CN109878482B - Braking system and engineering vehicle - Google Patents
Braking system and engineering vehicle Download PDFInfo
- Publication number
- CN109878482B CN109878482B CN201910275938.7A CN201910275938A CN109878482B CN 109878482 B CN109878482 B CN 109878482B CN 201910275938 A CN201910275938 A CN 201910275938A CN 109878482 B CN109878482 B CN 109878482B
- Authority
- CN
- China
- Prior art keywords
- brake
- oil
- valve
- hydraulic
- dry
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000007788 liquid Substances 0.000 claims abstract description 27
- 239000012530 fluid Substances 0.000 claims description 15
- 238000004891 communication Methods 0.000 claims description 5
- 238000012423 maintenance Methods 0.000 abstract description 10
- 238000000034 method Methods 0.000 abstract description 6
- 230000008569 process Effects 0.000 abstract description 6
- 239000012535 impurity Substances 0.000 description 11
- 230000009471 action Effects 0.000 description 10
- 238000011144 upstream manufacturing Methods 0.000 description 7
- 238000010438 heat treatment Methods 0.000 description 6
- 230000003749 cleanliness Effects 0.000 description 5
- 230000017525 heat dissipation Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000000994 depressogenic effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 241001391944 Commicarpus scandens Species 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 238000009412 basement excavation Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 238000001914 filtration Methods 0.000 description 1
- 238000002309 gasification Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- JEIPFZHSYJVQDO-UHFFFAOYSA-N iron(III) oxide Inorganic materials O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000191 radiation effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Landscapes
- Braking Arrangements (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
Abstract
The invention discloses a braking system and an engineering vehicle, and relates to the technical field of engineering machinery. The braking system comprises a hydraulic power system, a dry brake and a radiator, wherein the hydraulic power system is connected with the dry brake through a liquid path control module, and the liquid path control module is configured to: during service braking, the hydraulic power system can drive oil to enter the dry brake through the liquid path control module; when the service braking is released, at least part of oil in the dry brake flows back to the hydraulic power system after passing through the liquid path control module and the radiator. In the braking system, the full hydraulic drive is adopted to be matched with the dry brake, so that the failure rate and cost of the braking system can be reduced, and the maintenance cost is lower. By releasing the braking process, part of the oil in the dry brake is returned, so that the low-temperature oil in each braking process is mixed with the high Wen Youye in the dry brake, and the temperature of the oil in the dry brake is reduced. The returned oil can be rapidly cooled by the radiator.
Description
Technical Field
The invention relates to the technical field of engineering machinery, in particular to a braking system and an engineering vehicle.
Background
The loader is an important mechanical device in engineering machinery construction, and is mainly used for shoveling, loading, transporting, digging and other operations on loose materials. The working conditions of the loader are mainly shoveling operation and loading operation, and the working device needs to be used for bucket collection, lifting, unloading and descending, so that the whole loader needs to be braked frequently.
Currently, the brake system of a loader may be a gas cap oil caliper brake system. When the gas cap oil caliper disc type braking system needs to brake, high-pressure gas in the gas storage tank is sent to the booster pump through the gas brake valve, the booster pump converts the high-pressure gas into high-pressure oil liquid and sends the high-pressure oil liquid to the brake caliper of the bridge, and the bridge is braked. The gas cap oil caliper disc brake system has the advantages that the cost is low, the maintenance is relatively easy, but because impurities and moisture content in the air are high, after the gas is compressed by a high-pressure machine, the impurities, the moisture and the gas are separated, although the gas is filtered by a separator, the filtering effect is limited, the damage of the impurities and the moisture to a hydraulic element is large, the hydraulic element is easy to rust, abnormal sound and vibration are generated during working, the corrosion also causes further increase of impurities in the hydraulic element, the hydraulic element is generally failed, the brake system is further disabled, and the safety problem is caused.
To solve the above problem, the brake system of the loader may also adopt a full hydraulic wet brake system. When the full-hydraulic wet brake system needs to brake, the hydraulic pressure in the accumulator is transmitted to the inner brake caliper of the bridge through the foot brake valve, so that the bridge brakes. All hydraulic wet-type rotating systems are hydraulically driven, the cleanliness is relatively high, the system reliability is relatively good, and the reliability of a braking system is not damaged by moisture. However, the cost is 40000-50000 yuan higher than that of the gas cap oil caliper disc type braking system, and the friction plates in the brake caliper are arranged in the bridge, so that the shell of the bridge needs to be disassembled during maintenance, and the maintenance is relatively difficult.
However, both of the above-mentioned brake systems have a problem that brake oil heats.
In a gas cap oil caliper disc brake system, a dry brake caliper is generally adopted as a brake component of a bridge, and during long-time or high-frequency braking, the brake caliper generates heat by friction and transmits high temperature into oil in the brake system, so that the temperature of the oil is increased. Although the oil in the system can return to the oil cup of the booster pump for heat dissipation, the brake caliper is far away from the oil cup of the booster pump, so that a circulating heat dissipation effect cannot be generated. In addition, because the cavity of the brake caliper is sealed, high-temperature oil can form bubbles to flow to the high position in the oil again, so that the oil tank end of the booster pump sprays oil to the outside, the oil spraying failure of the booster pump is caused, the environmental pollution is caused, and the maintenance cost is extremely high.
