CN110116969B - Dynamic friction prevention system of winch clutch and dynamic compaction machine - Google Patents
Dynamic friction prevention system of winch clutch and dynamic compaction machine Download PDFInfo
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- CN110116969B CN110116969B CN201910291303.6A CN201910291303A CN110116969B CN 110116969 B CN110116969 B CN 110116969B CN 201910291303 A CN201910291303 A CN 201910291303A CN 110116969 B CN110116969 B CN 110116969B
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- 238000005056 compaction Methods 0.000 title claims description 11
- 230000002265 prevention Effects 0.000 title abstract description 5
- 230000005540 biological transmission Effects 0.000 claims description 87
- 230000009467 reduction Effects 0.000 claims description 74
- 238000012546 transfer Methods 0.000 claims description 74
- 239000003921 oil Substances 0.000 claims description 72
- 238000004804 winding Methods 0.000 claims description 63
- 239000010720 hydraulic oil Substances 0.000 claims description 23
- 230000007246 mechanism Effects 0.000 claims description 10
- 230000002441 reversible effect Effects 0.000 claims description 3
- 230000008859 change Effects 0.000 description 6
- 239000012530 fluid Substances 0.000 description 6
- 238000006243 chemical reaction Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 239000002689 soil Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
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Classifications
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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
- B66D5/24—Operating devices
- B66D5/26—Operating devices pneumatic or hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D2700/00—Capstans, winches or hoists
- B66D2700/03—Mechanisms with latches or braking devices in general for capstans, hoists or similar devices as well as braking devices actuated electrically or by fluid under pressure
- B66D2700/035—Fluid operated braking devices
Abstract
The invention discloses a dynamic friction prevention system of a winch clutch and a dynamic compactor, which comprise a winch, a controller, an engine speed driver and a winch handle, wherein the winch clutch is installed on the winch, the winch handle is used for controlling the winch clutch to be jointed and separated, the controller collects the actual rotating speed of an engine in real time through the engine speed driver, an engine speed threshold value is preset in the controller, and when the actual rotating speed of the engine is lower than the engine speed threshold value in the controller, the winch handle can only control the winch clutch to be jointed. The invention protects the hoisting clutch, prolongs the service life of the hoisting clutch and improves the use safety of the hoisting clutch.
Description
Technical Field
The invention relates to the field of engineering machinery, in particular to a dynamic friction prevention system of a winch clutch and a dynamic compactor.
Background
The dynamic compactor is a machine for compacting and loosening soil in building engineering, and has the working principle that after a rammer is repeatedly lifted to a certain height, the rammer is put down, and the freely falling rammer compacts and loosens the soil. The hoisting drive is generally driven by a machine or a hydraulic pressure. At present, because the hoist needs big moment of torsion when the lifting hook promotes the ram, general operating personnel can increase the throttle and promote engine speed increase drive hoist moment of torsion, treat the engine speed and rise the back, then handle the hoist handle and make the hoist clutch joint, and this operating mode can make the drive gear of hoist and the difference in speed between the reel great, and the inside dynamic friction aggravation of hoist clutch causes the too early damage of hoist clutch, and the security descends.
Disclosure of Invention
In view of the above, the invention provides a dynamic friction prevention system of a hoisting clutch and a dynamic compactor.
On one hand, the invention provides an anti-dynamic friction system of a winch clutch, which comprises an engine, a hydraulic torque converter, a winch, a controller, an engine speed driver and a winch handle, wherein the power of the engine is transmitted to the winch through the hydraulic torque converter;
the hydraulic pump, the first reversing valve, the winch handle and the control valve; the winch clutch comprises a winch clutch oil cylinder, hydraulic oil output by the hydraulic pump flows to the winch clutch oil cylinder through the first reversing valve, and pilot pressure oil output by the winch handle flows to a control oil port of the first reversing valve through the control valve; when the actual rotating speed of the engine exceeds an engine rotating speed threshold value in the controller, the controller controls the control valve to be electrified, so that pilot pressure oil output by the winch handle is disconnected from a control oil port of the first reversing valve, and the winch clutch is separated; when the actual rotating speed of the engine is lower than the rotating speed threshold value of the engine in the controller, the controller controls the control valve to lose power, pilot pressure oil output by the hoisting handle is sent to a control oil port of the first reversing valve to enable the first reversing valve to be reversed, and hydraulic oil output by the hydraulic pump is sent to a hoisting clutch oil cylinder through the first reversing valve to enable the hoisting clutch to be jointed;
the winch comprises a winding drum, a rotating shaft, a driving gear, a braking hydraulic oil cylinder and a braking mechanism; the winding drum is rotatably arranged on the rotating shaft, the driving gear is connected with the rotating shaft, the winding clutch cylinder is arranged on the driving gear, the driving gear is connected with the winding clutch, and the winding clutch cylinder drives the winding clutch to enable the driving gear to be jointed with and separated from the winding drum; the brake hydraulic oil cylinder drives the brake mechanism to brake the winding drum.
