An automatically variable speed capstan

Abstract

This invention provides an automatic speed-changing winch capable of autonomous clutch engagement and disengagement, as well as automatic speed adjustment based on load. The winch autonomously engages and disengages the drum and gear mechanism via a contact clutch. The gear mechanism automatically selects different transmission ratios based on the load on the drum: a smaller transmission ratio and higher speed under lower loads, and a larger transmission ratio and stronger load capacity under higher loads. This automatic speed-changing winch can achieve these functions entirely mechanically, or through a combination of mechanical structure and electromagnetic control.

Description

Technical Field

[0001] This invention relates to the field of transmission or traction equipment, specifically to an automatic speed-changing winch with autonomous clutch and automatic speed-changing functions. Background Technology

[0002] A winch, driven by a power source, winds a rope around a drum to achieve pulling or lifting of heavy objects. Depending on the power source, winches are classified as manual, electric, hydraulic, and pneumatic. Winches have a wide range of applications. Most winches do not have speed-changing capabilities, and those that do require manual or remote control operation to achieve the desired speed, making them relatively inconvenient to use. Furthermore, because winch transmission ratios are typically large, releasing the rope via a power source is slow and inefficient. Summary of the Invention

[0003] The purpose of this invention is to at least partially overcome the shortcomings of the prior art and provide an automatic speed-changing winch that can automatically adjust 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 present invention also aims to provide a winch with autonomous clutch, in which the drum separates when actively pulling and releasing the rope, allowing free control of the pulling speed, and the drum engages when retracting the rope and when releasing the rope under load, effectively improving work efficiency.

[0005] To achieve the above-mentioned objectives or one of them, the technical solution of the present invention is as follows: An automatic speed-changing winch is characterized in that: the winch includes a speed-changing unit, a fixing member, a friction clutch, a friction clutch control mechanism, and a clutch device; the speed-changing unit includes a speed-changing input element and a speed-changing output element; the friction clutch is disposed in the speed-changing unit and configured to enable the speed-changing input element and the speed-changing output element of the speed-changing unit to rotate at the same or different speeds; the friction clutch control mechanism is configured to enable the friction clutch to disengage when the load exceeds a given value and to engage when the load is below the given value; the clutch device is disposed between the speed-changing unit and the fixing member of the winch and is configured to enable the engagement and disengagement of the components of the speed-changing unit with the fixing member.

[0006] According to a preferred embodiment of the present invention, the system further includes a power transmission unit and a contact clutch; the power transmission unit includes a power input component and a power output component; the contact clutch is disposed in the power transmission unit and connects the power input component and the power output component of the power transmission unit; the contact clutch is configured to disengage the power output component from the power input component, and to engage the power output component with the power input component when the power input component rotates actively; the power transmission unit includes the connection between the actuation element and the speed input element of the transmission unit, the connection between the speed output element of the transmission unit and the speed input element of the next-level transmission unit, and the connection between the speed output element of the transmission unit and the drum of the winch. Specifically, the power transmission unit refers to the connection of power components in the winch other than the speed change unit, including the connection between the actuator and the speed change input element of the first-stage speed change unit, the connection between the speed change output element of the first-stage speed change unit and the speed change input element of the second-stage speed change unit, the connection between the speed change output element of the second-stage speed change unit and the speed change input element of the third-stage speed change unit, etc., that is, the connection between the speed change output element of the previous-stage 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 last-stage speed change unit and the drum.

[0007] According to a preferred embodiment of the present invention, 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.

[0008] Specifically, the friction clutch is located in the planetary gear mechanism, connecting the sun gear and the planet carrier, or connecting the planet carrier and the ring gear, or connecting 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 element A, a combined feature, and a curved surface feature; the combined feature includes a straight segment with a straight generatrix and / or a curved segment with a curved generatrix, the combined feature being configured such that when the elastic element A enters and / or leaves the curved segment, the elastic element A undergoes elastic deformation; the curved surface feature is configured to generate an axial force during rotation.

[0010] The friction clutch control mechanism controls the engagement and disengagement of the friction clutch. Specifically, when the drum load is high, the curved surface feature generates a large axial force. This force overcomes the elastic force of the elastic element A through the combined feature, causing the assembly to push the friction clutch disengage. When the drum load is low, the axial force generated by the curved surface feature is insufficient to overcome the elastic force of the elastic element A, and the friction clutch remains engaged. The elastic element A ensures that the friction clutch is fully engaged under low loads, unaffected by the friction clutch control mechanism. This avoids the risk of unreliable engagement and slippage failure of the friction clutch under low loads due to the axial force constantly generated by the curved surface feature and applied to it.

