CN115492183B - Regeneration valve group, hydraulic system for movable arm oil cylinder of excavator and hydraulic control method - Google Patents
Regeneration valve group, hydraulic system for movable arm oil cylinder of excavator and hydraulic control method Download PDFInfo
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- CN115492183B CN115492183B CN202211365407.5A CN202211365407A CN115492183B CN 115492183 B CN115492183 B CN 115492183B CN 202211365407 A CN202211365407 A CN 202211365407A CN 115492183 B CN115492183 B CN 115492183B
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- 230000008929 regeneration Effects 0.000 title claims abstract description 88
- 238000011069 regeneration method Methods 0.000 title claims abstract description 88
- 238000000034 method Methods 0.000 title claims abstract description 14
- 239000003921 oil Substances 0.000 claims description 343
- 239000010720 hydraulic oil Substances 0.000 claims description 32
- 230000009471 action Effects 0.000 claims description 7
- 238000007599 discharging Methods 0.000 claims description 4
- 230000005484 gravity Effects 0.000 claims description 4
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 238000005265 energy consumption Methods 0.000 abstract description 4
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
- E02F3/36—Component parts
- E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
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- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention belongs to the technical field of hydraulic pressure, and particularly relates to a regeneration valve group, a hydraulic system for an excavator movable arm oil cylinder and a hydraulic control method, wherein the regeneration valve group comprises a main reversing valve, a first reversing valve and a second reversing valve; an oil inlet of the main reversing valve is connected with an A1 oil port of the regeneration valve group, a spring cavity of the main reversing valve is connected with an A1 oil port of the regeneration valve group through a fixed hydraulic resistor, and an oil outlet of the main reversing valve is connected with a B1 oil port of the regeneration valve group through a one-way valve; the oil inlet of the first reversing valve is connected with the spring cavity of the main reversing valve, the oil outlet of the first reversing valve is connected with the oil inlet of the second reversing valve, and the oil outlet of the second reversing valve is connected with the L-shaped oil port of the regeneration valve group; the control cavity of the first reversing valve is connected with the X1 oil port of the regeneration valve group, and the control cavity of the second reversing valve is connected with the X2 oil port of the regeneration valve group. The movable arm of the excavator can be regenerated in flow when the movable arm of the excavator descends through the application of the regeneration valve group, the pump does not need to provide extra flow, the flow utilization rate is improved, and the energy consumption is reduced.
Description
Technical Field
The invention belongs to the technical field of hydraulic pressure, and particularly relates to a regeneration valve group, a hydraulic system for an excavator movable arm oil cylinder and a hydraulic control method.
Background
The movable arm of the medium-large excavator generally needs larger flow, the flow of the rodless cavity is generally regenerated to the rod cavity by utilizing the gravity influence when the movable arm descends, at the moment, the pump does not need to supply oil to the rod cavity or only needs to supply a small amount of oil, the rod cavity can be prevented from sucking air due to insufficient oil supply of the pump when the stop arm descends, and meanwhile, the flow recovery is carried out, so that the composite action efficiency is improved.
At present, a regeneration oil duct and a one-way valve are arranged in a valve core of a movable arm to carry out flow regeneration (as shown in figure 1) in the domestic large-medium excavator, and when the movable arm descends, part of hydraulic oil in a rodless cavity of the movable arm cylinder is regenerated to a rod cavity of the cylinder through a throttling groove I oil return tank and the other part of hydraulic oil is regenerated to the rod cavity of the cylinder through a throttling groove II, the regeneration oil duct and the one-way valve.
This approach has several problems:
1. the processing difficulty of the main valve and the valve core is increased;
2. the sizes of the throttling groove II and the regeneration oil duct are influenced by the diameter of the valve core, and the regeneration quantity requirement cannot be met generally;
3. the throttle groove II and the throttle groove I are difficult to match with each other, and the rod cavity is easily sucked or high pressure is easily generated when the movable arm descends.
In addition, china patent application of regeneration valve, multiple valve, hydraulic system and engineering machinery (publication number: 202111457130.4) mentions an external valve regeneration mode, which is to arrange pressure sensors in a movable arm rod cavity and a rodless cavity, wherein the regeneration valve is controlled by electric proportion, and the regeneration quantity is controlled by utilizing the pressure of the rod cavity and the rodless cavity.
The method has the following problems:
1. the electric proportional regeneration valve and the pressure sensor are high in cost, and electric components, particularly the pressure sensor, are distorted due to the impact of oil temperature and hydraulic pressure, so that control confusion is finally caused.
2. The regeneration valve is provided with a load holding valve alone, which makes the structure of the regeneration valve complex and costly.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides the regeneration valve group, the hydraulic system for the movable arm oil cylinder of the excavator and the hydraulic control method, and the flow can be regenerated when the movable arm of the excavator is lowered by using the regeneration valve group, so that the pump does not need to provide extra flow, the flow utilization rate is improved, and the energy consumption is reduced.
