阅读说明：本技术 一种卷扬机和强夯机 (Winch and dynamic compaction machine ) 是由 张俊强 于 2019-11-12 设计创作，主要内容包括：本发明公开了一种卷扬机和强夯机,包括转轴、卷筒、制动鼓、制动盘、抱刹机构、离合机构、大齿轮,第一轴承、第二轴承；转轴通过第一轴承安装在轴承座上,卷筒通过第二轴承安装在转轴上,制动盘与卷筒左侧连接,制动鼓与卷筒右侧连接；抱刹机构与制动鼓连接,离合机构分别与制动鼓和大齿轮连接,大齿轮与转轴连接；包括一级制动夹钳和二级制动夹钳,一级制动夹钳和二级制动夹钳分别安装在制动盘上。本发明的卷扬机和强夯机可以在非脱钩模式工作,对卷扬机实现多级制动,制动效果好,稳定性、安全性、耐久性强,抗冲击能力高。(The invention discloses a winch and a dynamic compactor, which comprise a rotating shaft, a winding drum, a brake disc, a brake mechanism, a clutch mechanism, a gearwheel, a first bearing and a second bearing, wherein the winding drum is arranged on the rotating shaft; the rotating shaft is arranged on the bearing block through a first bearing, the winding drum is arranged on the rotating shaft through a second bearing, the brake disc is connected with the left side of the winding drum, and the brake drum is connected with the right side of the winding drum; the brake mechanism is connected with the brake drum, the clutch mechanism is respectively connected with the brake drum and the gearwheel, and the gearwheel is connected with the rotating shaft; the brake device comprises a first-stage brake clamp and a second-stage brake clamp, wherein the first-stage brake clamp and the second-stage brake clamp are respectively arranged on a brake disc. The winch and the dynamic compactor can work in a non-unhooking mode, realize multi-stage braking on the winch, and have the advantages of good braking effect, high stability, safety, durability and high impact resistance.)

1. A winch is characterized by comprising a rotating shaft (2), a winding drum (1), a brake drum (3), a brake disc (19), an armful brake mechanism (9), a clutch mechanism (8), a large gear (5), a first bearing and a second bearing (4); the rotating shaft (2) is installed on the bearing seat (6) through a first bearing, the winding drum (1) is installed on the rotating shaft (2) through a second bearing (4), the brake disc (19) is connected with the left side of the winding drum (1), and the brake drum (3) is connected with the right side of the winding drum (1); the brake mechanism (9) is connected with the brake drum (3), the clutch mechanism (8) is respectively connected with the brake drum (3) and the gearwheel (5), and the gearwheel (5) is connected with the rotating shaft (2);

the brake disc brake caliper comprises a first-stage brake caliper (10) and a second-stage brake caliper (11), wherein the first-stage brake caliper (10) and the second-stage brake caliper (11) are respectively installed on a brake disc (19).

2. Hoisting machine as claimed in claim 1, characterized in that the braking force of the primary brake caliper (10) is smaller than the braking force of the secondary brake caliper (11).

3. The hoist as claimed in claim 1, wherein the brake mechanism (9) comprises a bracket (90), a first brake sheet (95), a first brake shoe (96), a brake cylinder (91), and a lever (92); the first brake sheet (95) is arranged on the first brake shoe (96), the first brake shoe (96) tightly holds the outer ring of the brake drum (3), and the first brake sheet (95) is positioned between the outer ring of the brake drum (3) and the first brake shoe (96); one end of a first brake shoe (96) is hinged with the bracket (90), the other end of the first brake shoe (96) is hinged with one end of a lever (92), the lever (92) is hinged with the bracket (90), the other end of the lever (92) is connected with a band-type braking oil cylinder (91), and the band-type braking oil cylinder (91) is arranged on the bracket (90).

4. The hoisting machine according to claim 3, characterized by comprising at least one pull rod (94), a first spring (93) and a first lock nut assembly, wherein the bracket (90) is positioned around the first brake shoe (96), one end of the pull rods (94) is connected with the periphery of the first brake shoe (96), the first lock nut assembly is connected with the pull rod (94), and two ends of the first spring (93) are respectively abutted against the bracket (90) and the first lock nut assembly.

5. The hoisting machine according to claim 3, characterized in that the band-brake cylinder (91) is a double-acting cylinder.