[0011] According to a preferred embodiment of the present invention, the clutch device is a one-way clutch or an electromagnetically controlled locking pin device. The one-way clutch can be a roller-groove type one-way clutch, a wedge type one-way clutch, or a ratchet mechanism, etc. The electromagnetically controlled locking pin device is an electromagnetically driven locking pin that is inserted into a component of the transmission unit to fix the component, or the locking pin separates from the component, freeing the component. The component of the transmission unit connected to the clutch device can be a gear ring or a planetary 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 fixing member, the control bracket has a groove, the outer end of the locking block passes through the groove and is rotatable around the inner end of the locking block; the locking block is configured to simultaneously contact the power input member and the power output member when rotated to a first position, and the contact clutch is engaged; when rotated to a 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 a friction plate, a pressure plate, and an elastic element B, wherein the elastic element B causes the pressure plate to press against the friction plate, and the pressure plate and the friction plate are respectively circumferentially fixedly connected to different components of the transmission unit.

[0014] According to a preferred embodiment of the present invention, the fastener includes a housing of the winch that is fixedly installed, and parts that are 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 causes the locking block to tend to move inward toward the power input element; the locking block is configured to simultaneously contact the power input element and the power output element when in the outer position, and the contact clutch is engaged; and to disengage from the power output element or the power input element when in the inner position.

[0016] The winch of the present invention has the following advantages: The winch of this invention automatically adjusts its speed according to the load, requiring no manual intervention: When the load is low, the winch automatically operates at a small transmission ratio, resulting in high speed and efficiency; when the load is high, it automatically switches to a large transmission ratio to meet the work requirements. The transmission ratio switching process is completed automatically, requiring no manual intervention.

[0017] Accurate load switching with no slippage: Through the action of elastic element A in the friction clutch control mechanism, the friction clutch can be fully engaged when the roller load is below a certain value, and completely disengaged when it exceeds this specific value. There will be no slippage caused by a force acting on the friction clutch while the friction clutch is engaged.

[0018] The system allows for switching between free and controlled rope release as needed: When rapid rope release is required, the clutch disengages, allowing the drum to rotate freely and the user to control the release speed. When controlled rope release is required, the clutch engages, enabling controlled rope release under load. During rope winding, the clutch engages, and the winch winds up the rope quickly or slowly depending on the load. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of an embodiment of the winch with autonomous clutch and automatic speed change of the present invention; Figure 2 This is a schematic diagram of the clutch device, friction clutch, and friction clutch control mechanism in Embodiment 1; Figure 3 This is a schematic diagram of the contact clutch structure installation in Example 1; Figure 4 This is an axial schematic diagram illustrating the working principle of the contact clutch structure in Example 1; Figure 5 This is a schematic diagram of Embodiment 2 of the clutch device and friction clutch control mechanism in this invention; Figure 6 This is a schematic diagram of Embodiment 3 of the friction clutch and friction clutch control mechanism in this invention; Figure 7 This is a schematic diagram of Embodiment 4 of the friction clutch, friction clutch control mechanism, and contact clutch in this invention; Figure 8 This is a schematic diagram of the combined features in the friction clutch control mechanism; Figure 9 This is a schematic diagram of embodiment five of the contact clutch. Detailed Implementation

[0020] Exemplary embodiments of the present invention are described in detail below with reference to the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements. Furthermore, in the following detailed description, numerous specific details are set forth for ease of explanation to provide a thorough understanding of the embodiments disclosed herein. However, it will be apparent that one or more embodiments may be practiced without these specific details. In other instances, well-known structures and apparatuses are illustrated to simplify the drawings.