The invention is realized by the following technical scheme: the regeneration valve group comprises a main reversing valve, a first reversing valve and a second reversing valve;
the oil inlet of the main reversing valve is connected with the A1 oil port of the regeneration valve group, the spring cavity of the main reversing valve is connected with the A1 oil port of the regeneration valve group through a fixed hydraulic resistor, the oil outlet of the main reversing valve is connected with the B1 oil port of the regeneration valve group through a one-way valve, and the one-way valve is in one-way conduction from the oil outlet of the main reversing valve to the B1 oil port of the regeneration valve group;
the main reversing valve comprises an initial position, a first working position and a second working position, and when the main reversing valve is in the initial position, an oil inlet of the main reversing valve and an oil outlet of the main reversing valve are in a cut-off state; when the main reversing valve is in the first working position, a throttle conduction state is formed between an oil inlet of the main reversing valve and an oil outlet of the main reversing valve; when the main reversing valve is in the second working position, an oil inlet of the main reversing valve and an oil outlet of the main reversing valve are in a non-throttling conduction state;
an oil inlet of the first reversing valve is connected with a spring cavity of the main reversing valve, an oil outlet of the first reversing valve is connected with an oil inlet of the second reversing valve, and an oil outlet of the second reversing valve is connected with an L oil port of the regeneration valve group; the control cavity of the first reversing valve is connected with the X1 oil port of the regeneration valve group, and the control cavity of the second reversing valve is connected with the X2 oil port of the regeneration valve group;
the first reversing valve comprises an initial position and a working position, and when the first reversing valve is in the initial position, the oil inlet of the first reversing valve and the oil outlet of the first reversing valve are in a cut-off state; when the first reversing valve is in a working position, an oil inlet of the first reversing valve and an oil outlet of the first reversing valve are in a conducting state;
the second reversing valve comprises an initial position and a working position, and when the second reversing valve is in the initial position, a throttled conduction state is formed between an oil inlet of the second reversing valve and an oil outlet of the second reversing valve; when the second reversing valve is in the working position, an oil inlet of the second reversing valve and an oil outlet of the second reversing valve are in a cut-off state.
In some embodiments, a valve core of the main reversing valve is arranged in the guide hole, one side of the valve core is an oil return cavity of the main reversing valve, the other side of the valve core is a spring cavity of the main reversing valve, a first oil duct communicated with the oil return cavity of the main reversing valve and a second oil duct communicated with the spring cavity of the main reversing valve are arranged on the main reversing valve, and the second oil duct is respectively communicated with the fixed liquid resistance and an oil inlet of the first reversing valve.
In some embodiments, the first oil passage is provided on a valve body of the main reversing valve, and the second oil passage is provided on an end cap of the main reversing valve; the valve core is provided with an inclined plane, and when the inclined plane of the valve core is in close contact with the valve body, the main reversing valve is in an initial position; and a throttling groove is formed between the valve core and the valve body, and the flow area of the throttling groove is increased along with the increase of the displacement of the valve core moving towards the spring cavity direction of the main reversing valve.
In some embodiments, the valve core is provided with a positioning boss on one side close to a spring cavity of the main reversing valve, and a spring of the main reversing valve is sleeved on the positioning boss.
In some embodiments, when the second reversing valve is in the initial position, the flow area of hydraulic oil between the oil inlet of the second reversing valve and the oil outlet of the second reversing valve is controlled by the pressure of the control cavity of the second reversing valve.
The invention also provides a hydraulic system for the movable arm cylinder of the excavator, which comprises the regeneration valve bank, wherein the hydraulic system comprises a reversing valve, an oil inlet of the reversing valve is connected with a pump, an oil return port of the reversing valve is connected with an oil tank, a first working oil port of the reversing valve is respectively connected with an A1 oil port of the regeneration valve bank and a rodless cavity of the movable arm cylinder, and a rod cavity of the movable arm cylinder is respectively connected with a second working oil port of the reversing valve and a B1 oil port of the regeneration valve bank; the reversing valve further comprises a left control cavity X3 and a right control cavity X4, an X1 oil port of the regeneration valve bank is connected with the right control cavity X4 of the reversing valve, an X2 oil port of the regeneration valve bank is connected with a rod cavity of the movable arm oil cylinder, and an L oil port of the regeneration valve bank is connected with the oil tank.
In some embodiments, the reversing valve includes a left station, an initial position, and a right station;
when the reversing valve is in an initial position, an oil inlet of the reversing valve, an oil return port of the reversing valve, a first working oil port of the reversing valve and a second working oil port of the reversing valve are all in a cut-off state;
when the left control cavity X3 of the reversing valve is connected with pilot oil, the reversing valve is in a left station, an oil inlet of the reversing valve is in a conducting state with a first working oil port of the reversing valve, and an oil return port of the reversing valve is in a conducting state with a second working oil port of the reversing valve;
when the right control cavity X4 of the reversing valve is connected with the pilot oil, the reversing valve is in a right station, an oil inlet of the reversing valve is in a conducting state with a second working oil port of the reversing valve, and an oil return port of the reversing valve is in a conducting state with a first working oil port of the reversing valve.