6. The hoist as claimed in claim 1, characterized in that the clutch mechanism (8) comprises a clutch cylinder (82), an elastic device (83), a crank arm (84), a second brake disc (81), and a second brake shoe (80); the second brake sheet (81) is arranged on the second brake shoe (80), the second brake shoe (80) tightly holds the outer ring of the brake drum (3), and the second brake sheet (81) is positioned between the outer ring of the brake drum (3) and the second brake shoe (80); one end of a second brake shoe (80) is hinged with the big gear (5), the other end of the second brake shoe (80) is hinged with the first end of a crank arm (84), the middle of the crank arm (84) is hinged with the big gear (5), two ends of a clutch oil cylinder (82) are hinged with the second end of the crank arm (84) and the big gear (5) respectively, and two ends of an elastic device (83) are hinged with the third end of the crank arm (84) and the big gear (5) respectively.

7. Winch according to claim 6, characterised in that a hydraulic swivel (7) for supplying oil to the clutch cylinder (82) is mounted on the shaft (2).

8. Hoist according to claim 6, characterized in that the clutch cylinder (82) is a single-acting cylinder.

9. Hoisting machine according to any of claims 1-8, characterized by comprising a first hydraulic control valve (14), a second hydraulic control valve (15), a pilot control valve (18), a hydraulic accumulator (13), a first shuttle valve (16), a second shuttle valve (17); the brake mechanism (9) comprises a brake cylinder (91), and the clutch mechanism (8) comprises a clutch cylinder (82);

the port B of the first hydraulic control valve (14) is communicated with the clutch oil cylinder (82), the port B of the second hydraulic control valve (15) is communicated with a rodless cavity of the brake cylinder (91), a rod cavity of the brake cylinder (91) is communicated with the hydraulic energy accumulator (13), and the port P of the first hydraulic control valve (14) and the port P of the second hydraulic control valve (15) are communicated with the hydraulic energy accumulator (13); an O port of the first hydraulic control valve (14) and an O port of the second hydraulic control valve (15) are oil return ports; the port A of the first hydraulic control valve (14) and the port A of the second hydraulic control valve (15) are plugging ports;

in a normal state, the first hydraulic control valve (14) is positioned at a left position, a port P of the first hydraulic control valve (14) is communicated with a port A of the first hydraulic control valve (14), and a port O of the first hydraulic control valve (14) is communicated with a port B of the first hydraulic control valve (14); when the first hydraulic control valve (14) is positioned at the right position, the port P of the first hydraulic control valve (14) is communicated with the port B of the first hydraulic control valve (14), and the port O of the first hydraulic control valve (14) is communicated with the port A of the first hydraulic control valve (14);

in a normal state, the second hydraulic control valve (15) is positioned at a left position, a port P of the second hydraulic control valve (15) is communicated with a port A of the second hydraulic control valve (15), and a port O of the second hydraulic control valve (15) is communicated with a port B of the second hydraulic control valve (15); when the second hydraulic control valve (15) is positioned at the right position, the port P of the second hydraulic control valve (15) is communicated with the port B of the second hydraulic control valve (15), and the port O of the second hydraulic control valve (15) is communicated with the port A of the second hydraulic control valve (15).

A control port of the second hydraulic control valve (15) is communicated with an output port of the first shuttle valve (16), a control port of the first hydraulic control valve (14) is communicated with a first input port of the first shuttle valve (16), a second input port of the first shuttle valve (16) is communicated with an output port of the second shuttle valve (17), a first input port of the second shuttle valve (17) is communicated with a port B of the pilot control valve (18), and a control port of the first hydraulic control valve (14) is communicated with a port A of the pilot control valve (18);

the pilot control valve (18) is a three-position four-way valve, the middle position of the pilot control valve (18) is a Y position function, when the pilot control valve (18) is positioned at the left position, a P port of the pilot control valve (18) is communicated with an A port of the pilot control valve (18), and an O port of the pilot control valve (18) is communicated with a B port of the pilot control valve (18); when the pilot control valve (18) is positioned at the right position, a port P of the pilot control valve (18) is communicated with a port B of the pilot control valve (18), and a port O of the pilot control valve (18) is communicated with a port A of the pilot control valve (18); the O port of the pilot control valve (18) is an oil return port.