[0021] Figure 1-4 This is a first embodiment of an automatic speed-changing winch applying the present invention, which has an autonomous clutch function. The winch includes an actuating device 700, a transmission and braking assembly 800, a drum assembly 900, an actuating element 001 connected to the actuating device 700 via the transmission and braking assembly 800, a fixedly installed fixing element 400, and a housing 410 fixedly installed with the fixing element 400. The fixing element 400 and the housing 410 contain a gear transmission mechanism, a clutch device, a friction clutch, a friction clutch control mechanism, and a contact clutch, etc. The gear transmission mechanism includes the following transmission 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 adjacent components. Curved surface features, combined features, and elastic elements A are provided on these components to achieve control of the friction clutch 500. The power transmission unit includes the connection between the actuator 001 and the transmission unit, the connection between the upper-level transmission unit and the lower-level transmission unit, and the connection between the transmission unit and the roller assembly 900, etc., and is divided into power input components and power output components according to the direction of power transmission. In this embodiment, the contact clutch 600 is set in the power transmission unit where the third-stage planetary gear mechanism 300 is connected to the roller assembly 900. The planet carrier 330 of the third-stage planetary gear mechanism 300 is the transmission output element of the transmission unit, and serves as the power input component in this power transmission unit. The roller assembly 900 is the power output component in this power transmission unit.

[0022] Figure 2The diagram illustrates the structural principle of the clutch device 1000, friction clutch 500, and friction clutch control mechanism in Embodiment 1. The clutch device 1000 is a roller-groove type one-way clutch, comprising a groove on the housing 410, a roller 1002 installed within the groove, and a spring 1001 acting on the roller 1002. The spring 1001 causes the roller 1002 to tend to move towards the narrow end of the groove. The gear ring 210 of the second-stage planetary gear mechanism is installed inside the housing 410. Due to the action of the spring 1001, the outer surface of the gear ring 210 is always in contact with the roller 1002; therefore, the gear ring 210 can only rotate in one direction. A groove is provided on one side of the gear ring 210, which cooperates with the friction plate 520. The friction plate 520 is circumferentially fixedly connected to the gear ring 210, allowing the friction plate 520 and the gear ring 210 to rotate as a unit. The friction plate 520 has steel plates on both sides, or parts with the same function as the steel plates, such as the pressure plate 510 and the planetary carrier 230. The pressure plate 510 has a non-circular cross-section or flange feature that mates with the planetary carrier 230, so that the pressure plate 510 and the planetary carrier 230 are circumferentially fixed and rotate as a whole. The spring 530 is mounted on the planetary carrier 230, and its other end is limited by the end cover 540. The pressure plate 510 has a threaded hole, and the spring 530 is compressed by bolting the end cover 540. Pressure and friction are generated between the pressure plate 510 and the friction plate 520, and between the friction plate 520 and the planetary carrier 230. The pressure plate 510, friction plate 520, planetary carrier 230, spring 530, and end cover 540 constitute a friction clutch 500, realizing the frictional connection between the gear ring 210 and the planetary carrier 230. As the spring 530 is compressed and deformed, there is pressure and friction between the friction plate 520, the pressure plate 510, and the planetary carrier 230, and the gear ring 210 rotates as a unit with the planetary carrier 230. When the end cover 540 is moved to the left to further compress the spring 530, the pressure plate 510 leaves the surface of the friction plate 520, the friction clutch 500 disengages, and the gear ring 210 and the planetary carrier 230 can rotate independently.

[0023] The planetary carrier 230 is connected to the transmission input element of the next transmission unit, namely the sun gear 340 of the third-stage planetary gear mechanism, via a journal. The journal, fixedly connected to the planetary carrier 230, has an inclined groove 503 with curved surface features and an annular groove 502. The inner bore of the sun gear 340, which mates with the journal, has an inclined boss 341 that matches the inclined groove 503. The sun gear 340 is a spur gear. The elastic element A is an annular open spring 501, disposed in the annular groove 502. The natural inner diameter of the open spring 501 is smaller than the diameter of the journal with the annular groove 502, but larger than the bottom diameter of the annular groove 502. That is, when the open spring 501 is installed in the annular groove 502, it cannot simultaneously and completely contact the bottom of the annular groove 502 in its natural state. The inner bore of the sun gear 340, on the side facing the friction clutch, includes a straight segment with a straight generatrix and a curved segment with a curved generatrix, specifically related to… Figure 8 The same applies as shown. The inner diameter of the large-diameter portion of the straight segment is close to the outer diameter of the open spring 501 in its natural state; the inner diameter of the small-diameter portion of the straight segment is close to the outer diameter of the open spring 501 when it is pressed into the annular groove 502. The curved segment serves as a transition between the large-diameter and small-diameter straight segments. Depending on specific design requirements, the lengths of the large-diameter and small-diameter straight segments can be set as needed, up to and including their elimination. The generatrix of the curved segment can be a straight line, circular arc, hyperbola, parabola, or a combination of these curves.

