CN211770092U - Hydraulic control system for forklift gearbox - Google Patents
Hydraulic control system for forklift gearbox Download PDFInfo
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- CN211770092U CN211770092U CN201921468760.XU CN201921468760U CN211770092U CN 211770092 U CN211770092 U CN 211770092U CN 201921468760 U CN201921468760 U CN 201921468760U CN 211770092 U CN211770092 U CN 211770092U
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Abstract
The utility model relates to a transport vehicle hydraulic transmission's proportion of shifting pressure regulating control technical field, and disclose a fork truck gearbox hydraulic control system, keep off clutch KA, one fender control valve, two keep off clutch KB, two keep off the control valve, keep off clutch KR, keep off the control valve, keep off clutch KV and keep off the control valve forward backward including controller, one, the upper right side of controller has from left to right set gradually one and keeps off clutch KA, two keep off clutch KB, keep off clutch KR and keep off clutch KV forward, one keeps off clutch KA, two keep off clutch KB, keep off clutch KR and keep off clutch KV forward and from left to right set gradually one below keeping off clutch KR, keeping off the control valve backward and keep off the control valve forward. An emergency risk avoiding function is added, so that the whole vehicle control is safer and more reliable; the self-tuning function fully solves the gear shifting impact caused by various differences and errors of the system.
Description
Technical Field
The utility model relates to a transport vehicle hydraulic transmission's proportion pressure regulating control technical field of shifting specifically is a fork truck gearbox hydraulic control system.
Background
The hydraulic transmission is adopted in a five-ton and above-tonnage forklift transmission system, the variable speed control system adopts a switch type on-off control valve to carry out the variable speed control of the forklift, the shifting and reversing control valves are mostly integrated electro-hydraulic control valves, and a hydraulic clutch (hereinafter referred to as a clutch) is adopted as an executing mechanism for reversing, shifting and power transmission.
Along with the increasingly high requirements on the driving comfort and safe operation of the forklift, the on-off control precision of the integrated electro-hydraulic control valve is poor, the control pressure cannot realize proportional adjustment, and in the gear shifting process, the pressure in an oil way can only be controlled in an on-off mode, so that the torque and the pressure transmitted by the clutch can realize pulse type change, and serious gear shifting impact of a vehicle can be caused. Strong shifting shocks shorten the service life of the transmission components and affect the riding comfort of the driver and passengers and the quality of the goods to be transported. For a carrying vehicle with frequent gear shifting and severe working environment, the smoothness of the transmission system is more important.
In order to improve the gear shifting quality of the whole forklift gear shifting and prolong the service life of a transmission part, the electro-hydraulic proportional cartridge valve is adopted on the basis of the original control system, a pressure regulating valve, a buffer valve, a inching valve and a valve body are omitted, the cost and the failure rate of a product are reduced, and meanwhile, the space occupied by the whole control valve is greatly reduced. The cancelled inching valve and the buffer valve realize the functions of the inching valve and the buffer valve through a proportional valve and a controller.
SUMMERY OF THE UTILITY MODEL
For realizing above-mentioned good travelling comfort and safe operation of driving, improve the whole car of fork truck and trade the quality of shifting and improve the life's of driving medium purpose, the utility model provides a following technical scheme: a hydraulic control system of a forklift gearbox comprises a controller, a first gear clutch KA, a first gear control valve, a second gear clutch KB, a second gear control valve, a reverse gear clutch KR, a reverse gear control valve, a forward gear clutch KV and a forward gear control valve, wherein the first gear clutch KA, the second gear clutch KB, the reverse gear clutch KR and the forward gear clutch KV are sequentially arranged at the upper right of the controller from left to right, a first gear control valve, a second gear control valve, a reverse gear control valve and a forward gear control valve are sequentially arranged below the first gear clutch KA, the second gear clutch KB, the reverse gear clutch KR and the forward gear clutch KV from left to right, the first gear control valve is respectively provided with a valve port A4, a valve port Y4, a valve port P4 and a valve port T4 from top to bottom, the second gear control valve is respectively provided with a valve port A3, a valve port T3, a valve port P3 and a valve port Y5 from top to bottom, the reverse gear control valve is provided with a valve port A2, a proportional control valve Y2, a valve port P2 and a valve port T2 from top to bottom, and the forward gear control valve is provided with a valve port A1, a valve port T1, a valve port P1 and a proportional control valve Y1 from top to bottom.