In the full-hydraulic wet-type rotating system, a brake caliper is soaked in oil, and part of heat generated in braking can flow through the oil in a bridge, so that heat dissipation is performed. However, in the working state of high strength for a long time, the brake oil in the closed area in the bridge cannot circulate and flow, and cannot completely dissipate heat, so that the oil is easy to deteriorate in a high-temperature environment for a long time, impurities and water are separated in the oil, and the reliability of a brake system is affected. Along with the rise of temperature, the ageing acceleration of sealing member in the brake caliper can lead to the brake caliper oil leak for fluid cluster goes into the transmission fluid in the bridge, has reduced the reliability and the life-span of bridge, and the reduction of fluid also can lead to braking system trouble in the brake caliper, and maintenance cost is very big.
Therefore, a brake system and an engineering vehicle are needed to solve the heat dissipation problem of the brake caliper.
Disclosure of Invention
The invention aims to provide a braking system which can solve the problem of heating of brake oil and has lower cost.
To achieve the purpose, the invention adopts the following technical scheme:
a braking system comprising a hydraulic power system, a dry brake, and a radiator, the hydraulic power system being connected to the dry brake by a fluid path control module configured to:
when in service braking, the hydraulic power system can drive oil to enter the dry brake through the liquid path control module; when the service braking is released, at least part of oil in the dry brake flows back to the hydraulic power system after passing through the liquid path control module and the radiator.
Wherein the fluid path control module comprises a hydraulic brake valve and a control valve bank configured to control communication of an oil outlet of the hydraulic power system and an inlet of the dry brake, and to control communication of an outlet of the dry brake and an oil return port of the hydraulic power system.
The control valve group comprises a first control valve and a second control valve, wherein one end of the first control valve is connected with an outlet of the dry brake, and the other end of the first control valve is connected with an oil return port of the hydraulic power system;
one end of the hydraulic brake valve is connected with an oil outlet of the hydraulic power system, and the other end of the hydraulic brake valve is connected with an inlet of the second control valve; the outlet of the second control valve is connected with the inlet of the dry brake.
The first control valve is a hydraulic switch valve, and the second control valve is an overflow valve or a hydraulic one-way valve.
The first control valve and the second control valve are electromagnetic switch valves.
The hydraulic braking valve is a three-way valve, one valve port of the three-way valve is communicated with the second control valve, and the other two valve ports of the three-way valve are respectively connected with an oil outlet and an oil return port of the hydraulic power system.
The radiator is located between the hydraulic path control module and an oil return port of the hydraulic power system.
The dry brake comprises four brake calipers, and the four brake calipers are connected in parallel and then connected with the liquid path control module.
The two dry brakes are arranged in parallel, two service brake driving loops are arranged in the hydraulic power system in parallel, and each service brake driving loop is connected with one dry brake through one liquid path control module.
The hydraulic power system comprises an oil tank, a hydraulic pump connected with an outlet of the oil tank and a first energy accumulator connected with the hydraulic pump, and the first energy accumulator is connected with the liquid path control module.
The oil in the braking system is high-temperature-resistant oil.
Wherein the braking system further comprises a parking brake and a parking brake valve, the hydraulic power system is connected with the parking brake through the parking brake valve, and the parking brake valve is configured to:
during parking braking, at least part of oil in the parking brake flows back to the hydraulic power system after passing through the parking brake valve and the radiator; when the parking brake is released, oil enters the parking brake through the parking brake valve by the hydraulic power system.
The invention further aims to provide an engineering vehicle which can solve the problem of heating of brake oil and has lower cost.
To achieve the purpose, the invention adopts the following technical scheme:
an engineering vehicle comprises the brake system.
The engineering vehicle further comprises an operation system, and a hydraulic circuit of the braking system and a hydraulic circuit of the operation system are arranged independently.
Wherein the engineering vehicle is a loader.
The beneficial effects are that: the invention provides a braking system and an engineering vehicle.
In the braking system, a full hydraulic drive is adopted to match with a dry brake, so that on one hand, the cleanliness of brake oil is ensured, and the failure rate of the braking system is reduced; on the other hand, the cost of the braking system can be reduced by adopting the dry brake, and the maintenance cost of the dry brake is lower. The dry brake is connected with the hydraulic power system through the liquid path control module, so that at least part of oil in the dry brake can return to the hydraulic power system through the liquid path control module when braking is released, and low-temperature oil is mixed in the dry brake when next service braking is performed, thereby reducing the temperature of the oil in the dry brake and avoiding the oil in the dry brake from being maintained in a high-temperature state for a long time. The oil returned by the dry brake can be cooled by the radiator and then returned to the hydraulic power system, so that the purpose of rapidly cooling the oil temperature is achieved.