The hydraulic reversing valve comprises a one-way valve and a hydraulic energy accumulator, wherein the one-way valve and the hydraulic energy accumulator are connected in an oil path between a hydraulic pump and a first reversing valve.
On the other hand, the invention provides another anti-dynamic friction system of a hoisting clutch, which comprises an engine, a hydraulic torque converter, a hoisting, a controller, an engine speed driver and a hoisting handle, wherein the power of the engine is transmitted to the hoisting through the hydraulic torque converter, the hoisting clutch is arranged on the hoisting, the hoisting handle is used for operating the connection and the separation of the hoisting clutch, the controller acquires the actual rotating speed of the engine in real time through the engine speed driver, an engine speed threshold value is preset in the controller, and the hoisting handle can only operate the connection of the hoisting clutch when the actual rotating speed of the engine is lower than the engine speed threshold value in the controller;
the hydraulic control system comprises a hydraulic pump, a first reversing valve, a hoisting handle and a control valve; the winch clutch comprises a winch clutch oil cylinder, hydraulic oil output by the hydraulic pump flows to the winch clutch oil cylinder through the first reversing valve and the control valve, and pilot pressure oil output by the winch handle flows to a control oil port of the first reversing valve; when the actual rotating speed of the engine exceeds an engine rotating speed threshold value in the controller, the controller controls the control valve to be electrified, so that an oil path between hydraulic oil output by the hydraulic pump and an oil cylinder of the hoisting clutch is disconnected, and the hoisting clutch is separated; when the actual rotating speed of the engine is lower than the rotating speed threshold value of the engine in the controller, the controller controls the control valve to lose power, pilot pressure oil output by the hoisting handle is sent to a control oil port of the first reversing valve to reverse the first reversing valve, and hydraulic oil output by the hydraulic pump is sent to a hoisting clutch oil cylinder to joint the hoisting clutch;
the winch comprises a winding drum, a rotating shaft, a driving gear, a braking hydraulic oil cylinder and a braking mechanism; the winding drum is rotatably arranged on the rotating shaft, the driving gear is connected with the rotating shaft, the winding clutch cylinder is arranged on the driving gear, the driving gear is connected with the winding clutch, and the winding clutch cylinder drives the winding clutch to enable the driving gear to be jointed with and separated from the winding drum; the brake hydraulic oil cylinder drives the brake mechanism to brake the winding drum;
the hydraulic reversing valve comprises a one-way valve and a hydraulic energy accumulator, wherein the one-way valve and the hydraulic energy accumulator are connected in an oil path between a hydraulic pump and a first reversing valve.
In addition, the invention also provides a dynamic compaction machine, which comprises the hoisting clutch anti-dynamic friction system,
Transfer case, gear box, transmission case, reduction box; one part of the power of the engine is transmitted to the hydraulic torque converter through the transfer case, and the other part of the power is transmitted to the hydraulic pump through the transfer case; the output power of the hydraulic torque converter is transmitted to the transmission case through the gearbox, and the output power of the transmission case drives the winch to rotate through the reduction gearbox; the output shaft of the engine is arranged along the X-axis direction, the rotating shaft of the winch is arranged along the Y-axis direction, and the engine, the transfer case, the hydraulic torque converter, the gearbox and the transmission case are arranged on the left side or the right side of the winch and the reduction gearbox along the X-axis direction; the input shaft of the transmission case is arranged along the X-axis direction, and the output shaft of the transmission case is arranged along the Y-axis direction; the engine, the transfer case, the hydraulic torque converter, the gearbox, the transmission case, the reduction gearbox and the winch are mutually independent units.
The hydraulic torque converter is connected with the gearbox through the first transmission shaft; the second transmission shaft is arranged in the Y-axis direction, and the transmission case is connected with the reduction gearbox through the second transmission shaft;
the transfer case comprises a transfer case input shaft, a transfer case intermediate shaft and a transfer case output shaft, wherein a transfer case main gear is installed on the transfer case input shaft, a transfer case intermediate gear is installed on the transfer case intermediate shaft, and a transfer case driven gear is installed on the transfer case output shaft; the transfer case main gear is meshed with a transfer case intermediate gear, and the transfer case intermediate gear is meshed with a transfer case driven gear; the hydraulic pump is connected with the output shaft of the transfer case; two ends of the input shaft of the transfer case are respectively connected with the engine and the hydraulic torque converter.
Further, the gearbox comprises a gearbox input gear, a gearbox output gear, a left reduction intermediate gear set, a right reduction intermediate gear set and a gearbox clutch; the left reduction intermediate gear set and the right reduction intermediate gear set comprise upper and lower intermediate gears which are coaxially connected, and the upper and lower intermediate gears have tooth number difference; the output power of the hydraulic torque converter is transmitted to an input gear shaft of the gearbox, and an output gear shaft of the gearbox is connected with the transmission case; the gearbox clutch is positioned between the gearbox input gear and the gearbox output gear, so that the gearbox input gear shaft is separated from or connected with the gearbox output gear shaft; the input gear of the gearbox is normally meshed with the upper middle gears of the left and right reduction middle gear sets, and the output gear of the gearbox is normally meshed with the lower middle gears of the left and right reduction middle gear sets.