10. A dynamic compaction machine comprising a hoisting machine according to any one of claims 1 to 9.

Technical Field

The invention relates to the field of machinery, in particular to a winch and a dynamic compactor.

Background

The dynamic compactor uses a winch to repeatedly and vertically lift a rammer, and uses high impact generated by the high fall of the rammer to tamp the foundation. The tamping energy of the dynamic compactor is the height of the falling distance x the weight of the rammer, for example: the weight of the rammer is 30T, the drop height is 15m, and the ramming energy is 30 multiplied by 15 to 450KN. The drop height refers to the free drop height of the ram. The working mode of the dynamic compactor comprises a unhooking mode and a non-unhooking mode, wherein the unhooking mode refers to the mode that a unhooking device is connected to a hoisting steel wire rope of the dynamic compactor, the unhooking device hooks a rammer to the height of a falling distance (namely a ramming state), the unhooking device releases the rammer (namely a ramming state), the rammer falls freely, and the unhooking device does not fall along with the rammer. The unhooking mode is that a hoisting steel wire rope of the dynamic compactor is directly connected with a rammer, after the rammer is lifted to a falling distance height (namely, in a rammer lifting state), a brake mechanism and a clutch mechanism of the winch are loosened, the rammer falls freely (namely, in a rammer releasing state), and the winch rotates reversely under the pulling force of the rammer. Because the unhooking mode is ramming the in-process at every turn, all need transfer jack-up wire rope and detacher and rammer couple the action, cause the work efficiency of unhooking mode very low, non-unhooking mode is ramming the in-process at every turn, need not transfer jack-up wire rope and couple the action, consequently, the work efficiency of non-unhooking mode is higher than the work efficiency of unhooking mode far away.

At present, current dynamic compactor can only work under unhook mode, can not work under non-unhook mode, because when non-unhook mode, the hoist engine reverses under the pulling force of ram, the ram falling speed of free fall is very fast, make hoist engine reverse speed very high, it is very big to the hoist engine impact force, cause the hoist engine to damage easily, in addition, after the ramming, the ram lands, the hoist engine is under inertial effect, the hoist engine chance continues to rotate, the jack-up wire rope play rope volume that causes the hoist engine can be many, next ramming of influence. Therefore, before the rammer is not landed, the speed is reduced, the descending speed of the rammer is controlled, the braking distance of secondary braking is reduced, and when the rammer is landed, the winch needs to be fully braked, so that the rope outlet amount of a hoisting steel wire rope of the winch is reduced. Because the existing dynamic compactor only comprises a brake mechanism, the functions cannot be realized. Therefore, a new braking system and a new winch need to be developed, and the dynamic compactor can work in a non-unhooking mode.

Disclosure of Invention

In view of the above, the invention provides a winch and a dynamic compactor, which can work in a non-unhooking mode, realize multi-stage braking on the winch, and have the advantages of good braking effect, high stability, safety, durability and high impact resistance.

On one hand, the invention provides a winch, which comprises a rotating shaft, a winding drum, a brake disc, a brake mechanism, a clutch mechanism, a gearwheel, a first bearing and a second bearing, wherein the winding drum is arranged on the rotating shaft; the rotating shaft is arranged on the bearing block through a first bearing, the winding drum is arranged on the rotating shaft through a second bearing, the brake disc is connected with the left side of the winding drum, and the brake drum is connected with the right side of the winding drum; the brake mechanism is connected with the brake drum, the clutch mechanism is respectively connected with the brake drum and the gearwheel, and the gearwheel is connected with the rotating shaft; the brake device comprises a first-stage brake clamp and a second-stage brake clamp, wherein the first-stage brake clamp and the second-stage brake clamp are respectively arranged on a brake disc.

Further, the braking force of the primary brake caliper is smaller than that of the secondary brake caliper.

Further, the brake mechanism comprises a bracket, a first brake sheet, a first brake shoe, a brake cylinder and a lever; the first brake disc is arranged on the first brake shoe, the first brake shoe tightly holds the outer ring of the brake drum, and the first brake disc is positioned between the outer ring of the brake drum and the first brake shoe; one end of the first brake shoe is hinged with the bracket, the other end of the first brake shoe is hinged with one end of a lever, the lever is hinged with the bracket, the other end of the lever is connected with a band-type braking oil cylinder, and the band-type braking oil cylinder is arranged on the bracket.

