CN110775848B - Winch and dynamic compactor - Google Patents
Winch and dynamic compactor Download PDFInfo
- Publication number
- CN110775848B CN110775848B CN201911103262.XA CN201911103262A CN110775848B CN 110775848 B CN110775848 B CN 110775848B CN 201911103262 A CN201911103262 A CN 201911103262A CN 110775848 B CN110775848 B CN 110775848B
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- control valve
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- brake
- hydraulic control
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- 230000007246 mechanism Effects 0.000 claims abstract description 64
- 238000004804 winding Methods 0.000 claims abstract description 24
- 230000000694 effects Effects 0.000 abstract description 7
- 239000003921 oil Substances 0.000 description 49
- 230000009471 action Effects 0.000 description 11
- 238000000034 method Methods 0.000 description 7
- 229910000831 Steel Inorganic materials 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 239000010959 steel Substances 0.000 description 6
- 239000010720 hydraulic oil Substances 0.000 description 4
- 230000009467 reduction Effects 0.000 description 3
- 238000005056 compaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 244000309464 bull Species 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/14—Power transmissions between power sources and drums or barrels
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
- B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
- B66D5/06—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with radial effect
- B66D5/08—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with radial effect embodying blocks or shoes
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
- B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
- B66D5/12—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect
- B66D5/14—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect embodying discs
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
- E02D3/02—Improving by compacting
- E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/088—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members being distinctly separate from the axis of rotation
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Structural Engineering (AREA)
- Soil Sciences (AREA)
- Environmental & Geological Engineering (AREA)
- Agronomy & Crop Science (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Mining & Mineral Resources (AREA)
- Paleontology (AREA)
- Civil Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
The invention discloses a winch and a dynamic compactor, which comprises a rotating shaft, a winding drum, a brake disc, a braking mechanism, a clutch mechanism, a large gear, a first bearing and a second bearing, wherein the first bearing is provided with a first bearing and a second bearing; the rotating shaft is arranged on the bearing seat 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 braking mechanism is connected with the brake drum, the clutch mechanism is respectively connected with the brake drum and the large gear, and the large gear is connected with the rotating shaft; the brake system comprises a primary brake clamp and a secondary brake clamp, wherein the primary brake clamp and the secondary 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 good braking effect, high stability, safety, durability and high impact resistance.
Description
Technical Field
The invention relates to the field of machinery, in particular to a winch and a dynamic compactor.
Background
The dynamic compactor repeatedly and vertically lifts the rammer by using a winch, and compacts the foundation by using high impact generated by the height difference of the rammer. Ramming energy = drop height x ram weight of dynamic compactor, for example: ram weight 30T, drop height 15m, ram energy = 30 x 15 = 450kn.m. The drop height refers to the free fall height of the ram. The working modes of the dynamic compactor comprise a unhooking mode and a non-unhooking mode, wherein the unhooking mode refers to that a unhooking device is connected to a lifting steel wire rope of the dynamic compactor, and after the unhooking device hooks the rammer to the falling distance height (namely, the lifting state is adopted), the unhooking device releases the rammer (namely, the discharging state is adopted), the rammer freely falls, and the unhooking device does not fall along with the rammer. The non-unhooking mode refers to that a lifting steel wire rope of the dynamic compactor is directly connected with the rammer, the rammer is lifted to the fall distance height (namely, the state of lifting the rammer), a brake mechanism and a clutch mechanism of the winch are loosened, the rammer falls freely (namely, the state of releasing the rammer), and the winch is reversed under the pulling force of the rammer. The unhooking mode has very low working efficiency because the lifting steel wire rope and the unhooking device need to be lowered to act with the rammer hook in each ramming process, and the unhooking mode does not need to be lowered to act with the lifting steel wire rope and the hook in each ramming process, so that the working efficiency of the unhooking mode is far higher than that of the unhooking mode.