Furthermore, the transmission case comprises two X-axis bevel gears symmetrically arranged along the X-axis direction and two Y-axis bevel gears symmetrically arranged along the Y-axis direction, each X-axis bevel gear is normally meshed with the two symmetrical Y-axis bevel gears respectively, and each Y-axis bevel gear is normally meshed with the two symmetrical X-axis bevel gears respectively; the reduction gear assembly is arranged in the reduction box and comprises a reduction box input gear, a reduction box output gear and a reduction box intermediate gear, the reduction box output gear is coaxially connected with the reduction box intermediate gear, the power of the transmission box is transmitted to the reduction box input gear, and the reduction box input gear is normally meshed with the reduction box intermediate gear; the output gear of the reduction box is constantly meshed with the driving gear of the winch.
The anti-dynamic friction system of the hoisting clutch and the dynamic compaction machine have the advantages that: the hoisting clutch is protected, the service life of the hoisting clutch is prolonged, and the use safety of the hoisting clutch is improved.
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 view of a first embodiment of a hoisting clutch anti-stiction system of the present invention;
FIG. 2 is a schematic view of a second embodiment of a hoisting clutch anti-friction system of the present invention;
fig. 3 is a schematic view of a control system of the hoisting clutch anti-dynamic friction system 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 invention provides a first embodiment of a friction-preventing system for a hoisting clutch, which includes a hoisting 10, a controller, an engine speed driver, and a hoisting handle 18, wherein the hoisting 10 is provided with the hoisting clutch 104, the hoisting handle 18 is used for operating the hoisting clutch 104 to engage and disengage, the controller acquires the actual engine speed in real time through the engine speed driver, an engine speed threshold is preset in the controller, and when the actual engine speed is lower than the engine speed threshold in the controller, the hoisting handle 18 can operate the hoisting clutch 104 to engage.
As shown in fig. 1, the hydraulic control system comprises a hydraulic pump 3, a first reversing valve 16, a winding handle 18, a control valve 17, a one-way valve 14 and a hydraulic accumulator 15; the hoisting clutch 104 comprises a hoisting clutch cylinder 107, hydraulic oil output by the hydraulic pump 3 passes through the first reversing valve 16 to reach the hoisting clutch cylinder 107, the one-way valve 14 and the hydraulic energy accumulator 15 are connected in an oil path between the hydraulic pump 3 and the first reversing valve 16, and an overflow valve 19 is further connected in an output oil path of the hydraulic pump 3. The pilot pressure oil output by the winding handle 18 passes through the control valve 17 to the control oil port of the first reversing valve 16. The control valve 17 may be a solenoid directional valve or a solenoid on-off valve.
The winch 10 comprises a winding drum 100, a rotating shaft 101, a driving gear 102, a brake hydraulic cylinder 105 and a brake mechanism 103; the winding drum 100 is rotatably installed on a rotating shaft 101, a driving gear 102 is connected with the rotating shaft 101, a winding clutch cylinder 107 is installed on the driving gear 102, the driving gear 102 is connected with a winding clutch 104, and the winding clutch cylinder 107 drives the winding clutch 104 to enable the driving gear 102 to be jointed with and separated from the winding drum 100; the brake hydraulic cylinder 105 drives the brake mechanism 103 to brake the spool (100).
When the engine is started, the hydraulic pump 3 rotates, when the first reversing valve 16 is in a left position, the pressure oil output by the hydraulic pump 3 supplies oil to the hydraulic energy storage 15 through the check valve 14, and when the output pressure of the hydraulic pump 3 reaches the overflow valve preset value, the pressure oil output by the hydraulic pump 3 flows back to the oil tank through the overflow valve.
When the actual rotating speed of the engine exceeds the engine rotating speed threshold value in the controller, the controller controls the control valve 17 to be electrified, and the control valve 17 is in the left position. At this time, the operator operates the hoisting handle 18 to operate, the pilot pressure oil output by the hoisting handle 18 is cut off to the control oil port of the first direction valve 16, the first direction valve 16 cannot be switched, the first direction valve 16 is in the left position, the hydraulic oil output by the hydraulic pump 3 cannot pass through the first direction valve 16 to the hoisting clutch cylinder 107, the hoisting clutch 104 is separated, and the driving gear 102 is separated from the winding drum 100.
When the actual rotating speed of the engine is lower than the threshold value of the rotating speed of the engine in the controller, the controller controls the control valve 17 to be powered off, and the control valve 17 is located at the right position. At this time, the operator operates the winding handle 18, the pilot pressure oil output from the winding handle 18 is supplied to the control port of the first direction valve 16 to change the direction of the first direction valve 16, the first direction valve 16 is in the right position, the hydraulic oil output from the hydraulic pump 3 is supplied to the winding clutch cylinder 107 through the first direction valve 16, the winding clutch 104 is engaged, and the driving gear 102 is engaged with the winding drum 100.