The utility model has the advantages that: the control system has the characteristics of intelligent control, high reliability, quick response and the like; the proportional valve replaces a pressure regulating valve, a buffer valve and a inching valve, and simultaneously, the functions of gear shifting and reversing are realized, so that the structure of the gearbox is more compact, the installation and the maintenance are more convenient, and the cost and the failure rate of the product are reduced; the smoothness of automatic gear shifting of the whole vehicle, the service life of a transmission part and the reliability of the whole vehicle are improved; an emergency risk avoiding function is added, so that the whole vehicle control is safer and more reliable; the self-tuning function fully solves the gear shifting impact caused by various differences and errors of the system.
Preferably, the first gear control valve, the second gear control valve, the reverse gear control valve and the forward gear control valve are electrically connected with electromagnetic coils, and the opening and closing of the valves can be controlled through the electromagnetic coils.
For optimization, the system pressure oil is divided into a node a, a node b and a node c, firstly, the system pressure oil is divided into two paths at the node a, one path passes through the point b and then enters the first-gear clutch KA and the second-gear clutch KB through the proportional control valves Y4 and Y5, respectively, and the other path passes through the point c and then enters the forward clutch KV and the reverse clutch KR through the proportional control valves Y1 and Y2, respectively.
Preferably, the controller is in signal connection with the proportional control valve Y4, the proportional control valve Y5, the proportional control valve Y2 and the proportional control valve Y1, and the controller outputs a signal of a calculation result to the proportional valve through a specified algorithm according to the detected state of the whole vehicle to adjust the pressure of the proportional valve to change according to a set rule.
Preferably, the first-gear clutch KA, the second-gear clutch KB, the reverse gear clutch KR and the forward gear clutch KV are electrically connected with the valve port T4, the valve port T3, the valve port T2 and the valve port T1 respectively, in a neutral state, the proportional control valve Y1, the proportional control valve Y2, the proportional control valve Y4 and the proportional control valve Y5 are in a neutral state, the first-gear clutch KA, the second-gear clutch KB, the reverse gear clutch KR and the forward gear clutch KV are connected with the valve port T4, the valve port T3, the valve port T2 and the valve port T1 respectively for oil discharge, no pressure oil enters into the four clutches, and no power output is generated when the vehicle is in the neutral state
Preferably, the valve port P4, the valve port P3, the valve port P2 and the valve port P1 are respectively matched with the valve port a4, the valve port A3, the valve port a2 and the valve port a1, the valve port a4, the valve port A3, the valve port a2 and the valve port a1 are respectively matched with the valve port T4, the valve port T3, the valve port T2 and the valve port T1, an electromagnetic coil of the proportional control valve Y1 is electrified to be in a conducting state, the valve port P1 is connected with the valve port a1 for oil feeding, and transmission oil enters the forward clutch KV. The electromagnetic coil of the proportional control valve Y2 is disconnected when power is lost, the clutch KR is in a non-working state, and the valve port A2 and the valve port T2 are communicated for oil discharge. Meanwhile, the electromagnetic coil of the proportional control valve Y4 is electrified to be in a conducting state, the valve port P4 is communicated with the valve port A4 to feed oil, the first-gear clutch KA works, and the vehicle runs at the speed of 1 gear and outputs power. Under the condition of forward 2-gear, the proportional control valve Y1 and the forward clutch KV are in working states, at the moment, the proportional control valve Y4 is in a power-off state, the valve port A4 and the valve port T4 are communicated with the first-gear clutch KA for oil discharge, the electromagnetic coil of the proportional control valve Y5 is electrified and is in a conducting state, the valve port P3 and the valve port A3 are communicated for oil inlet, the second-gear clutch KB works, and the vehicle runs at the speed of 2-gear and outputs power.
