CN213597094U - Hydraulic system and loader - Google Patents
Hydraulic system and loader Download PDFInfo
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- CN213597094U CN213597094U CN202021819214.9U CN202021819214U CN213597094U CN 213597094 U CN213597094 U CN 213597094U CN 202021819214 U CN202021819214 U CN 202021819214U CN 213597094 U CN213597094 U CN 213597094U
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Abstract
The utility model relates to a hydraulic technology, which aims to solve the problems of braking, steering and integrated sharing of a working hydraulic system pressure oil source on the existing loader; providing a hydraulic system and a loader, wherein a load-sensitive liquid filling valve in the hydraulic system is provided with a liquid filling oil path and a load pressure signal leading-out oil path, and the load pressure signal leading-out oil path compares a liquid filling oil outlet pressure signal with an LS1 port pressure signal and outputs a pressure with a higher pressure value from an LS2 port; the LS1 port, the P port and the LS2 port of the load-sensitive liquid filling valve are correspondingly connected with the LS port of the steering gear, the CF port and the LS port of the priority valve, and the priority valve responds dynamically according to the pressure signal of the LS2 port. The utility model discloses increase braking system's load signal feedback to select the feedback to the priority valve, the dynamic response fuel feeding with steering system's load signal comparison.
Description
Technical Field
The utility model relates to a hydraulic pressure technique, more specifically say, relate to a hydraulic system and loader.
Background
The loader is a common engineering machine, and a hydraulic system of the loader is divided into a brake system, a steering hydraulic system and a working hydraulic system according to functions of the loader.
The braking system is typically a fully hydraulic braking system. The full hydraulic brake system comprises a pressure oil source, a service brake valve and a service brake which are sequentially connected through a pipeline. And the pressure oil source also comprises a service brake accumulator and a charging valve.
For the purposes of cost reduction and energy saving, the brake system, the steering hydraulic system and the working hydraulic system are usually shared on the pressure oil source. The power required by the steering system and the braking system is small, and the steering system and the braking system work intermittently, but the two systems need to ensure the supply of hydraulic oil preferentially due to the safety requirement.
Therefore, how to realize the integration of the pressure oil source of the brake system, the steering hydraulic system and the working hydraulic system on the loader and meet the safety requirement becomes a problem which is always explored by the industry.
SUMMERY OF THE UTILITY MODEL
The to-be-solved technical problem of the utility model is to brake on the current loader, turn to and the problem of work hydraulic system pressure oil source integration sharing, and provide a hydraulic system and loader, realize on the loader that brake, turn to, work hydraulic system pressure oil source integration sharing and satisfy the safety demand, improve the efficiency of loader, reduce the energy consumption.
The utility model discloses a realize that the technical scheme of its purpose is like: a hydraulic system is provided, which comprises a full hydraulic braking system, a steering system and a working hydraulic system.
The full hydraulic brake system comprises a brake pressure oil source, a service brake valve and a service brake which are sequentially connected through a pipeline.
The steering system comprises a steering oil cylinder, a steering gear connected with the steering oil cylinder, a priority valve, a hydraulic oil tank and a constant delivery pump with an oil inlet end connected with the hydraulic oil tank.
And a pump port of the fixed displacement pump is connected with a port P of the priority valve, and a port CF and a port EF of the priority valve are correspondingly connected with a port P of the steering gear and a confluence port of the working hydraulic system.
The brake pressure oil source comprises a load sensitive liquid charging valve and a service brake accumulator.
The load-sensitive liquid filling valve is provided with a port P, a liquid filling and oil outlet, a port LS1 and a port LS 2; a liquid-filled oil path is arranged between the port P and the liquid-filled oil outlet; and a load pressure signal lead-out oil path is arranged among the liquid filling oil outlet, the LS1 port and the LS2 port, compares the pressure signal of the liquid filling oil outlet with the pressure signal of the LS1 port and outputs the pressure with higher pressure value from the LS2 port.