As shown in fig. 2, the second embodiment of the present invention provides a hoisting clutch anti-dynamic friction system, which is different from the first embodiment in that: the control valve 17 is provided in an oil path between the first direction changing valve 16 and the winding clutch cylinder 107.
When the actual rotating speed of the engine exceeds the engine rotating speed threshold value in the controller, the controller controls the control valve 17 to be electrified, and the control valve 17 is in the left position. At this time, the oil path between the first direction changing valve 16 and the winding clutch cylinder 107 is disconnected, the operator operates the winding handle 18, the pilot pressure oil output by the winding handle 18 flows to the control oil port of the first direction changing valve 16 to change the direction of the first direction changing valve 16, the first direction changing valve 16 is in the right position, the control valve 17 is in the left position, the hydraulic oil output by the hydraulic pump 3 cannot flow through the control valve 17 to the winding clutch cylinder 107, the winding clutch 104 is separated, and the driving gear 102 is separated from the winding drum 100.
When the actual rotating speed of the engine is lower than the threshold value of the rotating speed of the engine in the controller, the controller controls the control valve 17 to be powered off, and the control valve 17 is located at the right position. At this time, the operator operates the winding handle 18, the pilot pressure oil output from the winding handle 18 is supplied to the control oil port of the first direction valve 16 to change the direction of the first direction valve 16, the first direction valve 16 is in the right position, the hydraulic oil output from the hydraulic pump 3 is supplied to the winding clutch cylinder 107 through the first direction valve 16 and the control valve 17, the winding clutch 104 is engaged, and the driving gear 102 is engaged with the winding drum 100.
As shown in fig. 3, the invention provides a system for alarming the slipping of a hoisting clutch, which comprises a controller, a first rotating speed sensor, a second rotating speed sensor and an alarm; the first speed sensor detects the rotating speed of the driving gear 102, and the second speed sensor detects the rotating speed of the winding drum 100; when the hoisting clutch 104 is in an engaged state, the controller acquires signals of the first rotating speed sensor and the second rotating speed sensor, judges the rotating speed difference between the driving gear 102 and the winding drum 100, and sends an alarm signal to the alarm when the rotating speed difference reaches a preset value.
In order to determine the engaged and disengaged states of the hoisting clutch 104, two schemes are included, in the first scheme, a third sensor is included, the third sensor detects a position signal of the hoisting handle 18, and the controller acquires a signal of the third sensor to determine the engaged or disengaged state of the hoisting clutch 104. In the second aspect, a third sensor is included, and the third sensor detects the oil pressure value of the oil supply passage of the hoisting clutch cylinder 107. In the first embodiment of fig. 1, a third sensor is installed in the oil supply path between the hoisting clutch cylinder 107 to the first direction switching valve 16. In the second embodiment of fig. 2, a third sensor is installed in the oil supply path between the hoisting clutch cylinder 107 to the control valve 17. The controller acquires the third sensor signal to determine whether the hoisting clutch 104 is in the engaged or disengaged state.
As shown in fig. 1, the invention also provides a dynamic compaction machine, which comprises an engine 1, a hydraulic torque converter 4 and a winch 10, wherein the power of the engine 1 is transmitted to the winch 10 through the hydraulic torque converter 4.
As is known to those skilled in the art, a non-rigid torque converter, in which the torque converter 4 uses fluid as a working medium, is one form of hydraulic drive. The torque converter 4 has a closed working chamber in which the fluid circulates, wherein the pump impeller, the turbine impeller and the stator impeller are connected to the input shaft, the output shaft and the housing, respectively. When the engine 1 drives the input shaft to rotate, the liquid flows out of the centrifugal pump impeller, sequentially passes through the turbine and the guide wheel and then returns to the pump impeller, and circularly flows. The pump wheel transfers the mechanical energy of the input shaft to the liquid. The high-speed liquid pushes the turbine to rotate, and energy is transmitted to the output shaft. The torque converter 4 transfers torque by the change of momentum moment caused by the interaction of fluid and blades. The main feature of the torque converter 4, which is different from a fluid coupling, is that it has a fixed stator. The guide action of the guide wheels on the fluid allows the output torque of the hydrodynamic torque converter 4 to be higher or lower than the input torque, and is therefore referred to as a torque converter. The ratio of the output torque to the input torque is called a torque conversion coefficient, and the zero-speed torque conversion coefficient when the output rotation speed is zero is usually about 2-6. The torque conversion coefficient decreases as the output rotation speed increases. The input shaft and the output shaft of the hydraulic torque converter 4 are in fluid communication, and working components are not rigidly connected. The torque converter 4 is characterized in that: impact and vibration can be eliminated, and the overload protection performance and the starting performance are good; the rotating speed of the output shaft can be greater than or less than that of the input shaft, and the rotating speed difference of the two shafts is different along with the magnitude of the transmission torque; the automatic transmission has good automatic speed change performance, the output rotating speed automatically decreases when the load increases, and otherwise, the output rotating speed automatically increases; the stable working area of the engine 1 is ensured, and the transient change of the load is basically not reflected on the engine 1. The efficiency of the hydraulic torque converter 4 is high near the rated working condition, and the highest efficiency is 85-92%.