[0024] Figure 3 and Figure 4 The diagram shows a contact clutch 600 positioned between the third-stage planetary gear mechanism 300 and the roller assembly 900. The planetary carrier 330, the speed-changing output element of the third-stage planetary gear mechanism 300, is connected to the roller assembly 900 as a power transmission unit. The planetary carrier 330 is the power input component, and the outer ring 640, fixedly mounted to the roller assembly 900, is the power output component. The inner element 610 of the contact clutch 600 is fixedly mounted to the planetary carrier 330, the control bracket 620 is frictionally mounted to the fixing member 400, and the outer ring 640 is fixedly mounted inside the roller 910 of the roller assembly 900. A damping washer 920 is installed between the roller 910 and the fixing member 400 to support the roller 910 and reduce friction and vibration during operation. The inner element 610 has a groove 611 containing a partially circular hole. The inner end of the locking block 630 has a cylindrical surface that mates with the partially circular hole in the groove 611, and its outer end extends beyond the outer surface of the inner element 610 and inserts into the groove of the control bracket 620. The inner surface of the outer ring 640 has a groove that matches the protruding end of the locking block 630. The control bracket 620 includes a portion with this groove feature; its outer diameter is smaller than the minimum inner diameter of the outer ring 640, and its inner diameter is larger than the outer diameter of the inner element 610. The locking block 630 is rotatable about its cylindrical mounting end. Figure 4 The second position of the locking block 630 is shown, with its outer end inserted into the groove of the control bracket 620, and its outer surface not exceeding the outer surface of the control bracket 620. The locking block 630 does not contact the power output component 640, and the clutch 600 is disengaged. The first position of the locking block 630 is when it rotates clockwise around its cylindrical mounting end and its outer end is inserted into the groove of the outer ring 640. In this position, the locking block 630 simultaneously contacts both the planetary carrier 330 (power input component) and the power output component 640, and the clutch 600 is engaged.

[0025] Figure 5 The diagram shows a second embodiment of the clutch device and friction clutch control mechanism, which differs from the first embodiment in that: The clutch devices differ: In Embodiment 1, the clutch device is a one-way clutch; in Embodiment 2, the clutch device is an electromagnetically controlled locking pin device. 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. Together, they constitute a locking pin-type clutch device 1000. When the electromagnetic unit 1010 controls the locking pin to the upper position, the gear ring 210 separates 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 at the lower position, the gear ring 210 engages with the housing 410, and the gear ring 210 cannot rotate.

[0026] The friction clutch control mechanism differs: In Embodiment 2, the friction clutch is the same as in Embodiment 1, also located in the second-stage planetary gear mechanism 200. However, the friction clutch control mechanism differs slightly, specifically in its surface features. In Embodiment 1, the surface feature of the friction clutch control mechanism is the mounting fit between the journal and the sun gear 340. The sun gear 340 is a spur gear, and axial force is generated during rotation through the engagement of the inclined groove 503 and the inclined boss 341. In Embodiment 2, 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 straight lines. The axial force generated when the helical gear rotates pushes the sun gear 340 to move, thereby controlling the friction clutch 500.

[0027] Figure 6 The diagram shows a third embodiment of a friction clutch and its control mechanism. The friction clutch 500 is housed in the first-stage planetary gear mechanism 100 and connects the sun gear 140 and the planet carrier 130. The planetary gear 120 is mounted on the planet carrier 130. The corresponding friction clutch control mechanism is also based on the components of the first-stage planetary gear mechanism 100 and 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 cap 540, a friction plate 520, and a left side plate 139 of the planet carrier. The friction plate 520 engages with the non-circular cross-section portion 144 of the sun gear 140 via a non-circular cross-section, is circumferentially fixed, and rotates integrally. The pressure plate 510 engages with the left side plate 139 of the planet carrier via a flange feature, is circumferentially fixed, and rotates integrally. The end cap 540 is threadedly connected to the pressure plate 510, compressing the spring 530 to generate pressure and friction on both sides of the friction plate 520.

[0028] Actuator 001 is fixedly connected to inner drive member 580. Inner drive member 580 has a groove 503 containing a bidirectional curved surface feature and an annular groove 502. An open spring 501 is installed in the annular groove 502, as in Embodiment 1. Outer drive member 590 is fitted outside inner drive member 580. Its inner bore includes a bidirectional curved surface feature 591 matching the groove 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 mates with the spline portion 143 of sun gear 140, as shown below. Figure 8 As shown.

