CN203157804U - Hydraulic system of tilting mechanism of self-discharging type carrier vehicle - Google Patents
Hydraulic system of tilting mechanism of self-discharging type carrier vehicle Download PDFInfo
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- CN203157804U CN203157804U CN 201320126652 CN201320126652U CN203157804U CN 203157804 U CN203157804 U CN 203157804U CN 201320126652 CN201320126652 CN 201320126652 CN 201320126652 U CN201320126652 U CN 201320126652U CN 203157804 U CN203157804 U CN 203157804U
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Abstract
The utility model discloses a hydraulic system of a tilting mechanism of a self-discharging type carrier vehicle. Hydraulic power is provided for the hydraulic system by an oil pump. A first locking oil cylinder and a second locking oil cylinder are controlled through a first throttle valve, a first three-position four-way reversing valve, an alternating check valve, a first balance valve and a second balance valve so as to achieve positioning and locking of a vehicle frame and a cargo tank, four tilting oil cylinders are used for driving the cargo tank to ascend and descend and control ascending and descending of the cargo tank through a conductive liquid reversing valve, a second three-position four-way reversing valve, a third balance valve, a fourth balance valve, a split-flow valve and a plurality of one-way valves, and under the normal condition, descending of the cargo tank is driven through gravity. After weightlessness of the cargo tank, the four tilting oil cylinders are driven to move downwards through switching of the second three-position four-way reversing valve to achieve descending of the cargo tank, and an overflow valve is used for ensuring safety of the hydraulic system. The hydraulic system overcomes the defect that a traditional cargo tank descends by relying on the gravity effect, improves reliability of operations of tilting mechanism of the self-discharging type carrier vehicle, and ensures safety of cargo loading and unloading of the carrier vehicle.
Description
Technical field
The utility model relates to a kind of hydraulic efficiency pressure system of self lighting type transport trolley tilting mechanism.
Background technology
The hydraulic efficiency pressure system of general tilting mechanism is mainly used in load carrying ability at 30t and following self lighting type transport vehicle, and it is by rising and the decline of stretching out and shrinking control loading container of oil cylinder, thus the function of realization transport trolley discharging.Usually this hydraulic efficiency pressure system is shunk at oil cylinder, when container descends, is relied on the gravity effect of container to realize descending, and makes the problem that the time spent container descends and can not solve when losing gravity.
Summary of the invention
Technical problem to be solved in the utility model provides a kind of hydraulic efficiency pressure system of self lighting type transport trolley tilting mechanism, this hydraulic efficiency pressure system has overcome the defective that traditional dependence gravity effect container descends, improve transport trolley tilting mechanism reliability of operation, guaranteed the safety of transport trolley handling goods.
For solving the problems of the technologies described above, the hydraulic efficiency pressure system of the utility model self lighting type transport trolley tilting mechanism comprises fuel tank, oil pump, first by pass valve, first locking cylinder, second locking cylinder, first dump ram, second dump ram, the 3rd dump ram and the 4th dump ram, described oil pump input end is connected described fuel tank respectively with the first by pass valve mouth, the described first by pass valve input end connects described oil pump mouth, this hydraulic efficiency pressure system also comprises the first throttle valve, second flow regulating valve, the first 3-position 4-way solenoid directional control valve, the second 3-position 4-way solenoid directional control valve, replace non-return valve, first balance cock, second balance cock, the 3rd balance cock, the 4th balance cock, guide's electro-hydraulic reversing valve, second by pass valve, the 3rd by pass valve, flow divider valve, first check valve, second check valve, the 3rd check valve, the 4th check valve, the 5th check valve, the 6th check valve and the 7th check valve, described oil pump mouth connects described first 3-position 4-way solenoid directional control valve P end respectively, guide's electro-hydraulic reversing valve P end and the 3rd balance cock input end, described first