Therefore, the hydraulic torque converter 4 is applied to a transmission system of the dynamic compaction machine to drive the winch 10 to rotate, so that the reliability and stability of dynamic compaction construction can be improved, and the requirement of high-strength dynamic compaction construction can be met.
In addition, the engine 1 drives the conveying pump 11 to rotate, an oil inlet of the hydraulic torque converter 4 is connected with an oil outlet of the conveying pump 11 through an oil inlet path B, an oil outlet of the hydraulic torque converter 4 is connected with an oil inlet of the radiator 12 through an oil return path A, and an oil outlet of the radiator 12 is connected with an oil inlet of the conveying pump 11. The feed pump 11, the radiator 12, and the torque converter 4 constitute a forced cooling system.
In a further technical scheme, the transfer case comprises a transfer case 2, a first transmission shaft 5, a gearbox 6, a transmission case 7, a second transmission shaft 8 and a reduction gearbox 9; the engine 1, the transfer case 2, the hydraulic torque converter 4, the first transmission shaft 5, the gearbox 6 and the transmission case 7 are arranged on the right side of the winch 10 and the reduction gearbox 9 along the X-axis direction. As shown in fig. 2, the engine 1, the transfer case 2, the torque converter 4, the first transmission shaft 5, the transmission case 6, and the transmission case 7 are arranged on the left side of the winch 10 and the reduction gearbox 9 in the X-axis direction.
The Y-axis direction of the second transmission shaft 8 is arranged, the output shaft of the engine 1 is arranged along the X-axis direction, the rotating shaft 101 of the winch 10 is arranged along the Y-axis direction, the input shaft of the transmission case 7 is arranged along the X-axis direction, and the output shaft of the transmission case 7 is arranged along the Y-axis direction; the engine 1, the transfer case 2, the hydraulic torque converter 4, the first transmission shaft 5, the gearbox 6, the transmission case 7, the second transmission shaft 8, the reduction gearbox 9 and the winch 10 are mutually independent units, and each unit can be independently detached and replaced.
One part of the power of the engine 1 is transmitted to a hydraulic torque converter 4 through a transfer case 2, and the other part of the power is transmitted to a hydraulic pump 3 through the transfer case 2; the output power of the hydraulic torque converter 4 is transmitted to a transmission case 7 through a first transmission shaft 5 and a gearbox 6, and the output power of the transmission case 7 drives a winch 10 to rotate through a second transmission shaft 8 and a reduction gearbox 9. Hoisting 10 power transmission route: the engine 1, the transfer case 2, the hydraulic torque converter 4, the first transmission shaft 5, the gearbox 6, the transmission case 7, the reduction gearbox 9 and the winch 10. Hydraulic pump 3 transmission line: the engine 1, the transfer case 2 and the hydraulic pump 3. The two power transmission routes are mutually independent and do not interfere with each other. Compared with the prior art, the transmission route arrangement has the advantages that: the power of the hydraulic pump 3 does not pass through the hydraulic torque converter 4, and the transmission efficiency is improved. When the hydraulic pump 3 and the winch 10 are simultaneously operated, the engine 1 intermittently drives the winch 10 to rotate, so that torque fluctuation is generated and absorbed by the torque converter 4. The hydraulic transmission and the mechanical transmission do not interfere with each other, the pressure fluctuation of a hydraulic system of the dynamic compactor is small, and the working reliability and the stability of the dynamic compactor are high.
According to the invention, each functional module is separated to form an independent unit, and by adopting the modular design, the transmission device is compact in arrangement, convenient to install and maintain, and the space of the operating platform is saved, so that the width of the operating platform is reduced. In addition, each independent unit is positioned on two sides of the operating platform, so that replacement and maintenance operation can be facilitated.
As shown in fig. 1: the transfer case 2 comprises a transfer case input shaft, a transfer case intermediate shaft and a transfer case output shaft, wherein a transfer case main gear 20 is installed on the transfer case input shaft, a transfer case intermediate gear 21 is installed on the transfer case intermediate shaft, and a transfer case driven gear 22 is installed on the transfer case output shaft; the transfer case main gear 20 is meshed with a transfer case intermediate gear 21, and the transfer case intermediate gear 21 is meshed with a transfer case driven gear 22; the hydraulic pump 3 is connected with an output shaft of the transfer case; two ends of the input shaft of the transfer case are respectively connected with the engine 1 and the hydraulic torque converter 4. One part of power of the engine 1 is transmitted to the hydraulic pump 3 after being decelerated and torque-increased by the transfer case, the other part of power of the engine 1 is directly transmitted to the hydraulic torque converter 4 through the transfer case 2, and the transmission ratio at the moment is 1: 1. the engine 1 is rigidly connected with the transfer case 2 through a flange, and the transfer case 2 is connected with the hydraulic torque converter 4 through an elastic coupling.