The hydraulic circuit of the brake system and the hydraulic circuit of the operating system in the engineering vehicle are mutually independent, namely, the oil of the brake system and the oil of the operating system are not shared, and the brake system is independently provided with the oil tank, so that the heating problem of the brake system caused by high oil temperature in the operating system is avoided. The brake system is independent, and only a high-temperature resistant medium can be adopted in the brake system, so that the cost is reduced.
Drawings
FIG. 1 is a schematic diagram of a brake system according to a first embodiment of the present invention;
FIG. 2 is a schematic diagram of the direction of oil flow of a braking system according to a first embodiment of the present invention during service braking;
FIG. 3 is a schematic view of the direction of oil flow of a brake system according to a first embodiment of the present invention when the service brake is released;
FIG. 4 is a schematic diagram of the direction of oil flow of a braking system according to a first embodiment of the present invention during parking braking;
fig. 5 is a schematic diagram of the direction of oil flow of the braking system according to the first embodiment of the present invention when the parking brake is released.
Wherein:
100. a hydraulic power system;
11. an oil tank; 12. a hydraulic pump; 13. a filter; 14. a charging valve; 15. a first accumulator; 17. a second accumulator;
200. a braking mechanism;
21. a control valve group; 211. a hydraulic switching valve; 212. an overflow valve; 22. a dry brake; 221. a brake caliper; 23. a parking brake; 24. a parking brake valve; 25. a heat sink; 26. a hydraulic brake valve.
Detailed Description
Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present invention and should not be construed as limiting the invention.
In the description of the present invention, it should be noted that the directions or positional relationships indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. Wherein the terms "first position" and "second position" are two different positions.
Unless specifically stated or limited otherwise, the terms "mounted," "connected," and "fixed" are to be construed broadly, and may be, for example, either fixed or removable; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
Unless expressly stated or limited otherwise, a first feature being "above" or "below" a second feature may include the first feature and the second feature being in direct contact, or may include the first feature and the second feature not being in direct contact but being in contact with each other by way of additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.
The technical scheme of the invention is further described below by the specific embodiments with reference to the accompanying drawings.
Example 1
The present embodiment provides an engineering vehicle, which may be a transportation vehicle, a crane, an excavator, a bulldozer, a loader, or the like. In this embodiment, the engineering vehicle is a loader, and is mainly used for excavation work and loading work. The loader comprises a braking system and an operating system, wherein the braking system is mainly used for service braking and parking braking of the loader. The operating system is used for carrying out operations such as bucket collecting, lifting, unloading, descending and the like.
The loader needs to be braked frequently in the working process, and in the existing loader, a gas cap oil caliper disc type braking system and a full hydraulic wet type braking system are generally adopted as a braking system. The pneumatic oil-filled caliper disc type braking system converts high-pressure gas into high-pressure oil liquid through a booster pump, and sends the high-pressure oil liquid to a brake caliper of the bridge to brake the bridge. Because pneumatic drive is adopted, impurities and moisture in the air greatly damage the hydraulic element, the problems of abnormal sound, vibration and the like are easy to generate during working, the hydraulic element is easy to cause failure of a braking system after rusting and corrosion, and the safety problem is caused. In the all-hydraulic wet brake system, hydraulic drive is adopted, the cleanliness is relatively high, and the problem of poor system reliability caused by impurities in the gas cap oil caliper disc brake system can be solved, but the cost is high, and the maintenance is relatively difficult.
In order to solve the above problems, as shown in fig. 1, the braking system in the present embodiment adopts a hydraulic power system 100 to cooperate with a braking mechanism 200 having a dry brake 22, so as to ensure the cleanliness of the brake oil on the one hand and reduce the failure rate of the braking system; on the other hand, the use of the dry brake 22 reduces the cost of the braking system and the maintenance costs of the brake are lower.
In the prior art, both a gas cap oil caliper disc type braking system and a full-hydraulic wet type braking system have the problem of heating of braking oil, so that the braking system is easy to break down and has high maintenance cost.
In order to solve the problem of heating of brake oil, in this embodiment, the brake system further includes a hydraulic control module, where the hydraulic control module is connected to the hydraulic power system 100 and the dry brake 22, and when the brake system performs service braking, the hydraulic power system 100 drives the oil to enter the dry brake 22 through the hydraulic control module, and the brake caliper 221 in the dry brake 22 brakes the bridge, so as to implement service braking. When service braking is released, at least a portion of the oil within the dry brake 22 flows back into the hydraulic power system 100 through the fluid path control module.