The charging and oil outlet of the load sensitive charging valve is simultaneously communicated with the service brake accumulator and the service brake valve, an LS1 port of the load sensitive charging valve is connected with an LS port of the steering gear, a P port of the load sensitive charging valve is connected with a CF port of the priority valve, and an LS2 port of the load sensitive charging valve is connected with an LS port of the priority valve.
In the hydraulic system, the load pressure signal lead-out oil path comprises a hydraulic control switch valve and a shuttle valve.
And a first oil inlet end of the shuttle valve is connected with an LS1 port, a second oil inlet end of the shuttle valve is connected with the liquid-filled oil outlet through the hydraulic control switch valve, and an oil outlet end of the shuttle valve is connected with an LS2 port.
The hydraulic control end of the hydraulic control switch valve is connected with the liquid-filled oil outlet; and when the pressure of the hydraulic control end of the hydraulic control switch valve is smaller than the preset pressure, the second oil inlet end of the shuttle valve is communicated with the liquid-filled oil outlet through the hydraulic control switch valve.
In the hydraulic system, the load-sensitive prefill valve is further provided with a T port, the second oil inlet end of the shuttle valve is communicated with the T port through the hydraulic control switch valve when the pressure of the hydraulic control end of the hydraulic control switch valve is greater than a preset pressure value, and the T port is connected with a hydraulic oil tank.
In the hydraulic system, the liquid filling oil path is formed by an oil path which is communicated with the liquid filling oil outlet in a one-way mode from the port P of the load sensitive liquid filling valve through the first one-way valve.
In the hydraulic system, the system also comprises a parking brake, a parking brake accumulator and a parking brake valve connected with the parking brake; the load-sensitive liquid filling valve is also provided with a second liquid filling oil outlet, the liquid filling oil path also comprises a liquid filling branch oil path which is communicated with the second liquid filling oil outlet in a one-way mode from the oil outlet end of the first one-way valve through the second one-way valve, and the oil inlet end of the second one-way valve is connected between the oil outlet end of the first one-way valve and the liquid filling oil outlet; and the second liquid-filled oil outlet is simultaneously connected with the parking brake accumulator and the parking brake valve.
The utility model discloses a realize that the technical scheme of its purpose is like: a loader is provided, which is characterized by comprising the hydraulic system.
Compared with the prior art, the utility model discloses with braking system and the comprehensive consideration of a steering system, the brake pump cancellation, braking system oil source is got from a steering system's priority valve. The newly designed load sensitive prefill valve increases the load signal feedback of the brake system, and compares the load signal with the load signal of the steering system, and selects the load signal to be fed back to the priority valve through the control valve, so that the priority valve responds to the action according to the higher load pressure in the brake system and the steering system.
Drawings
Fig. 1 is a schematic diagram of the hydraulic system of the present invention.
Fig. 2 is a schematic diagram of the load sensitive prefill valve of the present invention.
Part names and serial numbers in the figure:
the hydraulic control system comprises a fixed displacement pump 1, a steering gear 5, a left steering oil cylinder 6, a right steering oil cylinder 7, a load sensitive liquid charging valve 8, a parking brake energy accumulator 9, a parking brake valve 10, a parking brake 11, a front axle brake energy accumulator 12, a rear axle brake energy accumulator 13, a service brake valve 14, a front axle brake 15, a rear axle brake 16, an oil return filter 17, a hydraulic oil tank 18, a distribution valve 19 and a priority valve 22.
Detailed Description
The following description of the embodiments refers to the accompanying drawings.
Fig. 1 shows a hydraulic system of a loader. The hydraulic system comprises a full hydraulic braking system, a steering system and a working hydraulic system.
The full hydraulic brake system comprises a brake pressure oil source, a service brake valve 14, a service brake, a parking brake valve 10 and a parking brake 11 which are sequentially connected through pipelines.
The service brake comprises a front axle brake 15 and a rear axle brake 16, and the service brake valve 14 is a double-oil-way brake valve with two oil outlet ends correspondingly connected with the front axle brake 15 and the rear axle brake 16. The oil outlet end of the parking brake valve 10 is connected to the parking brake 11 via a pipe.
