CN112279129B

CN112279129B - Electric capstan equipment

Info

Publication number: CN112279129B
Application number: CN202011245003.3A
Authority: CN
Inventors: 俞芷琳; 戴林吉; 张小彬; 叶岭
Original assignee: Zhejiang Runva Mechanical & Electrical Co ltd
Current assignee: Zhejiang Runva Mechanical & Electrical Co ltd
Priority date: 2019-11-07
Filing date: 2019-11-07
Publication date: 2021-10-29
Anticipated expiration: 2039-11-07
Also published as: CN112279130A; CN112279129A; CN110745724B; CN110745724A; CN112279130B

Abstract

The invention belongs to the field of winches, and particularly relates to an electric winch device which comprises an electric control module, a motor module, a roller, a clutch, a primary speed reducing component, a secondary speed reducing component, a tertiary speed reducing component, a transmission shaft and a braking unit, wherein a pressure sensor can identify whether a tertiary sun gear and a secondary planet carrier are completely meshed or not; when the third-stage sun gear is completely meshed with the second-stage planet carrier, the motor is started to enable the winch to be normally used. Through the design that the friction block A and the friction block B respectively perform friction braking with the friction ring A and the friction ring B, the braking between the transmission shaft and the friction ring at the support and the friction ring at the roller is achieved, and a better braking effect is achieved. When the A coupling and the B coupling move relatively, the rectangular spring deforms to generate friction with the A friction block and the B friction block, but the friction heat generation is small, so that the influence on the failure of the rectangular spring can be ignored. Thus, the service life of the rectangular spring can be prolonged.

Description

Electric capstan equipment

Technical Field

The invention belongs to the field of winches, and particularly relates to electric winch equipment.

Background

Currently, in the winches in the prior art, a brake unit in the winch is used for establishing brake between an intermediate transmission shaft and a friction ring at a bracket, or between the intermediate transmission shaft and a roller; it is known that the braking solution of the winch not of the present company is to brake the intermediate transmission shaft and the drum; through the innovative improvement of the braking unit, the middle transmission shaft can be respectively braked with the friction ring and the roller at the support, so that a better braking effect is realized.

In addition, in the winch in the prior art, the principle of the power connection or the clutch realized by the speed reduction assembly and the intermediate transmission shaft in the winch is as follows: the clutch is realized by changing the meshing relationship between the three-stage sun gear and the two-stage planet carrier, and when the three-stage sun gear and the two-stage planet carrier are switched from a separated state to a closed state, the situation that the three-stage sun gear cannot enter the two-stage planet carrier to be meshed occurs; under the condition, the twisted rope needs to be manually pulled to enable the roller to rotate, the roller drives the three-stage sun gear to rotate for a certain angle through the three-stage planet carrier and the three-stage planet gear, and therefore the three-stage sun gear can enter the two-stage planet carrier to be meshed. However, when a user forgets to pull the twisted rope and meets the condition that the elastic restoring force of the compression spring at the coupler is reduced after the compression spring is used for a long time, the speed of the third-stage sun gear entering the second-stage planet carrier is reduced, and at the moment, when the motor drives the inner teeth of the second-stage planet carrier to be in contact with the outer teeth of the entering third-stage sun gear and starts to transmit, the third-stage sun gear is probably not inserted in place; because there is pressure and produces the friction in the tooth meshing between tertiary sun gear and the second grade planet carrier among the transmission process, compression spring's thrust inadequately must lead to tertiary sun gear and second grade planet carrier to produce the width of meshing not enough, if this kind of state uses for a long time, the damage must appear with the tooth of second grade planet carrier to lead to the unable normal use of capstan winch.

The present invention is directed to an electric winch apparatus that solves the above problems.

Disclosure of Invention

In order to solve the above defects in the prior art, the invention discloses an electric winch device, which is realized by adopting the following technical scheme.

In the description of the present invention, it should be noted that the terms "inside", "below", "upper" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings or orientations or positional relationships that the products of the present invention usually place when using, and are only used for convenience of description and simplification of description, but do not indicate or imply that the devices or elements indicated must have a specific orientation, be constructed in a specific orientation or be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like are used merely to distinguish one description from another, and are not to be construed as indicating or implying relative importance.

An electric winch apparatus, characterized in that: the electric control device comprises an outer shell, wherein an electric control module is arranged in the upper side of the outer shell, a motor module is arranged in the left end side of the outer shell, a speed reduction module and a clutch are arranged in the right end side of the outer shell, a roller is arranged in the middle of the lower side of the outer shell, a motor in the motor module drives a transmission shaft positioned in the roller to rotate through a braking unit, the transmission shaft drives the roller to rotate through the speed reduction module, and the clutch controls the axial movement of the transmission shaft; the method is characterized in that: the speed reduction module consists of a first-stage speed reduction assembly, a second-stage speed reduction assembly and a third-stage speed reduction assembly; and a secondary planet carrier in the secondary speed reduction assembly is matched with a tertiary sun gear in the tertiary speed reduction assembly.