Further, including at least one pull rod, first spring, first lock nut component, the support is located first brake shoe all around, and a plurality of pull rod one end are connected all around with first brake shoe, and first lock nut component is connected with the pull rod, and the first spring both ends are supported respectively and are leaned on support and first lock nut component.

Furthermore, the brake cylinder is a double-acting cylinder.

Furthermore, the clutch mechanism comprises a clutch oil cylinder, an elastic device, a crank arm, a second brake disc and a second brake shoe; the second brake disc is arranged on the second brake shoe, the second brake shoe tightly holds the outer ring of the brake drum, and the second brake disc is positioned between the outer ring of the brake drum and the second brake shoe; one end of the second brake shoe is hinged with the big gear, the other end of the second brake shoe is hinged with the first end of the crank arm, the middle of the crank arm is hinged with the big gear, two ends of the clutch oil cylinder are respectively hinged with the second end of the crank arm and the big gear, and two ends of the elastic device are respectively hinged with the third end of the crank arm and the big gear.

Furthermore, a hydraulic rotary joint for supplying oil to the clutch oil cylinder is mounted on the rotating shaft.

Furthermore, the clutch oil cylinder is a single-acting oil cylinder.

The hydraulic control system further comprises a first hydraulic control valve, a second hydraulic control valve, a pilot control valve, a hydraulic accumulator, a first shuttle valve and a second shuttle valve; the brake mechanism comprises a brake cylinder, and the clutch mechanism comprises a clutch cylinder;

the port B of the first hydraulic control valve is communicated with the clutch oil cylinder, the port B of the second hydraulic control valve is communicated with the rodless cavity of the brake oil cylinder, the rod cavity of the brake oil cylinder is communicated with the hydraulic energy accumulator, and the port P of the first hydraulic control valve and the port P of the second hydraulic control valve are communicated with the hydraulic energy accumulator; an O port of the first hydraulic control valve and an O port of the second hydraulic control valve are oil return ports; the port A of the first hydraulic control valve and the port A of the second hydraulic control valve are plugging ports;

in a normal state, the first hydraulic control valve is positioned at a left position, a port P of the first hydraulic control valve is communicated with a port A of the first hydraulic control valve, and a port O of the first hydraulic control valve is communicated with a port B of the first hydraulic control valve; when the first hydraulic control valve is positioned at the right position, the port P of the first hydraulic control valve is communicated with the port B of the first hydraulic control valve, and the port O of the first hydraulic control valve is communicated with the port A of the first hydraulic control valve;

in a normal state, the second hydraulic control valve is positioned at a left position, a port P of the second hydraulic control valve is communicated with a port A of the second hydraulic control valve, and a port O of the second hydraulic control valve is communicated with a port B of the second hydraulic control valve; when the second hydraulic control valve is positioned at the right position, the port P of the second hydraulic control valve is communicated with the port B of the second hydraulic control valve, and the port O of the second hydraulic control valve is communicated with the port A of the second hydraulic control valve.

A control port of the second hydraulic control valve is communicated with an output port of the first shuttle valve, a control port of the first hydraulic control valve is communicated with a first input port of the first shuttle valve, a second input port of the first shuttle valve is communicated with an output port of the second shuttle valve, a first input port of the second shuttle valve is communicated with a port B of the pilot control valve, and a control port of the first hydraulic control valve is communicated with a port A of the pilot control valve;

the pilot control valve is a three-position four-way valve, the middle position of the pilot control valve is a Y position function, when the pilot control valve is positioned at the left position, a P port of the pilot control valve is communicated with an A port of the pilot control valve, and an O port of the pilot control valve is communicated with a B port of the pilot control valve; when the pilot control valve is positioned at the right position, the port P of the pilot control valve is communicated with the port B of the pilot control valve, and the port O of the pilot control valve is communicated with the port A of the pilot control valve; the O port of the pilot control valve is an oil return port.

In addition, the invention also provides a dynamic compaction machine which comprises the winch.

Compared with the prior art, the winch and the dynamic compactor have the beneficial effects that:

1. the dynamic compactor can work in a non-unhooking mode, the primary braking clamp and the secondary braking clamp are respectively arranged on the brake disc, multi-stage braking can be realized, the braking effect is good, the descending of the rammer is decelerated, the descending speed of the rammer is controlled, and the braking requirement of the dynamic compactor in the non-unhooking mode is met.