throttle valve is serially connected with between described oil pump mouth and the first 3-position 4-way solenoid directional control valve P end, described first 3-position 4-way solenoid directional control valve T end connects described fuel tank, the described first 3-position 4-way solenoid directional control valve side a and b connects described alternately two mouths of non-return valve respectively, first balance cock V end and second balance cock V end, described first balance cock C end connects described first locking cylinder and the second locking cylinder loculus respectively, described second balance cock C end connects described first locking cylinder and the big chamber of second locking cylinder respectively, described first balance cock X end connects described second balance cock V end, described second balance cock X end connects described first balance cock V end, described guide's electro-hydraulic reversing valve T end, the first check valve input end, the second by pass valve mouth is connected described fuel tank respectively with the 3rd by pass valve mouth, described guide's electro-hydraulic reversing valve A end connects described the 4th balance cock X end through described second flow regulating valve, described guide's electro-hydraulic reversing valve B end connects described the 4th balance cock V end, described the 4th balance cock X end connects described the 3rd by pass valve input end respectively and replaces the non-return valve input end, described the 4th balance cock C end connects the big chamber of described first dump ram respectively, the big chamber of second dump ram, the big chamber of the 3rd dump ram and the big chamber of the 4th dump ram, described the 3rd balance cock mouth connects described second 3-position 4-way solenoid directional control valve P end, described second 3-position 4-way solenoid directional control valve T end connects the described first check valve mouth, described second 3-position 4-way solenoid directional control valve A end connects first check valve respectively, the 4th check valve, the 5th check valve, the 6th check valve and the 7th check valve mouth, described second 3-position 4-way solenoid directional control valve B end connects described flow divider valve P end, described flow divider valve side a and b is connected the described second by pass valve input end through described second check valve respectively with the 3rd check valve, described flow divider valve A end connects the described first dump ram loculus respectively, the second dump ram loculus, the 7th check valve input end and the 6th check valve input end, described flow divider valve B end connects described the 3rd dump ram loculus respectively, the 4th dump ram loculus, the 5th check valve input end and the 4th check valve input end.
Further, above-mentioned first dump ram, second dump ram, the 3rd dump ram and the 4th dump ram are respectively the multi-joint telescoping oil cylinders.
Because the hydraulic efficiency pressure system of the utility model self lighting type transport trolley tilting mechanism has adopted technique scheme, be that this hydraulic efficiency pressure system provides hydraulic power by oil pump, first locking cylinder and second locking cylinder are by the first throttle valve, first three position four-way directional control valve, replace non-return valve, first balance cock and the control of second balance cock, realize the position and lock of vehicle frame and container, four dump rams are used for driving the lifting of container and pass through guide's electro-hydraulic reversing valve, second three position four-way directional control valve, the 3rd balance cock, the 4th balance cock, flow divider valve and the control of some check valves, container descends and passes through gravity drive under the normal circumstances, after container weightlessness, four dump rams of switching driving by second three position four-way directional control valve move downward, realize the decline of container, by pass valve is used for guaranteeing the safety of hydraulic efficiency pressure system.This hydraulic efficiency pressure system has overcome the defective that traditional dependence gravity effect container descends, and has improved transport trolley tilting mechanism reliability of operation, has guaranteed the safety of transport trolley handling goods.
Description of drawings
The utility model is described in further detail below in conjunction with drawings and embodiments:
Fig. 1 is the hydraulic efficiency pressure system scheme drawing of the utility model self lighting type transport trolley tilting mechanism.