The invention also provides a hydraulic control method, which comprises the hydraulic system for the movable arm oil cylinder of the excavator, wherein when the movable arm of the excavator rises: the left control cavity X3 of the reversing valve is connected with pilot oil, the right control cavity X4 of the reversing valve is connected with return oil, a pump supplies oil to the rodless cavity of the movable arm oil cylinder through the first working oil port of the reversing valve, and the rod cavity of the movable arm oil cylinder returns oil through the second working oil port of the reversing valve;
when the boom of the excavator is lowered: the right control cavity X4 of the reversing valve is connected with pilot oil, the left control cavity X3 of the reversing valve is connected with oil return, the reversing valve is switched to a right station, the first reversing valve is in a working position under the action of the pilot oil, the spring cavity of the main reversing valve sequentially discharges oil through the first reversing valve and the second reversing valve, and the main reversing valve is switched to a conducting state; the movable arm of the excavator descends under the action of gravity, so that hydraulic oil in the rodless cavity of the movable arm oil cylinder returns oil through the first working oil port of the reversing valve, and in addition, the hydraulic oil in the rodless cavity of the movable arm oil cylinder also supplies oil to the rod cavity of the movable arm oil cylinder through the main reversing valve.
In some embodiments, the flow area of the hydraulic oil between the oil inlet of the second reversing valve and the oil outlet of the second reversing valve is controlled by the pressure of the control cavity of the second reversing valve;
when the movable arm of the excavator descends, when the pressure of the movable arm oil cylinder with a rod cavity is lower than a set value, the flow area of the second reversing valve is increased, the oil unloading speed of the spring cavity of the main reversing valve is increased, the acting force of the spring cavity of the main reversing valve on the valve core is reduced, the flow area from the oil inlet of the main reversing valve to the oil outlet of the main reversing valve is increased, and the hydraulic oil flowing to the movable arm oil cylinder with the rod cavity through the main reversing valve is increased, so that the pressure of the movable arm oil cylinder with the rod cavity tends to the set value;
when the pressure of the movable arm cylinder with the rod cavity is higher than a set value, the flow area of the second reversing valve is reduced, the oil discharging speed of the spring cavity of the main reversing valve is reduced, the acting force of the spring cavity of the main reversing valve on the valve core is increased, the flow area from the oil inlet of the main reversing valve to the oil outlet of the main reversing valve is reduced, and the hydraulic oil flowing to the movable arm cylinder with the rod cavity through the main reversing valve is reduced, so that the pressure of the movable arm cylinder with the rod cavity tends to the set value.
The beneficial effects of the invention are as follows: 1. the hydraulic system can enable the movable arm of the excavator to regenerate by means of flow when the movable arm descends, the pump does not need to provide flow, the flow utilization rate is improved, and the energy consumption is reduced.
2. The pressure of the movable arm cylinder with a rod cavity is kept at a set value, and when the pressure of the movable arm cylinder with the rod cavity is higher than the set value, the regeneration quantity is regulated down by changing the throttling effect of the second reversing valve; when the pressure of the movable arm cylinder with the rod cavity is lower than a set value, the regeneration amount is increased. Through the feedback arrangement, the condition that the movable arm oil cylinder is in suction or high pressure is avoided.
3. The valve core of the main reversing valve has a load maintaining function, and the structure of the regeneration valve group is simplified.
Drawings
FIG. 1 is a schematic diagram of the prior art;
FIG. 2 is a hydraulic schematic diagram of a regeneration valve set of the present invention;
FIG. 3 is a schematic diagram of the main reversing valve of the present invention;
FIG. 4 is a hydraulic schematic of the present invention for an excavator boom cylinder;
FIG. 5 is a schematic diagram of the present invention for an excavator boom cylinder;
FIG. 6 is a schematic diagram of a B-half bridge constructed in accordance with the present invention;
in the figure, 1, a pump, 2, a reversing valve, 3, a regeneration valve group, 31, a main reversing valve, 311, a valve body, 312, a valve core, 3121, a positioning boss, 313, an end cover, 314, a guide hole, 315, a spring, 32, a fixed hydraulic resistor, 33, a first reversing valve, 34, a second reversing valve, 35, a one-way valve, 4 and a movable arm oil cylinder.
Detailed Description
The invention is further described below with reference to the drawings and examples.
As shown in fig. 2, a regeneration valve group includes a main directional valve 31, a first directional valve 33, and a second directional valve 34.
An oil inlet of the main reversing valve 31 is connected with an A1 oil port of the regeneration valve group 3, a spring cavity of the main reversing valve 31 is connected with the A1 oil port of the regeneration valve group 3 through a fixed hydraulic resistor 32, an oil outlet of the main reversing valve 31 is connected with an oil inlet of a one-way valve 35, and an oil outlet of the one-way valve 35 is connected with a B1 oil port of the regeneration valve group 3. The oil inlet of the first reversing valve 33 is connected with the spring cavity of the main reversing valve 31, the oil outlet of the first reversing valve 33 is connected with the oil inlet of the second reversing valve 34, and the oil outlet of the second reversing valve 34 is connected with the L-shaped oil port of the regeneration valve group 3; the control cavity of the first reversing valve 33 is connected with the X1 oil port of the regeneration valve group 3, and the control cavity of the second reversing valve 34 is connected with the X2 oil port of the regeneration valve group 3.
