CN108612693B - Double-cylinder control system with multi-way valve device - Google Patents
Double-cylinder control system with multi-way valve device Download PDFInfo
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- CN108612693B CN108612693B CN201810480550.6A CN201810480550A CN108612693B CN 108612693 B CN108612693 B CN 108612693B CN 201810480550 A CN201810480550 A CN 201810480550A CN 108612693 B CN108612693 B CN 108612693B
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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
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- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01B—SOIL WORKING IN AGRICULTURE OR FORESTRY; PARTS, DETAILS, OR ACCESSORIES OF AGRICULTURAL MACHINES OR IMPLEMENTS, IN GENERAL
- A01B15/00—Elements, tools, or details of ploughs
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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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
Abstract
The invention provides a double-cylinder control system with a multi-way valve device, which comprises: multiple unit valve device, lift bar, upset jar, solenoid directional valve, hydraulic pump, oil tank, multiple unit valve device includes: the valve body is provided with a first oil port, a second oil port and a third oil port; the first reversing valve is provided with a first working oil port, a second working oil port, a third working oil port and a fourth working oil port, the first working oil port is connected with the first oil port, the second working oil port is connected with the second oil port, and the third working oil port is connected with the third oil port; the second reversing valve is provided with fifth to eighth working oil ports, the fifth working oil port is connected with the fourth working oil port, the sixth working oil port is connected with the second oil port, the seventh working oil port is connected with the fifth oil port, and the eighth working oil port is connected with the sixth oil port; and the first end of the first overflow valve is connected with the fourth oil port, and the second end of the first overflow valve is connected with the sixth oil port. The double-cylinder control system with the multi-way valve device provided by the embodiment of the invention has the advantages of simple structure and low manufacturing cost.
Description
Technical Field
The invention relates to a double-cylinder control system with a multi-way valve device.
Background
In recent years, hydraulic reversible plows have begun to be popularized and applied in most areas of China. The turning plow is used for plowing and turning operation, and has the advantages of no ridge opening and closing, high production efficiency, energy conservation and the like. The hydraulic turnover plow uses the hydraulic system of tractor to control the alternate operation of left and right plow bodies, so as to achieve the purpose of no opening and closing ridges. At present, a single oil cylinder control mode is generally adopted for small-sized turnover plows, and a double-oil cylinder control mode is adopted for large-sized turnover plows. The hydraulic turnover plow controlled by double oil cylinders mainly comprises a lifting oil cylinder and a turnover oil cylinder, wherein the two oil cylinders are controlled by a hydraulic system of a tractor, and when the plow is in a working state, the lifting oil cylinder and the turnover oil cylinder are both in a maximum extension state. When the plough needs to be overturned and reversed, the lifting oil cylinder needs to be controlled to be shortened to lift the plough, the overturning oil cylinder is controlled to retract to drive the plough beam to overturn upwards after the plough beam is lifted to the right position, the overturning oil cylinder is controlled to extend out when the plough beam rotates to a position close to the vertical position, the plough beam is enabled to cross a dead point position, the plough beam continues to rotate under the action of thrust and gravity of the oil cylinder until the overturning oil cylinder extends out completely, and then the lifting oil cylinder is controlled to extend out completely. At present, the turning control valve used for controlling the double oil cylinders at home and abroad is mainly a manual hydraulic turning control valve. The manual mode is that a tractor driver directly operates a manual slide valve to control an oil way of a lifting oil cylinder to lift a bidirectional plough first, then operates the manual slide valve to reverse to control a reversing oil cylinder to start reversing, the plough shifts a shifting fork at an over-center position to drive a rotary valve to change the oil way of the oil cylinder to complete reversing, and then manually operates the slide valve to control the lifting oil cylinder to extend out; meanwhile, three control slide valves (1 slide valve for controlling the lifting oil cylinder and 2 slide valves for controlling the overturning) are adopted, so that the structure is complex and the cost is high.
Disclosure of Invention
The present invention is directed to solving, at least to some extent, one of the technical problems in the related art.
To this end, it is an object of the present invention to provide a two-cylinder control system with a multi-way valve arrangement that is simple and inexpensive to manufacture.