The specific embodiment
As shown in Figure 1, the hydraulic efficiency pressure system of the utility model self lighting type transport trolley tilting mechanism comprises fuel tank 3, oil pump 1, first by pass valve 2, first locking cylinder 41, second locking cylinder 42, first dump ram 51, second dump ram 52, the 3rd dump ram 53 and the 4th dump ram 54, described oil pump 1 input end is connected described fuel tank 3 respectively with first by pass valve, 2 mouths, described first by pass valve, 2 input ends connect described oil pump 1 mouth, this hydraulic efficiency pressure system also comprises first throttle valve 61, second flow regulating valve 75, the first 3-position 4-way solenoid directional control valve 62, the second 3-position 4-way solenoid directional control valve 72, replace non-return valve 63, first balance cock 64, second balance cock 65, the 3rd balance cock 78, the 4th balance cock 73, guide's electro-hydraulic reversing valve 71, second by pass valve 76, the 3rd by pass valve 77, flow divider valve 74, first check valve 81, second check valve 82, the 3rd check valve 83, the 4th check valve 84, the 5th check valve 85, the 6th check valve 86 and the 7th check valve 87, described oil pump 1 mouth connects the P end of the described first 3-position 4-way solenoid directional control valve 62 respectively, the P end of guide's electro-hydraulic reversing valve 71 and the input end of the 3rd balance cock 78, described first throttle valve 61 is serially connected with between the P end of described oil pump 1 mouth and the first 3-position 4-way solenoid directional control valve 62, the T end of the described first 3-position 4-way solenoid directional control valve 62 connects described fuel tank 3, the side a and b of the described first 3-position 4-way solenoid directional control valve 62 connects described alternately 63 two mouths of non-return valve respectively, the V end of first balance cock 64 and the V end of second balance cock 65, the C end of described first balance cock 64 connects the loculus of described first locking cylinder 41 and second locking cylinder 42 respectively, the C end of described second balance cock 65 connects the big chamber of described first locking cylinder 41 and second locking cylinder 42 respectively, the X end of described first balance cock 64 connects the V end of described second balance cock 65, the X end of described second balance cock 65 connects the V end of described first balance cock 64, the T end of described guide's electro-hydraulic reversing valve 71, first check valve, 81 input ends, second by pass valve, 76 mouths are connected described fuel tank 3 respectively with the 3rd by pass valve 77 mouths, the A end of described guide's electro-hydraulic reversing valve 71 connects the X end of described the 4th balance cock 73 through described second flow regulating valve 75, the B end of described guide's electro-hydraulic reversing valve 71 connects the V end of described the 4th balance cock 73, the X end of described the 4th balance cock 73 connects described the 3rd by pass valve 77 input ends respectively and replaces non-return valve 63 input ends, the C end of described the 4th balance cock 73 connects described first dump ram 51 big chambeies respectively, second dump ram, 52 big chambeies, the 3rd dump ram 53 big chambeies and the 4th dump ram 54 big chambeies, described the 3rd balance cock 78 mouths connect the P end of the described second 3-position 4-way solenoid directional control valve 72, the T end of the described second 3-position 4-way solenoid directional control valve 72 connects described first check valve, 81 mouths, the A end of the described second 3-position 4-way solenoid directional control valve 72 connects first check valve 81 respectively, the 4th check valve 84, the 5th check valve 85, the 6th check valve 86 and the 7th check valve 87 mouths, the B end of the described second 3-position 4-way solenoid directional control valve 72 connects the P end of described flow divider valve 74, the side a and b of described flow divider valve 74 is connected described second by pass valve, 76 input ends through described second check valve 82 respectively with the 3rd check valve 83, the A end of described flow divider valve 74 connects described first dump ram, 51 loculuses respectively, second dump ram, 52 loculuses, the 7th check valve 87 input ends and the 6th check valve 86 input ends, the B end of described flow divider valve 74 connects described the 3rd dump ram 53 loculuses respectively, the 4th dump ram 54 loculuses, the 5th check valve 85 input ends and the 4th check valve 84 input ends.
Further, above-mentioned first dump ram 51, second dump ram 52, the 3rd dump ram 53 and the 4th dump ram 54 are respectively the multi-joint telescoping oil cylinders, thereby realize the big stroke lifting of container.
In this hydraulic efficiency pressure system, the P of 3-position 4-way solenoid directional control valve and guide's electro-hydraulic reversing valve end is respectively the actuator port that is connected actuating unit or other valves for oil inlet, T end for return opening, side a and b; The P end of flow divider valve is respectively the actuator port that connects actuating unit or other valves for oil inlet, side a and b; Balance cock is made up of check valve and sequence valve and is constituted unidirectional balance cock, and the effect in this hydraulic efficiency pressure system is to make the kinematic velocity of dump ram not be subjected to the influence of load change, keeps balance; The V of balance cock holds external control port, the X end of balance cock is oil outlet when being oil inlet, reverse (decline) when dump ram forward (rising), and the C end of balance cock is oil inlet when being oil outlet, reverse (decline) when dump ram forward (rising).The balance cock principle of work is: V end oil-feed during forward, pressure oil arrives the C end by check valve, C end oil-feed in the time of oppositely, because the unidirectional logical oil effect of check valve, can't arrive the V end by check valve, this moment, external control port X end overcame the sequence valve spring force of sequence valve, and pressure oil flows to the V end from the C end.The bidirectional balanced valve of first balance cock and second balance cock formation in parallel in this hydraulic efficiency pressure system.