At present, the existing dynamic compactor can only work in a unhooking mode and cannot work in a non-unhooking mode, because in the non-unhooking mode, the winch reverses under the tension of the rammer, the descending speed of the free falling rammer is very high, the reversing speed of the winch is very high, the impact force to the winch is very high, the winch is easy to damage, in addition, after the compaction is finished, the rammer is grounded, the winch continuously rotates under the action of inertia, so that the rope outlet amount of a hoisting steel wire rope of the winch can be quite large, and the next compaction is influenced. Therefore, the reduction of the speed is required before the ram is not grounded, the descending speed of the ram is controlled, the braking distance of the secondary braking is reduced, and when the ram is grounded, the winch needs to be fully braked, so that the rope outlet amount of the hoisting steel wire rope of the winch is reduced. The existing dynamic compactor only comprises a brake mechanism, so that the functions cannot be realized. Therefore, there is a need to develop new braking systems and winches that meet the dynamic compactor operating 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 good braking effect, high stability, safety, durability and high impact resistance.
In one aspect, the invention provides a winch, which comprises a rotating shaft, a winding drum, a brake disc, a brake mechanism, a clutch mechanism, a large gear, a first bearing and a second bearing; the rotating shaft is arranged on the bearing seat 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 braking mechanism is connected with the brake drum, the clutch mechanism is respectively connected with the brake drum and the large gear, and the large gear is connected with the rotating shaft; the brake system comprises a primary brake clamp and a secondary brake clamp, wherein the primary brake clamp and the secondary brake clamp are respectively arranged on a brake disc.
Further, the braking force of the primary brake caliper is smaller than the braking force of the secondary brake caliper.
Further, the braking mechanism comprises a bracket, a first braking sheet, a first brake shoe, a braking cylinder and a lever; the first brake-holding sheet is arranged on the first brake shoe, the first brake shoe holds the outer ring of the brake drum tightly, and the first brake-holding sheet 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 the lever, the lever is hinged with the bracket, the other end of the lever is connected with the brake-holding oil cylinder, and the brake-holding oil cylinder is arranged on the bracket.
Further, including at least one pull rod, first spring, first lock nut subassembly, the support is located first brake shoe all around, and a plurality of pull rod one ends are connected all around with first brake shoe, and first lock nut subassembly is connected with the pull rod, and first spring both ends are supported respectively and are leaned on support and first lock nut subassembly.
Further, the brake oil cylinder is a double-acting oil cylinder.
Further, the clutch mechanism comprises a clutch oil cylinder, an elastic device, a crank arm, a second brake pad and a second brake shoe; the second brake-holding sheet is arranged on the second brake shoe, the second brake shoe holds the outer ring of the brake drum tightly, and the second brake-holding sheet 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 gear wheel, 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 gear wheel, two ends of the clutch oil cylinder are respectively hinged with the second end of the crank arm and the gear wheel, and two ends of the elastic device are respectively hinged with the third end of the crank arm and the gear wheel.
Further, a hydraulic rotary joint for supplying oil to the clutch cylinder is installed on the rotating shaft.
Further, the clutch oil cylinder is a single-acting oil cylinder.
Further, the hydraulic control system 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 braking mechanism comprises a braking 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 a rodless cavity of the brake oil cylinder, a rod cavity of the brake oil cylinder is communicated with the hydraulic 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 accumulator; the O port of the first hydraulic control valve and the 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 the left position, the P port of the first hydraulic control valve is communicated with the A port of the first hydraulic control valve, and the O port of the first hydraulic control valve is communicated with the B port of the first hydraulic control valve; when the first hydraulic control valve is positioned at the right position, the P port of the first hydraulic control valve is communicated with the B port of the first hydraulic control valve, and the O port of the first hydraulic control valve is communicated with the A port of the first hydraulic control valve;
in a normal state, the second hydraulic control valve is positioned at the left position, the P port of the second hydraulic control valve is communicated with the A port of the second hydraulic control valve, and the O port of the second hydraulic control valve is communicated with the B port of the second hydraulic control valve; when the second hydraulic control valve is positioned at the right position, the P port of the second hydraulic control valve is communicated with the B port of the second hydraulic control valve, and the O port of the second hydraulic control valve is communicated with the A port of the second hydraulic control valve.