[0029] Figure 7 The diagram shows an embodiment four of a friction clutch and its control mechanism, and a contact clutch. The contact clutch 600 is positioned between the planet carrier 130, the transmission output element of the first-stage planetary gear mechanism 100, and the sun gear 240, the transmission input element of the second-stage planetary gear mechanism 200. The planet carrier 130 serves as the power input element, and the sun gear 240 as the power output element. Its specific structure and principle are basically the same as in embodiment one, and will not be detailed here. The friction clutch 500 is located in the first-stage planetary gear mechanism 100, connecting 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 it. The sun gear 140 includes a spline portion 143, a non-circular cross-section portion 144, and a gear portion 145. The pressure plate 510, spring 530, and end cap 540 are all mounted on 144. Their specific structure and principle are similar to those in embodiment one, and will not be detailed here. The friction clutch control mechanism is similar to that of Embodiment 3, except that the surface features are different. Embodiment 3 uses a specially processed bidirectional curved surface feature, while this embodiment uses a slanted spline, which generates axial force when rotating.

[0030] Figure 9 The diagram shows a fifth embodiment of the contact clutch. The contact clutch 600 is positioned between the planetary carrier 330, the speed-changing output element of the third-stage planetary gear mechanism 300, and the roller assembly 900. The planetary carrier 330 serves as the power input element, and the outer ring 640, fixedly connected to the roller assembly 900, serves as the power output element. The inner element 610 of the contact clutch 600 is fixedly mounted to the planetary carrier 330. The inner element 610 has a wedge-shaped groove 611 for mounting a wedge-shaped locking block 630 with a cylindrical outer surface. An annular groove is also provided on the surface of the inner element 610 and the wedge-shaped locking block 630 facing the roller assembly 900 for mounting an annular return spring 650.

[0031] The following is in conjunction with the appendix Figure 1-4 and attached Figure 8 The combined features described in the first embodiment of the present invention describe the working process of the winch with autonomous clutch and automatic speed change functions: The actuating device 700 drives the actuating element 001 to rotate via the transmission and braking assembly 800. The actuating element 001 is connected to the sun gear 140 in the first-stage planetary gear mechanism 100, driving the sun gear 140 to rotate. The rotation is then transmitted to the second transmission unit via the first transmission unit. In the second-stage planetary gear mechanism 200, a friction clutch 500 frictionally connects the planet carrier 230 and the ring gear 210. A one-way clutch-type clutch device 1000 is provided between the ring gear 210 and the housing 410. The sun gear 340 of the third-stage planetary gear mechanism 300 is connected to the planet carrier 230 via a curved surface feature—an inclined groove 503 / an inclined boss 341. The connecting journal has an annular groove 502, on which an open spring 501 is mounted. The inner hole of the sun gear 340 facing the open spring 501 includes combined features, such as… Figure 8 As shown. The open spring 501 is located at the large end of the curved 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 planet carrier 330, the speed-changing output element of the third-stage planetary gear mechanism 300, and the roller assembly 900 is a power transmission unit, and a contact clutch 600 is installed. The control bracket 620 is frictionally connected to the fixed member 400. The locking block 630 is hinged to the inner element 610 with 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 inside the roller 910. Its inner ring has a groove, and the protruding end of the locking block 630 can be inserted into this groove when the locking block 630 is rotated to the first position. The gear ring 110 of the first-stage planetary gear mechanism 100 and the gear ring 310 of the third-stage planetary gear mechanism 300 are fixedly connected to the housing 410 and the fixed member 400, respectively.

[0032] When it is necessary to separate the roller assembly 900, if the locking block 630 is not in the second position, the actuator 700 reverses, causing the inner element 610 to rotate clockwise. Figure 4 (Looking at the inner end of the locking block 630), causing the inner end of the locking block 630 to rotate clockwise. The outer ring 640, which is fixedly connected to the roller assembly 900, remains stationary. Due to the friction between the control bracket 620 and the fixing member 400, the control bracket 620 tends to remain stationary, and the outer end of the locking block 630 inserted into the groove also tends to remain stationary. Therefore, the locking block 630 rotates inward 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 620, and it is not in contact with the outer ring 640 at all, allowing the roller assembly 900 to rotate freely.