During service braking, the hydraulic power system 100 delivers high pressure brake fluid into the dry brake 22 to actuate the dry brake 22. During braking, frictional heat is generated within the dry brake 22 and the heat is transferred to the brake fluid, causing the temperature of the high pressure brake fluid within the dry brake 22 to rise. In the process of releasing service braking, at least part of high-temperature brake oil in the dry brake 22 flows back to the hydraulic power system 100, so that the high-temperature brake oil in the dry brake 22 is reduced, the temperature in the dry brake 22 is reduced, and in the next service braking, the hydraulic power system 100 drives low-temperature brake oil to enter the dry brake 22 and be mixed with high Wen Youye in the dry brake 22, thereby achieving the purpose of reducing the temperature of the oil in the dry brake 22, avoiding the oil in the dry brake 22 from being in a high-temperature state for a long time, preventing impurities or moisture separation caused by high-temperature deterioration of the brake oil, and avoiding high-temperature failure of sealing elements in the dry brake 22, and further improving the reliability of the brake system.
Optionally, an outlet is provided at the upper portion of the dry brake 22, and when the brake is released, part of the height Wen Youye in the dry brake 22 flows back to the hydraulic power system 100 through the outlet at the upper end thereof, so that impurities at the bottom of the dry brake 22 are prevented from entering the hydraulic power system 100, and further pollution to oil is prevented.
Specifically, as shown in fig. 1, the hydraulic power system 100 includes an oil tank 11 and a hydraulic pump 12, the oil tank 11 stores brake oil, the hydraulic pump 12 is connected to an oil outlet of the oil tank 11, and the hydraulic pump 12 provides power for the brake oil in the oil tank 11, so as to drive the brake oil to enter the dry brake 22 through the hydraulic control module when the vehicle is braked.
In order to reduce the energy consumption of the brake system and improve the efficiency, the hydraulic power system 100 further includes a charging valve 14 and a first accumulator 15, where the charging valve 14 is connected to the hydraulic pump 12 and the first accumulator 15, and the first accumulator 15 is used for temporarily storing brake oil. As shown in fig. 1, when the loader works, the hydraulic pump 12 is started, so that the brake oil in the oil tank 11 forms high-pressure oil under the action of the hydraulic pump 12, and the high-pressure oil enters the first accumulator 15 through the charging valve 14 for temporary storage. As shown in fig. 2, when the service braking is required, the high-pressure oil is directly provided by the first accumulator 15, and the high-pressure oil enters the dry brake 22 after passing through the hydraulic control module, so that the flow stroke of the high-pressure oil can be reduced, the braking efficiency of the braking system can be improved, and the starting times of the hydraulic pump 12 can be reduced, thereby achieving the purpose of reducing energy consumption.
When the service brake is released, as shown in fig. 3, the brake oil in the dry brake 22 flows back into the oil tank 11 after passing through the outlet of the dry brake 22 and the hydraulic control module in order, and is mixed with the low-temperature oil in the oil tank 11 to be cooled. With the increase of the number of times of the loading machine braking, the high-pressure oil in the first accumulator 15 is reduced, and the braking system can control the hydraulic pump 12 to start according to the liquid level change in the first accumulator 15 so as to timely supplement the high-pressure oil in the first accumulator 15.
Optionally, a filter 13 may be further connected to an oil outlet of the oil tank 11, and the filter 13 may be disposed between the hydraulic pump 12 and the charge valve 14. The high-pressure oil passing through the hydraulic pump 12 is filtered by the filter 13 to prevent the impurities from entering into the downstream components thereof, thereby ensuring the reliability of the brake system.
In order to avoid that the height Wen Youye of the return flow into the tank 11 influences the temperature of the oil in the tank 11, which leads to an increase in the temperature of the oil in the brake system, the oil returned from the outlet of the dry brake 22 may pass through the fluid circuit control module and the radiator 25 and then enter the tank 11 through the return opening of the tank 11. By providing the radiator 25, the high Wen Youye returned from the dry brake 22 can be cooled quickly, the heat radiation effect can be improved, and the temperature of the oil in the oil tank 11 can be prevented from rising. Alternatively, the radiator 25 may be provided between the hydraulic control module and the return port of the hydraulic power system 100, i.e., between the hydraulic control module and the return port of the tank 11.
In this embodiment, the fluid circuit control module includes a hydraulic brake valve 26 and a control valve block 21. The hydraulic brake valve 26 is connected to a brake pedal. The control valve group 21 can control the oil outlet of the hydraulic power system 100 (i.e. the outlet of the first accumulator 15) to communicate with the inlet of the dry brake 22, and can also control the outlet of the dry brake 22 to communicate with the oil return port of the hydraulic power system 100 (i.e. the oil return port of the oil tank 11), so as to control the flow direction of the oil during the service braking and release of the service braking.
Specifically, the control valve group 21 includes a first control valve having an inlet connected to the outlet of the dry brake 22 and an outlet connected to the return port of the tank 11 so as to return at least a portion Wen Youye of the dry brake 22 back to the tank 11 during the release of the service brake.
One end of the hydraulic brake valve 26 is connected to the outlet of the first accumulator 15, and the other end is connected to the inlet of the second control valve, the outlet of which is connected to the inlet of the dry brake 22, so as to communicate the oil outlet of the hydraulic power system 100 with the inlet of the dry brake 22. During service braking, the second control valve is opened, and the first control valve is closed, so that high-pressure oil liquid sequentially passes through the hydraulic brake valve 26 and the second control valve and then enters the dry brake 22. When the service brake is released, the second control valve is closed and the first control valve is opened so that the high Wen Youye in the dry brake 22 flows back into the oil tank 11.
