CN209012289U - Ladder hydraulic adjustment device - Google Patents
Ladder hydraulic adjustment device Download PDFInfo
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- CN209012289U CN209012289U CN201821505457.8U CN201821505457U CN209012289U CN 209012289 U CN209012289 U CN 209012289U CN 201821505457 U CN201821505457 U CN 201821505457U CN 209012289 U CN209012289 U CN 209012289U
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Abstract
The utility model provides a kind of ladder hydraulic adjustment device, mainly solves the problems, such as that traditional oil pressure regulative mode is easy to happen the bored vehicle of host.The control oil circuit of friction clutch uses high-pressure oil pump fuel feeding, maximum pressure is adjusted by overflow valve, control ladder oil pressure by 2 mechanical adjustable pressure reducing valves, the 1st mechanical relief valve controls clutch precharge pressure, the 2nd mechanical relief valve control clutch run in sliding rub when pressure.Maximum pressure after 24 three-way electromagnetic valves controls are run in is set.On-off solenoid valve is set before each mechanical relief valve, and pressure reducing valve and on-off solenoid valve constitute series relationship.Mechanical relief valve+on-off solenoid valve is connect side by side with 24 three-way electromagnetic valves.The utility model is effectively reduced friction clutch fever and abrasion, improves friction clutch service life, can make the smooth soft start of host, it is not easy to bored vehicle.
Description
Technical field
The present invention relates to oil pressure to adjust field, in particular for controlling one kind of wet-type multi-chip friction clutch operating oil pressure
Ladder hydraulic adjustment device.
Background technique
Wet-type multi-chip friction clutch (hereinafter referred to as friction clutch) is mainly used in the transmission of ship, vehicle, lathe
In device, for controlling transmitting of the host to drive train power；Friction clutch compresses one group of friction plate by operating cylinder,
Utilize the torque of the frictional force transmitting host between friction plate.
The performance of friction clutch is generally measured by two indexs of maximum torque transmission capacity and heat absorption ability；Friction clutch
Device maximum torque transmission capacity usually presses load characteristic selection, such as friction clutch maximum torsion pass energy in general marine transmission
Power is usually not less than 1.5 times of host nominal torque.Maximum torque transmission capacity is usually by most senior engineer after the completion of friction clutch design
Make oil pressure decision.
For internal combustion engines such as diesel engines, working characteristics is that the torque one that can issue when working speed is lower is smaller than as；
Therefore it using the transmission device of the internal combustion engines such as diesel engine, needs to be arranged friction clutch or fluid coupling realizes that the soft of host is opened
It is dynamic, avoid host tape from carrying starting and lead to " bored vehicle "；Friction clutch realizes that the working principle of soft start is run in clutch
When control operating oil pressure, namely pressing force and friction torque between control friction plate make the cunning of friction clutch rub the torque beginning
It is less than the torque that host can issue under current rotating speed eventually, avoids the bored vehicle of host, while guarantees that the sliding torque that rubs is greater than load and turns round again
Square realizes load raising speed.During friction clutch runs in, principal and subordinate moved end rotational speed difference, that is, slippageω(t) 0 is gradually narrowed down to,
Sliding state of rubbing, the sliding torque that rubs are constantly in during this between principal and subordinate's movable friction plateT d(t) a large amount of heat is generated, when the sliding heat that rubs
More than the ability to bear of friction plate, friction plate is burnt, clutch failure.
Measuring friction plate heat absorption ability usually has following three indexs:
1) the instantaneous unit friction power of unit areaA(t)
Rub secondary unit apparent areaA pOn, once sliding rub slides the torque that rubs to friction clutch in the processT d(t) and slippageω
(t) product.
2) unit area unit friction workE
Rub secondary unit apparent areaA pOn, once sliding rub slides the torque that rubs to friction clutch in the processT d(t) in slippageω
(t) under work.
3) thermic loadC
Friction clutch once it is sliding rub during unit area unit friction work and the instantaneous unit friction power maximum value of unit area
Product；
C=EA(t)max
From defined above it can be seen that the sliding torque that rubsT d(t) and slippageω(t) product is bigger, sliding friction time tsIt is longer, it rubs
The thermic load that pad is subject to is bigger；Reducing friction clutch oil pressure when starting that runs in can reduce initial instantaneous unit friction work
Rate avoids Friction Disk Surface from burning, but will increase sliding friction time, while will increase friction plate and running in the mean temperature finished.