Drawings
FIG. 1 is a schematic diagram of a proportional pressure regulating shift control system;
FIG. 2 is a schematic diagram of a primary electro-hydraulic shift control system.
In the figure: 1-controller, 2-first gear clutch KA, 3-first gear control valve, 4-second gear clutch KB, 5-second gear control valve, 6-reverse gear clutch KR, 7-reverse gear control valve, 8-forward gear clutch KV, 9-forward gear control valve, 10-proportional control valve Y4, 11-valve port T4, 12-node b, 13-valve port T3, 14-valve port P3, 15-proportional control valve Y5, 16-proportional control valve Y2, 17-valve port P2, 18-valve port T2, 19-node a, 20-node c, 21-valve port T1, 22-valve port P1, 23-proportional control valve Y1, 24-valve port A1, 25-electromagnetic coil, 26-valve port A2, 27-valve port A3, 28-A4, 29-port P4.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
Referring to fig. 1, a hydraulic control system for a forklift transmission comprises a controller, a proportional control valve Y4, a proportional control valve Y5, a proportional control valve Y2 and a proportional control valve Y1, wherein the controller outputs a calculation result signal to the proportional valve to adjust the pressure of the calculation result signal according to the detected state of the whole forklift through a specified algorithm and changes according to a set rule, a first gear clutch KA, a first gear control valve, a second gear clutch KB, a second gear control valve, a reverse gear clutch KR, a reverse gear control valve, a forward gear clutch KV and a forward gear control valve are sequentially arranged at the upper right of the controller from left to right, a first gear clutch KA, a second gear clutch KB, a reverse gear clutch KR and a forward gear clutch KV are respectively and electrically connected with valve ports T4, T3, T2 and T1, in a neutral gear state, the proportional control valve Y1, the proportional control valve Y2, the proportional control valve Y4 and the proportional control valve Y5 are in a neutral position state, the first gear clutch KA, the second gear clutch KB, the reverse gear clutch KR and the forward gear clutch KV are respectively communicated with the valve port T4, the valve port T3, the valve port T2 and the valve port T1 for oil unloading, no pressure oil enters the four clutches, the vehicle is in the neutral gear state and has no power output, a first gear control valve, a second gear control valve, a reverse gear control valve and a forward gear control valve are sequentially arranged below the first gear clutch KA, the second gear clutch KB, the reverse gear clutch KR and the forward gear clutch KV from left to right, the first gear control valve is respectively provided with the valve port A4, the proportional control valve Y4, the valve port P4 and the valve port T4 from top to bottom, the first gear control valve, the second gear control valve, the reverse gear control valve and the forward gear control valve are respectively and electrically connected with electromagnetic coils, the switch of the valve can be controlled by an electromagnetic coil, a second gear control valve is respectively provided with a valve port A3, a valve port T3, a valve port P3 and a proportional control valve Y5 from top to bottom, a back gear control valve is respectively provided with a valve port A2, a proportional control valve Y2, a valve port P2 and a valve port T2 from top to bottom, a forward gear control valve is respectively provided with a valve port A2, a valve port T2, a valve port P2 and a proportional control valve Y2 from top to bottom, the valve port P2 and the valve port P2 are respectively matched with the valve port A2, the valve port A2 and the valve port P2, the electromagnetic coil of the proportional control valve Y2 is electrified to be in a conducting state, the forward gear port P2 is connected with the valve port A2, and oil enters the clutch. The electromagnetic coil of the proportional control valve Y2 is disconnected when power is lost, the clutch KR is in a non-working state, and the valve port A2 and the valve port T2 are communicated for oil discharge. Meanwhile, the electromagnetic coil 25 of the proportional control valve Y4 is electrified to be in a conducting state, the valve port P429 is communicated with the valve port A428 to feed oil, the first-gear clutch KA works, and the vehicle runs at the speed of 1 gear and outputs power. Under the condition of forward 2 gear, the proportional control valve Y1 and the forward gear clutch KV are in a working state, at the moment, the proportional control valve Y4 is in a power-off state, the valve port A4 and the valve port T4 are communicated with the first gear clutch KA clutch for oil discharge, the electromagnetic coil of the proportional control valve Y5 is electrified to be in a conducting state, the valve port P3 and the valve port A3 are communicated for oil inlet, the second gear clutch KB works, the vehicle runs at the 2-gear speed and outputs power, the system pressure oil is divided into a node a, a node b and a node c, firstly, the system pressure oil is divided into two paths at the node a, one path passes through the node b and then enters the first gear clutch KA and the second gear clutch KB respectively through the proportional control valve Y4 and the proportional control valve Y5, and the other path passes through the node c and then enters the forward clutch KV and the reverse clutch KR respectively through the proportional control valve Y1 and the proportional control valve Y2.