The brake pressure oil source comprises a load sensitive liquid charging valve 8, a service brake accumulator and a parking brake accumulator 9; the service brake energy accumulator comprises a front axle brake energy accumulator 12 and a rear axle brake energy accumulator 13.
The front axle brake accumulator 12 and the rear axle brake accumulator 13 respectively supply hydraulic oil to the front axle brake 15 and the rear axle brake 16 through an A1 port and an A2 port of the service brake valve 14. The parking brake accumulator 9 supplies pressure oil for braking to the parking brake 11 via the parking brake valve 10.
And a liquid filling and oil outlet of the load sensitive liquid filling valve is simultaneously connected with the oil inlet ends of the front axle brake accumulator 12, the rear axle brake accumulator 13 and the service brake valve 14. The second charge outlet port a3 of the load sensitive charge valve 8 is connected to both the parking brake accumulator 9 and the parking brake valve 10.
As shown in fig. 2, the load-sensitive filling valve 8 in this example includes a P port, a filling oil outlet, an LS1 port, an LS2 port, and a second filling oil outlet A3, a filling oil path is provided between the P port and the filling oil outlet, a load pressure signal lead-out oil path is provided between the filling oil outlet, the LS1 port, and the LS2 port, and the load pressure signal lead-out oil path compares a filling oil outlet pressure signal with an LS1 port pressure signal and outputs a pressure with a higher pressure value from an LS2 port.
The load pressure signal lead-out oil path comprises a hydraulic control switch valve 82 and a shuttle valve 83; a first oil inlet end of the shuttle valve 83 is connected with an LS1 port, a second oil inlet end is connected with a liquid-filled oil outlet through a hydraulic control switch valve 82, and an oil outlet end is connected with an LS2 port; the hydraulic control end of the hydraulic control switch valve 82 is connected with the liquid-filled oil outlet; the predetermined pressure, which is higher than the maximum brake pressure of the transaxle, can be set by designing the spring in the spring chamber of the pilot-operated switching valve 82. When the pressure of the hydraulic control end of the hydraulic control switch valve 82 is lower than the preset pressure, the second oil inlet end of the shuttle valve 83 is communicated with the liquid-filled oil outlet through the hydraulic control switch valve, and when the pressure of the hydraulic control end of the hydraulic control switch valve 82 is higher than the preset pressure, the second oil inlet end of the shuttle valve is communicated with the T port through the hydraulic control switch valve. The pressure at the hydraulic control end of the hydraulic control switch valve 82 is the pressure at the charging and discharging port of the load sensitive charging valve 8, namely the pressure of the service brake accumulator. When the pressure of the hydraulic control end of the hydraulic control switch valve 82 is larger than the preset value, the pressure in the service braking energy accumulator meets the requirement of the braking system, and liquid charging is not needed, otherwise, the service braking energy accumulator needs to be charged to ensure the pressure of the braking oil source of the braking system.
The liquid filling oil path mainly comprises an oil path with a P port communicated with the liquid filling oil outlet in a one-way mode through the first one-way valve 81, the liquid filling oil path also comprises a liquid filling branch oil path, the liquid filling branch oil path is arranged between the oil outlet end of the first one-way valve 81 and the second liquid filling oil outlet A3, and the liquid filling branch oil path comprises an oil path with an oil outlet end of the first one-way valve 81 communicated with the second liquid filling oil outlet A3 in a one-way mode through the second one-way valve 84.
The load sensitive prefill valve 8 also has a T port for connection with a hydraulic tank.
The working hydraulic system comprises a movable arm oil cylinder, a rotating bucket oil cylinder, a distribution valve connected with the movable arm oil cylinder and the rotating bucket oil cylinder, a hydraulic pump connected with the distribution valve and a pilot valve. The oil inlet end of the hydraulic pump is connected with the hydraulic oil tank. The distribution valve 19 has a confluence port for connecting with a pressure oil source, and the pressure oil source connected with the confluence port is converged with the hydraulic pump to form a confluence oil supply system for supplying oil to the boom cylinder and the swing bucket cylinder in the same direction.