The control port of the second hydraulic control valve is communicated with the output port of the first shuttle valve, the control port of the first hydraulic control valve is communicated with the first input port of the first shuttle valve, the second input port of the first shuttle valve is communicated with the output port of the second shuttle valve, the first input port of the second shuttle valve is communicated with the port B of the pilot control valve, and the control port of the first hydraulic control valve is communicated with the 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, the P port of the pilot control valve is communicated with the A port of the pilot control valve, and the O port of the pilot control valve is communicated with the B port of the pilot control valve; when the pilot control valve is positioned at the right position, the P port of the pilot control valve is communicated with the B port of the pilot control valve, and the O port of the pilot control valve is communicated with the A port 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 compactor, which comprises the winch.
Compared with the prior art, the winch and the dynamic compactor have the beneficial effects that:
1. the invention can work in a non-unhooking mode, the primary braking clamp and the secondary braking clamp are respectively arranged on the braking 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 respectively provided with a brake drum and a brake disc, and a brake-holding mechanism on the brake drums is mainly used for braking after the rammer is lifted to a preset height and is matched with a clutch mechanism to realize the hooking and unhooking work in a non-unhooking mode. The primary braking clamp and the secondary braking clamp of the brake disc realize deceleration braking and high-altitude braking in the descending process of the rammer. Therefore, the braking mechanism, the primary braking clamp and the secondary braking clamp realize different functions, the respective advantages of the drum brake and the disc brake are fully utilized, and the braking efficiency and the braking effect are improved. In addition, the brake drum and the brake disc are arranged left and right, and the first bearing and the second bearing are balanced in left and right stress.
2. When the clutch mechanism is closed, the large gear is connected with the winding drum into a whole, and the winding drum bears the forward rotation moment. 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 high speed, the winding drum bears the impact of the counter torque, in the process, the rotating shaft basically does not bear the positive and negative rotation torque, the stress of the rotating shaft is improved, and the stability, the safety and the durability of the winch are improved.
3. The braking mechanism and the clutch mechanism have smart structure, good stability and safety.
4. According to the invention, the clutch oil cylinder and the brake oil cylinder are linked through the first shuttle valve and the pilot control valve, when the pilot control valve is at the left position, the clutch mechanism is closed, and the brake mechanism is opened, so that the lifting action of the hook is realized. When the pilot control valve is in the right position, the clutch mechanism is opened, the brake mechanism is opened, and unhooking free falling body descending 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 in 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 have smart structure for controlling the hydraulic oil circuit, and good stability and safety.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
FIG. 1 is a schematic view of a hoist according to the present invention;
FIG. 2 is a schematic diagram of the clutch mechanism of FIG. 1;
FIG. 3 is a schematic view of the brake mechanism of FIG. 1;
fig. 4 is a schematic diagram of the hydraulic oil circuit principle of the present invention.
Detailed Description
It should be noted that, without conflict, the embodiments of the present invention and features of the embodiments may be combined with each other. The invention will be described in detail below with reference to the drawings in connection with embodiments.
As shown in fig. 1, the invention provides a winch, 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 large gear 5, a first bearing (not shown in the figure) and a second bearing 4; the rotating shaft 2 is arranged on the bearing seat 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 braking mechanism 9 is connected with the brake drum 3, the clutch mechanism 8 is respectively connected with the brake drum 3 and the large gear 5, and the large gear 5 is connected with the rotating shaft 2. As shown in fig. 2, the pinion 12 drives the large gear 5 to rotate.