As shown in fig. 2, 4 and 5, the main directional valve 31 includes an initial position, a first operating position and a second operating position. When the main reversing valve 31 is in the initial position, the oil inlet of the main reversing valve 31 and the oil outlet of the main reversing valve 31 are in a cut-off state, namely hydraulic oil entering from the A1 oil port of the regeneration valve group 3 cannot reach the B1 oil port of the regeneration valve group 3 through the main reversing valve 31. When the main reversing valve 31 is in the first working position, the oil inlet of the main reversing valve 31 and the oil outlet of the main reversing valve 31 are in a throttled conduction state, namely hydraulic oil entering from the A1 oil port of the regeneration valve group 3 can reach the B1 oil port of the regeneration valve group 3 through the main reversing valve 31, but the flow is limited by the throttling of the throttling groove in the main reversing valve 31. When the main reversing valve 31 is in the second working position, the oil inlet of the main reversing valve 31 and the oil outlet of the main reversing valve 31 are in an unthrottled conduction state, namely hydraulic oil entering from the A1 oil port of the regeneration valve group 3 can reach the B1 oil port of the regeneration valve group 3 through the main reversing valve 31, and at the moment, the throttling groove in the main reversing valve 31 does not play a throttling role.
In order to realize the functions of the main directional valve 31, the present invention provides a structural form of the main directional valve 31 capable of realizing the functions, the main directional valve 31 has a specific structure as shown in fig. 3 and 5, the main directional valve 31 comprises a valve body 311, a valve core 312, an end cover 313 and a spring 315, a guide hole 314 is arranged in the valve body 311, the valve core 312 is arranged in the guide hole 314, an oil return cavity of the main directional valve 31 is formed between the valve core 312 and the valve body 311, and the oil return cavity of the main directional valve 31 is communicated with a first oil duct Y1 arranged on the valve body 311. The end cover 313 is provided at one side of the valve body 311, a spring chamber of the main directional valve 31 is formed between the valve body 311, the end cover 313 and the valve body 312, and the spring chamber of the main directional valve 31 communicates with a second oil passage provided at the end cover 313. The stepped structure on the valve core 312 is matched with the stepped structure of the valve body 311 at the guide hole 314, so that a throttling groove Y3 is formed at the oil outlet of the main reversing valve 31, a containing cavity Y4 is formed at the oil inlet of the main reversing valve 31, and the throttling groove Y3 is communicated with the containing cavity Y4. The valve core 312 is provided with an inclined plane Y5, when the main reversing valve 31 is in the initial position, a linear seal is formed between the inclined plane Y5 of the valve core 312 and the valve body 311, an oil inlet of the main reversing valve 31 is separated from the containing cavity Y4, and the oil inlet of the main reversing valve 31 and an oil outlet of the main reversing valve 31 are in a cut-off state. In the process that the valve core 312 overcomes the resistance provided by the spring cavity of the main reversing valve 31 and moves towards the spring cavity of the main reversing valve 31, the flow area of the throttling groove Y3 is increased along with the increase of displacement, and when the flow area of the throttling groove Y3 is large to a certain extent, the throttling groove Y3 loses the throttling effect. As shown in fig. 3, when the main directional valve 31 is turned on, the balance equation of the spool 312: p1=f1+p2×s2, where P1 is the oil pressure of the oil inlet of the main reversing valve, S1 is the force area on which the oil in the oil inlet of the main reversing valve can act, F1 is the elastic force provided by the spring of the main reversing valve, P2 is the oil pressure in the spring cavity of the main reversing valve, and S2 is the force area on which the oil in the spring cavity of the main reversing valve can act. That is, as shown in fig. 3, when the force provided by the oil in the oil inlet of the main directional valve 31 to the valve element 312 is equal to the sum of the force provided by the oil in the spring chamber of the main directional valve 31 to the valve element 312 and the elastic force of the spring to the valve element 312, the valve element 312 is in a balanced state.
The main directional valve 31 shown in fig. 3 is applied to the regeneration valve group 3 of the present invention, a first oil passage of the main directional valve 31 is connected to an oil inlet of the check valve 35, and a second oil passage of the main directional valve 31 is respectively communicated with the fixed hydraulic resistor 32 and the oil inlet of the first directional valve 33.
In some embodiments, as shown in fig. 3 and fig. 5, the valve core 312 is provided with a positioning boss 3121 at a side close to the spring cavity of the main directional valve 31, the spring 315 of the main directional valve 31 is sleeved on the positioning boss 3121, and the positioning boss 3121 plays a role in positioning the spring 315.
As shown in fig. 2, 4 and 5, the first reversing valve 33 of the present invention includes an initial position and an operating position. When the first reversing valve 33 is in the initial position, the oil inlet of the first reversing valve 33 and the oil outlet of the first reversing valve 33 are in a cut-off state, i.e. hydraulic oil at the oil inlet of the first reversing valve 33 cannot reach the oil outlet of the first reversing valve 33 through the first reversing valve 33. When the first reversing valve 33 is in the working position, the oil inlet of the first reversing valve 33 and the oil outlet of the first reversing valve 33 are in a conducting state, and hydraulic oil at the oil inlet of the first reversing valve 33 can reach the oil outlet of the first reversing valve 33 through the first reversing valve 33. In combination with the connection relationship between the first directional valve 33 and the main directional valve 31, when the first directional valve 33 is in the working position, the spring cavity of the main directional valve 31 is conducted with the oil outlet of the first directional valve 33.