The braking unit comprises a coupling A, a coupling B, a rectangular spring, a friction block A, a friction block B and a sliding disc, wherein the side surface of the disc A of the coupling A is provided with a column A, the outer column surface of the column A is symmetrically provided with two arc blocks A, and one arc block A is provided with an A notch; one side surface of a B disc of the coupler B is provided with a B column, the other side surface of the B disc is symmetrically provided with two B arc blocks, and one B arc block is provided with a B notch; the outer circular surface of the B disc is provided with a B sleeve, the periphery of the B sleeve is uniformly provided with a plurality of groups of sliding chutes, each group of sliding chutes consists of an A sliding chute and a B sliding chute, and the B sliding chute is positioned between the B disc and the A sliding chute; an arc-shaped A friction block is slidably mounted in each A sliding groove, and an arc-shaped B friction block is slidably mounted in each B sliding groove; one end of the transmission shaft is slidably arranged in a shaft groove of the B column, one end of the compression spring is connected with the end surface of the transmission shaft, which is positioned in the shaft groove, and the other end of the compression spring is connected with the groove surface of the shaft groove; the two arc blocks B are sleeved on the column A and are respectively matched with the two arc blocks A; the A incision and the B incision are opposite in position; one end of a rectangular spring sleeved on the arc block A and the arc block B is fixedly arranged in the notch A of the arc block A, and the other end of the rectangular spring is fixedly arranged in the notch B of the arc block B; a sliding disc is fixedly arranged on the transmission shaft, a plurality of arc-shaped pushing strips are uniformly distributed on the disc surface of the sliding disc close to the B coupling in the circumferential direction, and the pushing strips respectively correspond to the plurality of friction blocks B in position; one end of the push bar, which is far away from the sliding disc, is provided with an inclined plane, the side surface of the B friction block, which corresponds to the push bar, is provided with an inclined plane, and the inclined plane of the push bar is matched with the inclined plane of the corresponding B friction block; the rectangular spring is respectively in friction fit with the inner arc surface of the friction block A and the inner arc surface of the friction block B.

The shell is internally provided with a support, the center of the side surface of the support is provided with a friction ring A, the position of the roller close to the support is fixedly provided with a friction ring B, and the friction ring A corresponds to the friction ring B in position; the outer cambered surface of the friction block A is in friction fit with the friction ring A; the outer cambered surface of the friction block B is in friction fit with the friction ring B.

One end of the transmission shaft, which is far away from the B shaft coupler, is rotatably connected with a clamping sleeve, and the clamping sleeve is fixedly connected with a clutch sliding block in a clutch; and a pressure sensor fixedly arranged in the speed reducer shell is matched with the clutch sliding block, and the pressure sensor is electrically connected with the electric control module.

Preferably, two slots B are distributed on the transmission shaft; a B clamp is arranged in each B clamp groove; the sliding disk is clamped by two B clamps.

Preferably, two A clamping grooves are distributed on the transmission shaft; a clamp A is arranged in each clamp groove A; two sides of the third-stage sun gear are clamped by the two A hoops.

Preferably, the shaft groove of the column B is in a regular inner hexagonal shape, the outer wall of the transmission shaft is in a regular outer hexagonal shape, and the outer wall of the transmission shaft and the inner wall of the shaft groove slide in a surface-to-surface fit manner. This facilitates the B-coupling to drive the drive shaft to rotate.

Preferably, a clamping groove is formed in one end, far away from the coupler B, of the transmission shaft; the clamping sleeve consists of a middle sleeve, an outer ring disc and an inner ring disc, wherein one end of the middle sleeve is provided with the outer ring disc, and the other end of the middle sleeve is provided with the inner ring disc; the inner ring disc is clamped in the clamping groove of the transmission shaft; the outer ring disc is installed on the side face of the center of the clutch sliding block through a bolt. The design of joint cover makes the transmission shaft can not drive the clutch slide rotatory through the joint cover when rotatory, but the transmission shaft can carry out synchronous axial displacement through joint cover and clutch slide.

Preferably, the clutch is composed of a clutch handle, a clutch shaft sleeve and a clutch slider; a clutch handle is rotatably arranged on the outer side of the outer shell, and a clutch shaft sleeve rotatably arranged at the center of the reducer shell is fixedly connected with the clutch handle; the clutch shaft sleeve is provided with two symmetrical spiral structures; three support bars which are uniformly distributed on the clutch sliding block in the circumferential direction are respectively arranged in three support sliding chutes which are uniformly distributed in the circumferential direction at the center of the speed reducer shell in a sliding mode along the axial direction of the transmission shaft, and two spiral structures on the clutch shaft sleeve are matched with the support bars on the clutch sliding block to enable the clutch sliding block to axially move; the axial movement of the clutch sliding block is controlled by rotating the clutch handle to drive the clutch shaft sleeve to rotate.

Preferably, a pressure sensor is installed on a groove surface in a supporting chute of the speed reducer housing, and a supporting bar in the supporting chute provided with the pressure sensor is in press fit with the pressure sensor.