In certain boat diesel engine transmission devices, there are some load staring torques very big, rotary inertia is also very
Big occasion, when using second voltage regulation valve control friction clutch, only when pressure reaches 0.65MPa, friction clutch is produced
The raw cunning torque that rubs can just overcome the staring torque of load, and load is made to start to rotate.When oil pressure is between 0.3-0.65MPa,
Friction clutch is constantly in the slipping state of maximum (top) speed difference, can generate a large amount of frictional heat, increases the abrasion of friction plate,
Reduce service life；After oil pressure liter reaches 0.65 MPa, oil pressure can be increased to the moment of friction of generation quickly, if it exceeds
The maximum moment that host can issue, it will make the quick reduction of speed of host to minimum stable engine speed hereinafter, lead to the bored vehicle of host, run in
Failure.
Summary of the invention
The purpose of the present invention is to solve the above-mentioned problems of the prior art, and then provide a kind of ladder oil pressure adjusting
Device；Output oil pressure curve is stairstepping, and controllable friction clutch keeps low oil pressure when running in, avoids the bored vehicle of host；Run in
After keep high oil pressure, guarantee clutch maximum torque transmission capacity；The friction clutch that existing second voltage regulation valve is controlled is overcome to produce
The problem of raw biggish fever abrasion, host are easy bored vehicle.
The purpose of the present invention is what is be achieved through the following technical solutions:
A kind of ladder hydraulic adjustment device, including ladder hydraulic pressure control device and ladder hydraulic pressure control device outlet end lead to
The fueller assembly portion that the clutch assembly part of piping connection, ladder hydraulic pressure control device arrival end are connected by pipeline
Point, which is characterized in that in the ladder hydraulic pressure control device, the outlet end of filter A connects two four by pipeline respectively
Three-way electromagnetic valve A arrival end, two-position two-way solenoid valve arrival end, two-position four-way solenoid valve B arrival end, hydraulic control bi-bit bi-pass valve inlet
End, wherein the outlet end pipeline of the two-position four-way solenoid valve B is connected to the entrance of check valve B by mechanical relief valve B
End；The two-position two-way solenoid valve outlet end is connected to the arrival end of mechanical relief valve A；The hydraulic control bi-bit bi-pass valve outlet
End, the outlet end check valve B, mechanical relief valve A the pipeline of outlet end connect all the way with overflow valve A, another way enters with check valve A
The connection of mouth end；The pipeline and two-position four-way pilot-controlled electroma netic valve of the outlet end check valve A and the outlet end two-position four-way solenoid valve A
Arrival end connection, the outlet end of two-position four-way pilot-controlled electroma netic valve is i.e. and ladder hydraulic pressure control device outlet end and clutch assembly
Oil cylinder oil inlet chamber connection in part.
Further, in the clutch assembly part, host by the dynamic load of friction clutch connecting band, rub from
Clutch is internally provided with oil cylinder, includes oil cylinder oil inlet chamber and reset spring in oil cylinder；Oil return opening is additionally provided on friction clutch
With oil inlet, the oil inlet and fueller assembly part connect.
Further, the fueller assembly part includes motor and motor-driven oil pump, the outlet of oil pump
Arrival end of the end pipe road all the way through filter A in filter B connection ladder hydraulic pressure control device, another way are connected through overflow valve C
The oil inlet of friction clutch in clutch assembly part；The outlet end pipeline of oil pump, which is also set up, is connected with overflow valve B, overflow valve
Overflow valve D is connected on the pipeline of the outlet end C.
The beneficial effects of the present invention are: by using technical solution of the present invention, load staring torque is very big, rotation
Inertia also very big occasion provides a kind of ladder hydraulic pressure control device for friction clutch control, using oil pressure of the invention
The friction clutch of control device, it is possible to reduce fever and abrasion, improve service life, host can smooth soft start, it is not bored
Vehicle.
Detailed description of the invention
Fig. 1 a is that all valves of ladder hydraulic pressure control device of the present invention are in closing shutdown oil circuit status diagram.
Fig. 1 b is the pressure curve schematic diagram of ladder hydraulic pressure control device of the present invention output.
Fig. 2 a is that two-position four-way pilot-controlled electroma netic valve 10 opens the tentatively oil-filled oil circuit status diagram of clutch oil cylinder.