When the system is used, firstly, system pressure oil is divided into two paths at a node a, one path of the system pressure oil passes through a node b and then respectively enters a first-gear clutch KA and a second-gear clutch KB after passing through a proportional control valve Y4 and a proportional control valve Y5, and the other path of the system pressure oil passes through a node c and then respectively enters a forward clutch KV and a backward clutch KR after passing through a proportional control valve Y1 and a proportional control valve Y2; then, the controller outputs a calculation result signal to the proportional valve through a specified algorithm according to the detected state of the whole vehicle to adjust the pressure of the proportional valve to change according to a set rule, and at the moment, the system can be divided into the following working states according to the function of the proportional control valve:
first, neutral state, proportional valve Y1, Y2, Y4 and Y5 are in neutral state, first gear clutch KA, second gear clutch KB, reverse gear clutch KR and forward gear clutch KV are respectively communicated with valve port T4, valve port T3, valve port T2 and valve port T1 for oil discharge, no pressure oil enters into the four clutches, and the vehicle is in neutral state and has no power output.
The working condition of the forward gear can be divided into working conditions of forward 1 gear and forward 2 gears:
1. under the condition of forward 1 gear, the electromagnetic coil of the proportional control valve Y1 is electrified to be in a conducting state, the valve port P1 is communicated with the valve port A1 for oil feeding, transmission oil enters the forward gear clutch KV, the electromagnetic coil of the proportional control valve Y2 is electrified and disconnected, the reverse gear clutch KR is in a non-working state, and the valve port A2 is communicated with the valve port T2 for oil discharging. Meanwhile, an electromagnetic coil of the proportional control valve Y4 is electrified to be in a conducting state, a valve port P4 is communicated with a valve port A4 to feed oil, the first-gear clutch KA works, and the vehicle runs at the speed of 1 gear and outputs power.
2. Under the condition of forward 2-gear, the proportional control valve Y1 and the forward gear clutch KV are in working states, at the moment, the proportional control valve Y4 shift valve is in a power-off state, the valve port A4 and the valve port T4 are communicated with the first gear clutch KA for oil discharge, the electromagnetic coil of the proportional control valve Y5 is electrified and is in a conducting state, the valve port P3 and the valve port A3 are communicated for oil inlet, the second gear clutch KB works, and the vehicle runs at the speed of 2-gear and outputs power.
Thirdly, the working condition of the reverse gear is also divided into working conditions of reverse 1 gear and reverse 2 gear:
1. under the condition of backing 1 gear, an electromagnetic coil of the proportional control valve Y2 is in a conducting state, a valve port P2 is communicated with a valve port A2 for oil feeding, transmission oil enters a backing gear clutch KR, the proportional control valve Y1, the electromagnetic coil and a forward gear clutch KV are in a non-working state, and the valve port A1 is communicated with a valve port T1 for oil discharging. At the moment, the proportional control valve Y4 is in a working conduction state, pressure oil enters A4 through a valve port P4, and finally the pressure oil enters the first-gear clutch KA through a valve port A4, so that the vehicle runs at the speed of 1 gear and outputs power.