Preferably, a wire casing is arranged in the speed reducer shell, one end of the wire casing is communicated with the space of the shell body, which is provided with the electric control module, and the other end of the wire casing is communicated with a place for installing the pressure sensor; one end of the wire is electrically connected with the pressure sensor, and the other end of the wire penetrates through the wire slot to be electrically connected with the electric control module.

Compared with the traditional winch, the winch has the advantages that:

1. through innovating the improvement to the clutch, can discern behind the pressure sensor whether tertiary sun gear realizes complete meshing with the second grade planet carrier. When the third-stage sun gear is completely meshed with the second-stage planet carrier, the clutch sliding block in the clutch is at an initial position, the clutch sliding block and the pressure sensor are extruded to generate a signal, the motor can reach a starting condition, a motor switch is pressed, and the motor is started; when the third-stage sun gear is not meshed with the second-stage planet carrier, the clutch sliding block in the clutch is not located at the initial position, the clutch sliding block and the pressure sensor do not extrude and generate signals, the motor cannot reach the starting condition, and the motor cannot be started even if a motor starting button is pressed; whether the operation that can not be started through the motor judges tertiary sun gear and whether complete meshing of second grade planet carrier, has improved the result of use of capstan winch, if the discovery does not start, then pulls wire rope and rotates the cylinder, through rotating a small-angle back, tertiary sun gear will mesh with the second grade planet carrier, and the cylinder can't continue to rotate, after discovering that the cylinder can't rotate, then judges the meshing and accomplishes, can press starter motor's button starter motor.

2. Through the structural improvement of the brake unit, the brake effect is better than that realized by a transmission brake unit. One end of the rectangular spring is arranged on the coupler A, and the other end of the rectangular spring is arranged on the coupler B; when the motor is powered off, the coupling A and the coupling B move relatively; the rectangular spring deforms and expands, the outer diameter is enlarged, the friction block A and the friction block B are stretched and are respectively subjected to friction braking with the friction ring A and the friction ring B, and therefore braking is respectively established between the transmission shaft and the friction ring at the support and the friction ring at the roller, and a better braking effect is achieved.

3. One end of the rectangular spring is connected with the B arc block on the B coupling and always keeps moving synchronously with the B coupling, and the other end of the rectangular spring is connected with the A arc block on the A coupling and moves along with the A coupling; when the A coupling and the B coupling move relatively, the rectangular spring deforms to generate friction with the A friction block and the B friction block, but the friction heat generation is small, so that the influence on the failure of the rectangular spring can be ignored. Thus, the service life of the rectangular spring can be prolonged.

Drawings

FIG. 1 is an elevational view, in whole and in section, of a winch.

Fig. 2 is a partially enlarged front view (one) of fig. 1.

Fig. 3 is a partially enlarged front view (ii) of fig. 1.

Fig. 4 is a cross-sectional mating view of the pressure sensor and clutch slide.

Fig. 5 is a cross-sectional view of the clutch.

FIG. 6 is a clutch detail view.

Fig. 7 is a sectional view showing the installation of the bayonet coupling and a structure of the drive shaft.

FIG. 8 is a view of the internal transmission of the winch.

Fig. 9 is a partially enlarged view (one) of fig. 8.

Fig. 10 is a partially enlarged view (ii) of fig. 8.

FIG. 11 is a cross-sectional view of the engagement of the three-stage sun gear with the two-stage carrier.

Fig. 12 is a view of the a coupling and the B coupling.

Fig. 13 is a sectional view of the B-coupling.

FIG. 14 is a cross-sectional view of the friction block and push bar of FIG. B.

Fig. 15 is an installation view of a rectangular spring.

FIG. 16 is a front view of the rectangular spring mated with the A and B pads, respectively.

Number designation in the figures: 1. an electronic control module; 2. a motor module; 3. a drum; 4. a clutch; 5. a first-stage speed reduction assembly; 6. a secondary speed reduction assembly; 7. a tertiary deceleration component; 8. a drive shaft; 9. a brake unit; 10. a motor; 12. b, clamping a hoop; 13. a sliding disk; 14. pushing the strips; 15. b, coupling; 16. a, coupling; 17. a support; 18. a, rubbing a ring; 19. a rectangular spring; 20. b, rubbing a ring; 21. a reducer housing; 22. a wire slot; 23. a pressure sensor; 24. a clutch handle; 25. a clutch shaft sleeve; 26. a clutch slide block; 27. a clamping sleeve; 28. a clamping groove; 29. a, a clamping groove; 30. a card slot B; 31. a compression spring; 32. a, a friction block; 33. b, a friction block; 34. a secondary planet carrier; 35. a third-stage sun gear; 36. a, clamping a hoop; 37. a disc; 38. a column A; 39. a, an arc block; 40. a, cutting; 41. a column B; 42. b, disc; 43. b, sheathing; 44. a chute B; 45. a, a chute; 46. b, an arc block; 47. b, cutting; 48. a shaft groove; 49. an outer housing; 50. a middle sleeve; 51. an outer ring disc; 52. an inner ring disc; 53. a support chute; 54. a support strip.