The gearbox 6 comprises a gearbox input gear 60, a gearbox output gear 61, a left reduction intermediate gear set 62, a right reduction intermediate gear set 64 and a gearbox clutch 63; the left reduction intermediate gear set 62 and the right reduction intermediate gear set 64 comprise two intermediate gears of an upper layer and a lower layer which are coaxially connected, and the two intermediate gears of the upper layer and the lower layer have tooth number difference; the hydraulic torque converter 4 is connected with a transmission input gear 60 shaft through a first transmission shaft 5, a transmission output gear 61 shaft is connected with a transmission case 7, and the transmission input gear and the transmission case are connected through an elastic coupling. A transmission clutch 63 is positioned between the transmission input gear 60 and the transmission output gear 61 to allow the transmission input gear 60 shaft to be disengaged or engaged with the transmission output gear 61 shaft; the transmission input gear 60 is in constant mesh with the upper intermediate gears of the left and right reduction intermediate gear sets 62, 64, and the transmission output gear 61 is in constant mesh with the lower intermediate gears of the left and right reduction intermediate gear sets 62, 64.
When the transmission clutch 63 is engaged, the transmission input gear 60 shaft is connected to the transmission output gear 61 shaft, at which point the transmission ratio is 1: 1. when the transmission clutch 63 is disengaged, the power transmission path is: the gearbox input gear 60, the left reduction intermediate gear set 62, the right reduction intermediate gear set 64 and the gearbox output gear 61 realize speed reduction and torque increase transmission.
The transmission case 7 comprises two X-axis bevel gears 70 symmetrically arranged along the X-axis direction and two Y-axis bevel gears 71 symmetrically arranged along the Y-axis direction, each X-axis bevel gear 70 is normally meshed with the two symmetrical Y-axis bevel gears 71 respectively, and each Y-axis bevel gear 71 is normally meshed with the two symmetrical X-axis bevel gears 70 respectively. And a connecting flange is arranged on each of the X-axis bevel gear 70 shaft and the Y-axis bevel gear 71 shaft.
The four directions of the transmission case 7 are all provided with flanges, so the engine 1, the transfer case 2, the hydraulic torque converter 4, the gearbox 6 and the transmission case 7 can be arranged on the left side of the operation platform and also can be arranged on the right side of the operation platform, and the transmission case can adapt to different arrangement forms of the operation platform. As shown in fig. 2, the second drive shaft 8 is flange-connected to the right side of the drive housing 7.
A reduction gear assembly is arranged in the reduction gearbox 9, the reduction gear assembly comprises a reduction gearbox input gear 90, a reduction gearbox output gear 92 and a reduction gearbox intermediate gear 91, the reduction gearbox output gear 92 is coaxially connected with the reduction gearbox intermediate gear 91, the power of the transmission box 7 is transmitted to the reduction gearbox input gear 90, and the reduction gearbox input gear 90 is normally meshed with the reduction gearbox intermediate gear 91; the reduction gearbox output gear 92 is in constant mesh with the drive gear 102 of the hoist 10.
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.
Claims (6)
1. The anti-dynamic friction system of the winch clutch is characterized by comprising an engine (1), a hydraulic torque converter (4), a winch (10), a controller, an engine speed driver and a winch handle (18); the power of the engine (1) is transmitted to the winch (10) through the hydraulic torque converter (4); the winch (10) is provided with a winch clutch (104), a winch handle (18) is used for operating the winch clutch (104) to be connected and separated, the controller acquires the actual rotating speed of the engine in real time through an engine rotating speed driver, an engine rotating speed threshold value is preset in the controller, and the winch handle (18) can operate the winch clutch (104) to be connected when the actual rotating speed of the engine is lower than the engine rotating speed threshold value in the controller;
comprises a hydraulic pump (3), a first reversing valve (16), a winding handle (18) and a control valve (17); the hoisting clutch (104) comprises a hoisting clutch oil cylinder (107), hydraulic oil output by the hydraulic pump (3) passes through the first reversing valve (16) to reach the hoisting clutch oil cylinder (107), and pilot pressure oil output by the hoisting handle (18) passes through the control valve (17) to reach a control oil port of the first reversing valve (16); when the actual rotating speed of the engine exceeds an engine rotating speed threshold value in the controller, the controller controls the control valve (17) to be electrified, pilot pressure oil output by the winch handle (18) is disconnected from a control oil port of the first reversing valve (16), and the winch clutch (104) is separated; when the actual rotating speed of the engine is lower than an engine rotating speed threshold value in the controller, the controller controls the control valve (17) to lose power, pilot pressure oil output by the hoisting handle (18) is sent to a control oil port of the first reversing valve (16) to reverse the first reversing valve (16), and hydraulic oil output by the hydraulic pump (3) is sent to a hoisting clutch oil cylinder (107) through the first reversing valve (16) to enable a hoisting clutch (104) to be jointed;
the winch (10) comprises a winding drum (100), a rotating shaft (101), a driving gear (102), a braking hydraulic oil cylinder (105) and a braking mechanism (103); the winding drum (100) is rotatably arranged on a rotating shaft (101), a driving gear (102) is connected with the rotating shaft (101), a winding clutch oil cylinder (107) is arranged on the driving gear (102), the driving gear (102) is connected with a winding clutch (104), and the winding clutch oil cylinder (107) drives the winding clutch (104) to enable the driving gear (102) to be jointed with and separated from the winding drum (100); the brake hydraulic oil cylinder (105) drives the brake mechanism (103) to brake the winding drum (100);
the hydraulic control system comprises a one-way valve (14) and a hydraulic energy accumulator (15), wherein the one-way valve (14) and the hydraulic energy accumulator (15) are connected in an oil path between a hydraulic pump (3) and a first reversing valve.