2. Under the condition of the backward 2-gear, the proportional control valve Y2 and the backward gear clutch KR are still in working states, the proportional control valve Y1 and the forward gear clutch KV are in non-working states, the proportional control valve Y1 is in a working conduction state, pressure oil enters a valve port A3 through a valve port P3, finally the pressure oil enters a secondary gear clutch KB through a valve port A3, and the vehicle runs at the speed of 2-gear and outputs power.
And fourthly, controlling the working condition at the moment of gear shifting and lapping, wherein all control valves in the figure 1 are controlled by an automatic speed change controller according to the change of two parameters of the speed of the whole vehicle and the opening of an accelerator of an engine and the working state of the control valves according to an automatic gear shifting rule. When the vehicle is shifted up in the 1-gear and 2-gear, the proportional control valve Y2, the proportional control valve Y4 and the proportional control valve Y5 jointly control the forward gear clutch KV, the first gear clutch KA and the second gear clutch KB, and the pressure change rule of the signals output by the controller is set, namely the second gear clutch KB starts to charge oil to build pressure at the initial time of pressure reduction of the first gear clutch KA, when the speed of the 1-gear vehicle is equal to the speed of the 2-gear vehicle, the pressure of the first gear clutch KA and the pressure of the second gear clutch KB are equal, the pressure of the first gear clutch KA is rapidly reduced, the pressure of the second gear clutch KB is slowly increased, the first gear clutch KA and the second gear clutch KB are regularly switched to control gears, the phenomenon of instantaneous power interruption and impact in the transmission process of power flow is fully avoided, and the gear shifting smoothness is improved.
And fifthly, an emergency risk avoiding function, wherein the power transmission of each power flow is controlled by two clutches and two control valves together to realize the power transmission, and if the phenomenon that the power transmission cannot be cut off occurs, a logic control rule of emergency risk avoiding is preset in the controller for protection. In the working process of the whole machine, the power can not be cut off because faults such as ablation of a friction plate and a separation plate, blockage of an oil return port of an oil duct and the like can occur in the clutch, and faults such as valve core blocking, blockage of the oil return port and the like can occur in the control valve. According to the difference of the control valve and the clutch failure part, the emergency function has the following working states: 1. when the clutch fails, the emergency danger avoiding function of cutting off the power is realized by controlling the unloading of the other clutch by the control valve; 2. when the control valve fails, the other control valve controls the unloading of the clutch controlled by the control valve to realize the emergency danger avoiding function of power cut-off.
And sixthly, the pressure characteristic self-setting function of the clutches is realized, after each vehicle is assembled, the influence on the gear shifting smoothness is brought by superposition of the characteristic difference of transmission oil products of the gearbox and various errors generated by a transmission part, and the control rule set in the controller can self-set the rule established by the pressure of each clutch so as to eliminate gear shifting impact caused by the difference and the errors.
Above, only be the concrete implementation of the preferred embodiment of the present invention, but the protection scope of the present invention is not limited thereto, and any person skilled in the art is in the technical scope of the present invention, according to the technical solution of the present invention and the design of the present invention, equivalent replacement or change should be covered within the protection scope of the present invention.