Detailed Description

The invention will be described with reference to the accompanying drawings; it is to be understood that the structural proportions in the figures are exemplary only, and are not intended as limitations on the scope of the present disclosure.

An electric winch device is shown in fig. 1 and comprises an outer shell 49, wherein an electric control module 1 is arranged in the upper side of the outer shell 49, a motor module 2 is arranged in the left end side of the outer shell 49, a speed reduction module and a clutch 4 are arranged in the right end side of the outer shell 49, a roller 3 is arranged in the middle of the lower side of the outer shell 49, a motor 10 in the motor module 2 drives a transmission shaft 8 in the roller 3 to rotate through a braking unit 9, the transmission shaft 8 drives the roller 3 to rotate through the speed reduction module, and the clutch 4 controls the axial movement of the transmission shaft 8; the speed reducing module consists of a first-stage speed reducing component 5, a second-stage speed reducing component 6 and a third-stage speed reducing component 7; as shown in fig. 8, 10 and 11, the secondary planet carrier 34 of the secondary reduction assembly 6 cooperates with the tertiary sun gear 35 of the tertiary reduction assembly 7.

The brake unit 9 comprises an A coupling 16, a B coupling 15, a rectangular spring 19, an A friction block 32, a B friction block 33 and a sliding disk 13, as shown in FIG. 12, wherein the side surface of the A disk 37 of the A coupling 16 is provided with an A column 38, the outer cylindrical surface of the A column 38 is symmetrically provided with two A arc blocks 39, and one A arc block 39 is provided with an A notch 40; as shown in fig. 12 and 13, the B disc 42 of the B coupling 15 has a B pillar 41 on one side, and two B arc blocks 46 symmetrically on the other side, wherein one B arc block 46 has a B notch 47; the outer circular surface of the B disk 42 is provided with a B sleeve 43, a plurality of groups of sliding grooves are uniformly formed in the circumferential direction of the B sleeve 43, each group of sliding grooves is composed of an A sliding groove 45 and a B sliding groove 44, and the B sliding groove 44 is positioned between the B disk 42 and the A sliding groove 45; an arc-shaped A friction block 32 is slidably mounted in each A sliding groove 45, and an arc-shaped B friction block 33 is slidably mounted in each B sliding groove 44; as shown in fig. 2 and 9, one end of the transmission shaft 8 is slidably mounted in the shaft groove 48 of the B-pillar 41, one end of the compression spring 31 is connected with the end surface of the transmission shaft 8 located in the shaft groove 48, and the other end is connected with the groove surface of the shaft groove 48; as shown in fig. 15, two B arc blocks 46 are sleeved on the a column 38, and the two B arc blocks 46 are respectively matched with the two a arc blocks 39; the A incision 40 and the B incision 47 are opposite; one end of a rectangular spring 19 sleeved on the arc block A39 and the arc block B46 is fixedly arranged in the notch A40 of the arc block A39, and the other end of the rectangular spring is fixedly arranged in the notch B47 of the arc block B46; as shown in fig. 9 and 14, a sliding disk 13 is fixedly mounted on the transmission shaft 8, a plurality of arc-shaped pushing strips 14 are uniformly distributed on the disk surface of the sliding disk 13 close to the B coupling 15 in the circumferential direction, and the plurality of pushing strips 14 correspond to the plurality of B friction blocks 33 respectively; one end of the push bar 14, which is far away from the sliding disc 13, is provided with an inclined surface, the side surface of the B friction block 33, which corresponds to the push bar 14, is provided with an inclined surface, and the inclined surface of the push bar 14 is matched with the inclined surface of the corresponding B friction block 33; as shown in fig. 16, the rectangular springs 19 are frictionally engaged with the intrados of the a pad 32 and the intrados of the B pad 33, respectively.

As shown in fig. 13 and 14, the outer shell 49 has a bracket 17 therein, and the center of the side surface of the bracket 17 has an a friction ring 18, a B friction ring 20 is fixedly mounted on the drum 3 near the bracket 17, and the positions of the a friction ring 18 and the B friction ring 20 correspond to each other; as shown in fig. 14 and 16, the extrados of the a friction block 32 is in friction fit with the a friction ring 18; the outer cambered surface of the B friction block 33 is in friction fit with the B friction ring 20.

As shown in fig. 5 and 12, one end of the transmission shaft 8, which is far away from the B-coupling 15, is rotatably connected with a clamping sleeve 27, and the clamping sleeve 27 is fixedly connected with a clutch sliding block 26 in the clutch 4; as shown in fig. 3 and 4, a pressure sensor 23 fixed in the reducer housing 21 is engaged with the clutch slider 26, and the pressure sensor 23 is electrically connected with the electronic control module 1.

As shown in fig. 7, 8 and 9, two B slots 30 are distributed on the transmission shaft 8; a B clamp 12 is arranged in each B clamping groove 30; the slider tray 13 is held by two B clips 12.