A dual cylinder control system having a multi-way valve apparatus according to an embodiment of the present invention includes:
a multiple way valve apparatus, comprising: the valve body, the first reversing valve, the second reversing valve and the first overflow valve; the valve body is provided with a first oil port, a second oil port, a third oil port, a fourth oil port, a fifth oil port and a sixth oil port; the first reversing valve is provided with a first working oil port, a second working oil port, a third working oil port and a fourth working oil port, the first working oil port is connected with the first oil port, the second working oil port is connected with the second oil port, the third working oil port is connected with the third oil port, and the first reversing valve can be switched between a first position and a second position; the second reversing valve is provided with a fifth working oil port, a sixth working oil port, a seventh working oil port and an eighth working oil port, the fifth working oil port is connected with the fourth working oil port, the sixth working oil port is connected with the second oil port, the seventh working oil port is connected with the fifth oil port, the eighth working oil port is connected with the sixth oil port, the second reversing valve is switchable between a third position and a fourth position, the first end of the first overflow valve is connected with the fourth oil port, the second end of the first overflow valve is connected with the sixth oil port, and the first overflow valve is used for normally breaking the connection between the fourth oil port and the sixth oil port;
a rod cavity of the lifting rod is connected with the third oil port, and a rodless cavity of the lifting rod is connected with the fourth oil port;
a rod cavity of the turning cylinder is connected with the fifth oil port, and a rodless cavity of the turning cylinder is connected with the sixth oil port;
the electromagnetic reversing valve is provided with a ninth working oil port, a tenth working oil port, an eleventh working oil port and a twelfth working oil port, the eleventh working oil port is connected with the first oil port, the twelfth working oil port is connected with the second oil port, and when the electromagnetic reversing valve is powered off, the eleventh working oil port and the twelfth working oil port are both connected with the tenth working oil port; when the electromagnetic reversing valve is electrified, the ninth working oil port is connected with the eleventh working oil port, and the tenth working oil port is connected with the twelfth working oil port;
the output end of the hydraulic pump is connected with the ninth working oil port;
and the oil tank is respectively connected with the input end of the hydraulic pump and the tenth working oil port.
Advantageously, when the first direction valve is in the first position, the first working oil port is communicated with the third working oil port and the second working oil port is communicated with the fourth working oil port; when the first reversing valve is located at the second position, the first working oil port is communicated with the fourth working oil port, and the second working oil port is communicated with the third working oil port; when the second reversing valve is located at the third position, the fifth working oil port is communicated with the seventh working oil port, and the sixth working oil port is communicated with the eighth working oil port; and when the second reversing valve is located at the fourth position, the fifth working oil port is communicated with the eighth working oil port, and the sixth working oil port is communicated with the seventh working oil port.
Advantageously, the first direction valve further comprises a first spring for normally urging the spool of the first direction valve to place the first direction valve in the first position, the first direction valve further comprising:
the first control cavity is coaxial with the valve hole of the first reversing valve and is arranged on the same side of the first spring, and the first control cavity is connected with the first oil port;
the first piston is arranged in the first control cavity and used for pushing a valve core of the first reversing valve;
the second control cavity is coaxial with the valve hole of the first reversing valve and is arranged on the opposite side of the first spring, the second control cavity is connected with the third oil port through a second overflow valve, the second control cavity is connected with the fourth working oil port through a first damping hole, and the second overflow valve is used for normally breaking the connection between the third oil port and the second control cavity;
the second piston is arranged in the second control cavity and used for pushing the valve core of the first reversing valve;
wherein the cross-section of the first control chamber is smaller than the cross-section of the second control chamber.
Advantageously, the second direction valve further includes a second spring, the second spring is configured to normally push the valve element of the second direction valve to enable the second direction valve to be in the third position, the second direction valve further includes a third control chamber coaxial with the valve hole of the second direction valve and located on the opposite side of the second spring, the third control chamber is connected to the fifth oil port through a third overflow valve, and the third control chamber is connected to the eighth working oil port through a second damping hole, and the third overflow valve is configured to normally disconnect the fifth oil port from the third control chamber.
Advantageously, when the first direction valve is in the first position and the second direction valve is in the third position, the first port is in communication with the third port and the fourth port is in communication with the second port.
Advantageously, when the first direction valve is in the second position and the second direction valve is in the third position, the first port is in communication with the fifth port and the fifth port is in communication with the second port.
Advantageously, when the first direction valve is in the second position and the second direction valve is in the fourth position, the first port is in communication with the sixth port and the fifth port is in communication with the second port.
Advantageously, when the first direction valve is in the second position and the second direction valve is in the third position, the first port is in communication with the fourth port and the third port is in communication with the second port.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
FIG. 1 is a schematic illustration of a multi-way valve arrangement of a two cylinder control system having a multi-way valve arrangement according to one embodiment of the present invention;
FIG. 2 is a schematic diagram of a two cylinder control system having a multi-way valve arrangement according to one embodiment of the present invention.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and are intended to be illustrative of the invention and should not be construed as limiting the invention.
A two-cylinder control system having a multi-way valve apparatus according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.