Claims (6)
1. The utility model provides a fork truck gearbox hydraulic control system, keeps off clutch KA (2), a fender control valve (3), keeps off clutch KB (4), keeps off control valve (5), keeps off clutch KR (6) backward, keeps off control valve (7) backward, keeps off clutch KV (8) and keeps off control valve (9) forward including controller (1), one, keep off control valve (3), keep off control valve (5), backward keep off control valve (7) and keep off control valve (9) connection system pressure oil circuit forward, its characterized in that forward: the automatic transmission controller is characterized in that a first-gear clutch KA (2), a second-gear clutch KB (4), a backward-gear clutch KR (6) and a forward-gear clutch KV (8) are sequentially arranged on the upper right of the controller (1) from left to right, a first-gear control valve (3), a second-gear control valve (5), a backward-gear control valve (7) and a forward-gear control valve (9) are sequentially arranged below the first-gear clutch KA (2), the second-gear clutch KB (4), the backward-gear clutch KR (6) and the forward-gear clutch KV (8) from left to right, the first-gear control valve (3) is respectively provided with a valve port A4 (28), a proportional control valve Y4 (10), a valve port P4 (29) and a valve port T4 (11) from top to bottom, the second-gear control valve (5) is respectively provided with a valve port A3 (27), a valve port T3 (13), a valve port P3 (14) and a proportional control valve port Y5 (15) from top to bottom, and the backward-gear control valve (7) is respectively provided with a valve, The forward gear control valve (9) is provided with a valve port A1 (24), a valve port T1 (21), a valve port P1 (22) and a proportional control valve Y1 (23) from top to bottom respectively.
2. The forklift transmission hydraulic control system according to claim 1, characterized in that: and the upper surfaces of the first gear control valve (3), the second gear control valve (5), the backward gear control valve (7) and the forward gear control valve (9) are all electrically connected with electromagnetic coils (25).
3. The forklift transmission hydraulic control system according to claim 1, characterized in that: the system pressure circuit is divided into a node a (18), a node b (12), and a node c (20).
4. The forklift transmission hydraulic control system according to claim 1, characterized in that: the controller (1) is in signal connection with a proportional control valve Y4 (10), a proportional control valve Y5 (15), a proportional control valve Y2 (16) and a proportional control valve Y1 (23).
5. The forklift transmission hydraulic control system according to claim 1, characterized in that: the first gear clutch KA (2), the second gear clutch KB (4), the reverse gear clutch KR (6) and the forward gear clutch KV (8) are electrically connected with the valve port T4 (11), the valve port T3 (13), the valve port T2 (19) and the valve port T1 (21), respectively.
6. The forklift transmission hydraulic control system according to claim 1, characterized in that: the valve port P4 (29), the valve port P3 (14), the valve port P2 (17) and the valve port P1 (22) are respectively matched with the valve port A4 (28), the valve port A3 (27), the valve port A2 (26) and the valve port A1 (24), and simultaneously the valve port A4 (28), the valve port A3 (27), the valve port A2 (26) and the valve port A1 (24) are respectively matched with the valve port T4 (11), the valve port T3 (13), the valve port T2 (19) and the valve port T1 (21).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921468760.XU CN211770092U (en) | 2019-09-05 | 2019-09-05 | Hydraulic control system for forklift gearbox |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921468760.XU CN211770092U (en) | 2019-09-05 | 2019-09-05 | Hydraulic control system for forklift gearbox |
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| CN211770092U true CN211770092U (en) | 2020-10-27 |
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| CN201921468760.XU Active CN211770092U (en) | 2019-09-05 | 2019-09-05 | Hydraulic control system for forklift gearbox |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114278713A (en) * | 2021-12-22 | 2022-04-05 | 采埃孚合力传动技术(合肥)有限公司 | Hydraulic transmission case of small-tonnage forklift |
| CN115560065A (en) * | 2022-10-24 | 2023-01-03 | 安徽合力股份有限公司 | Gear shifting system and method based on bus technology |
-
2019
- 2019-09-05 CN CN201921468760.XU patent/CN211770092U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114278713A (en) * | 2021-12-22 | 2022-04-05 | 采埃孚合力传动技术(合肥)有限公司 | Hydraulic transmission case of small-tonnage forklift |
| CN115560065A (en) * | 2022-10-24 | 2023-01-03 | 安徽合力股份有限公司 | Gear shifting system and method based on bus technology |
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