As shown in fig. 7, 8 and 10, two a slots 29 are distributed on the transmission shaft 8; an A clamp 36 is arranged in each A clamp groove 29; the third-stage sun gear 35 is sandwiched on both sides by two a-yokes 36.

The shaft groove 48 of the B column 41 is in a regular inner hexagonal shape, the outer wall of the transmission shaft 8 is in a regular outer hexagonal shape, and the outer wall of the transmission shaft 8 and the inner wall of the shaft groove 48 slide in a surface-to-surface fit manner.

As shown in fig. 5, 7 and 8, a clamping groove 28 is formed at one end of the transmission shaft 8 away from the B-coupling 15; the clamping sleeve 27 is composed of a middle sleeve 50, an outer ring disc 51 and an inner ring disc 52, wherein the outer ring disc 51 is arranged at one end of the middle sleeve 50, and the inner ring disc 52 is arranged at the other end of the middle sleeve 50; the inner ring disc 52 is clamped in the clamping groove 28 of the transmission shaft 8; the outer ring disk 51 is mounted on the side face at the center of the clutch slider 26 by bolts. The design of the clamping sleeve 27 is such that the driving shaft 8 does not drive the clutch slider 26 to rotate through the clamping sleeve 27 when rotating, but the driving shaft 8 can move axially synchronously with the clutch slider 26 through the clamping sleeve 27. When a specific product is processed, the clamping sleeve can be assembled and installed on the transmission shaft by two halves, and can also be installed by other prior art.

As shown in fig. 4, 5 and 6, the clutch 4 is composed of a clutch handle 24, a clutch sleeve 25 and a clutch slider 26; the outer side of the outer shell 49 is rotatably provided with a clutch handle 24, and a clutch shaft sleeve 25 rotatably arranged at the center of the reducer shell 21 is fixedly connected with the clutch handle 24; the clutch shaft sleeve 25 is provided with two symmetrical spiral structures; three support bars 54 which are uniformly distributed on the clutch sliding block 26 in the circumferential direction are respectively slidably mounted in three support sliding grooves 53 which are uniformly distributed in the circumferential direction at the center of the speed reducer casing 21 along the axial direction of the transmission shaft 8, and two spiral structures on the clutch shaft sleeve 25 are matched with the support bars 54 on the clutch sliding block 26 to enable the clutch sliding block 26 to axially move; the axial movement of the clutch slider 26 is controlled by rotating the clutch handle 24 with the clutch sleeve 25 rotating.

As shown in fig. 4, the pressure sensor 23 is mounted on a groove surface of one supporting chute 53 of the reducer case 21, and the supporting bar 54 in the supporting chute 53 in which the pressure sensor 23 is mounted is press-fitted to the pressure sensor 23.

As shown in fig. 3 and 4, a wire slot 22 is provided in the reducer housing 21, one end of the wire slot 22 is communicated with the space of the outer housing 49 where the electronic control module 1 is installed, and the other end is communicated with the place where the pressure sensor 23 is installed; one end of the wire is electrically connected with the pressure sensor 23, and the other end of the wire penetrates through the wire slot 22 to be electrically connected with the electronic control module 1.

The inner diameters of the friction ring A18 and the friction ring B20 are the same; the radial thicknesses of the friction blocks a 32 and B33 are the same.

The clutch handle 24, the clutch sleeve 25 and the clutch slider 26 in the clutch 4 of the present invention are specifically installed by referring to the prior art.

The primary speed reduction assembly 5 consists of a primary sun gear, a primary planet carrier and a primary gear ring, the secondary speed reduction assembly 6 consists of a secondary sun gear, a secondary planet carrier 34 and a secondary gear ring, and the tertiary speed reduction assembly 7 consists of a tertiary sun gear 35, a tertiary planet gear, a tertiary planet carrier and a tertiary gear ring; the transmission shaft 8 drives the second-stage speed reduction assembly 6 to move through the first-stage speed reduction assembly 5, a second-stage planet carrier 34 in the second-stage speed reduction assembly 6 is in transmission fit with a third-stage sun gear 35 in the third-stage speed reduction assembly 7, and the third-stage speed reduction assembly 7 is in transmission connection with the roller 3.

The design of the A notch 40, the B notch 47 and the two ends of the rectangular spring 19 in the invention is as follows: when the rectangular spring 19 is compressed, two ends of the rectangular spring 19 are respectively connected with the arc block A39 and the arc block B46 in a pulling manner, so that the force bearing aspect is better; in addition, the a and

B cutouts

40 and 47 receive the ends of the rectangular spring 19 to facilitate the engagement of the a arc blocks 39 with the corresponding B arc blocks 46. The deformation of the rectangular spring 19 can effectively buffer the impact between the arc block A39 and the arc block B46, and the protection effect is achieved.

In the invention, the A hoop 36 and the third-stage sun gear 35 are in sliding friction fit; the B clamp 12 and the sliding disc 13 are in static friction fit. The starting of the motor 10 in the present invention is controlled by the electronic control module 1 and the pressure sensor 23.