In order to control the descending speed of the rammer, the multi-stage speed reduction braking requirement of the dynamic compactor in a non-unhooking mode is met in the speed reduction braking process of the rammer, the hydraulic dynamic compactor further comprises a primary braking clamp 10 and a secondary braking clamp 11, and the primary braking clamp 10 and the secondary braking clamp 11 are respectively arranged on a braking disc 19. The braking force of the primary braking clamp 10 is smaller than that of the secondary braking clamp 11, the primary braking clamp 10 realizes primary braking, and the secondary braking clamp 11 realizes secondary braking. In the non-unhooking mode of the dynamic compactor, before the rammer is not landed, namely before the rammer freely falls into a rammer pit, the primary braking clamp 10 carries out primary braking on the winch, so that the winch is braked slowly, and the winch is not locked. When the rammer lands, namely, after the rammer freely falls into the rammer 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 gearwheel 5 is integrally connected with the spool 1, the spool 1 assuming a positive rotational moment. 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 high speed, the winding drum 1 bears the impact of the counter torque, in the process, the rotating shaft 2 basically does not bear the positive and negative rotation torque, the stress of the rotating shaft 2 is improved, and the stability, the safety and the durability of the winch are improved.
The brake drum 3 and the brake disc 19 are arranged on the left side and the right side of the winch, the advantages of the drum brake and the disc brake are fully utilized, and the braking efficiency and the braking effect are improved. In addition, the brake drum 3 and the brake disc 19 are arranged right and left, and the first bearing and the second bearing 4 are balanced in force.
As shown in fig. 3, in a further technical scheme, the invention improves the braking mechanism 9 and improves the braking effect and the braking efficiency of the braking mechanism 9. The brake mechanism 9 comprises a bracket 90, a first brake pad 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-holding sheet 95 is arranged on the first brake shoe 96, the first brake shoe 96 holds the outer ring of the brake drum 3 tightly, and the first brake-holding 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 brake oil cylinder 91, and the brake oil cylinder 91 is arranged on the bracket 90. The bracket 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, a first lock nut assembly (not shown) is connected with the pull rods 94, and two ends of the first spring 93 respectively abut against the bracket 90 and the first lock nut assembly.
The braking mechanism 9 adopts a double-acting oil cylinder, and in a normal state, a rod cavity of the braking oil cylinder 91 is supplied with oil and pressure through the hydraulic accumulator 13 and under the action of the first spring 93, the braking mechanism 9 is in a closed state, namely a braking state. When the second hydraulic control valve 15 obtains the pilot oil, the rod cavity of the brake oil cylinder 91 is communicated with the rodless cavity of the brake oil cylinder 91, under the action of the difference of the action areas of the rod cavity and the rodless cavity of the brake oil cylinder 91, the flow rate of hydraulic oil entering the rodless cavity of the brake oil cylinder 91 is increased, the piston rod of the brake oil cylinder 91 is rapidly extended to push the first brake shoe 96 to release the brake drum 3, and the brake mechanism 9 is in an open state, namely a non-brake state.
As shown in fig. 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 pad 81 and a second brake shoe 80; the second brake-holding sheet 81 is arranged on the second brake shoe 80, the second brake shoe 80 holds the outer ring of the brake drum 3 tightly, and the second brake-holding 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 large 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 large gear 5, two ends of a clutch oil cylinder 82 are respectively hinged with the second end of the crank arm 84 and the large gear 5, and two ends of an elastic device 83 are respectively hinged with the third end of the crank arm 84 and the large gear 5. A hydraulic rotary joint 7 for supplying oil to the clutch cylinder 82 is mounted on the rotary shaft 2.
The clutch cylinder 82 of the present invention is a single-acting cylinder, and the elastic device 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 obtains the pilot oil, the rodless cavity of the clutch oil cylinder 82 is communicated with the hydraulic accumulator 13, the piston rod of the clutch oil cylinder 82 rapidly stretches out to overcome the acting force of the elastic device 83 to push the second brake shoe 80 to hold the brake drum 3 tightly, and the clutch mechanism 8 is in a closed state, namely the large gear 5 is engaged with the brake drum 3.