Fig. 2 b is that two-position four-way pilot-controlled electroma netic valve 10 opens the tentatively oil-filled state ladder hydraulic pressure control device of clutch oil cylinder
The pressure curve schematic diagram of output.
Fig. 3 a is two-position four-way pilot-controlled electroma netic valve 10, unlatching oil-filled 90% oil circuit of clutch oil cylinder of hydraulic control two position two-way valve 50
Status diagram.
Fig. 3 b is two-position four-way pilot-controlled electroma netic valve 10, unlatching oil-filled 90% state of clutch oil cylinder of hydraulic control two position two-way valve 50
The pressure curve schematic diagram of ladder hydraulic pressure control device output.
Fig. 4 a is the closing of hydraulic control two position two-way valve 50, two-position four-way pilot-controlled electroma netic valve 10, mechanical relief valve B40 are opened, from
The schematic diagram of the oil-filled 100% oil circuit state of clutch oil cylinder.
Fig. 4 b is the closing of hydraulic control two position two-way valve 50, two-position four-way pilot-controlled electroma netic valve 10, mechanical relief valve B40 are opened, from
The oil-filled 100% state oil cylinder working-pressure of clutch oil cylinder reaches the curve synoptic diagram of P0.
Fig. 5 a is mechanical relief valve B40 closing, and two-position four-way pilot-controlled electroma netic valve 10, mechanical relief valve A30 are opened, clutch
The oil-filled 100% oil circuit status diagram of oil cylinder.
Fig. 5 b is mechanical relief valve B40 closing, and two-position four-way pilot-controlled electroma netic valve 10, mechanical relief valve A30 are opened, clutch
The oil-filled 100% state oil cylinder working-pressure of oil cylinder reaches the curve synoptic diagram of P1.
Fig. 6 a be mechanical relief valve A30 close, two-position four-way pilot-controlled electroma netic valve 10, two-position four-way solenoid valve A20 open from
The oil-filled 100% oil circuit status diagram of clutch oil cylinder.
Fig. 6 b be mechanical relief valve A30 close, two-position four-way pilot-controlled electroma netic valve 10, two-position four-way solenoid valve A20 open from
The oil-filled 100% state oil cylinder working-pressure of clutch oil cylinder reaches the curve synoptic diagram of P2.
Fig. 7 a is that two-position four-way pilot-controlled electroma netic valve 10 closes clutch oil cylinder oil pressure rapid decrease oil circuit status diagram.
Fig. 7 b is that two-position four-way pilot-controlled electroma netic valve 10 closes clutch oil cylinder oil pressure rapid decrease condition curve schematic diagram.
Fig. 8 is structural schematic diagram of the invention.
Fig. 9 a is that cylinder oil gradually boosts curve synoptic diagram.
Fig. 9 b is cylinder oil ladder boosting curve synoptic diagram.
Figure 10 is coefficient of friction coefficient of friction and length velocity relation schematic diagram.
Figure 11 a, Figure 11 b, Figure 11 c are that load staring torque is big, when using gradually boosting curve controlled friction clutch
Each performance curve schematic diagram.
Figure 12 a, Figure 12 b, Figure 12 c are that load staring torque is big, when using ladder boosting curve controlled friction clutch
Each performance curve schematic diagram.
Figure 13 is that load staring torque is big, using gradually boosting and using two kinds of oil pressure curve comparison signals of ladder boosting
Figure.
Figure 14 is that load staring torque is big, using gradually boosting and using ladder two kinds of oil pressure curves of boosting, friction clutch
The sliding torque contrast schematic diagram of rubbing of device.
Figure 15 is that load staring torque is big, using gradually boosting and using ladder two kinds of oil pressure curves of boosting, loads raising speed
Curve comparison schematic diagram.
Figure 16 a is that load staring torque is big, using the curve that gradually boosts, friction clutch thermic load curve synoptic diagram.
Figure 16 b is that load staring torque is big, using ladder boosting curve, friction clutch thermic load curve synoptic diagram.
Specific embodiment
Below in conjunction with attached drawing, the present invention is described in further detail: the present embodiment is being with technical solution of the present invention
Under the premise of implemented, give detailed embodiment, but protection scope of the present invention is not limited to following embodiments.