2. The left side and the right side of the winch are provided with a brake drum and brake discs, and a brake mechanism on the brake drum is mainly used for braking after the rammer is lifted to a preset height and is matched with a clutch mechanism to realize hooking and unhooking work in a non-unhooking mode. The first-stage brake clamp and the second-stage brake clamp of the brake disc realize deceleration braking and high-altitude braking in the descending process of the rammer. Therefore, different functions of the brake mechanism, the primary brake clamp and the secondary brake clamp are realized, the respective advantages of drum brake and disc brake are fully utilized, the brake efficiency is improved, and the brake effect is good. In addition, the brake drum and the brake disc are arranged left and right, and the first bearing and the second bearing are stressed in a left-right balance mode.

2. When the clutch mechanism is closed, the large gear and the winding drum are connected into a whole, and the winding drum bears the positive rotation torque. When the clutch mechanism is opened, the large gear is separated from the winding drum, the rammer freely descends to drive the winding drum to rotate reversely at a high speed, and the winding drum bears the impact of the counter torque.

3. The brake mechanism and the clutch mechanism have the advantages of ingenious structure, good stability and good safety.

4. According to the invention, the linkage of the clutch oil cylinder and the brake oil cylinder is realized through the first shuttle valve and the pilot control valve, when the pilot control valve is in the left position, the clutch mechanism is closed, the brake mechanism is opened, and the hook lifting action is realized. When the pilot control valve is in the right position, the clutch mechanism is opened, the brake mechanism is opened, and the unhooking free-fall body lowering action is realized. When the pilot control valve is in the middle position, the clutch mechanism is opened, the brake mechanism is closed, and the air start-stop action is realized. In addition, the clutch oil cylinder and the brake oil cylinder are supplied with oil through the hydraulic energy accumulator, the brake oil cylinder adopts a double-acting oil cylinder, and under a normal state, a rod cavity of the brake oil cylinder is supplied with oil through the hydraulic energy accumulator, so that the brake mechanism is in a normal brake state. The clutch oil cylinder and the brake oil cylinder control hydraulic oil circuit is ingenious in structure and good in stability and safety.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:

fig. 1 is a schematic structural view of a hoist according to the present invention;

FIG. 2 is a schematic structural view of the clutch mechanism of FIG. 1;

FIG. 3 is a schematic structural view of the brake mechanism of FIG. 1;

fig. 4 is a schematic diagram of the hydraulic circuit of the present invention.

Detailed Description

It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.

As shown in fig. 1, the present invention provides a hoisting machine, which comprises a rotating shaft 2, a winding drum 1, a brake drum 3, a brake disc 19, a brake mechanism 9, a clutch mechanism 8, a gearwheel 5, a first bearing (not shown in the figure) and a second bearing 4; the rotating shaft 2 is arranged on the bearing block 6 through a first bearing, the winding drum 1 is arranged on the rotating shaft 2 through a second bearing 4, the brake disc 19 is connected with the left side of the winding drum 1, and the brake drum 3 is connected with the right side of the winding drum 1; the brake mechanism 9 is connected with the brake drum 3, the clutch mechanism 8 is respectively connected with the brake drum 3 and the gearwheel 5, and the gearwheel 5 is connected with the rotating shaft 2. As shown in fig. 2, the pinion gear 12 drives the bull gear 5 to rotate.

In order to control the descending speed of the rammer, the rammer is decelerated and braked in the descending process of the rammer so as to meet the requirement of multi-stage deceleration and braking of the dynamic compactor in a non-unhooking mode, the dynamic compactor further comprises a first-stage braking clamp 10 and a second-stage braking clamp 11, and the first-stage braking clamp 10 and the second-stage braking clamp 11 are respectively installed on a brake disc 19. The braking force of the first-stage braking clamp 10 is smaller than that of the second-stage braking clamp 11, the first-stage braking clamp 10 realizes first-stage braking, and the second-stage braking clamp 11 realizes second-stage braking. Under the non-unhooking mode of the dynamic compaction machine, before the rammer is not grounded, namely the rammer falls freely to the front of a ramming pit, the primary braking clamp 10 performs primary braking on the winch, so that the speed reduction braking of the winch is realized, and the winch cannot be locked. When the rammer lands, namely the rammer falls freely to the ramming pit, the secondary braking clamp 11 performs secondary braking on the winch to lock the winch. Thereby realizing multi-stage braking and having good braking effect.