The friction blocks are arranged into the friction block A32 and the friction block B33, and the friction block A32 and the friction block B33 are respectively in friction fit with the friction ring A18 and the friction ring B20: in the actual process of machining the friction ring A18 and the friction ring B20, because machining errors easily cause the inner diameters of the friction ring A18 and the friction ring B20 to be different, the radial thicknesses of the friction block A32 and the friction block B33 do not need to be guaranteed to be very accurate during machining, and the friction block A32 and the friction block B33 can be in good friction fit with the friction ring A18 and the friction ring B20 respectively. If A friction block 32 and B friction block 33 are one integral friction block, although a friction fit with A friction ring 18 and B friction ring 20 could also be achieved; however, once the inner diameters differ due to machining errors in the a friction ring 18 and the B friction ring 20, the friction fit of the integral friction block with the a friction ring 18 and the B friction ring 20 is affected. Therefore, the friction blocks arranged as the a friction block 32 and the B friction block 33 can be suitably processed with less precision.

The specific working process of the invention is as follows: in the initial state where the winch is not in use, the tertiary sun gear 35 meshes with the secondary planet carrier 34; the side surface of the clutch slider 26 is in pressing contact with the pressure sensor 23; the outer diameter of the rectangular spring 19 reaches the maximum, the rectangular spring 19 has thrust on the A friction block 32, so that the A friction block 32 and the A friction ring 18 are in friction braking, and the rectangular spring 19 has thrust on the B friction block 33, so that the B friction block 33 and the B friction ring 20 are in friction braking; the side of arc a 39 abuts the side of arc B46. In this state, the drum 3 on the winch cannot release the wire wound thereon.

When the winch needs to release a stranded rope wound on the winch, the clutch handle 24 is manually rotated, the clutch handle 24 pushes the clutch sliding block 26 to move towards the roller 3 through the clutch shaft sleeve 25, the clutch sliding block 26 pushes the transmission shaft 8 to move towards the motor 10 through the clamping sleeve 27, and the clutch sliding block 26 is separated from the extrusion contact with the pressure sensor 23. The transmission shaft 8 pushes the third-stage sun gear 35 to move synchronously in a clamping manner through the two A clamps 36, the third-stage sun gear 35 is disengaged from the second-stage planet carrier 34, the transmission shaft 8 slides in the shaft groove 48 of the B column 41, and the compression spring 31 is compressed. When the transmission shaft 8 is pushed to the extreme position, the acting force of the clutch handle 24 is removed, and the position of the clutch sliding block 26 is kept still; two B clamps 12 on the transmission shaft 8 push the sliding disc 13 to move synchronously in a clamping mode, the push bar 14 moves synchronously along with the sliding disc 13, during the period, the inclined end of the push bar 14 is in press fit with the inclined surface of the corresponding B friction block 33, the push bar 14 pushes the corresponding B friction block 33 to move towards the center of the B sleeve 43, the corresponding part of the rectangular spring 19 deforms, and the B friction block 33 no longer rubs and brakes with the B friction ring 20. Because the friction block B33 and the friction ring B20 are braked, the third-stage sun gear 35 and the second-stage planet carrier 34 are not meshed any more, so that the power transmission between the transmission shaft 8 and the roller 3 is not existed, the transmission shaft 8 still limits the rotation of the first-stage speed reduction assembly 5 and the second-stage speed reduction assembly 6, the rotation limitation of the third-stage speed reduction assembly 7 and the second-stage speed reduction assembly 6 is removed, and the rotation of the roller 3 is not limited indirectly by the transmission shaft 8 any more. So that the winch rope on the winch can be released.

When it is desired to rewind the released hank onto the drum 3, the clutch handle 24 is rotated in reverse to rotate the clutch sleeve 25 in reverse. When the outer teeth of the third-stage sun gear 35 are opposite to the inner teeth of the second-stage planet carrier 34 at intervals, under the reset action of the compression spring 31, the transmission shaft 8 pushes the clutch sliding block 26 to move towards the direction of the clutch shaft sleeve 25 through the clamping sleeve 27 to reset until the side surface of the clutch sliding block 26 is extruded with the pressure sensor 23 again; during the period, the external teeth of the third-stage sun gear 35 can be rapidly and smoothly inserted into the internal teeth interval of the second-stage planet carrier 34 to realize meshing of the two, the sliding disc 13 and the pushing strip 14 move and reset along with the transmission shaft 8, the pushing strip 14 is separated from the extrusion with the B friction block 33, and the B friction block 33 and the B friction ring 20 rub and brake again under the elastic deformation reset of the rectangular spring 19. When the twisted rope is manually pulled in this state, since the B friction block 33 and the B friction ring 20 are friction-braked again, the third-stage sun gear 35 is engaged with the second-stage planet carrier 34, so that the indirect braking relationship is generated between the roller 3 and the transmission shaft 8 again, and the roller 3 does not rotate, which means that the third-stage sun gear 35 and the second-stage planet carrier 34 are engaged. When the outer teeth of the third-stage sun gear 35 are not opposite to the inner teeth of the second-stage planet carrier 34 at intervals, the side face of the third-stage sun gear 35 is attached to the side face of the second-stage planet carrier 34, the B friction block 33 is still extruded by the push bar 14, and no friction fit exists between the B friction block 33 and the B friction ring 20; the twisted rope is pulled manually to enable the roller 3 to rotate at a certain angle, the roller 3 drives the three-level speed reduction assembly 7 to enable the three-level sun gear 35 to rotate at a certain angle, the outer teeth of the three-level sun gear 35 can rotate in the process of being just opposite to the inner teeth of the second-level planet carrier 34 at intervals, and the process that the three-level sun gear 35 is inserted into the second-level planet carrier 34 and meshed is achieved under the condition is repeated.