[0033] When the roller assembly 900 needs to be engaged, the actuator 700 rotates clockwise, causing the inner element 610 and the inner end of the locking block 630 to rotate counterclockwise together. Since the control bracket 620 tends to be 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 support end and opens outward. When it rotates 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 roller assembly 900 is engaged with the actuator.

[0034] When the winch is in operation, under no-load or light load conditions, the actuator 700 rotates forward to wind up the rope. The first-stage planetary gear mechanism 100 operates normally in gear shifting mode. Due to the engagement of the friction clutch 500, the second-stage planetary gear mechanism 200 rotates at the same speed as the ring gear 210 and planetary carrier 230, rotating as a unit with the sun gear 240. The one-way clutch-type clutch 1000 allows the ring gear 210 to rotate. The sun gear 340 is connected to the planetary carrier 230 via a curved surface feature. The open spring 501 is located at the large end of the curved segment 593 of the combined feature. Due to the light load, the axial force generated by the curved surface feature is small, preventing the open spring 501 from deforming into the curved segment 593. Therefore, the sun gear 340 remains stationary in its axial position, and the friction clutch 500 is unaffected by external forces. The contact clutch 600 engages due to the forward rotation of the actuator 700, and the winch operates with the transmission ratio of the first gear shift unit superimposed on the transmission ratio of the third gear shift unit. The second gear shift unit, equipped with the friction clutch 500, does not change speed, resulting in a small transmission ratio, high speed, and high efficiency.

[0035] When the load exceeds a certain value, the axial force generated by the curved surface feature connecting the sun gear 340 and the planetary carrier 230 is large. Under the action of this axial force, the open spring 501 elastically deforms and enters the curved section 593, causing the sun gear 340 to move to the left and eliminate the gap. When the open spring 501 enters the small-diameter straight section, the sun gear 340 presses against the end cover 540, and the axial force acts almost entirely on the end cover 540, compressing the spring 530 and causing the friction clutch 500 to disengage. The ring gear 210 and the planetary carrier 230 can then operate at different speeds. At this time, since the planetary carrier 230 is a speed-changing output element connected to the load on the roller assembly 900, it has a tendency to stop, thus causing the ring gear 210 to have a tendency to reverse. The clutch device 1000, which is in the form of a one-way clutch, prevents the ring gear 210 from rotating in the opposite direction. Therefore, the second-stage planetary gear mechanism 200 performs speed-changing transmission. The winch superimposes the transmission ratios of the three speed-changing units and operates at the maximum transmission ratio, resulting in the maximum working torque. Due to the action of the open spring 501, the friction clutch 500 is completely unaffected by axial force when the winch load is below the given value, and when the winch load exceeds the given value, it is sufficient to disengage the friction clutch 500. Therefore, the friction clutch 500 will not slip under certain load conditions.

[0036] Figure 5 In the illustrated embodiment two, the friction clutch 500 is the same as in embodiment one, except that 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-type sun gear 340 exceeds a certain value, the compression spring 530 disengages the friction clutch 500. The major difference is that the clutch device has been changed from a one-way clutch in embodiment one to an electromagnetically controlled locking pin device. When the load is small, the electromagnetic unit 1010 controls the locking pin to be in the upper position, allowing the gear ring 210 to rotate freely. When the load is large, the electromagnetic unit 1010 controls the locking pin to insert into the groove 211 on the gear ring 210, causing the sun gear 340 to move to the left and press against the end cover 540, thus disengaging the friction clutch 500 and enabling the second-stage planetary gear mechanism 200 to perform speed change 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 side of the groove 503 has the curved surface features of the friction clutch control mechanism, which can work in both forward and reverse directions and is a bidirectional curved surface feature. Figure 7 In the fourth embodiment shown, the friction clutch 500 connects the sun gear 140 and the ring gear 110 of the first-stage planetary gear mechanism 100, and the curved surface feature of the friction clutch control mechanism is achieved by a slanted spline. In both embodiments, a clutch device (not shown in the figure) is provided between the ring gear 110 of the first-stage planetary gear mechanism 100 and the housing 410.

[0038] Figure 7 In the fourth embodiment shown, the contact clutch 600 is also installed in the power transmission unit that connects the speed output element of the first speed transmission unit and the speed input element of the second speed transmission unit. The control bracket 620 is frictionally connected to the fixing member 400 or the part that is fixedly connected to the fixing member 400. 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 described in detail here.