In the non-unhooking mode, when the clutch mechanism 8 is closed, the large gear 5 and the winding drum 1 are connected into a whole, and the winding drum 1 bears forward rotation torque. When the clutch mechanism 8 is opened, the large gear 5 is separated from the winding drum 1, the rammer freely descends to drive the winding drum 1 to rotate reversely at a high speed, and the winding drum 1 bears the impact of the torque.

The left side and the right side of the winch are provided with the brake drum 3 and the brake disc 19, the respective advantages of drum braking and disc braking are fully utilized, and the braking efficiency is improved and the braking effect is good. In addition, the brake drum 3 and the brake disc 19 are arranged left and right, and the first bearing and the second bearing 4 are balanced in left and right force.

As shown in fig. 3, in a further technical scheme, the invention improves the brake mechanism 9, and improves the braking effect and the braking efficiency of the brake mechanism 9. The brake mechanism 9 comprises a bracket 90, a first brake sheet 95, a first brake shoe 96, a brake cylinder 91 and a lever 92; the brake cylinder 91 is a double-acting cylinder. The first brake sheet 95 is mounted on the first brake shoe 96, the first brake shoe 96 tightly holds the outer ring of the brake drum 3, and the first brake sheet 95 is positioned between the outer ring of the brake drum 3 and the first brake shoe 96; one end of the first brake shoe 96 is hinged with the bracket 90, the other end of the first brake shoe 96 is hinged with one end of a lever 92, the lever 92 is hinged with the bracket 90, the other end of the lever 92 is connected with the band-type brake cylinder 91, and the band-type brake cylinder 91 is arranged on the bracket 90. The support 90 is located around the first brake shoe 96, one end of the plurality of pull rods 94 is connected around the first brake shoe 96, the first lock nut assembly (not shown) is connected with the pull rods 94, and two ends of the first spring 93 are respectively abutted against the support 90 and the first lock nut assembly.

The brake mechanism 9 of the invention adopts a double-acting oil cylinder, and in a normal state, the rod cavity of the brake oil cylinder 91 is supplied with oil and maintained pressure through the hydraulic accumulator 13 and the brake mechanism 9 is in a closed state, namely a braking state under the action of the first spring 93. When the second hydraulic control valve 15 is supplied with pilot oil, the rod chamber of the brake cylinder 91 is communicated with the rodless chamber of the brake cylinder 91, the flow of hydraulic oil entering the rodless chamber of the brake cylinder 91 is increased under the action of the difference in the action areas of the rod chamber and the rodless chamber of the brake cylinder 91, the piston rod of the brake cylinder 91 rapidly extends out to push the first brake shoe 96 to release the brake drum 3, and the brake mechanism 9 is in an open state, i.e., a non-braking state.

As shown in figure 3, in a further technical scheme, the clutch mechanism 8 is improved, and the clutch mechanism 8 is ingenious in structure and good in performance. The clutch mechanism 8 comprises a clutch oil cylinder 82, an elastic device 83, a crank arm 84, a second brake disc 81 and a second brake shoe 80; the second brake sheet 81 is arranged on the second brake shoe 80, the second brake shoe 80 tightly holds the outer ring of the brake drum 3, and the second brake sheet 81 is positioned between the outer ring of the brake drum 3 and the second brake shoe 80; one end of the second brake shoe 80 is hinged with the big gear 5, the other end of the second brake shoe 80 is hinged with the first end of the crank arm 84, the middle of the crank arm 84 is hinged with the big gear 5, two ends of the clutch cylinder 82 are respectively hinged with the second end of the crank arm 84 and the big gear 5, and two ends of the elastic device 83 are respectively hinged with the third end of the crank arm 84 and the big gear 5. A hydraulic rotary joint 7 for supplying oil to the clutch cylinder 82 is attached to the rotary shaft 2.

The clutch cylinder 82 of the present invention is a single-acting cylinder and the elastic means 83 is a spring cylinder. In a normal state, under the action of the elastic device 83, the second brake shoe 80 is pushed by the crank arm 84 to release the brake drum 3, and the clutch mechanism 8 is in an open state, i.e. the bull gear 5 is separated from the brake drum 3. When the first hydraulic control valve 14 is supplied with pilot oil, the rodless cavity of the clutch cylinder 82 is communicated with the hydraulic accumulator 13, the piston rod of the clutch cylinder 82 rapidly extends out to overcome the acting force of the elastic device 83 to push the second brake shoe 80 to tightly hold the brake drum 3, and the clutch mechanism 8 is in a closed state, namely the bull gear 5 is engaged with the brake drum 3.