Alternatively, the hydraulic brake valve 26 may be a three-way valve, one port of which communicates with the inlet of the second control valve, and the remaining two ports of which communicate with the outlet of the first accumulator 15 and the return port of the tank 11, respectively. When the brake pedal is depressed, two ports of the three-way valve, which connect the outlet of the first accumulator 15 and the inlet of the second control valve, are communicated so that high-pressure oil enters the dry brake 22. When the brake pedal is released, the two valve ports of the three-way valve, which are connected with the inlet of the second control valve and the oil return port of the oil tank 11, are communicated, and the second control valve is closed at the moment, so that residual oil liquid positioned at the upstream of the second control valve flows back into the oil tank 11 through the three-way valve, and the oil liquid is prevented from being detained in a brake system.
Alternatively, the first control valve may be a hydraulic switch valve 211 and the second control valve may be a relief valve 212. Specifically, the hydraulic switching valve 211 is a two-position two-way valve. For convenience of description, the direction shown in fig. 3 is taken as an example, and the upper position of the two-position two-way valve is conducted, and the lower position is closed. The upper end of the two-position two-way valve can be communicated with the outlet of the dry brake 22 and the oil return port of the hydraulic power system 100. Two ends of the pilot valve of the two-position two-way valve are respectively connected with the lower position and the upstream of the overflow valve 212. When service brakes are applied, the relief valve 212 is opened by the pressure of the oil to allow the oil to enter the dry brake 22. The high-pressure oil enters the pilot valve so that the two-position two-way valve overcomes the acting force of the spring in the pilot valve under the action of oil, and the lower position of the two-position two-way valve is respectively connected with the outlet of the dry brake 22 and the oil return port of the hydraulic power system 100, thereby avoiding the oil in the dry brake 22 from flowing back. When the vehicle brakes are contacted, the overflow valve 212 is closed, the oil liquid at the upstream of the overflow valve 212 flows back into the oil tank 11, and the two-position two-way valve is reset under the action of the spring in the overflow valve, so that the upper positions of the two-position two-way valve are respectively connected with the outlet of the dry brake 22 and the oil return port of the hydraulic power system 100, and part of the oil liquid in the dry brake 22 flows back into the oil tank 11.
In other embodiments, the second control valve may also be a one-way valve. However, the single-way valve is generally cone-sealed, if the cleanliness of the oil in the braking system is not high, the check valve is easy to be blocked, so that when the service braking is released, the inlet of the dry brake 22 is communicated with the hydraulic brake valve 26, the oil in the dry brake 22 flows back through the check valve, and the oil cannot flow back from the outlet at the upper part of the dry brake 22, so that the heat dissipation effect cannot be achieved.
In other embodiments, the control valve group 21 may have other structures, for example, the first control valve and the second control valve are electromagnetic switch valves, or at least one of the first control valve and the second control valve is an electromagnetic switch valve, so long as the second control valve is opened and the first control valve is closed during service braking, and the second control valve is closed and the first control valve is opened during service braking release.
Service brakes of a loader generally include front side wheel brakes and rear side wheel brakes, and for this purpose, in this embodiment, the dry brakes 22 are provided with two, one for front side wheel brakes and the other for rear side wheel brakes. Correspondingly, two service brake driving circuits are arranged in parallel in the hydraulic power system 100, each service brake driving circuit is provided with a first accumulator 15 connected with the charging valve 14, and each service brake driving circuit is correspondingly provided with a hydraulic brake valve 26, a control valve group 21 and a dry brake 22. The other hydraulic brake valves 26 are connected to a brake pedal, and when the brake pedal is depressed or released, the two hydraulic brake valves 26 operate synchronously.
In the present embodiment, the dry brake 22 includes four calipers 221, two calipers 221 are grouped, and the two groups of calipers 221 in each dry robot brake the wheels on the left and right sides, respectively. To improve the synchronization of the left and right wheel brakes, four calipers 221 may be provided in parallel. Specifically, two brake calipers 221 in each group are connected in parallel, two groups of brake calipers 221 are connected in parallel, namely four brake calipers 221 can be connected in parallel, and the two groups of brake calipers 221 are symmetrically arranged, so that the inlet of the dry brake 22 is positioned at the middle position of the two groups of brake calipers 221, the distance of oil entering the brake calipers 221 is short, the braking efficiency is improved, and the four brake calipers 221 are ensured to synchronously work, so that the problem that the abrasion is aggravated due to the fact that a certain brake calipers 221 are braked first can be avoided, and the problem of eccentric wear of the dry brake 22 can be avoided.