As shown in fig. 2, 4 and 5, the second reversing valve 34 of the present invention includes an initial position and a working position, when the second reversing valve 34 is in the initial position, the oil inlet of the second reversing valve 34 and the oil outlet of the second reversing valve 34 are in a throttled conducting state, that is, the hydraulic oil at the oil inlet of the second reversing valve 34 can reach the oil outlet of the second reversing valve 34 through the second reversing valve 34, but the flow of the hydraulic oil is throttled. When the second reversing valve 34 is in the working position, the oil inlet of the second reversing valve 34 and the oil outlet of the second reversing valve 34 are in a cut-off state, namely hydraulic oil at the oil inlet of the second reversing valve 34 cannot reach the oil outlet of the second reversing valve 34 through the second reversing valve 34. When the second reversing valve 34 is in the initial position, the flow area of hydraulic oil between the oil inlet of the second reversing valve 34 and the oil outlet of the second reversing valve 34 is controlled by the pressure of the control cavity of the second reversing valve 34, and the control cavity of the second reversing valve 34 is controlled by the pressure of the hydraulic oil acting on the control cavity.
As shown in fig. 2 to 5, the invention further provides a hydraulic system for the movable arm cylinder of the excavator, which comprises the regeneration valve group 3, wherein the hydraulic system comprises a reversing valve 2, an oil inlet of the reversing valve 2 is connected with a pump 1, an oil return port of the reversing valve 2 is connected with an oil tank, a first working oil port of the reversing valve 2 is respectively connected with an A1 oil port of the regeneration valve group 3 and a rodless cavity of the movable arm cylinder 4, and a rod cavity of the movable arm cylinder 4 is respectively connected with a second working oil port of the reversing valve 2 and a B1 oil port of the regeneration valve group 3; the reversing valve 2 further comprises a left control cavity X3 and a right control cavity X4, an X1 oil port of the regeneration valve group 3 is connected with the right control cavity X4 of the reversing valve 2, an X2 oil port of the regeneration valve group 3 is connected with a rod cavity of the movable arm oil cylinder 4, and an L oil port of the regeneration valve group 3 is connected with an oil tank.
As shown in fig. 4 and 5, the reversing valve 2 includes a left station, an initial station, and a right station;
when the reversing valve 2 is in the initial position, an oil inlet of the reversing valve 2, an oil return port of the reversing valve 2, a first working oil port of the reversing valve 2 and a second working oil port of the reversing valve 2 are all in a cut-off state.
When the left control cavity X3 of the reversing valve 2 is connected with pilot oil, the reversing valve 2 is at a left station, and an oil inlet of the reversing valve 2 is in a conducting state with a first working oil port of the reversing valve 2. The oil return port of the reversing valve 2 is in a conducting state with the second working oil port of the reversing valve 2, and the reversing valve 2 is used for controlling the movable arm of the excavator to ascend when being in a left station.
When the right control cavity X4 of the reversing valve 2 is connected with the pilot oil, the reversing valve 2 is in a right station, an oil inlet of the reversing valve 2 is in a conducting state with a second working oil port of the reversing valve 2, and an oil return port of the reversing valve 2 is in a conducting state with a first working oil port of the reversing valve 2. The reversing valve 2 is used for controlling the movable arm of the excavator to descend when being at the right station.
As shown in fig. 2 to 5, the present invention further provides a hydraulic control method, including the hydraulic system for an excavator boom cylinder, when the boom of the excavator is lifted: the left control cavity X3 of the reversing valve 2 is connected with pilot oil, the right control cavity X4 of the reversing valve 2 is connected with return oil, the pump 1 supplies oil to the rodless cavity of the movable arm cylinder 4 through the first working oil port of the reversing valve 2, and the rod cavity of the movable arm cylinder 4 returns oil through the second working oil port of the reversing valve 2. At this time, the X1 oil port of the regeneration valve group 3 is connected to the return oil, that is, the first reversing valve 33 keeps the initial position, hydraulic oil cannot pass through between the oil inlet of the first reversing valve 33 and the oil outlet of the first reversing valve 33, the acting force of the spring cavity of the main reversing valve 31 on the valve core 312 is large, the valve core 312 of the main reversing valve 31 does not act, the main reversing valve 31 is at the initial position, and the A1 oil port of the regeneration valve group 3 is not communicated with the B1 oil port of the regeneration valve group 3, so that the rod cavity of the boom cylinder 4 is not communicated with the rodless cavity of the boom cylinder 4. That is, when the boom of the excavator is raised, the regeneration valve group 3 does not affect the operation of the boom cylinder 4.