The steering system comprises a left steering oil cylinder 6, a right steering oil cylinder 7, a steering gear 5 connected with the left steering oil cylinder and the right steering oil cylinder, a constant delivery pump 1 with a pump port connected with a port P of a priority valve 22, and a hydraulic oil tank 18 connected with an oil inlet end of the constant delivery pump 1.
The steering gear 5 is provided with an A port, a B port, a P port, a T port for oil return and an LS port for outputting a steering load pressure signal, wherein the A port and the B port are connected with a left steering oil cylinder 6 and a right steering oil cylinder 7.
The pump port of the fixed displacement pump is connected to the port P of the priority valve, and the port CF and the port EF of the priority valve are connected to the port P of the steering gear and the merging port of the working hydraulic system distribution valve 19.
An LS1 port of the load-sensitive charging valve is connected with an LS port of the steering gear 5, a P port of the load-sensitive charging valve is connected with a CF port of the priority valve, and an LS2 port of the load-sensitive charging valve is connected with an LS port of the priority valve.
The T-port of the steering gear 5 is connected to a hydraulic oil tank 18 via a return oil filter 17.
In this embodiment, when braking is needed during driving, the service brake valve is operated, the double-oil-way valve rod of the service brake valve 14 moves to the left position at the same time, the hydraulic oil stored in the front axle brake energy accumulator 12 and the rear axle brake energy accumulator 13 is released and is supplied to the front axle brake 15 and the rear axle brake 16 through the left position of the service brake valve 14, so that the service brake of the whole vehicle is realized.
When the parking brake is needed after the machine is stopped stably, the electromagnetic valve of the parking brake valve 10 is electrified and acts on the left position, high-pressure oil stored in the parking brake energy accumulator 9 is supplied to the parking brake 11 through the parking brake valve 10, the parking brake is in a working state, and the normal operation of the whole machine is ensured.
In the hydraulic system in the present embodiment, a brake pump for supplying oil only to the brake system is not provided. After the pressure signal of the service brake accumulator is compared with the steering load pressure signal of the steering gear by the load sensitive charging valve 8, the pressure signal with the higher pressure value is transmitted to the priority valve 22. The specific working principle is as follows:
if the pressure of the hydraulic control end of the hydraulic control switch valve in the load-sensitive charging valve 8 is lower than the preset pressure, the hydraulic control switch valve 82 is reversed under the spring action of the spring cavity, so that the second oil inlet end of the shuttle valve 83 is communicated with the charging oil outlet through the hydraulic control switch valve 82, namely, the service braking energy accumulator, and the pressure in the service braking energy accumulator is transmitted to the second oil inlet end of the shuttle valve 83 through the hydraulic control switch valve 82. The steering load pressure of the LS port of the steering gear 5 is transmitted to the first oil inlet end of the shuttle valve through the LS1 port of the load sensitive prefill valve 8, and after the pressure of the first oil inlet end of the shuttle valve 83 is compared with the pressure of the second oil inlet end through the shuttle valve, the pressure with high pressure is output through the oil outlet end of the shuttle valve 83 and is transmitted to the LS port of the priority valve.
If the pressure of the hydraulic control end of the hydraulic control switch valve in the load sensitive liquid charging valve 8 is higher than the preset pressure, the hydraulic control switch valve 82 is reversed under the action of the pressure of the hydraulic control end, so that the second oil inlet end of the shuttle valve 83 is connected to the liquid charging outlet through the hydraulic control switch valve 82, namely, is cut off from the oil path of the service braking energy accumulator, and the pressure in the service braking energy accumulator cannot be transmitted to the port LS2 of the load sensitive liquid charging valve 8. At this point, if the pressure at port P of the load sensitive charge valve 8 is higher than the pressure of the service accumulator, the accumulator may be charged, but at this point the priority valve 22 does not respond dynamically to the service accumulator pressure.
