or a part fixedly connected to the fixed part 400, and the outer ring 640 is fixedly connected to the sun gear 240. Its working principle is basically the same as that of the first embodiment, and will not be elaborated here.

[0039] Figure 9 Shown is the fifth embodiment of the contact clutch 600. The return spring 650 makes the wedge-shaped lock block 630 tend to move inward. When the wedge-shaped lock block 630 is at the innermost side, its outer surface does not exceed the outer surface of the inner element 610 and does not contact the outer ring 640, and the contact clutch 600 is separated. When the inner element 610 rotates clockwise ( Figure 9In the direction of the line of sight), under the action of centrifugal force, the wedge locking block 630 moves outward against the force of the return spring 650 and contacts the outer ring 640. Due to the centrifugal force generating frictional force on the arc-shaped contact surface, the wedge locking block 630 tends to move towards its small end. The combined action of the frictional force on the outer surface and the supporting force on the supporting surface of the wedge-shaped groove 611 causes the wedge locking block 630 to be stuck between the inner element 610 and the outer ring 640, and the contact clutch 600 is engaged. When the inner element 610 rotates counterclockwise, the frictional force on the outer surface of the wedge locking block 630 causes it to move towards the large end. The combined action with the supporting force on the other supporting surface of the wedge-shaped groove 611 causes the wedge locking block 630 to tend to move inward, and the contact clutch 600 cannot be reliably engaged.

[0040] In other preferred embodiments of the present invention, the friction clutch 500 can be arranged in any one of the speed change units and can act between any components within the speed change unit. The contact clutch 600 can be arranged in any one of the power transmission units. In the case of the load paying out the rope, the drum rotates actively, and the contact clutch 600 can also be reliably engaged.

[0041] The above working process, that is, the transmission ratio change process and the drum clutch process can be completely automatically realized by mechanical means or can be realized in combination with electromagnetic control means. The winch can quickly take in the rope in the no-load state, freely pay out the rope, automatically adjust the transmission ratio according to the load size in the load state, and the rope paying out in the load state and keeping the winch in the braking effect through the transmission and braking unit are not affected.

[0042] Although the embodiments of the present invention have been shown and described, for those of ordinary skill in the art, it can be understood that these embodiments can be changed without departing from the principle and spirit of the present invention. The scope of application of the present invention is defined by the appended claims and their equivalents.

Claims

1. An automatically variable-speed winch, characterized in that: The winch includes a speed change unit, a fixing member, a friction clutch, a friction clutch control mechanism, and a clutch device; the speed change unit includes a speed change input element and a speed change output element; the friction clutch is arranged in the speed change unit and is configured to enable the speed change input element and the speed change output element of the speed change unit to have the same or different rotational speeds; the friction clutch control mechanism is configured to enable the friction clutch to disengage when the load exceeds a given load, and the friction clutch engages when the load is lower than the given load; the clutch device is arranged between the speed change unit and the fixing member of the winch and is configured to enable the components of the speed change unit to be combined with and separated from the fixing member.

2. The automatic transmission winch according to claim 1, characterized in that: It further includes a power transmission unit and a contact clutch; the power transmission unit includes a power input member and a power output member; the contact clutch is arranged in the power transmission unit and connects the power input member and the power output member of the power transmission unit; the contact clutch is configured to enable the power output member to be separated from the power input member, and when the power input member rotates actively, the power output member can be combined with the power input member; the power transmission unit includes the connection between the speed change output element of the speed change unit and the speed change input element of the next-stage speed change unit and the connection between the speed change output element of the speed change unit and the drum of the winch.

3. The automatic speed-changing winch according to claim 1, wherein: The speed change unit is a planetary gear mechanism, including a sun gear, a ring gear, and a planet carrier; the speed change input element is the sun gear, and the speed change output element is the planet carrier or the ring gear.

4. The automatic transmission winch according to claim 1, wherein: The friction clutch control mechanism includes an elastic member A, a combined feature, and a curved surface feature; the combined feature includes a straight line segment with a straight generatrix and / or a curved line segment with a curved generatrix, and the combined feature is configured to cause the elastic member A to undergo elastic deformation when the elastic member A enters and / or exits the curved line segment; the curved surface feature is configured to be able to generate an axial force during rotation.

5. The automatic transmission winch according to claim 1, characterized in that: The clutch device is a one-way clutch or an electromagnetic control lock pin device.

6. The automatic speed change winch according to claim 2, characterized in that: The contact clutch includes a control bracket and a locking block; the control bracket is frictionally connected to the fixing member, there is a groove on the control bracket, and the outer end of the locking block passes through the groove and can rotate around the inner end of the locking block. The locking block is configured to be able to contact both the power input member and the power output member simultaneously when rotating to the first position, and the contact clutch engages; when rotating to the second position, it does not contact the power output member or the power input member, and the contact clutch disengages.

7. The automatic speed-changing winch according to claim 1, characterized in that: The friction clutch includes friction plates, a pressure plate, and an elastic member B. The elastic member B presses the pressure plate against the friction plates, and the pressure plate and the friction plates are respectively fixedly connected circumferentially to different components of the speed change unit.

8. The automatic speed-changing winch according to claim 1, characterized in that: The fixing member includes the housing of the winch fixedly installed, and parts directly or indirectly fixedly connected to the housing.

9. The automatic speed-changing winch according to claim 2, wherein: The contact clutch includes a locking block and a return spring; the return spring biases the locking block to move inwardly into the power input element; the locking block is configured to be able to contact both the power input member and the power output member when in an outer position, and the contact clutch is engaged, and not to contact the power output member or the power input member when in an inner position, and the contact clutch is disengaged.

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