When the boom of the excavator is lowered: the right control cavity X4 of the reversing valve 2 is connected with pilot oil, the left control cavity X3 of the reversing valve 2 is connected with return oil, the reversing valve 2 is switched to a right station, and hydraulic oil in a rodless cavity of the movable arm oil cylinder 4 returns oil through a first working oil port of the reversing valve 2 under the action of the gravity of the movable arm of the excavator. Meanwhile, the first reversing valve 33 is switched to a working position under the action of pilot oil, and an oil inlet of the first reversing valve 33 is communicated with an oil outlet of the first reversing valve 33. The second direction valve 34 is at the initial position, the spring cavity of the main direction valve 31 discharges oil through the first direction valve 33 and the second direction valve 34 in sequence, the acting force of the spring cavity of the main direction valve 31 is reduced, the valve core 312 of the main direction valve 31 is switched to the conducting state, and the main direction valve 31 is switched to the conducting state. Part of hydraulic oil in the rodless cavity of the movable arm oil cylinder 4 is supplied to the rod-containing cavity of the movable arm oil cylinder 4 through the main reversing valve 31, the hydraulic oil in the rodless cavity of the movable arm oil cylinder 4 is introduced into the rod-containing cavity of the movable arm oil cylinder 4, flow regeneration is realized when the movable arm of the excavator descends, the pump 1 does not need to provide flow, the flow utilization rate is improved, and the energy consumption is reduced.
In some embodiments, it is necessary to control the lowering speed of the boom of the excavator, so that it is necessary to maintain the oil pressure of the boom cylinder 4 with the rod chamber at the set value, so that the shortage of the regeneration amount is avoided, so that the suction of the oil pressure of the boom cylinder 4 with the rod chamber is too low, and the high pressure cannot be generated due to the excessive regeneration amount. For this purpose, the flow area of the hydraulic oil between the oil inlet of the second reversing valve 34 and the oil outlet of the second reversing valve 34 is controlled by the pressure of the control chamber of the second reversing valve 34, and the control chamber of the second reversing valve 34 is communicated with the rod chamber of the boom cylinder 4, that is, the throttling effect of the second reversing valve 34 is controlled by the hydraulic pressure of the rod chamber of the boom cylinder 4. By adjusting the valve core of the second reversing valve 34 under the condition of the change of the oil pressure of the control cavity of the second reversing valve 34, the oil pressure of the rod cavity of the movable arm oil cylinder 4 always floats up and down near a set value. The method to be realized specifically comprises the following steps:
when the first directional valve 33 is in the working position and the second directional valve 34 is in the initial position, the hydraulic oil in the spring chamber of the main directional valve 31 flows back to the oil tank through the first directional valve 33 and the second directional valve 34 in sequence. At this time, the fixed hydraulic resistor 32, the second reversing valve 34 and the spring cavity of the main reversing valve 31 form a B-type half bridge, and the characteristics of the B-type half bridge can control the oil pressure P2 in the spring cavity of the main reversing valve 31 to change from 0 to P1 by changing the flow area of the second reversing valve 34; p1=p2 when the first directional valve 33 is in the initial position or the second directional valve 34 is in the operating position. P1 is the pressure of the rodless cavity of the movable arm cylinder 4, and because the rodless cavity of the movable arm cylinder 4 is communicated with the oil inlet of the main reversing valve 31, the oil pressure of the oil inlet of the main reversing valve 31 is also P1.
In the boom lowering process of the excavator, when the pressure of the rod cavity of the boom cylinder 4 is lower than a set value, the valve core of the second reversing valve 34 acts, the flow area of the second reversing valve 34 increases, the oil discharging speed of the spring cavity of the main reversing valve 31 increases, the acting force of the spring cavity of the main reversing valve 31 on the valve core 312 decreases, the flow area from the oil inlet of the main reversing valve 31 to the oil outlet of the main reversing valve 31 increases, the hydraulic oil flowing to the rod cavity of the boom cylinder 4 through the main reversing valve 31 increases, and the pressure of the rod cavity of the boom cylinder 4 tends to the set value.
When the pressure of the rod cavity of the boom cylinder 4 is higher than the set value, the valve core of the second reversing valve 34 acts reversely, the flow area of the second reversing valve 34 is reduced, the oil discharging speed of the spring cavity of the main reversing valve 31 is reduced, the acting force of the spring cavity of the main reversing valve 31 on the valve core 312 is increased, the flow area from the oil inlet of the main reversing valve 31 to the oil outlet of the main reversing valve 31 is reduced, the hydraulic oil flowing to the rod cavity of the boom cylinder 4 through the main reversing valve 31 is reduced, and the pressure of the rod cavity of the boom cylinder 4 tends to the set value.
The hydraulic system is adopted to control the movable arm of the excavator in the descending process, the movable arm oil cylinder 4 is provided with a rod cavity, oil is not required to be supplied by a pump, the pressure floats up and down near a set value, and the hydraulic system can not suck air or generate high pressure due to overlarge regeneration quantity.
The foregoing description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and any simple modification, equivalent variation and modification made to the above embodiments according to the technical principles of the present invention are within the scope of the technical solutions of the present invention.