As shown in figure 8, a kind of ladder hydraulic adjustment device involved in the present embodiment, including ladder hydraulic pressure control device 1
And 1 outlet end of ladder hydraulic pressure control device connected by pipeline clutch assembly part, 1 entrance of ladder hydraulic pressure control device
Hold the fueller assembly part that connects by pipeline, in the ladder hydraulic pressure control device 1, the outlet end of filter A110
Two-position four-way solenoid valve A20 arrival end, 70 arrival end of two-position two-way solenoid valve, two-position four-way solenoid valve are connected by pipeline respectively
B80 arrival end, 50 arrival end of hydraulic control two position two-way valve, wherein the outlet end pipeline of the two-position four-way solenoid valve B80 passes through
Mechanical relief valve B40 is connected to the arrival end of check valve B100；70 outlet end of two-position two-way solenoid valve is connected to machinery and subtracts
The arrival end of pressure valve A30；50 outlet end of hydraulic control two position two-way valve, the outlet end check valve B100, mechanical relief valve A30
The pipeline of outlet end is connect with overflow valve A60 all the way, and another way is connect with check valve A90 arrival end；The check valve A90 goes out
Mouth end is connect with the pipeline of the outlet end two-position four-way solenoid valve A20 with the arrival end of two-position four-way pilot-controlled electroma netic valve 10, and two four
The outlet end of logical pilot-controlled electroma netic valve 10 be and 1 outlet end 3 of ladder hydraulic pressure control device and the oil cylinder in clutch assembly part into
Oil pocket 301 connects.
Further, in the clutch assembly part, host 320 passes through 300 connecting band dynamic load of friction clutch
310, friction clutch 300 is internally provided with oil cylinder, includes oil cylinder oil inlet chamber 301 and reset spring 302 in oil cylinder；Friction clutch
Be additionally provided with oil return opening 360 and oil inlet 370 on device 300, the oil inlet 370 and fueller assembly part connect.
Further, the fueller assembly part includes the oil pump 210 that motor 200 and motor 200 drive, oil
Arrival end of the outlet end pipeline of pump 210 all the way through filter A110 in filter B220 connection ladder hydraulic pressure control device 1, separately
Oil inlet 370 all the way through friction clutch 300 in overflow valve C240 connection clutch assembly part；The outlet end of oil pump 210
Pipeline, which is also set up, is connected with overflow valve B230, is connected with overflow valve D260 on the pipeline of the outlet end overflow valve C240.
Host 320 rotates raising speed, the control friction of ladder hydraulic pressure control device 1 with dynamic load 310 by friction clutch 300
The operating oil pressure of clutch 300；Lubricating oil passes through 370 engaging friction clutch of throttle orifice, passes through after the cooling friction plate of lubricating oil
Oil return opening 360 flows back to fuel tank.
Oil pump electrical machinery 200 drives oil pump 210 to generate pressure oil, and pressure oil is miscellaneous by the filtering larger particles of filter B 220
Matter, overflow valve C240 control the pressure into ladder hydraulic pressure control device 1；Overflow valve B230 is the safety valve of oil pump；Overflow
Valve D260 controls the lubricating oil pressure lubricated to gear, bearing, friction clutch.
The outlet end of ladder hydraulic pressure control device 1 can generate ladder oil pressure curve 500, and arrival end charge oil pressure is ladder oil
The maximum pressure P2 of pressure, pressure oil enters oil cylinder oil inlet chamber 301, and compression cylinder reset spring 302 when work；Ladder oil pressure control
When device 1 processed does not work, oil cylinder oil suction chamber 301 is flowed out under the action of oil cylinder 302 spring restoring force of reset spring.