In a further embodiment, as shown in fig. 4, in the non-unhooking mode, the clutch cylinder 82 and the brake cylinder 91 are linked. Comprises a first hydraulic control valve 14, a second hydraulic control valve 15, a pilot control valve 18, a hydraulic accumulator 13, a first shuttle valve 16 and a second shuttle valve 17; the brake mechanism 9 comprises a brake cylinder 91, and the clutch mechanism 8 comprises a clutch cylinder 82;

the port B of the first hydraulic control valve 14 is communicated with the clutch oil cylinder 82, the port B of the second hydraulic control valve 15 is communicated with the rodless cavity of the band-type brake oil cylinder 91, the rod cavity of the band-type brake oil cylinder 91 is communicated with the hydraulic energy accumulator 13, and the port P of the first hydraulic control valve 14 and the port P of the second hydraulic control valve 15 are communicated with the hydraulic energy accumulator 13; the O port of the first hydraulic control valve 14 and the O port of the second hydraulic control valve 15 are oil return ports; the port a of the first hydraulic control valve 14 and the port a of the second hydraulic control valve 15 are plugging ports;

in a normal state, the first hydraulic control valve 14 is located at the left position, the port P of the first hydraulic control valve 14 communicates with the port a of the first hydraulic control valve 14, and the port O of the first hydraulic control valve 14 communicates with the port B of the first hydraulic control valve 14; when the first hydraulic control valve 14 is positioned at the right position, the port P of the first hydraulic control valve 14 communicates with the port B of the first hydraulic control valve 14, and the port O of the first hydraulic control valve 14 communicates with the port a of the first hydraulic control valve 14;

in a normal state, the second hydraulic control valve 15 is located at a left position, a port P of the second hydraulic control valve 15 is communicated with a port a of the second hydraulic control valve 15, and a port O of the second hydraulic control valve 15 is communicated with a port B of the second hydraulic control valve 15; when the second hydraulic control valve 15 is positioned at the right position, the port P of the second hydraulic control valve 15 communicates with the port B of the second hydraulic control valve 15, and the port O of the second hydraulic control valve 15 communicates with the port a of the second hydraulic control valve 15.

A control port of the second hydraulic control valve 15 is communicated with an output port of the first shuttle valve 16, a control port of the first hydraulic control valve 14 is communicated with a first input port of the first shuttle valve 16, a second input port of the first shuttle valve 16 is communicated with an output port of the second shuttle valve 17, a first input port of the second shuttle valve 17 is communicated with a port B of the pilot control valve 18, and a control port of the first hydraulic control valve 14 is communicated with a port A of the pilot control valve 18;

the pilot control valve 18 is a three-position four-way valve, the middle position of the pilot control valve 18 is a Y position function, when the pilot control valve 18 is positioned at the left position, a P port of the pilot control valve 18 is communicated with a port A of the pilot control valve 18, and an O port of the pilot control valve 18 is communicated with a port B of the pilot control valve 18; when the pilot control valve 18 is positioned at the right position, the port P of the pilot control valve 18 communicates with the port B of the pilot control valve 18, and the port O of the pilot control valve 18 communicates with the port a of the pilot control valve 18; the O port of the pilot control valve 18 is an oil return port.

When the pilot control valve 18 is in the left position, the clutch mechanism 8 is closed, and the brake mechanism 9 is opened (i.e. in a non-braking state), so that the hook-lifting action is realized. When the pilot control valve 18 is in the right position, the clutch mechanism 8 is separated, the brake mechanism 9 is opened (i.e. in a non-braking state), and the unhooking free-falling body lowering action is realized. When the pilot control valve 18 is in the middle position, the clutch mechanism 8 is separated, the brake mechanism 9 is closed (i.e. in a braking state), and the air start-stop action is realized, and the clutch oil cylinder 82 and the brake oil cylinder 91 control the hydraulic oil path to have ingenious structure and good stability and safety.

The techniques not described above are common general knowledge of the skilled person. The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.