Claims (9)
1. A regeneration valve group, characterized in that: comprises a main reversing valve (31), a first reversing valve (33) and a second reversing valve (34);
an oil inlet of the main reversing valve (31) is connected with an A1 oil port of the regeneration valve group (3), a spring cavity of the main reversing valve (31) is connected with the A1 oil port of the regeneration valve group (3) through a fixed hydraulic resistor (32), an oil outlet of the main reversing valve (31) is connected with a B1 oil port of the regeneration valve group (3) through a one-way valve (35), and the one-way valve (35) is unidirectionally communicated from the oil outlet of the main reversing valve (31) to the B1 oil port of the regeneration valve group (3);
the main reversing valve (31) comprises an initial position, a first working position and a second working position, and when the main reversing valve (31) is in the initial position, an oil inlet of the main reversing valve (31) and an oil outlet of the main reversing valve (31) are in a cut-off state; when the main reversing valve (31) is in the first working position, a throttle conduction state is formed between an oil inlet of the main reversing valve (31) and an oil outlet of the main reversing valve (31); when the main reversing valve (31) is in the second working position, an oil inlet of the main reversing valve (31) and an oil outlet of the main reversing valve (31) are in a non-throttling conduction state;
an oil inlet of the first reversing valve (33) is connected with a spring cavity of the main reversing valve (31), an oil outlet of the first reversing valve (33) is connected with an oil inlet of the second reversing valve (34), and an oil outlet of the second reversing valve (34) is connected with an L oil port of the regeneration valve group (3); the control cavity of the first reversing valve (33) is connected with the X1 oil port of the regeneration valve group (3), and the control cavity of the second reversing valve (34) is connected with the X2 oil port of the regeneration valve group (3);
the first reversing valve (33) comprises an initial position and a working position, and when the first reversing valve (33) is in the initial position, an oil inlet of the first reversing valve (33) and an oil outlet of the first reversing valve (33) are in a cut-off state; when the first reversing valve (33) is in a working position, an oil inlet of the first reversing valve (33) and an oil outlet of the first reversing valve (33) are in a conducting state;
the second reversing valve (34) comprises an initial position and a working position, and when the second reversing valve (34) is in the initial position, an oil inlet of the second reversing valve (34) and an oil outlet of the second reversing valve (34) are in a throttled conduction state; when the second reversing valve (34) is in a working position, an oil inlet of the second reversing valve (34) and an oil outlet of the second reversing valve (34) are in a cut-off state.
2. The regeneration valve group of claim 1, wherein: the valve core (312) of the main reversing valve (31) is arranged in the guide hole (314), one side of the valve core (312) is an oil return cavity of the main reversing valve (31), the other side of the valve core is a spring cavity of the main reversing valve (31), a first oil duct communicated with the oil return cavity of the main reversing valve (31) and a second oil duct communicated with the spring cavity of the main reversing valve (31) are arranged on the main reversing valve (31), and the second oil duct is respectively communicated with the fixed hydraulic resistor (32) and an oil inlet of the first reversing valve (33).
3. The regeneration valve group of claim 2, wherein: the first oil passage is arranged on a valve body (311) of the main reversing valve (31), and the second oil passage is arranged on an end cover (313) of the main reversing valve (31); the valve core (312) is provided with an inclined plane, and when the inclined plane of the valve core (312) is tightly contacted with the valve body (311), the main reversing valve (31) is in an initial position; a throttle groove is formed between the valve core (312) and the valve body (311), and the flow area of the throttle groove increases with the increase of the displacement of the valve core (312) moving towards the spring cavity direction of the main reversing valve (31).
4. The regeneration valve group of claim 2, wherein: the valve core (312) is provided with a positioning boss (3121) at one side close to a spring cavity of the main reversing valve (31), and a spring (315) of the main reversing valve (31) is sleeved on the positioning boss (3121).
5. The regeneration valve group of claim 2, wherein: when the second reversing valve (34) is in the initial position, the flow area of hydraulic oil between the oil inlet of the second reversing valve (34) and the oil outlet of the second reversing valve (34) is controlled by the pressure of a control cavity of the second reversing valve (34).
6. A hydraulic system for a mobile arm cylinder of an excavator, comprising: the hydraulic system comprises a reversing valve (2), wherein an oil inlet of the reversing valve (2) is connected with a pump (1), an oil return port of the reversing valve (2) is connected with an oil tank, a first working oil port of the reversing valve (2) is respectively connected with an A1 oil port of the reversing valve (3) and a rodless cavity of a movable arm oil cylinder (4), and a rod cavity of the movable arm oil cylinder (4) is respectively connected with a second working oil port of the reversing valve (2) and a B1 oil port of the reversing valve (3); the reversing valve (2) further comprises a left control cavity X3 and a right control cavity X4, an X1 oil port of the regeneration valve group (3) is connected with the right control cavity X4 of the reversing valve (2), an X2 oil port of the regeneration valve group (3) is connected with a rod cavity of the movable arm oil cylinder (4), and an L oil port of the regeneration valve group (3) is connected with an oil tank.