Pressure oil is filtered by filter 110, prevents oil residue from blocking solenoid valve, two-position four-way pilot-controlled electroma netic valve
10 controls flow into and out the pressure oil of friction clutch 300, and two-position four-way pilot-controlled electroma netic valve 10 has biggish latus rectum, allow
By bigger flow, can reduce friction clutch 300 into, oil extraction time, two-position four-way pilot-controlled electroma netic valve 10 is with organic
Tool positioning and hand push button can be realized power-off holding and manual operation function；Two-position four-way solenoid valve A20 is used to control highest
The switching of pressure P2；Two-position four-way solenoid valve A20 has machinery positioning and hand push button, and mechanical relief valve A30 controls pressure P1,
When pressure oil flows through mechanical relief valve A30, mechanical relief valve A30 outlet pressure is maintained at the sliding pressure P1 that rubs, mechanical relief valve
B40 controls precharge pressure P0, and when pressure oil flows through mechanical relief valve B40, the outlet pressure of mechanical relief valve B40 is maintained at oil-filled
Pressure P0, hydraulic control two position two-way valve 50 equally have big orifice, for realizing to quick oil-filled, the overflow valve of friction clutch 300
A60 has a big orifice, the range of the sliding pressure P1 that rubs of control, and when the sliding pressure P1 that rubs is excessive, overflow valve A60 starts overflow, and two
The control of two-way electromagnetic valve 70 flows into the oil of mechanical relief valve A30, and two-position four-way solenoid valve B80 control flows into mechanical relief valve B40
Oil and 50 hydraulic control mouth of hydraulic control two position two-way valve, realize that mechanical relief valve B40 and hydraulic control two position two-way valve 50 alternately circulate, unidirectionally
Pressure oil reverse flow is to mechanical relief valve A30, mechanical relief valve when valve A90 prevents two-position four-way pilot-controlled electroma netic valve 10 from powering off
B40, hydraulic control two position two-way valve 50, overflow valve A60；Check valve B100 prevents mechanical relief valve B40, hydraulic control two position two-way valve 50 from handing over
For pressure oil reverse flow when circulation to mechanical relief valve B40.
As shown in Fig. 1 a, Fig. 1 b, two-position four-way pilot-controlled electroma netic valve 10, two-position four-way solenoid valve 20, two-position two-way solenoid valve
70, two-position four-way solenoid valve B80 is in off-position, and hydraulic control two position two-way valve 50, overflow valve A60 are in close state, pressure
Power oil stream is through filter A110, two-position four-way solenoid valve B80, mechanical relief valve B40, check valve B100, check valve A90, two
Four-way pilot-controlled electroma netic valve 10, two-position four-way pilot-controlled electroma netic valve 10 is in close state generation, but can generate a little leakage, ladder oil
The outlet pressures of pressure control device 1 are 0, and it is as shown in Figure 1 b that whole work process generates ladder oil pressure curve.
Such as Fig. 2 a, two-position four-way pilot-controlled electroma netic valve 10 is opened, and pressure oil is followed by filter A110, two-position four-way electromagnetism
Valve B80, mechanical relief valve B40, check valve B100, check valve A90,10 engaging friction clutch of two-position four-way pilot-controlled electroma netic valve
300, the dead volume of oil cylinder in friction clutch 300 is full of, the pressure curve A510 of outlet end is as shown in Figure 2 b.
The present invention flows through the pressure reducing valve of different set pressure by the pressure oil of the several solenoid valve control elevated pressures of setting
Decompression is to control ladder pressure curve.
If Fig. 3 a, two-position four-way solenoid valve B80 are powered, hydraulic control two position two-way valve 50 is opened, and pressure oil is followed by filtering
Device A110, hydraulic control two position two-way valve 50, check valve A90,10 engaging friction clutch 300 of two-position four-way pilot-controlled electroma netic valve, compression
The pressure curve B520 of 302 to 90% stroke of oil cylinder reset spring, outlet end is as shown in Figure 3b.
If Fig. 4 a, two-position four-way solenoid valve B80 are powered off, hydraulic control two position two-way valve 50 is closed, and pressure oil is followed by filtering
Device A110, two-position four-way solenoid valve B80, mechanical relief valve B40, check valve B100, check valve A90, two-position four-way hydraulic control electromagnetism
10 engaging friction clutch 300 of valve, 302 to 100% stroke of compression cylinder reset spring, the pressure curve C530 of outlet end reach
Precharge pressure P0, as shown in Figure 4 b.
Such as Fig. 5 a, two-position two-way solenoid valve 70 is powered, and hydraulic control two position two-way valve 50 is closed, and pressure oil is followed by filter
A110, two-position two-way solenoid valve 70, mechanical relief valve A30, check valve A90,10 engaging friction of two-position four-way pilot-controlled electroma netic valve from
Clutch 300 continues that oil cylinder reset spring 302 is kept to be compressed to 100% stroke, and the pressure curve D540 of outlet end is shown in Fig. 5 b, reaches
The sliding pressure P1 that rubs of pressure.