Oil pump provides hydraulic power for whole hydraulic efficiency pressure system in this hydraulic efficiency pressure system; First by pass valve plays the safety guard-safeguard effect of system, when system overpressure, opens overflow, prevents the oil pump overload; First balance cock, second balance cock and the 4th balance cock are respectively the combine valve of check valve and sequence valve, when being in container rising operating mode, pressure oil enters each dump ram fast by the check valve oil circuit, increase the speed of stretching out of dump ram, when container was in the decline operating mode, because the nonreturn flow of check valve, hydraulic oil can only flow back to fuel tank from the sequence valve passage, and sequence valve must be opened at the pressure Shi Caineng that acquires a certain degree, excessive velocities when avoiding container to descend and having an accident; First locking cylinder and second locking cylinder are single acting oil cylinder, but when oil cylinder stretches out position and lock vehicle frame and container; Flow divider valve is used for when container descends, even still can obtain identical flow when each dump ram bears different loads, thereby guarantees when each dump ram is withdrawn synchronous; Each dump ram is two-way cylinder, when oil cylinder is withdrawn, can feed the mode of pressure oil by the oil cylinder loculus, promotes oil cylinder and moves downward, and guarantees that the oil cylinder withdrawal puts in place; In guide's electro-hydraulic reversing valve when the priority valve electromagnet is not switched on, under the effect of spring force, pilot valve core is in meta, and the valve core of main valve pressure at two ends is zero, is in meta under the effect of spring force, when the priority valve electromagnet is switched on, pilot valve core moves, and changes pressure oil and flows to, the be under pressure effect of oil of the end in the valve core of main valve two ends, valve core of main valve is moved, realize the change of pressure oil flow direction.
This hydraulic efficiency pressure system mainly is made of locking oil circuit and the oil circuit of tumbling, and its principle of work is respectively:
Locking oil circuit: during locking state, the energising of the first 3-position 4-way solenoid directional control valve left end electromagnet, spool moves right, change-over valve left side position work, the pressure oil that comes from oil pump enter two big chambeies of locking cylinder enter the check valve of second balance cock through first throttle valve, the first 3-position 4-way solenoid directional control valve after; Pressure oil is opened the sequence valve passage of first balance cock simultaneously, and oil return is flowed back to fuel tank by the sequence valve of two locking cylinder loculuses through first balance cock by the first 3-position 4-way solenoid directional control valve.During released state, the energising of the first 3-position 4-way solenoid directional control valve right-hand member electromagnet, spool is moved to the left, change-over valve right position work, and the pressure oil that comes from oil pump enters two locking cylinder loculuses enter the check valve of first balance cock through first throttle valve, the first 3-position 4-way solenoid directional control valve after; Pressure oil is opened the sequence valve passage of second balance cock simultaneously, and oil return is flowed back to fuel tank by the first 3-position 4-way solenoid directional control valve by two big chambeies of locking cylinder behind the sequence valve of second balance cock.
The oil circuit of tumbling: during propradation, the priority valve right side energising of guide's electro-hydraulic reversing valve, the promotion spool is moved to the left, priority valve right position work, the pressure oil that comes from oil pump is divided into two-way: the control oil circuit is by the priority valve right side, arrive the main valve left side, promote main valve plug and move right, make the position work of a main valve left side; Working connection enters the check valve of the 4th balance cock by main valve, arrives the big chamber of each dump ram and promotes oil cylinder and stretch out step by step, drives container and tumbles, and realizes unloading.During the decline state, the energising of the priority valve of guide's electro-hydraulic reversing valve left side promotes spool and moves right, the position work of a priority valve left side, the pressure oil that comes from oil pump is divided into two-way: the control oil circuit arrives the main valve right side by the priority valve left side, the promotion main valve plug is moved to the left, and makes main valve right position work; Working connection passes through main valve, enter second flow regulating valve, arrive the sequence valve of the 4th balance cock, when reaching the settling pressure of the 4th balance cock sequence valve, the sequence valve of the 4th balance cock is opened, the pressure oil in each big chamber of dump ram is got back to fuel tank by the sequence valve of the 4th balance cock, the right position of main valve of guide's electro-hydraulic reversing valve under the effect of container deadweight gravity, realizes the progressively decline of container.Simultaneously, a part of pressure oil by second flow regulating valve also enters the locking oil circuit by replacing non-return valve, the reliability of assurance locking oil circuit work.