7. The hydraulic system for an excavator boom cylinder of claim 6 wherein: the reversing valve (2) comprises a left station, an initial position and a right station;
when the reversing valve (2) is in an initial position, an oil inlet of the reversing valve (2), an oil return port of the reversing valve (2), a first working oil port of the reversing valve (2) and a second working oil port of the reversing valve (2) are in a cut-off state;
when the left control cavity X3 of the reversing valve (2) is connected with pilot oil, the reversing valve (2) is positioned at a left station, an oil inlet of the reversing valve (2) is in a conducting state with a first working oil port of the reversing valve (2), and an oil return port of the reversing valve (2) is in a conducting state with a second working oil port of the reversing valve (2);
when the right control cavity X4 of the reversing valve (2) is connected with pilot oil, the reversing valve (2) is positioned at a right station, an oil inlet of the reversing valve (2) is in a conducting state with a second working oil port of the reversing valve (2), and an oil return port of the reversing valve (2) is in a conducting state with a first working oil port of the reversing valve (2).
8. A hydraulic control method comprising the hydraulic system for an excavator arm cylinder of claim 7, characterized in that: when the boom of the excavator is lifted up: the left control cavity X3 of the reversing valve (2) is connected with pilot oil, the right control cavity X4 of the reversing valve (2) is connected with return oil, the pump (1) supplies oil to the rodless cavity of the movable arm oil cylinder (4) through the first working oil port of the reversing valve (2), and the rod cavity of the movable arm oil cylinder (4) returns oil through the second working oil port of the reversing valve (2);
when the boom of the excavator is lowered: the right control cavity X4 of the reversing valve (2) is connected with pilot oil, the left control cavity X3 of the reversing valve (2) is connected with oil return, the reversing valve (2) is switched to a right station, the first reversing valve (33) is in a working position under the action of the pilot oil, the spring cavity of the main reversing valve (31) discharges oil through the first reversing valve (33) and the second reversing valve (34) in sequence, and the main reversing valve (31) is switched to a conducting state; the movable arm of the excavator descends under the action of gravity, so that hydraulic oil in the rodless cavity of the movable arm oil cylinder (4) returns oil through a first working oil port of the reversing valve (2), and in addition, the hydraulic oil in the rodless cavity of the movable arm oil cylinder (4) also supplies oil to the rod cavity of the movable arm oil cylinder (4) through the main reversing valve (31).
9. The hydraulic control method according to claim 8, characterized in that the flow area of the hydraulic oil between the oil inlet of the second directional valve (34) and the oil outlet of the second directional valve (34) is controlled by the pressure to which the control chamber of the second directional valve (34) is subjected;
when the movable arm of the excavator descends, when the pressure of a rod cavity of the movable arm oil cylinder (4) is lower than a set value, the flow area of the second reversing valve (34) is increased, the oil discharging speed of a spring cavity of the main reversing valve (31) is increased, the acting force of the spring cavity of the main reversing valve (31) on the valve core (312) is reduced, the flow area from an oil inlet of the main reversing valve (31) to an oil outlet of the main reversing valve (31) is increased, and the hydraulic oil flowing to the rod cavity of the movable arm oil cylinder (4) through the main reversing valve (31) is increased, so that the pressure of the rod cavity of the movable arm oil cylinder (4) tends to the set value;
when the pressure of the rod cavity of the movable arm oil cylinder (4) is higher than a set value, the flow area of the second reversing valve (34) is reduced, the oil unloading speed of the spring cavity of the main reversing valve (31) is reduced, the acting force of the spring cavity of the main reversing valve (31) on the valve core (312) is increased, the flow area from the oil inlet of the main reversing valve (31) to the oil outlet of the main reversing valve (31) is reduced, the hydraulic oil flowing to the rod cavity of the movable arm oil cylinder (4) through the main reversing valve (31) is reduced, and the pressure of the rod cavity of the movable arm oil cylinder (4) tends to the set value.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211365407.5A CN115492183B (en) | 2022-11-03 | 2022-11-03 | Regeneration valve group, hydraulic system for movable arm oil cylinder of excavator and hydraulic control method |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202211365407.5A CN115492183B (en) | 2022-11-03 | 2022-11-03 | Regeneration valve group, hydraulic system for movable arm oil cylinder of excavator and hydraulic control method |
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| CN115492183B true CN115492183B (en) | 2023-12-19 |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN204982991U (en) * | 2015-07-03 | 2016-01-20 | 西安科技大学 | Excavator swing arm decline hydraulic control system |
| CN107676325A (en) * | 2017-11-23 | 2018-02-09 | 徐工集团工程机械有限公司 | Energy regenerating valve group and hydraulic crawler excavator |
| CN113882459A (en) * | 2021-09-30 | 2022-01-04 | 徐州徐工挖掘机械有限公司 | Excavator energy recovery system and excavator |
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- 2022-11-03 CN CN202211365407.5A patent/CN115492183B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN204982991U (en) * | 2015-07-03 | 2016-01-20 | 西安科技大学 | Excavator swing arm decline hydraulic control system |
| CN107676325A (en) * | 2017-11-23 | 2018-02-09 | 徐工集团工程机械有限公司 | Energy regenerating valve group and hydraulic crawler excavator |
| CN113882459A (en) * | 2021-09-30 | 2022-01-04 | 徐州徐工挖掘机械有限公司 | Excavator energy recovery system and excavator |
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