As shown in fig. 4, in a further technical solution, in the non-unhooking mode, the clutch cylinder 82 and the brake cylinder 91 are interlocked. 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 braking mechanism 9 comprises a braking 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 oil cylinder 91, a rod cavity of the brake oil cylinder 91 is communicated with the hydraulic 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 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 positioned at the left position, the P port of the first hydraulic control valve 14 is communicated with the A port of the first hydraulic control valve 14, and the O port of the first hydraulic control valve 14 is communicated with the B port of the first hydraulic control valve 14; when the first hydraulic control valve 14 is positioned at the right position, the P port of the first hydraulic control valve 14 is communicated with the B port of the first hydraulic control valve 14, and the O port of the first hydraulic control valve 14 is communicated with the A port of the first hydraulic control valve 14;
in a normal state, the second hydraulic control valve 15 is positioned at the left position, the P port of the second hydraulic control valve 15 is communicated with the A port of the second hydraulic control valve 15, and the O port of the second hydraulic control valve 15 is communicated with the B port of the second hydraulic control valve 15; when the second hydraulic control valve 15 is in the right position, the P port of the second hydraulic control valve 15 communicates with the B port of the second hydraulic control valve 15, and the O port of the second hydraulic control valve 15 communicates with the a port of the second hydraulic control valve 15.
The control port of the second hydraulic control valve 15 is communicated with the output port of the first shuttle valve 16, the control port of the first hydraulic control valve 14 is communicated with the first input port of the first shuttle valve 16, the second input port of the first shuttle valve 16 is communicated with the output port of the second shuttle valve 17, the first input port of the second shuttle valve 17 is communicated with the port B of the pilot control valve 18, and the control port of the first hydraulic control valve 14 is communicated with the 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, the P port of the pilot control valve 18 is communicated with the A port of the pilot control valve 18, and the O port of the pilot control valve 18 is communicated with the B port of the pilot control valve 18; when the pilot control valve 18 is positioned at the right position, the P port of the pilot control valve 18 is communicated with the B port of the pilot control valve 18, and the O port of the pilot control valve 18 is communicated with the A port 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, the brake mechanism 9 is opened (i.e. in an unbraked state), and 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 an unbraked state), and unhooked 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 ((namely, the brake state) to realize the air start-stop action, and the clutch oil cylinder 82 and the brake oil cylinder 91 are ingenious in control of the hydraulic oil way structure and good in stability and safety.
The techniques not described above are common general knowledge to a person skilled in the art. The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the invention.
Claims (7)
1. The winch is characterized by comprising a rotating shaft (2), a winding drum (1), a brake drum (3), a brake disc (19), a braking mechanism (9), a clutch mechanism (8), a large gear (5), a first bearing and a second bearing (4); the rotating shaft (2) is arranged on the bearing seat (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 braking mechanism (9) is connected with the brake drum (3), the clutch mechanism (8) is respectively connected with the brake drum (3) and the large gear (5), and the large gear (5) is connected with the rotating shaft (2);
the brake system comprises a primary brake clamp (10) and a secondary brake clamp (11), wherein the primary brake clamp (10) and the secondary brake clamp (11) are respectively arranged on a brake disc (19); the braking force of the primary braking clamp (10) is smaller than that of the secondary braking clamp (11);
the hydraulic control system 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 oil cylinder (91), and the brake oil cylinder (91) is a double-acting oil cylinder; the clutch mechanism (8) comprises a clutch oil 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 oil cylinder (91), a rod cavity of the brake oil cylinder (91) is communicated with the hydraulic 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 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 positioned at the left position, the P port of the first hydraulic control valve (14) is communicated with the A port of the first hydraulic control valve (14), and the O port of the first hydraulic control valve (14) is communicated with the B port of the first hydraulic control valve (14); when the first hydraulic control valve (14) is positioned at the right position, the P port of the first hydraulic control valve (14) is communicated with the B port of the first hydraulic control valve (14), and the O port of the first hydraulic control valve (14) is communicated with the A port of the first hydraulic control valve (14);