Such as Fig. 6 a, two-position two-way solenoid valve 70 is powered off, and two-position four-way solenoid valve 20, which is powered, to be opened, and pressure oil flows through filter
A110, two-position four-way solenoid valve 20,10 engaging friction clutch 300 of two-position four-way pilot-controlled electroma netic valve continue compression and keep oil cylinder
Reset spring 302 is compressed to 100% stroke, and the pressure curve E550 of outlet end such as Fig. 6 b reaches maximum pressure P2.
Such as Fig. 7 a, two-position four-way pilot-controlled electroma netic valve 10 is powered off, pressure oil in oil cylinder oil inlet chamber 301 in friction clutch 300
It is quickly discharged through two-position four-way pilot-controlled electroma netic valve 10, the pressure curve G570 of outlet end such as Fig. 7 b, pressure drop to 0.Two four
The flow area of logical pilot-controlled electroma netic valve 10 is far longer than the flow area of two-position four-way solenoid valve 20, and flow area is bigger, flowing
Speed is faster.
Such as Fig. 9 a, for the gradually boosting curve that second voltage regulation valve generates, pressure is increased to maximum pressure P2 required time by 0
It is 6.0 seconds, reaching precharge pressure P0 time is 2 seconds, and reaching the sliding P1 times of pressure of rubbing is 3.5 seconds, and Fig. 9 b is ladder oil pressure
The ladder oil pressure curve 500 that control device generates.
Such as Figure 10, moment of friction is in 700 state of moment of friction-speed curves as revolving speed lowers and reduces, when revolving speed is low
When to some numerical value, moment of friction is will increase suddenly to a biggish value in friction 710 state of staring torque.
Such as Figure 11 a, staring torque graticule 330 is loaded, moment of friction is reduced as revolving speed lowers, the sliding torque curve that rubs
A810 is in the state of moment of friction-speed curves 700, loads climb curve A820, and load torque curve A830 is adopted such as Figure 11 b
With the curve 840 that gradually boosts, control oil pressure starts to increase within the 2nd second, reaches within the 6th second maximum pressure P2, loads since the 3.7th second
Raising speed, raising speed terminates within 5.5 seconds, and slipping of clutch 3.5 seconds, if Figure 11 c, unit area unit friction power curve A860 are 0.3, unit
Area unit friction work curve A850 maximum value 0.7, unit area thermic load curve A870 maximum value 0.15.
Such as Figure 12 a, staring torque graticule 330 is loaded, moment of friction is reduced as revolving speed lowers, the sliding torque curve that rubs
B910 is in the state of moment of friction-speed curves 700, loads climb curve B920, and load torque curve B930 is adopted such as Figure 12 b
With ladder boosting curve 940, control oil pressure starts to increase within the 2nd second, reaches within the 6th second maximum pressure P2, loads since the 2.1st second
Raising speed, raising speed terminates within 3.7 seconds, slipping of clutch 1.6 seconds, single if Figure 12 c, unit area unit friction power curve B960 are 0.4
Plane accumulates unit friction work curve B950 maximum value 0.5, unit area thermic load curve B970 maximum value 0.08.
Such as Figure 13, ladder boosts curve 940 with the comparison of curve 840 of gradually boosting, and the interval time of boosting is almost the same.
Such as Figure 14, sliding rub torque curve B910 and the sliding torque curve A810 comparison that rubs are controlled using ladder boosting curve 940
Friction clutch, the sliding torque curve B910 that rubs is more than load staring torque graticule 330 faster, it is sliding rub after, using rank
The cunning of the terraced boosting rectifier control mode torque that rubs is less than and is rubbed torque using the cunning of gradually boosting rectifier control mode, is not easy so that host is opposite
Bored vehicle occurs.
Such as Figure 15, climb curve A820 and load climb curve B920 comparison are loaded, using the control of ladder boosting mode
Friction clutch, faster, sliding friction time is shorter for torque loads raising speed.
Such as Figure 16 a and Figure 16 b, unit area unit friction work curve A850 and unit area unit friction work curve B950 are compared, single
Plane accumulated heat load curve A870 and unit area thermic load curve B970 are compared, using the control of ladder boosting mode friction from
Clutch, unit friction work is smaller, thermic load is also smaller.
The foregoing is only a preferred embodiment of the present invention, these specific embodiments are all based on the present invention
Different implementations under general idea, and scope of protection of the present invention is not limited thereto, it is any to be familiar with the art
Technical staff in the technical scope disclosed by the present invention, any changes or substitutions that can be easily thought of, should all cover of the invention
Within protection scope.Therefore, the scope of protection of the invention shall be subject to the scope of protection specified in the patent claim.