After container loses the gravity effect, the energising of second 3-position 4-way solenoid directional control valve left side, spool moves to right, make it in the work of position, a left side, the pressure oil from oil pump arrives the loculus of each dump ram after the flow regulating valve of the 3rd balance cock enters the second 3-position 4-way solenoid directional control valve, flow divider valve, promote each dump ram and move downward, after container decline puts in place, the outage of the second 3-position 4-way solenoid directional control valve, pressure oil stops to enter the loculus of each dump ram, realizes that the container decline after the weightlessness puts in place.
This hydraulic efficiency pressure system has overcome the defective that can't descend and put in place after traditional transport vehicle container weightlessness, has improved transport trolley tilting mechanism reliability of operation, can be applicable to all kinds of self lighting type transport vehicles such as 120t tilt bed chassis of steel mill's steel scrap transportation.
Claims (2)
1. the hydraulic efficiency pressure system of a self lighting type transport trolley tilting mechanism, comprise fuel tank, oil pump, first by pass valve, first locking cylinder, second locking cylinder, first dump ram, second dump ram, the 3rd dump ram and the 4th dump ram, described oil pump input end is connected described fuel tank respectively with the first by pass valve mouth, the described first by pass valve input end connects described oil pump mouth, it is characterized in that: also comprise the first throttle valve, second flow regulating valve, the first 3-position 4-way solenoid directional control valve, the second 3-position 4-way solenoid directional control valve, replace non-return valve, first balance cock, second balance cock, the 3rd balance cock, the 4th balance cock, guide's electro-hydraulic reversing valve, second by pass valve, the 3rd by pass valve, flow divider valve, first check valve, second check valve, the 3rd check valve, the 4th check valve, the 5th check valve, the 6th check valve and the 7th check valve, described oil pump mouth connects described first 3-position 4-way solenoid directional control valve P end respectively, guide's electro-hydraulic reversing valve P end and the 3rd balance cock input end, described first throttle valve is serially connected with between described oil pump mouth and the first 3-position 4-way solenoid directional control valve P end, described first 3-position 4-way solenoid directional control valve T end connects described fuel tank, the described first 3-position 4-way solenoid directional control valve side a and b connects described alternately two mouths of non-return valve respectively, first balance cock V end and second balance cock V end, described first balance cock C end connects described first locking cylinder and the second locking cylinder loculus respectively, described second balance cock C end connects described first locking cylinder and the big chamber of second locking cylinder respectively, described first balance cock X end connects described second balance cock V end, described second balance cock X end connects described first balance cock V end, described guide's electro-hydraulic reversing valve T end, the first check valve input end, the second by pass valve mouth is connected described fuel tank respectively with the 3rd by pass valve mouth, described guide's electro-hydraulic reversing valve A end connects described the 4th balance cock X end through described second flow regulating valve, described guide's electro-hydraulic reversing valve B end connects described the 4th balance cock V end, described the 4th balance cock X end connects described the 3rd by pass valve input end respectively and replaces the non-return valve input end, described the 4th balance cock C end connects the big chamber of described first dump ram respectively, the big chamber of second dump ram, the big chamber of the 3rd dump ram and the big chamber of the 4th dump ram, described the 3rd balance cock mouth connects described second 3-position 4-way solenoid directional control valve P end, described second 3-position 4-way solenoid directional control valve T end connects the described first check valve mouth, described second 3-position 4-way solenoid directional control valve A end connects first check valve respectively, the 4th check valve, the 5th check valve, the 6th check valve and the 7th check valve mouth, described second 3-position 4-way solenoid directional control valve B end connects described flow divider valve P end, described flow divider valve side a and b is connected the described second by pass valve input end through described second check valve respectively with the 3rd check valve, described flow divider valve A end connects the described first dump ram loculus respectively, the second dump ram loculus, the 7th check valve input end and the 6th check valve input end, described flow divider valve B end connects described the 3rd dump ram loculus respectively, the 4th dump ram loculus, the 5th check valve input end and the 4th check valve input end.