If the hydraulic system does not have steering action, and only when the pressure of the service brake accumulator is lower than the preset pressure value (needing to be filled) of the hydraulic control switch valve, the service brake accumulator is filled, the pressure of the service brake accumulator is transmitted to the priority valve 22 through the load sensitive liquid filling valve 8 in the liquid filling process, and the priority valve 22 dynamically responds according to a pressure signal of the service brake accumulator and outputs pressure oil from a CF port of the service brake accumulator to fill the service brake accumulator. In the process of charging the service brake accumulator, the load sensitive charging valve 8 also charges the parking brake accumulator through the charging branch oil way.
When the hydraulic system has steering action and the pressure of the service brake accumulator is lower than the preset pressure value (steering and charging) of the hydraulic control switch valve, the pressure signal of the service brake accumulator is transmitted to the second oil inlet end of the shuttle valve through the hydraulic control switch valve, the steering load pressure signal of the steering gear is transmitted to the first oil inlet end of the shuttle valve through an LS1 port of the load sensitive charging valve 8, the shuttle valve transmits the pressure signal with the higher pressure value to the priority valve after comparison, and the priority valve dynamically responds according to the pressure signal and outputs pressure oil from a CF port of the priority valve to charge the service brake accumulator and supply steering oil to the steering gear.
If the pressure of the service brake accumulator of the hydraulic system is higher than the preset pressure value of the hydraulic control switch valve (no charging is needed), but the steering action is performed, the pressure in the service brake accumulator can not be transmitted to the second oil inlet end of the shuttle valve, the steering load pressure signal of the steering gear is transmitted to the first oil inlet end of the shuttle valve through the LS1 port of the load sensitive charging valve 8 and is output to the priority valve 22 through the shuttle valve and the LS2 port, and the priority valve dynamically responds according to the steering load pressure signal and outputs pressure oil from the CF port of the priority valve to supply steering oil to the steering gear.
After the priority valve supplies the hydraulic oil output by the fixed displacement pump to the liquid filling valve and the steering gear, the redundant oil of the fixed displacement pump 1 is supplied to a distribution valve 19 of a working hydraulic system through an EF port of the priority valve, and if the working hydraulic system does not have the oil demand at the moment, the redundant oil returns to a hydraulic oil tank through an open middle position distribution valve of the working hydraulic system.
Claims (6)
1. A hydraulic system comprises a full hydraulic braking system, a steering system and a working hydraulic system;
the full hydraulic brake system comprises a brake pressure oil source, a service brake valve and a service brake which are sequentially connected through a pipeline;
the steering system comprises a steering oil cylinder, a steering gear connected with the steering oil cylinder, a priority valve, a hydraulic oil tank and a constant delivery pump with an oil inlet end connected with the hydraulic oil tank; the pump port of the fixed displacement pump is connected with the P port of the priority valve, and the CF port and the EF port of the priority valve are correspondingly connected with the P port of the steering gear and the confluence port of the working hydraulic system;
the method is characterized in that:
the brake pressure oil source comprises a load sensitive liquid charging valve and a service brake accumulator;
the load-sensitive liquid filling valve is provided with a port P, a liquid filling and oil outlet, a port LS1 and a port LS 2; a liquid-filled oil path is arranged between the port P and the liquid-filled oil outlet; a load pressure signal lead-out oil path is arranged among the liquid filling oil outlet, the LS1 port and the LS2 port, compares a liquid filling oil outlet pressure signal with an LS1 port pressure signal and outputs a pressure with a higher pressure value from an LS2 port;
the charging and oil outlet of the load sensitive charging valve is simultaneously communicated with the service brake accumulator and the service brake valve, an LS1 port of the load sensitive charging valve is connected with an LS port of the steering gear, a P port of the load sensitive charging valve is connected with a CF port of the priority valve, and an LS2 port of the load sensitive charging valve is connected with an LS port of the priority valve.