In this embodiment, the brake system further includes a parking brake 23 and a parking brake valve 24, and the hydraulic power system 100 is connected to the parking brake 23 through the parking brake valve 24. When in parking braking, at least part of oil in the parking brake 23 flows back to the hydraulic power system 100 after passing through the parking brake valve 24 and the radiator 25; when the parking brake is released, oil enters the parking brake 23 from the hydraulic power system 100 through the parking brake valve 24.
Specifically, as shown in fig. 1, to improve parking brake efficiency and reduce energy consumption, the brake system further includes a second accumulator 17, and the second accumulator 17 is connected to the hydraulic pump 12 through a charge valve 14 so as to supply high-pressure oil into the second accumulator 17.
Alternatively, the parking brake valve 24 may also be a three-way valve, the three ports of which are connected to the outlet of the second accumulator 17, the return line of the oil tank 11 and the parking brake 23, respectively. Specifically, as shown in fig. 4, in the present embodiment, the parking brake valve 24 is a two-position three-way valve, and takes the direction shown in fig. 4 as an example, the upper position thereof allows the oil to flow from the second accumulator 17 to the parking brake 23, and the lower position thereof allows the oil to flow from the parking brake 23 to the oil return port of the oil tank 11.
During parking braking, the parking brake valve 24 is positioned at the lower position under the action of the spring in the parking brake valve, and at least part of oil in the parking brake 23 flows back into the oil tank 11 through the parking brake valve 24 and the radiator 25 so that the parking brake 23 brakes an output flange of a gearbox in the loader. When the parking brake is released, as shown in fig. 5, the parking brake valve 24 is in the upper position against the spring force thereof, so that the high-pressure oil in the second accumulator 17 can enter the parking brake 23 through the parking brake valve 24. At this time, the low-temperature oil in the oil tank 11 is mixed with the high Wen Youye in the parking brake 23, so that the temperature of the oil in the parking brake 23 can be reduced, and the problem of heating of the oil during the parking brake is solved.
Alternatively, the operator may control the parking brake valve 24 by operating the handbrake while parking braking. In this embodiment, the operator can control the switching of the valve position in the parking brake valve 24 by a button. The operator can control the parking brake valve 24 by an electric signal generated when the button is pressed, so that the intensity of the worker can be greatly reduced.
Alternatively, the parking brake 23 may employ a rodless oil chamber, so that noise generated during the parking brake and the release of the parking brake is small, and noise pollution of an operator can be reduced.
In this embodiment, the parking brake valve 24 is normally in the down position, i.e., the braking position. When there is oil leakage or other problems with the braking system, the parking brake valve 24 will complete the parking brake of the loader under the action of the spring therein, thereby avoiding potential safety hazards.
The working process of the braking system provided in this embodiment is as follows:
as shown in fig. 1, the oil in the oil tank 11 forms high-pressure oil under the action of the hydraulic pump 12, and the high-pressure oil passes through the filter 13 and the charge valve 14 and then enters the first accumulator 15 and the second accumulator 17 to be stored.
As shown in fig. 2, when the brake pedal is depressed during service braking, the hydraulic brake valve 26 overcomes the resistance of the spring therein, so that the hydraulic control valve 26 is located at its upper position, i.e., the outlet of the first accumulator 15 communicates with the relief valve 212. The high pressure oil in the first accumulator 15 passes through the hydraulic brake valve 26 and opens the relief valve 212 to enter the dry brake 22. In this process, the high-pressure oil upstream of the relief valve 212 acts on the hydraulic switching valve 211 through the pilot valve, so that the hydraulic switching valve 211 is located at a lower position against the resistance of the internal spring thereof, that is, the hydraulic switching valve 211 is closed, preventing the outlet of the dry brake 22 from communicating with the radiator 25.
When the service brake is released, the brake pedal is released, and the hydraulic brake valve 26 is positioned at the lower position under the action of the spring therein, namely, the upstream of the overflow valve 212 is communicated with the radiator 25, so that the oil liquid at the upstream of the overflow valve 212 flows back to the oil tank 11 after being cooled by the radiator 25. Meanwhile, since the oil liquid at the upstream of the overflow valve 211 flows back to the oil tank 11 through the hydraulic brake valve 26, the hydraulic switch valve 211 is located at an upper position under the action of the spring therein, that is, the outlet of the dry brake 22 is communicated with the radiator 25, and at least part of the oil liquid in the dry brake 22 flows back to the oil tank 11 after passing through the hydraulic switch valve 211 and the radiator 25.
As shown in fig. 4, during parking braking, an operator controls the parking brake valve 24 through a button, so that the parking brake valve 24 is positioned at a lower position under the action of a spring in the parking brake valve 24, the parking brake 23 is communicated with the oil tank 11, and at least part of oil in the parking brake 23 flows back into the oil tank 11 through the parking brake valve 24 and the radiator 25, so that an output flange of a gearbox in the loader is braked.
When releasing the parking brake, as shown in fig. 5, the operator controls the parking brake valve 24 by means of a push button, so that the parking brake valve 24 is located in an upper position against the action of the spring therein, i.e. the outlet of the second accumulator 17 communicates with the parking brake 23. The high-pressure oil in the second accumulator 17 enters the parking brake 23 via the parking brake valve 24 in order to release the brake on the output flange.