in a normal state, the second hydraulic control valve (15) is positioned at the left position, the P port of the second hydraulic control valve (15) is communicated with the A port of the second hydraulic control valve (15), and the O port of the second hydraulic control valve (15) is communicated with the B port of the second hydraulic control valve (15); when the second hydraulic control valve (15) is positioned at the right position, the P port of the second hydraulic control valve (15) is communicated with the B port of the second hydraulic control valve (15), and the O port of the second hydraulic control valve (15) is communicated with the A port of the second hydraulic control valve (15);
the control port of the second hydraulic control valve (15) is communicated with the output port of the first shuttle valve (16), the control port of the first hydraulic control valve (14) is communicated with the first input port of the first shuttle valve (16), the second input port of the first shuttle valve (16) is communicated with the output port of the second shuttle valve (17), the first input port of the second shuttle valve (17) is communicated with the B port of the pilot control valve (18), and the control port of the first hydraulic control valve (14) is communicated with the A port 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, the P port of the pilot control valve (18) is communicated with the A port of the pilot control valve (18), and the O port of the pilot control valve (18) is communicated with the B port of the pilot control valve (18); when the pilot control valve (18) is positioned at the right position, the P port of the pilot control valve (18) is communicated with the B port of the pilot control valve (18), and the O port of the pilot control valve (18) is communicated with the A port of the pilot control valve (18); the O port of the pilot control valve (18) is an oil return port.
2. The winch according to claim 1, characterized in that the brake mechanism (9) comprises a bracket (90), a first brake pad (95), a first brake shoe (96), a brake cylinder (91) and a lever (92); the first brake-holding sheet (95) is arranged on a first brake shoe (96), the first brake shoe (96) holds the outer ring of the brake drum (3), and the first brake-holding 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 brake-holding oil cylinder (91), and the brake-holding oil cylinder (91) is arranged on the bracket (90).
3. The winch of claim 2, comprising at least one pull rod (94), a first spring (93) and a first lock nut assembly, wherein the bracket (90) is located around the first brake shoe (96), one end of the pull rods (94) is connected around the first brake shoe (96), the first lock nut assembly is connected with the pull rods (94), and two ends of the first spring (93) respectively abut against the bracket (90) and the first lock nut assembly.
4. The hoisting machine according to 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 pad (81), a second brake shoe (80); the second brake-holding sheet (81) is arranged on the second brake shoe (80), the second brake shoe (80) holds the outer ring of the brake drum (3), and the second brake-holding 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 large 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 large gear (5), two ends of a clutch oil cylinder (82) are respectively hinged with the second end of the crank arm (84) and the large gear (5), and two ends of an elastic device (83) are respectively hinged with the third end of the crank arm (84) and the large gear (5).
5. The hoisting machine according to claim 4, characterized in that a hydraulic swivel (7) for supplying oil to the clutch cylinder (82) is mounted on the rotating shaft (2).
6. The hoist according to claim 4, characterized in that the clutch cylinder (82) is a single-acting cylinder.
7. A dynamic compactor comprising a hoist as claimed in any one of claims 1 to 6.
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| CN201911103262.XA CN110775848B (en) | 2019-11-12 | 2019-11-12 | Winch and dynamic compactor |
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| CN201911103262.XA CN110775848B (en) | 2019-11-12 | 2019-11-12 | Winch and dynamic compactor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114808913B (en) * | 2022-04-12 | 2022-11-04 | 中国建筑第二工程局有限公司 | Dynamic compaction mechanical rapid energy level changing mechanism and construction method thereof |
| CN115215242B (en) * | 2022-09-19 | 2023-04-18 | 杭州未名信科科技有限公司 | Winch gradient brake power system of intelligent tower crane and intelligent tower crane |
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