2. The anti-dynamic friction system of the winch clutch is characterized by comprising an engine (1), a hydraulic torque converter (4), a winch (10), a controller, an engine speed driver and a winch handle (18); the power of the engine (1) is transmitted to the winch (10) through the hydraulic torque converter (4); the winch (10) is provided with a winch clutch (104), a winch handle (18) is used for operating the winch clutch (104) to be connected and separated, the controller acquires the actual rotating speed of the engine in real time through an engine rotating speed driver, an engine rotating speed threshold value is preset in the controller, and the winch handle (18) can operate the winch clutch (104) to be connected when the actual rotating speed of the engine is lower than the engine rotating speed threshold value in the controller;
comprises a hydraulic pump (3), a first reversing valve (16), a winding handle (18) and a control valve (17); the hoisting clutch (104) comprises a hoisting clutch oil cylinder (107), hydraulic oil output by the hydraulic pump (3) passes through the first reversing valve (16) and the control valve (17) to the hoisting clutch oil cylinder (107), and pilot pressure oil output by the hoisting handle (18) is delivered to a control oil port of the first reversing valve (16); when the actual rotating speed of the engine exceeds an engine rotating speed threshold value in the controller, the controller controls the control valve (17) to be electrified, so that an oil path between hydraulic oil output by the hydraulic pump (3) and a winch clutch cylinder (107) is disconnected, and the winch clutch (104) is separated; when the actual rotating speed of the engine is lower than an engine rotating speed threshold value in the controller, the controller controls the control valve (17) to lose power, pilot pressure oil output by the hoisting handle (18) is sent to a control oil port of the first reversing valve (16) to reverse the first reversing valve (16), and hydraulic oil output by the hydraulic pump (3) is sent to a hoisting clutch oil cylinder (107) to enable a hoisting clutch (104) to be connected;
the winch (10) comprises a winding drum (100), a rotating shaft (101), a driving gear (102), a braking hydraulic oil cylinder (105) and a braking mechanism (103); the winding drum (100) is rotatably arranged on a rotating shaft (101), a driving gear (102) is connected with the rotating shaft (101), a winding clutch oil cylinder (107) is arranged on the driving gear (102), the driving gear (102) is connected with a winding clutch (104), and the winding clutch oil cylinder (107) drives the winding clutch (104) to enable the driving gear (102) to be jointed with and separated from the winding drum (100); the brake hydraulic oil cylinder (105) drives the brake mechanism (103) to brake the winding drum (100);
the hydraulic control system comprises a one-way valve (14) and a hydraulic energy accumulator (15), wherein the one-way valve (14) and the hydraulic energy accumulator (15) are connected in an oil path between a hydraulic pump (3) and a first reversing valve.
3. A dynamic compaction machine, characterized by comprising a hoisting clutch anti-dynamic friction system according to any one of claims 1 to 2, a transfer case (2), a gearbox (6), a transmission case (7) and a reduction gearbox (9); one part of the power of the engine (1) is transmitted to the hydraulic torque converter (4) through the transfer case (2), and the other part of the power is transmitted to the hydraulic pump (3) through the transfer case (2); the output power of the hydraulic torque converter (4) is transmitted to the transmission case (7) through the gearbox (6), and the output power of the transmission case (7) drives the winch (10) to rotate through the reduction gearbox (9); the output shaft of the engine (1) is arranged along the X-axis direction, the rotating shaft (101) of the winch (10) is arranged along the Y-axis direction, and the engine (1), the transfer case (2), the hydraulic torque converter (4), the gearbox (6) and the transmission case (7) are arranged on the left side or the right side of the winch (10) and the reduction gearbox (9) along the X-axis direction; the input shaft of the transmission case (7) is arranged along the X-axis direction, and the output shaft of the transmission case (7) is arranged along the Y-axis direction; the engine (1), the transfer case (2), the hydraulic torque converter (4), the gearbox (6), the transmission case (7), the reduction gearbox (9) and the winch (10) are mutually independent units.
4. The dynamic compaction machine according to claim 3, characterized by comprising a first transmission shaft (5) and a second transmission shaft (8), wherein the first transmission shaft (5) is arranged in the X-axis direction, and the hydraulic torque converter (4) is connected with the gearbox (6) through the first transmission shaft (5); the second transmission shaft (8) is arranged in the Y-axis direction, and the transmission case (7) is connected with the reduction gearbox (9) through the second transmission shaft (8);
the transfer case (2) comprises a transfer case input shaft, a transfer case intermediate shaft and a transfer case output shaft, wherein a transfer case main gear (20) is installed on the transfer case input shaft, a transfer case intermediate gear (21) is installed on the transfer case intermediate shaft, and a transfer case driven gear (22) is installed on the transfer case output shaft; the transfer case main gear (20) is meshed with a transfer case intermediate gear (21), and the transfer case intermediate gear (21) is meshed with a transfer case driven gear (22); the hydraulic pump (3) is connected with the output shaft of the transfer case; two ends of the transfer case input shaft are respectively connected with the engine (1) and the hydraulic torque converter (4).