Example two
The embodiment provides an engineering vehicle, which is different from the first embodiment in that the brake oil adopted by the brake system is high-temperature-resistant oil. When the dry brake 22 is used for braking, the temperature of the brake disc in the dry brake 22 can reach more than 200 ℃, the temperature of the friction plate in the brake caliper 221 can also reach more than 100 ℃, and the high-temperature-resistant Wen Youye is adopted as a working medium, so that the problems of deterioration, blackening, gasification and the like of the brake oil in the high-temperature state can be avoided, the brake oil can be kept within a required viscosity range, and the reliability of a braking system can be further ensured.
Example III
The present embodiment provides an engineering vehicle, which is different from the above embodiment in that in the present embodiment, a hydraulic circuit of an operating system and a hydraulic circuit of a brake system are provided independently of each other, and the brake system adopts a separate oil tank 11 to provide hydraulic drive for a hydraulic power system 100. The brake system adopts an independent oil tank 11, and the hydraulic circuit of the brake system is independent from the hydraulic circuit of the operation system, so that the oil liquid which is deteriorated, blackened, mixed with impurities and water in the brake system and enters the operation system due to frequent braking can be prevented, and the reliability of the operation system is further influenced; and the high-resistance Wen Youye can be adopted for the braking system only, thereby being beneficial to reducing the cost.
Optionally, the brake system and the operation system can be controlled independently, which is beneficial to simplifying the control system, facilitating the control and improving the reliability of the engineering vehicle.
The foregoing is merely exemplary of the present invention, and those skilled in the art should not be considered as limiting the invention, since modifications may be made in the specific embodiments and application scope of the invention in light of the teachings of the present invention.
Claims (10)
1. A braking system characterized by comprising a hydraulic power system (100), a dry brake (22), and a radiator (25), the hydraulic power system (100) being connected to the dry brake (22) by a fluid path control module configured to:
when in service braking, the hydraulic power system (100) can drive oil to enter the dry brake (22) through the liquid path control module; when the service braking is released, at least part of oil in the dry brake (22) flows back to the hydraulic power system (100) after passing through the liquid path control module and the radiator (25).
2. The braking system of claim 1, wherein the fluid circuit control module comprises a hydraulic braking valve (26) and a control valve block (21), the control valve block (21) being configured to control communication of an oil outlet of the hydraulic power system (100) and an inlet of the dry brake (22), and to control communication of an outlet of the dry brake (22) and an oil return of the hydraulic power system.
3. A braking system according to claim 2, characterized in that the control valve group (21) comprises a first control valve and a second control valve, wherein one end of the first control valve is connected to the outlet of the dry brake (22) and the other end is connected to the return port of the hydraulic power system (100);
one end of the hydraulic brake valve (26) is connected with an oil outlet of the hydraulic power system (100), and the other end of the hydraulic brake valve is connected with an inlet of the second control valve; the outlet of the second control valve is connected to the inlet of the dry brake (22).
4. A brake system according to claim 3, wherein the first control valve is a hydraulic on-off valve (211) and the second control valve is a relief valve (212) or a hydraulic non-return valve; or (b)
The first control valve and the second control valve are electromagnetic switch valves.
5. A brake system according to claim 3, characterized in that the hydraulic brake valve (26) is a three-way valve, one port of which is in communication with the second control valve, the remaining two ports of which are connected to the oil outlet and return port of the hydraulic power system (100), respectively.
6. A brake system according to any one of claims 1-5, characterized in that the radiator (25) is located between the fluid circuit control module and the return port of the hydraulic power system (100).
7. A brake system according to any one of claims 1-5, characterized in that the dry brake (22) comprises four brake calipers (221), the four brake calipers (221) being connected in parallel and then connected to the fluid circuit control module.
8. The brake system of any one of claims 1-5, wherein the oil within the brake system is a high temperature resistant oil.