2. The hydraulic system according to claim 1, wherein the load pressure signal lead-out oil passage includes a pilot-operated on-off valve, a shuttle valve;
the first oil inlet end of the shuttle valve is connected with an LS1 port, the second oil inlet end of the shuttle valve is connected with the liquid-filled oil outlet through the hydraulic control switch valve, and the oil outlet end of the shuttle valve is connected with an LS2 port;
the hydraulic control end of the hydraulic control switch valve is connected with the liquid-filled oil outlet; and when the pressure of the hydraulic control end of the hydraulic control switch valve is smaller than the preset pressure, the second oil inlet end of the shuttle valve is communicated with the liquid-filled oil outlet through the hydraulic control switch valve.
3. The hydraulic system of claim 2, wherein the load-sensitive charging valve further comprises a T-port, and the second oil inlet of the shuttle valve is connected to the T-port through the hydraulic control switching valve when the pressure at the hydraulic control end of the hydraulic control switching valve is greater than a predetermined pressure value, and the T-port is connected to the hydraulic oil tank.
4. The hydraulic system according to any one of claims 1 to 3, wherein the charge oil path is formed by an oil path in which a port P of the load-sensitive charge valve is communicated to a charge oil outlet in a single direction through a first check valve.
5. The hydraulic system of claim 4, further comprising a parking brake, a parking brake accumulator, and a parking brake valve coupled to the parking brake; the load-sensitive liquid filling valve is also provided with a second liquid filling oil outlet, the liquid filling oil path also comprises a liquid filling branch oil path which is communicated with the second liquid filling oil outlet in a one-way mode from the oil outlet end of the first one-way valve through the second one-way valve, and the oil inlet end of the second one-way valve is connected between the oil outlet end of the first one-way valve and the liquid filling oil outlet; and the second liquid-filled oil outlet is simultaneously connected with the parking brake accumulator and the parking brake valve.
6. A loader characterized by comprising a hydraulic system according to any one of claims 1 to 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021819214.9U CN213597094U (en) | 2020-08-27 | 2020-08-27 | Hydraulic system and loader |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021819214.9U CN213597094U (en) | 2020-08-27 | 2020-08-27 | Hydraulic system and loader |
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| Publication Number | Publication Date |
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| CN213597094U true CN213597094U (en) | 2021-07-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202021819214.9U Active CN213597094U (en) | 2020-08-27 | 2020-08-27 | Hydraulic system and loader |
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| CN (1) | CN213597094U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116771740A (en) * | 2023-08-18 | 2023-09-19 | 湖南星邦智能装备股份有限公司 | High-position forklift truck, hydraulic control system and method based on single-pump oil supply |
| CN117090818A (en) * | 2023-10-17 | 2023-11-21 | 湖南星邦智能装备股份有限公司 | High-position forklift and hydraulic control system and method thereof |
-
2020
- 2020-08-27 CN CN202021819214.9U patent/CN213597094U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116771740A (en) * | 2023-08-18 | 2023-09-19 | 湖南星邦智能装备股份有限公司 | High-position forklift truck, hydraulic control system and method based on single-pump oil supply |
| CN116771740B (en) * | 2023-08-18 | 2023-11-07 | 湖南星邦智能装备股份有限公司 | High-position forklift truck, hydraulic control system and method based on single-pump oil supply |
| CN117090818A (en) * | 2023-10-17 | 2023-11-21 | 湖南星邦智能装备股份有限公司 | High-position forklift and hydraulic control system and method thereof |
| CN117090818B (en) * | 2023-10-17 | 2024-01-30 | 湖南星邦智能装备股份有限公司 | High-position forklift and hydraulic control system and method thereof |
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| Date | Code | Title | Description |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20230428 Address after: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Patentee after: GUANGXI LIUGONG MACHINERY Co.,Ltd. Patentee after: Guangxi Zhongyuan Machinery Co.,Ltd. Address before: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Patentee before: GUANGXI LIUGONG MACHINERY Co.,Ltd. Patentee before: LIUZHOU LIUGONG HYDRAULIC COMPONENTS Co.,Ltd. |
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| TR01 | Transfer of patent right |