When a user forgets to pull the twisted rope and the interval between the outer teeth of the third-stage sun gear 35 and the inner teeth of the second-stage planet carrier 34 is not opposite, the side surface of the third-stage sun gear 35 is attached to the side surface of the second-stage planet carrier 34, the transmission shaft 8 cannot enable the clutch sliding block 26 to move and reset through the clamping sleeve 27, and then the clutch sliding block 26 cannot be extruded with the pressure sensor 23; at this time, the pressure sensor 23 does not receive the pressure signal, and the motor 10 cannot be started when the user starts the motor 10 through the electronic control module 1. In this case, in order to inform the user that the third-stage sun gear 35 and the second-stage planet carrier 34 are not yet engaged, the user is reminded to manually pull the twisted rope to rotate the drum 3 by a certain angle, so that the third-stage sun gear 35 and the second-stage planet carrier 34 can be engaged.

When a user is reminded to operate to enable the third-stage sun gear 35 and the second-stage planet carrier 34 to be meshed, the transmission shaft 8 can drive the clutch sliding block 26 to move and reset through the clamping sleeve 27, and the clutch sliding block 26 and the pressure sensor 23 are extruded again; the pressure sensor 23 receives the pressure signal, and the motor 10 can be started when the user starts the motor 10 through the electronic control module 1.

The shaft of the motor 10 drives the a coupling 16 to rotate, as shown in fig. 15 and 16, the a arc block 39 on the a coupling 16 moves towards the other B arc block 46 until striking fit is generated with the B arc block 46, the rectangular spring 19 is compressed in the process, the outer diameter of the rectangular spring 19 is reduced, and the rectangular spring 19 cannot maintain the friction braking fit of the a friction block 32 and the B friction block 33 with the a friction ring 18 and the B friction ring 20 respectively. When the arc block A39 stirs the arc block B46 to rotate, the coupling A16 and the coupling B15 synchronously rotate, the coupling A16 drives the transmission shaft 8 to rotate through the coupling B15, and the transmission shaft 8 drives the roller 3 to rotate through the first-stage speed reduction assembly 5, the second-stage speed reduction assembly 6 and the third-stage speed reduction assembly 7 to wind the twisted rope.

When the winch operation is stopped according to actual needs, the motor 10 is de-energized. Under the reset force of the rectangular spring 19, the a coupling 16 can rotate reversely relative to the B coupling 15, and the a arc block 39 on the a coupling 16 can move towards the B arc block 46 on the B coupling 15 in the initial state until the side surface of the a arc block 39 is attached to the side surface of the B arc block 46 to return to the initial state. The outer diameter of the rectangular spring 19 returns to the maximum in the initial state, the rectangular spring 19 pushes the friction blocks A32 and B33 to rub and brake with the friction rings A18 and B20, respectively, again, and the roller 3 will not rotate any more.

While the present invention has been described in conjunction with the above embodiments, the present invention is not limited to the above embodiments but is limited only by the appended claims, and those skilled in the art can easily make modifications and variations thereto without departing from the true spirit and scope of the present invention.

Claims

1. An electric capstan device comprises an outer shell, wherein an electric control module is arranged in the upper side of the outer shell, a motor module is arranged in the left end side of the outer shell, a speed reduction module and a clutch are arranged in the right end side of the outer shell, a roller is arranged in the middle of the lower side of the outer shell, a motor in the motor module drives a transmission shaft in the roller to rotate through a braking unit, the transmission shaft drives the roller to rotate through the speed reduction module, and the clutch controls the axial movement of the transmission shaft; the speed reduction module consists of a first-stage speed reduction assembly, a second-stage speed reduction assembly and a third-stage speed reduction assembly; a secondary planet carrier in the secondary speed reduction assembly is matched with a tertiary sun gear in the tertiary speed reduction assembly; the brake unit comprises a coupler A, a coupler B and a rectangular spring;