[0039] Figure 9 The diagram shows a fifth embodiment of the contact clutch 600. The return spring 650 causes the wedge-shaped locking block 630 to tend to move inward. When the wedge-shaped locking block 630 is at its innermost position, its outer surface does not exceed the outer surface of the inner element 610 and does not contact the outer ring 640, thus disengaging the contact clutch 600. When the inner element 610 rotates clockwise (… Figure 9(View from the outside), the wedge-shaped locking block 630 moves outward under the action of centrifugal force, overcoming the force of the return spring 650, and contacts the outer ring 640. Due to the friction generated by the centrifugal force on the arc-shaped contact surface, the wedge-shaped locking block 630 tends to move towards its smaller end. The friction on the outer surface and the supporting force on the supporting surface of the wedge-shaped groove 611 work together to make the wedge-shaped locking block 630 stuck between the inner element 610 and the outer ring 640, engaging the clutch 600. When the inner element 610 rotates counterclockwise, the friction on the outer surface of the wedge-shaped locking block 630 causes it to move towards its larger end. This, combined with the supporting force on the supporting surface on the other side of the wedge-shaped groove 611, causes the wedge-shaped locking block 630 to tend to move inward, preventing the clutch 600 from reliably engaging.

[0040] In other preferred embodiments of the invention, the friction clutch 500 can be disposed within any transmission unit and can act between any components within the transmission unit. The contact clutch 600 can be disposed within any power transmission unit. When the load is released from the rope, the drum rotates actively, and the contact clutch 600 can reliably engage.

[0041] The above-mentioned working process, namely the transmission ratio change process and the drum clutch process, can be fully realized automatically by mechanical means, or it can be realized by a combination of electromagnetic control. The winch can quickly take in the rope and release the rope freely in the no-load state, automatically adjust the transmission ratio according to the load size in the load state, release the rope in the load state, and maintain the braking effect of the winch through the transmission and braking unit without being affected.

[0042] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that variations may be made to these embodiments without departing from the principles and spirit of the invention. The scope of the invention is defined by the appended claims and their equivalents.

Claims

1. An automatic speed-changing winch, characterized in that: The winch includes a transmission unit, a fixing member, a friction clutch, a friction clutch control mechanism, and a clutch device. The transmission unit includes a transmission input element and a transmission output element. The friction clutch is disposed in the transmission unit and configured to enable the transmission input element and the transmission output element of the transmission unit to rotate at the same or different speeds. The friction clutch control mechanism is configured to enable the friction clutch to disengage when the load exceeds a given value and to engage when the load is below the given value. The clutch device is disposed between the transmission unit and the fixing member of the winch and is configured to enable the engagement and disengagement of the components of the transmission unit with the fixing member.

2. The automatic speed-changing winch according to claim 1, characterized in that: It also includes a power transmission unit and a contact clutch; the power transmission unit includes a power input component and a power output component; the contact clutch is disposed in the power transmission unit and connects the power input component and the power output component of the power transmission unit; the contact clutch is configured to disengage the power output component from the power input component, and to engage the power output component with the power input component when the power input component rotates actively; 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-level 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, characterized in that: 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 speed-changing winch according to claim 1, characterized in that: The friction clutch control mechanism includes an elastic element A, a combined feature, and a curved surface feature; the combined feature includes a straight segment with a straight generatrix and / or a curved segment with a curved generatrix, the combined feature being configured such that when the elastic element A enters and / or leaves the curved segment, the elastic element A undergoes elastic deformation; the curved surface feature is configured to generate an axial force during rotation.

5. The automatic speed-changing winch according to claim 1, characterized in that: The clutch device is a one-way clutch or an electromagnetically controlled locking pin device.

6. The automatic speed-changing 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, the control bracket has a groove, 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 simultaneously contact the power input and the power output when rotated to a first position, wherein the contact clutch engages; and to disengage from the power output or the power input when rotated to a second position.

7. The automatic speed-changing winch according to claim 1, characterized in that: The friction clutch includes a friction plate, a pressure plate, and an elastic element B. The elastic element B causes the pressure plate to press the friction plate tightly. The pressure plate and the friction plate are respectively circumferentially fixedly connected to different components of the transmission unit.

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

9. The automatic speed-changing winch according to claim 2, characterized in that: The contact clutch includes a locking block and a return spring; the return spring causes the locking block to tend to move inward toward the power input member; the locking block is configured to simultaneously contact the power input member and the power output member when in the outer position, and the contact clutch is engaged; and to disengage from the power output member or the power input member when in the inner position.

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