2. the hydraulic efficiency pressure system of self lighting type transport trolley tilting mechanism according to claim 1, it is characterized in that: described first dump ram, second dump ram, the 3rd dump ram and the 4th dump ram are respectively the multi-joint telescoping oil cylinders.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320126652 CN203157804U (en) | 2013-03-20 | 2013-03-20 | Hydraulic system of tilting mechanism of self-discharging type carrier vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320126652 CN203157804U (en) | 2013-03-20 | 2013-03-20 | Hydraulic system of tilting mechanism of self-discharging type carrier vehicle |
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| CN203157804U true CN203157804U (en) | 2013-08-28 |
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| CN 201320126652 Expired - Fee Related CN203157804U (en) | 2013-03-20 | 2013-03-20 | Hydraulic system of tilting mechanism of self-discharging type carrier vehicle |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106536944A (en) * | 2014-06-18 | 2017-03-22 | 凯斯纽荷兰(中国)管理有限公司 | A safety hydraulic circuit |
| CN110056552A (en) * | 2019-03-27 | 2019-07-26 | 中铁隧道股份有限公司 | A kind of monoblock type turns over slag workbench hydraulic system |
| CN111173790A (en) * | 2020-01-14 | 2020-05-19 | 福建侨龙应急装备股份有限公司 | Emergency self-loading and unloading equipment and hydraulic control system thereof |
| CN111268600A (en) * | 2020-02-28 | 2020-06-12 | 安徽合力股份有限公司 | Forklift integrated control hydraulic system for log clamp |
| CN113639839A (en) * | 2021-03-19 | 2021-11-12 | 徐州工程学院 | Logistics vehicle weighing sensor protection device and control method |
| CN118544922A (en) * | 2024-07-29 | 2024-08-27 | 江苏常矿工程机械有限公司 | Unmanned pure electric mining rigid dump truck lifting system and control method |
-
2013
- 2013-03-20 CN CN 201320126652 patent/CN203157804U/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106536944A (en) * | 2014-06-18 | 2017-03-22 | 凯斯纽荷兰(中国)管理有限公司 | A safety hydraulic circuit |
| CN106536944B (en) * | 2014-06-18 | 2019-04-16 | 凯斯纽荷兰(中国)管理有限公司 | Safe hydraulic pressure circuit |
| CN110056552A (en) * | 2019-03-27 | 2019-07-26 | 中铁隧道股份有限公司 | A kind of monoblock type turns over slag workbench hydraulic system |
| CN111173790A (en) * | 2020-01-14 | 2020-05-19 | 福建侨龙应急装备股份有限公司 | Emergency self-loading and unloading equipment and hydraulic control system thereof |
| CN111173790B (en) * | 2020-01-14 | 2022-09-13 | 福建侨龙应急装备股份有限公司 | Emergency self-loading and unloading equipment and hydraulic control system thereof |
| CN111268600A (en) * | 2020-02-28 | 2020-06-12 | 安徽合力股份有限公司 | Forklift integrated control hydraulic system for log clamp |
| CN111268600B (en) * | 2020-02-28 | 2024-05-03 | 安徽合力股份有限公司 | Fork truck integrated control hydraulic system for log clamp |
| CN113639839A (en) * | 2021-03-19 | 2021-11-12 | 徐州工程学院 | Logistics vehicle weighing sensor protection device and control method |
| CN118544922A (en) * | 2024-07-29 | 2024-08-27 | 江苏常矿工程机械有限公司 | Unmanned pure electric mining rigid dump truck lifting system and control method |
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| C14 | Grant of patent or utility model | ||
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130828 Termination date: 20160320 |
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| CF01 | Termination of patent right due to non-payment of annual fee |