Claims (3)
1. a kind of ladder hydraulic adjustment device, including ladder hydraulic pressure control device (1) and ladder hydraulic pressure control device (1) outlet
The clutch assembly part connected by pipeline, ladder hydraulic pressure control device (1) arrival end is held to fill by the fuel feeding that pipeline connects
Set assembly part, which is characterized in that in the ladder hydraulic pressure control device (1), filter A(110) outlet end lead to respectively
Piping connects two-position four-way solenoid valve A(20) arrival end, two-position two-way solenoid valve (70) arrival end, two-position four-way solenoid valve B
(80) arrival end, hydraulic control two position two-way valve (50) arrival end, wherein the two-position four-way solenoid valve B(80) outlet end pipe
Road pass through mechanical relief valve B(40) be connected to check valve B(100) and arrival end；Two-position two-way solenoid valve (70) outlet end
Be connected to mechanical relief valve A(30) arrival end；Described hydraulic control two position two-way valve (50) outlet end, check valve B(100) outlet
End, mechanical relief valve A(30) the pipeline of outlet end connect all the way with overflow valve A(60), another way and check valve A(90) entrance
End connection；The check valve A(90) pipeline and two-position four-way hydraulic control of the outlet end with the outlet end two-position four-way solenoid valve A(20)
The arrival end of solenoid valve (10) connects, and the outlet end of two-position four-way pilot-controlled electroma netic valve (10) is i.e. and ladder hydraulic pressure control device (1)
Outlet end (3) is connect with the oil cylinder oil inlet chamber (301) in clutch assembly part.
2. ladder hydraulic adjustment device according to claim 1, which is characterized in that in the clutch assembly part,
Host (320) is internally provided with oil cylinder by friction clutch (300) connecting band dynamic load (310), friction clutch (300),
Include in oil cylinder oil cylinder oil inlet chamber (301) and reset spring (302)；Oil return opening (360) are additionally provided on friction clutch (300)
With oil inlet (370), the oil inlet (370) and fueller assembly part connect.
3. ladder hydraulic adjustment device according to claim 1, which is characterized in that the fueller assembly part packet
The oil pump (210) that motor (200) and motor (200) drive is included, the outlet end pipeline of oil pump (210) is all the way through filter B
(220) connect ladder hydraulic pressure control device (1) in filter A(110) arrival end, another way through overflow valve C(240) connect from
The oil inlet (370) of friction clutch (300) in clutch assembly part；The outlet end pipeline of oil pump (210), which is also set up, to be connected with
Overflow valve B(230), overflow valve C(240) overflow valve D(260 is connected on the pipeline of outlet end).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821505457.8U CN209012289U (en) | 2018-09-14 | 2018-09-14 | Ladder hydraulic adjustment device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821505457.8U CN209012289U (en) | 2018-09-14 | 2018-09-14 | Ladder hydraulic adjustment device |
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| Publication Number | Publication Date |
|---|---|
| CN209012289U true CN209012289U (en) | 2019-06-21 |
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ID=66833119
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|---|---|---|---|
| CN201821505457.8U Active CN209012289U (en) | 2018-09-14 | 2018-09-14 | Ladder hydraulic adjustment device |
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| CN (1) | CN209012289U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109058319A (en) * | 2018-09-14 | 2018-12-21 | 中国船舶重工集团公司第七0三研究所 | Ladder hydraulic adjustment device |
| CN112453388A (en) * | 2020-11-28 | 2021-03-09 | 湖南富栊新材料股份有限公司 | Aluminum-based binding agent, grinding block and preparation method thereof |
-
2018
- 2018-09-14 CN CN201821505457.8U patent/CN209012289U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109058319A (en) * | 2018-09-14 | 2018-12-21 | 中国船舶重工集团公司第七0三研究所 | Ladder hydraulic adjustment device |
| CN109058319B (en) * | 2018-09-14 | 2023-12-22 | 中国船舶重工集团公司第七0三研究所 | Ladder oil pressure adjusting device |
| CN112453388A (en) * | 2020-11-28 | 2021-03-09 | 湖南富栊新材料股份有限公司 | Aluminum-based binding agent, grinding block and preparation method thereof |
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