5. The dynamic compaction machine according to claim 4, wherein the gearbox (6) comprises a gearbox input gear (60), a gearbox output gear (61), a left reduction intermediate gear set (62), a right reduction intermediate gear set (64), a gearbox clutch (63); the left reduction intermediate gear set (62) and the right reduction intermediate gear set (64) comprise two intermediate gears of an upper layer and a lower layer which are coaxially connected, and the two intermediate gears of the upper layer and the lower layer have tooth number difference; the output power of the hydraulic torque converter (4) is transmitted to a shaft of a gearbox input gear (60), and a shaft of a gearbox output gear (61) is connected with a transmission case (7); the gearbox clutch (63) is positioned between the gearbox input gear (60) and the gearbox output gear (61) to separate or engage the gearbox input gear (60) shaft from the gearbox output gear (61) shaft; the gearbox input gear (60) is in constant mesh with the upper intermediate gears of the left reduction intermediate gear set (62) and the right reduction intermediate gear set (64), and the gearbox output gear (61) is in constant mesh with the lower intermediate gears of the left reduction intermediate gear set (62) and the right reduction intermediate gear set (64).
6. The dynamic compactor according to claim 5, wherein the transmission case (7) comprises two X-axis bevel gears (70) symmetrically arranged along the X-axis direction and two Y-axis bevel gears (71) symmetrically arranged along the Y-axis direction, each X-axis bevel gear (70) is respectively and constantly meshed with two symmetrical Y-axis bevel gears (71), and each Y-axis bevel gear (71) is respectively and constantly meshed with two symmetrical X-axis bevel gears (70); a reduction gear assembly is arranged in the reduction box (9), the reduction gear assembly comprises a reduction box input gear (90), a reduction box output gear (92) and a reduction box intermediate gear (91), the reduction box output gear (92) is coaxially connected with the reduction box intermediate gear (91), the power of the transmission box is transmitted to the reduction box input gear (90), and the reduction box input gear (90) is normally meshed with the reduction box intermediate gear (91); the output gear (92) of the reduction gearbox is constantly meshed with a driving gear (102) of the winch.
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| CN201910291303.6A CN110116969B (en) | 2019-04-11 | 2019-04-11 | Dynamic friction prevention system of winch clutch and dynamic compaction machine |
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| CN201910291303.6A CN110116969B (en) | 2019-04-11 | 2019-04-11 | Dynamic friction prevention system of winch clutch and dynamic compaction machine |
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| CN110116969B true CN110116969B (en) | 2021-02-26 |
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Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2280721B (en) * | 1993-08-03 | 1998-03-11 | Luk Getriebe Systeme Gmbh | Motor vehicle automatic clutch control |
| JP4782274B2 (en) * | 2000-10-18 | 2011-09-28 | いすゞ自動車株式会社 | Friction clutch control device for vehicle drive device |
| JP6183454B2 (en) * | 2013-03-27 | 2017-08-23 | アイシン・エィ・ダブリュ株式会社 | Control device for vehicle drive device |
| CN204041783U (en) * | 2014-09-01 | 2014-12-24 | 江西五十铃发动机有限公司 | A kind of electric-control motor clutch protective gear |
| CN207330195U (en) * | 2017-03-16 | 2018-05-08 | 张俊强 | A kind of torque converter drive system and dynamic compaction machinery for dynamic compaction machinery |
| CN207072772U (en) * | 2017-03-16 | 2018-03-06 | 张俊强 | A kind of transmission device and dynamic compaction machinery for being used to drive elevator |
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Denomination of invention: A Winch Clutch Anti friction System and Dynamic Compactor Effective date of registration: 20220923 Granted publication date: 20210226 Pledgee: Hunan Ningxiang Rural Commercial Bank Co.,Ltd. Xiaduopu Sub branch Pledgor: HUNAN BOBANG HEAVY INDUSTRY Co.,Ltd. Registration number: Y2022430000090 |
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Granted publication date: 20210226 Pledgee: Hunan Ningxiang Rural Commercial Bank Co.,Ltd. Xiaduopu Sub branch Pledgor: HUNAN BOBANG HEAVY INDUSTRY Co.,Ltd. Registration number: Y2022430000090 |
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Denomination of invention: A winch clutch anti moving friction system and dynamic compaction machine Granted publication date: 20210226 Pledgee: Hunan Ningxiang Rural Commercial Bank Co.,Ltd. Xiaduopu Sub branch Pledgor: HUNAN BOBANG HEAVY INDUSTRY Co.,Ltd. Registration number: Y2024980001226 |
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