9. An engineering vehicle comprising a brake system according to any one of claims 1-8.
10. The work vehicle of claim 9, further comprising a work system, wherein the hydraulic circuit of the brake system and the hydraulic circuit of the work system are disposed independently of each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910275938.7A CN109878482B (en) | 2019-04-08 | 2019-04-08 | Braking system and engineering vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910275938.7A CN109878482B (en) | 2019-04-08 | 2019-04-08 | Braking system and engineering vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109878482A CN109878482A (en) | 2019-06-14 |
| CN109878482B true CN109878482B (en) | 2024-02-02 |
Family
ID=66936451
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910275938.7A Active CN109878482B (en) | 2019-04-08 | 2019-04-08 | Braking system and engineering vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109878482B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110588600B (en) * | 2019-09-23 | 2024-03-29 | 山东临工工程机械有限公司 | Air-cooled braking heat dissipation system and loader |
| CN113734123B (en) * | 2021-09-22 | 2023-05-12 | 一汽解放汽车有限公司 | Automatic driving hydraulic braking system |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0826097A (en) * | 1994-07-15 | 1996-01-30 | Toyo Umpanki Co Ltd | Brake device for vehicle |
| DE10053084C1 (en) * | 2000-10-26 | 2002-05-29 | Renk Ag | Drive and braking unit for commercial vehicle has single hydrodynamic brake acting as primary retarder or secondary retarder for switched drive transmission |
| WO2010024734A1 (en) * | 2008-08-29 | 2010-03-04 | Volvo Construction Equipment Ab | Brake system and vehicle comprising a brake system |
| WO2012001128A1 (en) * | 2010-07-01 | 2012-01-05 | Societe De Technologie Michelin | Motorized hub comprising an electric traction unit |
| CN106314405A (en) * | 2016-09-17 | 2017-01-11 | 西安科技大学 | Large-tonnage hydraulic mining vehicle braking system and method |
| CN206012580U (en) * | 2016-09-17 | 2017-03-15 | 西安科技大学 | Large-tonnage mine vehicle brake fluid system with refrigerating function |
| CN206107227U (en) * | 2016-10-25 | 2017-04-19 | 厦门厦工机械股份有限公司 | Two oil circuit tiny loop braking system |
| CN209719559U (en) * | 2019-04-08 | 2019-12-03 | 山东临工工程机械有限公司 | A kind of braking system and engineering truck |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20130187353A1 (en) * | 2012-01-23 | 2013-07-25 | Erwin Mock | Multi-brake system having independent control |
-
2019
- 2019-04-08 CN CN201910275938.7A patent/CN109878482B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0826097A (en) * | 1994-07-15 | 1996-01-30 | Toyo Umpanki Co Ltd | Brake device for vehicle |
| DE10053084C1 (en) * | 2000-10-26 | 2002-05-29 | Renk Ag | Drive and braking unit for commercial vehicle has single hydrodynamic brake acting as primary retarder or secondary retarder for switched drive transmission |
| WO2010024734A1 (en) * | 2008-08-29 | 2010-03-04 | Volvo Construction Equipment Ab | Brake system and vehicle comprising a brake system |
| WO2012001128A1 (en) * | 2010-07-01 | 2012-01-05 | Societe De Technologie Michelin | Motorized hub comprising an electric traction unit |
| CN102958729A (en) * | 2010-07-01 | 2013-03-06 | 米其林集团总公司 | Motorized hub comprising electric traction unit |
| CN106314405A (en) * | 2016-09-17 | 2017-01-11 | 西安科技大学 | Large-tonnage hydraulic mining vehicle braking system and method |
| CN206012580U (en) * | 2016-09-17 | 2017-03-15 | 西安科技大学 | Large-tonnage mine vehicle brake fluid system with refrigerating function |
| CN206107227U (en) * | 2016-10-25 | 2017-04-19 | 厦门厦工机械股份有限公司 | Two oil circuit tiny loop braking system |
| CN209719559U (en) * | 2019-04-08 | 2019-12-03 | 山东临工工程机械有限公司 | A kind of braking system and engineering truck |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109878482A (en) | 2019-06-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102120447B (en) | Forklift hydraulic system matched with multi-functional wet brakes | |
| CN106143456A (en) | The brakes of large-tonnage storage battery forktruck | |
| CN109878482B (en) | Braking system and engineering vehicle | |
| CN102791549A (en) | Construction machine | |
| CN201712591U (en) | Braking system for electric forklift truck | |
| CN105864133B (en) | A kind of diesel engine monorail crane hydraulic system | |
| CN206049646U (en) | The brakes of large-tonnage storage battery forktruck | |
| CN110745121A (en) | Hydraulic-mechanical combined braking control system for underground coal mine explosion-proof vehicle | |
| CN102785652B (en) | Integrated control system of wheel type engineering machine | |
| CN110843740B (en) | Hydraulic-mechanical combined braking system for coal mine articulated explosion-proof vehicle | |
| CN103264691B (en) | Brake system of empty container forklift | |
| CN106194859A (en) | The electro-hydraulic brake hydraulic system of straddle carrier and control method thereof | |
| CN202764956U (en) | Wheel type engineering machinery integrated control system | |
| CN101922524A (en) | Enclosed multi-disc wet type braking device | |
| CN117864084A (en) | Fork truck braking system and fork truck that has it | |
| CN108248588B (en) | Loader braking system | |
| KR20190073495A (en) | Vehicle hydraulic brake system | |
| CN103661340B (en) | Vehicle braking system and vehicle | |
| CN207902416U (en) | Mechanical loader braking system | |
| CN209719559U (en) | A kind of braking system and engineering truck | |
| CN112721890B (en) | Hydraulic braking system of engineering machinery vehicle | |
| CN108082151B (en) | Wet-type bridge braking and external cooling circulation system | |
| CN110541856B (en) | Unmanned automatic control's fork truck braking hydraulic system | |
| CN111059101B (en) | Big arm oil cylinder control valve group | |
| CN210949328U (en) | Power output flexible combination control valve block assembly for tractor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |