CN111963499A - Pneumatic control hydraulic reversing valve with two ways of different pressures and flows - Google Patents
Pneumatic control hydraulic reversing valve with two ways of different pressures and flows Download PDFInfo
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- CN111963499A CN111963499A CN201911233773.3A CN201911233773A CN111963499A CN 111963499 A CN111963499 A CN 111963499A CN 201911233773 A CN201911233773 A CN 201911233773A CN 111963499 A CN111963499 A CN 111963499A
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- lifting
- reversing
- valve
- valve rod
- oil
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60P—VEHICLES ADAPTED FOR LOAD TRANSPORTATION OR TO TRANSPORT, TO CARRY, OR TO COMPRISE SPECIAL LOADS OR OBJECTS
- B60P1/00—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading
- B60P1/04—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element
- B60P1/16—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element actuated by fluid-operated mechanisms
- B60P1/162—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element actuated by fluid-operated mechanisms the hydraulic system itself
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/007—Overload
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
- F16K11/20—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating members
- F16K11/22—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating members with an actuating member for each valve, e.g. interconnected to form multiple-way valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/1225—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston with a plurality of pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/875—Control measures for coping with failures
Abstract
The invention discloses a pneumatic control hydraulic reversing valve with two paths of different pressures and flows, which mainly relates to the technical field of hydraulic system control and comprises a valve body (1), a lifting valve rod (6), a reversing valve rod (9), a reversing cylinder (12) and a lifting cylinder (18).
Description
Technical Field
The invention mainly relates to the technical field of hydraulic system control, in particular to a pneumatic control hydraulic reversing valve with two paths of different pressures and flows.
Background
At present, most of the transportation of a large amount of bulk materials such as sand, stones, mineral products, coal and muck in the society is preferably finished by a dumper. In the transportation process of the vehicles, the carried goods can scatter and fall in different degrees, and the dust is blown by wind and is scattered all over the day, so that the environmental protection requirement is seriously endangered. In recent years, with the development and progress of society and the improvement of environmental protection, the above vehicles need to be provided with automatic or semi-automatic closing devices, such as currently adopted push-pull tarpaulin covers, double butterfly covers, integral environmental protection covers, and the like.
Although the dump trucks have various varieties and series, the hydraulic lifting and dumping devices are basically adopted to carry out manual automatic unloading. Although different hydraulic lifting self-discharging devices of various self-discharging trucks are provided, the working principles of various hydraulic lifting systems are approximately equivalent. The working pressure of these hydraulic lifting systems is generally in the range of 15-22 Mpa. The opening and closing of the sealing device of the environmental protection cover are roughly divided into three types, the first type is to drive a speed reducer by a motor to drive the opening and closing of the environmental protection cover, and the environmental protection cover is mainly used for a tarpaulin cover structure. The second is to use the motor to drive the oil pump to establish the independent hydraulic system to control the opening and closing of the environmental protection cover, which is mostly used for the butterfly cover structure, and the system working pressure is generally in the range of 8-15 Mpa. The third is to drive a duplex oil pump by the gear box and power takeoff of the vehicle through a universal transmission shaft to an oil pump support, one duplex oil pump is used for connecting a lifting valve for controlling unloading, and the working pressure is generally in the range of 15-22 Mpa. The other is connected with a hydraulic reversing valve for controlling the environment-friendly cover → a two-way balance valve and an environment-friendly cover oil cylinder. Is mainly used for double-layered butterfly cover and integral environmental protection cover structure. The hydraulic reversing valve → bidirectional oil motor is also used for connecting a control environmental protection cover to drive the tarpaulin cover structure, and the working pressure of the tarpaulin cover structure is generally in the range of 6-15 Mpa.
The practice proves that the above is combined; the first one is because of loading goods irregularly, the tarpaulin lid is opened and shut reason such as being obstructed, overcomes the little easy burning motor of overload potential, and the fault rate is high. The second is that two sets of hydraulic systems are arranged on the same trolley, one set is a hydraulic lifting unloading device which drives an oil pump by a gearbox power takeoff, and the other set is an independent hydraulic station which is driven by a motor and is specially used for opening and closing the environmental protection cover. The scheme has the advantages of complex structure, large occupied space, high cost, easy motor burning and the like. The two structures have the motor which is arranged on the outer surface of the vehicle body, so that the temperature rise and the humidity are difficult to avoid being exposed to the sun and the rain, the insulation is damaged, and the motor is easy to burn. In view of the above two defects and shortcomings, the existing individual manufacturer is changed into the third structure, and the structure has the defects of high cost, complex structure, large dead weight, inconvenience in installation, disordered and complex pipelines, large installation space, high failure rate, inconvenience in maintenance and the like.
Disclosure of Invention
In view of the defects in the prior art, the invention provides a pneumatic control hydraulic reversing valve with two paths of different pressures and flows.
In order to solve the technical problems, the invention adopts the following technical scheme:
pneumatic control hydraulic reversing valve of different pressure of double-circuit and flow, its characterized in that: the hydraulic lifting valve comprises a valve body, a reversing cylinder and a lifting cylinder, wherein a lifting valve rod and a reversing valve rod are respectively arranged in the valve body, the lifting valve rod is connected with an oil inlet hole P, the reversing valve rod is connected with an oil return port I and an oil return port II, the lifting valve rod and the reversing valve rod are communicated through an oil duct K, an oil opening and an oil opening for communicating the reversing valve rod are respectively arranged on the valve body, a lifting oil port for communicating the lifting valve rod is arranged on the valve body, the oil return port I and the oil return port II are communicated with an oil return channel L, the oil return channel L is respectively communicated with a front oil return channel L and a rear oil return channel L which are arranged at two ends of the valve body and penetrate through the lifting valve rod and the reversing valve rod, a secondary pressure overflow valve assembly is arranged at the joint of the front oil return channel L and the oil inlet hole P between the reversing valve rod and the lifting, one end of a lifting valve rod is arranged in the valve body, the other end of the lifting valve rod is connected with a lifting cylinder, a fixed lifting fixed piston is arranged in the lifting cylinder, the end part of the lifting valve rod penetrates through the lifting fixed piston and is connected with a lifting moving piston, a lifting adjusting rod is arranged on a lifting cylinder rear cover of the lifting cylinder and is connected with a slow-falling piston, a lifting reset spring is arranged on the lifting valve rod between the valve body and the lifting fixed piston, a descending air port is arranged on the lifting cylinder between the lifting fixed piston and the lifting moving piston, a lifting air port is arranged between the lifting moving piston and the slow-falling piston, a slow-falling air port is arranged between the slow-falling piston and the lifting cylinder rear cover, and the diameter of the lifting moving piston is smaller than that; one end of a reversing valve rod is arranged in the valve body and is connected with an adjusting seat on the valve body, the other end of the reversing valve rod is connected with a reversing cylinder, a fixed reversing fixed piston is arranged in the reversing cylinder, the end part of the reversing valve rod penetrates through the reversing fixed piston to be connected with a reversing movable piston, a reversing adjusting rod is arranged on a reversing cylinder rear cover on the reversing cylinder, a reversing reset spring is arranged on the reversing valve rod between the valve body and the reversing fixed piston, a cover closing air port is arranged between the reversing fixed piston and the reversing movable piston on the reversing cylinder, and an opening air port is arranged between the reversing movable piston and the reversing cylinder.
As a further improvement of the invention, the middle parts of the lifting valve rod and the reversing valve rod are respectively provided with an undercut groove, and the undercut grooves are respectively connected with an oil duct K.
As a further improvement of the invention, the oil return port I T and the oil return port II T are communicated.
As a further improvement of the invention, a ventilation cover is arranged on the valve body and one end of the lifting valve rod.
As a further improvement of the invention, an adjusting screw is arranged on the adjusting seat.
As a further improvement of the invention, the reversing valve rod is fixedly connected with the reversing return spring.
As a further improvement of the invention, a spare oil port communicated with the lifting valve rod is arranged on the valve body.
As a further improvement of the invention, a relief valve spring is arranged on the secondary pressure relief valve.
As a further improvement of the invention, a sealing ring is arranged on the oil return port T and is connected with the valve seat of the oil tank.
As a further improvement of the present invention, a split valve needle is provided in the oil passage K.
Compared with the prior art, the invention has the beneficial effects that:
the invention of the compound valve can use a pressure oil source of an inlet valve to be converted into two hydraulic systems with two different pressures and different flow rates, namely, one hydraulic oil pump can be used in cooperation with the valve, and two oil pumps (or two hydraulic systems consisting of a duplex pump and two hydraulic reversing valves) can be replaced.
1. For example, the third structure in the second one of the first background art is not repeated, and if the composite valve is used, the original dual gear oil pump can be changed into single connection, for example, the flow rates of the dual pumps are 100/50ml, and the flow rate is 100 ml. If the duplex pump is adopted originally, the failure rate of the duplex oil pump is far higher than that of the simplex pump, the service life is short, moreover, because the duplex oil pump is relatively large in size and relatively heavy in weight, the oil pump is required to be independently arranged on an independent special support, the power is connected with the oil pump from the power takeoff by the universal transmission shaft, if the duplex oil pump is changed into the simplex pump, the duplex pump can be directly arranged on the power takeoff and directly connected with the power takeoff, a large amount of installation space can be saved, the universal transmission shaft and an oil pump support mechanism are omitted, an oil absorption and oil supply pipeline connected with the oil pump is saved, and leakage points are reduced. Meanwhile, the mounting working hours are saved, the mechanism failure rate is reduced, the production efficiency is improved, and the production cost is greatly reduced. And the structure is compact, the layout is reasonable, the appearance is beautiful, the performance is reliable, the service life is long, the maintenance is convenient, and the like. Is popular with users.
2. For example, the third structure in the second one of the first background art is not repeated, and a lifting valve for unloading the container and a reversing valve for controlling the opening and closing of the environmental protection cover which are originally adopted can be changed into a composite valve of the invention, so that the original whole functions can be perfected. Two valves in the original third structure are limited by installation space on the hydraulic oil tank, generally, a lifting valve with large flow is installed on a valve seat of the hydraulic oil tank, the other valve is installed on a special valve seat beside the hydraulic oil tank independently, oil inlet of the valve is connected with an oil pump, and oil return is connected with the hydraulic oil tank. Therefore, the hydraulic control system on the vehicle occupies large installation space, is not centralized, has more used pipelines, is difficult to tidy and disguise the pipelines, and has high cost and the like. If the valve is used, the valve can be directly arranged on a valve seat of a hydraulic oil tank, and as a lifting valve in the original structure, an environmental protection cover opening and closing reversing valve which is arranged beside the hydraulic oil tank in the original structure is eliminated. Therefore, the installation space is saved, the production cost is reduced, and the high-pressure oil pipe is saved, so that the pressure drop and the frictional heat generated due to the oil supply resistance are reduced, the heating speed of the hydraulic oil is reduced, and the mechanical efficiency is improved. The leakage points are reduced, the reliability is improved, and the whole hydraulic control system has the advantages of compact structure, small volume, light weight, reasonable layout, tidy pipelines, attractive appearance, convenience in maintenance and the like.
3. The design invention of the compound valve is universal for an integral environmental protection cover dumper, a double-separation butterfly cover dumper, a tarpaulin cover dumper driven by a hydraulic motor and the like, and lays a foundation for the universality of selected parts in the automobile manufacturing industry. The valve is not only used, but also can be widely used in other similar hydraulic circuits.
Drawings
The invention will be further described with reference to the following drawings and detailed description:
FIG. 1 is a cross-sectional view of a two-way pneumatic hydraulic directional valve of different pressures and flows of the present invention;
FIG. 2 is a cross-sectional view of the invention A-A;
FIG. 3 is a schematic view illustrating an opened structure of the environmental protection cover according to the present invention;
FIG. 4 is a schematic view of the closed structure of the environmental protection cover;
FIG. 5 is a schematic view of the lifting of the cargo box of the present invention;
fig. 6 is a schematic view of the lowered cargo box of the present invention;
FIG. 7 is a schematic view of the slow lowering configuration of the cargo box of the present invention;
a front view; a top view; a left view; a right view; a top view; a bottom view;
in the figure: 1 valve body, 2 shunt valve needles, 3 sealing rings, 4 secondary pressure overflow valves, 5 primary pressure overflow valves, 6 lifting valve rods, 7 vent hoods, 8 overflow valve springs, 9 reversing valve rods, 10 adjusting screws, 11 adjusting seats, 12 reversing cylinders, 13 reversing reset springs, 14 reversing fixed pistons, 15 reversing movable pistons, 16 reversing cylinder rear covers, 17 reversing adjusting rods, 18 lifting cylinders, 19 lifting fixed pistons, 20 lifting movable pistons and 21 lifting adjusting rods, the hydraulic cylinder lifting device comprises a 22 slow-falling piston, a 23 lifting cylinder rear cover, a 24 lifting reset spring, a 25 cover opening oil port, a 26 cover closing oil port, a 27 lifting oil port, a 29 spare oil port, a 30 descending air port, a 31 lifting air port, a 32 slow-falling air port, a 33 cover opening air port, a 34 cover closing air port, a 35 oil tank valve seat, a P oil inlet hole, a K oil duct, an L oil return channel, an L1 front oil return channel, an L2 rear oil return channel, a T1 oil return port I and a T2 oil return port II.
Detailed Description
For better understanding of the technical solutions and advantages of the present invention, the following detailed description of the present invention is provided with specific embodiments, it should be understood that the specific embodiments described herein are only for understanding the present invention and are not intended to limit the present invention, and all other embodiments obtained by those of ordinary skill in the art without creative efforts will fall within the protection scope of the present invention.
As is known from the above, the working pressure of these hydraulic lifting systems is generally in the range of 15-22MPa, and the flow rate thereof is generally required to be 70-100L. The working pressure of the environment-friendly cover is generally in the range of 6-15Mpa, and the flow rate of the environment-friendly cover is generally required to be 20-50L. The two are not operating simultaneously. Therefore, the composite valve is comprehensively designed according to the characteristics that the pressure of the former is high and the flow is large, and the pressure of the latter is relatively low and the flow is small, and the composite pneumatic control hydraulic reversing valve with two paths of different pressures and flows is invented. The valve features that a quantitative oil pump is used to supply oil, so it can realize two alternatively operated control oil channels with different pressures and flows, and only one composite valve can replace the original oil channel in the third structure scheme controlled by two valves. The valve not only can be used, but also can be widely used in similar hydraulic circuits.
The pneumatic hydraulic reversing valve with two paths of different pressures and flows comprises a valve body 1, a reversing cylinder 12 and a lifting cylinder 18, wherein a lifting valve rod 6 and a reversing valve rod 9 are respectively arranged in the valve body 1, the lifting valve rod 6 is connected with an oil inlet P, the reversing valve rod 9 is connected with an oil return port I T1 and an oil return port II T2, the lifting valve rod 6 and the reversing valve rod 9 are communicated through an oil duct K, an opening oil port 25 and a closing oil port 26 which are communicated with the reversing valve rod 9 are respectively arranged on the valve body 1, a lifting oil port 27 which is communicated with the lifting valve rod 6 is arranged on the valve body 1, the oil return port I T1 and the oil return port II T2 are communicated with an oil return channel L, the oil return channel L is respectively communicated with and arranged at two ends of the valve body 1, a front oil return channel L1 and a rear oil return channel L2 which penetrate through the lifting valve rod 6 and the reversing valve rod 9, a front oil return channel L1 and an, a primary pressure overflow valve component 5 is arranged at the front oil return channel L1 and the oil inlet hole P on one side of the lifting valve rod 6, one end of the lifting valve rod 6 is arranged in the valve body 1, the other end is connected with the lifting cylinder 18, a fixed lifting fixed piston 19 is arranged in the lifting cylinder 18, the end part of the lifting valve rod 6 penetrates through the lifting fixed piston 19 and is connected with a lifting movable piston 20, a lifting adjusting rod 21 is arranged on a lifting cylinder rear cover 23 of the lifting cylinder 18, the lifting adjusting rod 21 is connected with a slow-falling piston 22, a lifting reset spring 24 is arranged on a lifting valve rod 6 between the valve body 1 and the lifting fixed piston 19, on the lifting cylinder 18, a descending air port 30 is arranged between the lifting fixed piston 19 and the lifting movable piston 20, a lifting air port 31 is arranged between the lifting movable piston 20 and the slow descending piston 22, a slow descending air port 32 is arranged between the slow descending piston 22 and the lifting cylinder rear cover 23, and the diameter of the lifting movable piston 20 is smaller than that of the slow descending piston 22; one end of a reversing valve rod 9 is arranged in the valve body 1 and is connected with an adjusting seat 11 on the valve body 1, the other end of the reversing valve rod is connected with a reversing cylinder 12, a fixed reversing fixed piston 14 is arranged in the reversing cylinder 12, the end part of the reversing valve rod 9 penetrates through the reversing fixed piston 14 to be connected with a reversing movable piston 15, a reversing adjusting rod 17 is arranged on a reversing cylinder rear cover 16 on the reversing cylinder 12, a reversing reset spring 13 is arranged on the reversing valve rod 9 between the valve body 1 and the reversing fixed piston 14, a cover closing air port 34 is arranged on the reversing cylinder 12 between the reversing fixed piston 14 and the reversing movable piston 15, and an cover opening air port 33 is arranged between the reversing movable piston 15 and the reversing; a ventilation cover 7 is arranged on the valve body 1 and one end of the lifting valve rod 6, and an adjusting screw 10 is arranged on the adjusting seat 11.
And the middle parts of the lifting valve rod 6 and the reversing valve rod 9 are respectively provided with an undercut groove, and the undercut grooves are respectively connected with an oil duct K. And a spare oil port 29 communicated with the lifting valve rod 6 is arranged on the valve body 1. And an overflow valve spring 8 is arranged on the secondary pressure overflow valve 4. The first oil return port T1 is provided with a seal ring 34 connected to a tank valve seat 35. The oil duct K is provided with a flow dividing valve needle 2.
The working principle is only to take the hydraulic dumper with the environmental protection cover as an example
1: the non-working state valve rod is in the middle position
As shown in FIG. 1: the valve is generally arranged on a valve seat of a hydraulic oil tank of a dumper with an environment-friendly cover, and oil return of the valve is directly returned to the oil tank through an oil return port I T1, an oil return port I T1 and an oil return port II T2 which are communicated. When the valve needs to be installed at other positions, the oil return port II T2 can be selected, and the hydraulic oil tank can be connected through an oil return pipe.
The valve can realize the control of two sets of hydraulic systems with different pressures and flows, one set is used for controlling the unloading work of the hydraulic lifting self-discharging single-action oil cylinder, and the pressure of the system is adjusted and determined by a primary pressure overflow valve 5 and is generally within the range of 15-22 Mpa. The flow rate is determined by the selected matched quantitative hydraulic oil pump. The other set is the double-acting oil cylinder working for controlling the opening and closing of the environmental protection cover or the driving working of the bidirectional hydraulic motor, the pressure of the system is adjusted and determined by a secondary pressure overflow valve 4, and the pressure is generally within the range of 8-15 Mpa. The flow rate is adjusted by the shunting valve needle 2.
The two systems can realize different pressures, different flow rates, independent control and alternate work by using one quantitative oil pump. When the right lifting cylinder 18 and the reversing cylinder 12 do not work, the lifting valve rod 6 and the reversing valve rod 9 are both in the equilibrium state shown in the figure position under the pre-pressure action of the two lifting return springs 24 and the reversing return spring 13. The lifting oil port 27 is completely closed by the lifting valve rod 6, and the lifting oil cylinder is in a static state, namely the cargo box is in a static state. The cover closing oil port 26 and the cover opening oil port 25 are both closed by the reversing valve rod 9, and the oil cylinder or the hydraulic motor which drives the environment-friendly cover is in a static state, namely the environment-friendly cover is in a static state.
When oil fed by the oil supply pump enters the valve body through the oil inlet, passes through the oil duct K through the undercut groove in the middle of the lifting valve rod 6, enters the undercut groove in the middle of the reversing valve rod 9, and performs pressure-free oil return through the oil return port, the hydraulic system is in an unloading state at the moment, and the matched power loss is very small.
2: the opening reversing valve rod of the environmental protection cover is arranged at the left end
As shown in fig. 3: when the cover closing air port 34 exhausts air and the cover opening air port 33 admits air, the reversing movable piston 15 drives the reversing valve rod 9 under the action of air pressure and overcomes the axial thrust of the reversing return spring 13 to move leftwards until the left end adjusting screw 10 is limited. At the moment, pressure oil enters the valve body through the oil inlet P, passes through the oil passage K through the undercut groove in the middle of the lifting valve rod 6, enters the undercut groove at the right end of the reversing valve rod 9 and is communicated with the cover opening oil port 25 to supply oil to the cover opening end of the cover opening and closing oil cylinder; the other end of the oil cylinder returns oil to the cover closing oil port 26, passes through a rear oil return channel L2 and an oil return channel L through a sink groove on the left side of the reversing valve rod 9 and returns to the hydraulic oil tank through an oil return port; and (5) opening the cover.
If overload occurs during work, the secondary pressure overflow valve 4 is automatically opened to return oil through the rear oil return channel L2 and the oil return channel L. When the speed of opening the cover needs to be adjusted, the size of the section of the annular slit at the point E can be adjusted through the adjusting screw 10 to control the oil return speed, so that the ideal running speed is realized.
3: closed reversing valve rod of environment-friendly cover at right end
As shown in fig. 4: when the cover opening air port 33 exhausts air and the cover closing air port 34 admits air, the reversing moving piston 15 drives the reversing valve rod 9 under the action of air pressure and overcomes the axial thrust of the reversing return spring 13 to move rightwards until the right reversing adjusting rod 17 is limited. At the moment, pressure oil enters the valve body through an oil inlet, passes through an undercut groove in the middle of the lifting valve rod 6 through an oil duct K, enters a undercut groove at the left end of the reversing valve rod 9 and is directly communicated with a cover closing oil port to supply oil to a cover closing end of the cover opening and closing oil cylinder; the other end of the oil cylinder returns oil to an oil opening of the cover and returns to the hydraulic oil tank through a front oil return channel, an oil return channel L and an oil return opening through a sinking groove at the right side of the reversing valve rod 9; and (5) closing the cover. If overload occurs during work, the overflow valve 4 is automatically opened to return oil through the rear oil return channel and the oil return channel L. When the cover closing speed needs to be adjusted, the size of the section of the annular slit at the point F can be adjusted through the reversing adjusting rod 17 to control the oil return speed, so that the ideal running speed is realized.
4: the lifting valve rod for lifting the cargo box is arranged at the left end
As shown in fig. 5: when the descending air port 30 exhausts air, the lifting air port 31 admits air, the slow descending air port 32 exhausts air, the lifting piston 20 drives the lifting valve rod 6 under the action of air pressure, overcomes the axial thrust of the lifting return spring 24, moves to the left until a dead point, and moves to the right until the dead point by the slow descending piston 22. At the moment, pressure oil enters the valve body through the oil inlet P, passes through the undercut groove at the right end of the lifting valve rod 6 and is directly communicated with the lifting oil port to supply oil to the lifting oil cylinder; and carrying out lifting and unloading work.
In the lifting process, if overload occurs in the working process, the overflow valve 5 is automatically opened to perform oil return unloading through the rear oil return channel L2 and the oil return channel L, so that the overload safety protection effect of the lifting system is achieved.
5: the lifting valve rod for lowering the cargo box is arranged at the right end
As shown in fig. 6: when the air enters the lower air inlet, the lifting air inlet exhausts air slowly, the lifting piston 20 drives the lifting valve rod 6 under the action of air pressure, overcomes the axial thrust of the lifting return spring 24, moves rightwards until a dead point, and slowly lowers to the position of the rightmost dead point. At the moment, oil supplied by the oil pump enters the valve body through the oil inlet, passes through the two undercut grooves at the left end of the lifting valve rod 6, enters the two undercut grooves in the middle of the reversing valve rod 9 through the oil duct K, and is unloaded and returned through the oil return port. The hydraulic oil in the lifting oil cylinder is pressed back to the lifting oil port under the action of the gravity of the container and returns to the oil tank through the undercut groove at the right end of the lifting valve rod 6, the front oil return channel and the oil return channel L through the oil return port. As seen from the above, the cargo box descends by means of self gravity, and even if the oil pump is closed, the oil pump has no influence.
6: the container slow-lifting valve rod is inclined to the right in the middle position
As shown in fig. 7: when the container normally descends, the descending of the container is accelerated by gravity, and the container descends faster and falls to the bottom, so that the downward impact force is given to the chassis of the frame at the moment of descending to the bottom, and the corresponding damage is caused. In order to avoid the phenomenon, the slow descending mode can be switched to when the descending is close to the bottom, and the slow descending air port is switched from the exhaust state to the air inlet state in the normal descending mode. The diameter of the lifting piston 20 is phi 46 mm, the left pressed area is 15.08 square cm, the diameter of the slow-lowering piston 22 is phi 47.5 mm, the right pressed area is 15.71 square cm, the area difference between the two is 0.63 square cm, and when the working air pressure is 0.7Mpa, the pneumatic thrust difference generated by the two is 4.41 kg. Because the thrust of the slow-lowering piston 22 is greater than the acting force of the movable piston 20 plus the lifting return spring 24, the slow-lowering piston 22 will move 7 mm to the dead point of the reducing step of the cylinder, and at the same time, the lifting adjusting rod 21 will be driven to push the movable piston 20 to move the lifting valve rod 6 to the left to the position shown in the figure, and the lifting return spring 24 will release and push the spring seat to the left to the corresponding shoulder of the lifting valve rod 6. At the moment, oil supplied by the oil pump enters the valve body through the oil inlet P, passes through the two undercut grooves at the left end of the lifting valve rod 6, enters the two undercut grooves in the middle of the reversing valve rod 9 through the oil duct K, and is unloaded through the oil return port to return oil. The hydraulic oil in the lifting oil cylinder is pressed back to the lifting oil port under the action of the gravity of the container and returns to the oil tank through the oil return port via the undercut groove at the right end of the lifting valve rod 6, the slow-lowering notch H, the front oil return channel and the oil return channel L. The descending speed is related to the opening size of the slow descending gap H, the opening size of the slow descending gap H can be adjusted through the lifting adjusting rod 21, the smaller the opening is, the slower the descending speed is, and the larger the opening is, the vice versa. The ideal slow-down speed can be realized by adjusting according to the actual situation, and the impact caused by the rapid slow-down to the bottom is avoided.
In the normal descending process, the descending speed is faster according to the principle of the gravity acceleration, and the descending speed can be controlled by slowly descending at any time point.
It is noted that in the description of the present invention, the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Claims (10)
1. Pneumatic control hydraulic reversing valve of different pressure of double-circuit and flow, its characterized in that: including valve body (1), switching-over cylinder (12), lift cylinder (18) be equipped with respectively in valve body (1) and lift valve rod (6), switching-over valve rod (9), oil inlet (P) is connected to lift valve rod (6), and oil return opening (T1), oil return opening two (T2) are connected to switching-over valve rod (9), lift valve rod (6), switching-over valve rod (9) communicate with each other through oil duct (K) be equipped with the lid oil port (25) that opens the lid of intercommunication switching-over valve rod (9) respectively on valve body (1), close lid oil port (26) be equipped with the lifting oil port (27) that communicate lift valve rod (6) on valve body (1), oil return opening one (T1), oil return opening two (T2) intercommunication oil return passageway L, oil return passageway L communicates respectively and arranges valve body (1) both ends in, runs through the preceding oil return passageway (L1) that lift valve rod (6), switching-over valve rod (9, A rear oil return passage (L2), a secondary pressure overflow valve component (4) is arranged at the joint of a front oil return passage (L1) and an oil return passage L between a reversing valve rod (9) and a lifting valve rod (6), a primary pressure overflow valve component (5) is arranged at the joint of a front oil return passage (L1) and an oil inlet (P) at one side of the lifting valve rod (6), one end of the lifting valve rod (6) is arranged in the valve body (1) and the other end of the lifting valve rod is connected with a lifting cylinder (18), a fixed lifting fixed piston (19) is arranged in the lifting cylinder (18), the end part of the lifting valve rod (6) penetrates through the lifting fixed piston (19) to be connected with a lifting piston (20), a lifting adjusting rod (21) is arranged on a lifting cylinder rear cover (23) of the lifting cylinder (18), the lifting adjusting rod (21) is connected with a slow-falling piston (22), a lifting reset spring (24) is arranged on the lifting piston (6) between the valve body, on the lifting cylinder (18), a descending air port (30) is arranged between the lifting fixed piston (19) and the lifting movable piston (20), a lifting air port (31) is arranged between the lifting movable piston (20) and the slow-descending piston (22), a slow-descending air port (32) is arranged between the slow-descending piston (22) and the lifting cylinder rear cover (23), and the diameter of the lifting movable piston (20) is smaller than that of the slow-descending piston (22); one end of a reversing valve rod (9) is arranged in the valve body (1), the reversing valve rod is connected with an adjusting seat (11) on the valve body (1), the other end of the reversing valve rod is connected with a reversing cylinder (12), a fixed reversing fixed piston (14) is arranged in the reversing cylinder (12), the end part of the reversing valve rod (9) penetrates through the reversing fixed piston (14) to be connected with a reversing movable piston (15), a reversing adjusting rod (17) is arranged on a reversing cylinder rear cover (16) on the reversing cylinder (12), a reversing reset spring (13) is arranged on the reversing valve rod (9) between the valve body (1) and the reversing fixed piston (14), a cover closing air port (34) is arranged between the reversing fixed piston (14) and the reversing movable piston (15) on the reversing cylinder (12), and an opening air port (33) is arranged between the reversing movable piston (15) and the reversing.
2. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: and the middle parts of the lifting valve rod (6) and the reversing valve rod (9) are respectively provided with an undercut groove, and the undercut grooves are respectively connected with an oil duct (K).
3. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: the first oil return port (T1) and the second oil return port (T2) are communicated.
4. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: a ventilation cover (7) is arranged on the valve body (1) and at one end of the lifting valve rod (6).
5. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: an adjusting screw (10) is arranged on the adjusting seat (11).
6. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: the reversing valve rod (9) is fixedly connected with a reversing return spring (13).
7. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: and a spare oil port (29) communicated with the lifting valve rod (6) is arranged on the valve body (1).
8. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: and an overflow valve spring (8) is arranged on the secondary pressure overflow valve (4).
9. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: and a sealing ring (34) is arranged on the first oil return opening (T1) and is connected with an oil tank valve seat (35).
10. The pneumatic control hydraulic reversing valve with two paths of different pressures and flows according to claim 1, characterized in that: the oil duct (K) is provided with a shunt valve needle (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911233773.3A CN111963499A (en) | 2019-12-05 | 2019-12-05 | Pneumatic control hydraulic reversing valve with two ways of different pressures and flows |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911233773.3A CN111963499A (en) | 2019-12-05 | 2019-12-05 | Pneumatic control hydraulic reversing valve with two ways of different pressures and flows |
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| Publication Number | Publication Date |
|---|---|
| CN111963499A true CN111963499A (en) | 2020-11-20 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201911233773.3A Pending CN111963499A (en) | 2019-12-05 | 2019-12-05 | Pneumatic control hydraulic reversing valve with two ways of different pressures and flows |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112524295A (en) * | 2020-12-09 | 2021-03-19 | 江苏天域阀业制造有限公司 | Multi-way angle valve for PTA, polyolefin and residual oil hydrogenation industry |
-
2019
- 2019-12-05 CN CN201911233773.3A patent/CN111963499A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112524295A (en) * | 2020-12-09 | 2021-03-19 | 江苏天域阀业制造有限公司 | Multi-way angle valve for PTA, polyolefin and residual oil hydrogenation industry |
| CN112524295B (en) * | 2020-12-09 | 2022-04-05 | 江苏天域阀业制造有限公司 | Multi-way angle valve |
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