the method is characterized in that: the braking unit further comprises a friction block A, a friction block B and a sliding disc, wherein the side surface of the disc A of the coupling A is provided with a column A, the outer column surface of the column A is symmetrically provided with two arc blocks A, and one of the arc blocks A is provided with an A notch; one side surface of a B disc of the coupler B is provided with a B column, the other side surface of the B disc is symmetrically provided with two B arc blocks, and one B arc block is provided with a B notch; the outer circular surface of the B disc is provided with a B sleeve, the periphery of the B sleeve is uniformly provided with a plurality of groups of sliding chutes, each group of sliding chutes consists of an A sliding chute and a B sliding chute, and the B sliding chute is positioned between the B disc and the A sliding chute; an arc-shaped A friction block is slidably mounted in each A sliding groove, and an arc-shaped B friction block is slidably mounted in each B sliding groove; one end of the transmission shaft is slidably arranged in a shaft groove of the B column, one end of the compression spring is connected with the end surface of the transmission shaft, which is positioned in the shaft groove, and the other end of the compression spring is connected with the groove surface of the shaft groove; the two arc blocks B are sleeved on the column A and are respectively matched with the two arc blocks A; the A incision and the B incision are opposite in position; one end of a rectangular spring sleeved on the arc block A and the arc block B is fixedly arranged in the notch A of the arc block A, and the other end of the rectangular spring is fixedly arranged in the notch B of the arc block B; a sliding disc is fixedly arranged on the transmission shaft, a plurality of arc-shaped pushing strips are uniformly distributed on the disc surface of the sliding disc close to the B coupling in the circumferential direction, and the pushing strips respectively correspond to the plurality of friction blocks B in position; one end of the push bar, which is far away from the sliding disc, is provided with an inclined plane, the side surface of the B friction block, which corresponds to the push bar, is provided with an inclined plane, and the inclined plane of the push bar is matched with the inclined plane of the corresponding B friction block; the rectangular spring is respectively in friction fit with the inner arc surface of the friction block A and the inner arc surface of the friction block B;

the shell is internally provided with a support, the center of the side surface of the support is provided with a friction ring A, the position of the roller close to the support is fixedly provided with a friction ring B, and the friction ring A corresponds to the friction ring B in position; the outer cambered surface of the friction block A is in friction fit with the friction ring A; the outer cambered surface of the friction block B is in friction fit with the friction ring B;

one end of the transmission shaft, which is far away from the B shaft coupler, is rotatably connected with a clamping sleeve, and the clamping sleeve is fixedly connected with a clutch sliding block in a clutch; a pressure sensor fixedly arranged in the speed reducer shell is matched with the clutch sliding block, and the pressure sensor is electrically connected with the electric control module;

two clamping grooves B are distributed on the transmission shaft; a B clamp is arranged in each B clamp groove; the sliding disc is clamped by the two B hoops;

two A clamping grooves are distributed on the transmission shaft; a clamp A is arranged in each clamp groove A; two sides of the third-stage sun gear are clamped by the two A hoops;

the shaft groove of the B column is in a right-inner hexagonal shape, the outer wall of the transmission shaft is in a right-outer hexagonal shape, and the outer wall of the transmission shaft and the inner wall of the shaft groove slide in a surface-to-surface fit manner;

a clamping groove is formed in one end, far away from the coupler B, of the transmission shaft; the clamping sleeve consists of a middle sleeve, an outer ring disc and an inner ring disc, wherein one end of the middle sleeve is provided with the outer ring disc, and the other end of the middle sleeve is provided with the inner ring disc; the inner ring disc is clamped in the clamping groove of the transmission shaft; the outer ring disc is installed on the side face of the center of the clutch sliding block through a bolt.

2. An electric capstan apparatus according to claim 1, characterized in that: the clutch is composed of a clutch handle, a clutch shaft sleeve and a clutch sliding block; a clutch handle is rotatably arranged on the outer side of the outer shell, and a clutch shaft sleeve rotatably arranged at the center of the reducer shell is fixedly connected with the clutch handle; the clutch shaft sleeve is provided with two symmetrical spiral structures; three support bars which are uniformly distributed on the clutch sliding block in the circumferential direction are respectively arranged in three support sliding chutes which are uniformly distributed in the circumferential direction at the center of the speed reducer shell in a sliding mode along the axial direction of the transmission shaft, and two spiral structures on the clutch shaft sleeve are matched with the support bars on the clutch sliding block to enable the clutch sliding block to axially move; the axial movement of the clutch sliding block is controlled by rotating the clutch handle to drive the clutch shaft sleeve to rotate.

3. An electric winch arrangement according to claim 2, characterized in that: a pressure sensor is arranged on the groove surface in one supporting chute of the speed reducer shell, and a supporting bar in the supporting chute provided with the pressure sensor is in extrusion fit with the pressure sensor.

4. An electric winch arrangement according to claim 3, characterized in that: a wire groove is arranged in the speed reducer shell, one end of the wire groove is communicated with the space of the shell body, which is provided with the electric control module, and the other end of the wire groove is communicated with a place for installing the pressure sensor; one end of the wire is electrically connected with the pressure sensor, and the other end of the wire penetrates through the wire slot to be electrically connected with the electric control module.

5. An electric capstan apparatus according to claim 1, characterized in that: the inner diameters of the friction ring A and the friction ring B are the same; the radial thicknesses of the friction block A and the friction block B are the same.