As shown in fig. 1 and 2, a dual cylinder control system having a multi-way valve apparatus according to an embodiment of the present invention includes: the multi-way valve device comprises a lifting rod G1, a turnover cylinder G2, an electromagnetic directional valve 10, a hydraulic pump 11 and an oil tank 12.
Specifically, the multiple-way valve device includes: the valve comprises a valve body 100, a first reversing valve 200, a second reversing valve 300 and a first overflow valve 400.
The valve body 100 has a first port P, a second port T, a third port V1, a fourth port C1, a fifth port V2, and a sixth port C2.
The first direction valve 200 has a first working port P1, a second working port T1, a third working port a1 and a fourth working port B1, the first working port P1 is connected with the first port P, the second working port T1 is connected with the second port T, the third working port a1 is connected with the third port V1, and the first direction valve 200 is switchable between a first position and a second position.
The second reversing valve 300 is provided with a fifth working oil port P2, a sixth working oil port T2, a seventh working oil port a2 and an eighth working oil port B2, the fifth working oil port P2 is connected with a fourth working oil port B1, the sixth working oil port T2 is connected with the second oil port T, the seventh working oil port a2 is connected with a fifth oil port V2, the eighth working oil port B2 is connected with a sixth oil port C2, and the second reversing valve 300 is switchable between a third position and a fourth position.
The first end of the first relief valve 400 is connected to the fourth port C1, the second end of the first relief valve 400 is connected to the sixth port C2, and the first relief valve 400 is configured to normally disconnect the fourth port C1 from the sixth port C2.
The rod chamber of the lift rod G1 is connected to the third port V1 and the rodless chamber of the lift rod G1 is connected to the fourth port C1.
The rod chamber of the tilt cylinder G2 is connected to the fifth port V2 and the rodless chamber of the tilt cylinder G2 is connected to the sixth port C2.
The electromagnetic directional valve 10 is provided with a ninth working oil port P3, a tenth working oil port T3, an eleventh working oil port A3 and a twelfth working oil port B3, the eleventh working oil port A3 is connected with the first oil port P, the twelfth working oil port B3 is connected with the second oil port T, and when the electromagnetic directional valve 10 is in power failure, the eleventh working oil port A3 and the twelfth working oil port B3 are both connected with the tenth working oil port T3; when the electromagnetic directional valve 10 is powered on, the ninth working oil port P3 is connected with the eleventh working oil port A3, and the tenth working oil port T3 is connected with the twelfth working oil port B3.
The output end of the hydraulic pump 11 is connected to a ninth working port P3.
The oil tank 12 is connected to an input end of the hydraulic pump 11 and the tenth working port T3, respectively.
Further, when the first direction valve 200 is at the first position, the first working port P1 is communicated with the third working port a1 and the second working port T1 is communicated with the fourth working port B1; when the first direction changing valve 200 is at the second position, the first working port P1 is communicated with the fourth working port B1, and the second working port T1 is communicated with the third working port a 1; when the second direction valve 300 is at the third position, the fifth working port P2 is communicated with the seventh working port a2 and the sixth working port T2 is communicated with the eighth working port B2; when the second direction valve 300 is at the fourth position, the fifth working port P2 is in communication with the eighth working port B2 and the sixth working port T2 is in communication with the seventh working port a 2.
Further, when the first direction valve 200 is in the first position and the second direction valve 300 is in the third position, the first port P is in communication with the third port V1 and the fourth port C1 is in communication with the second port T. When the first direction valve 200 is in the second position and the second direction valve 300 is in the third position, the first port P is in communication with the fifth port V2 and the fifth port V2 is in communication with the second port T. When the first direction valve 200 is in the second position and the second direction valve 300 is in the fourth position, the first port P is in communication with the sixth port C2 and the fifth port V2 is in communication with the second port T. When the first direction valve 200 is in the second position and the second direction valve 300 is in the third position, the first port P is in communication with the fourth port C1 and the third port V1 is in communication with the second port T.
According to one example of the present invention, the first direction valve 200 further includes a first spring 201, and the first spring 201 is used for normally pushing the spool of the first direction valve 200 to make the first direction valve 200 be in the first position. The first direction valve 200 further includes: a first control chamber 202, a first piston 203, a second control chamber 204, a second piston 207.
The first control chamber 202 is coaxial with the valve hole of the first direction valve 200 and is arranged at the same side of the first spring 201, and the first control chamber 202 is connected with the first oil port P.
A first piston 203 is provided in the first control chamber 202 for urging the spool of the first direction valve 200.
The second control chamber 204 is coaxial with the valve hole of the first directional valve 200 and is disposed opposite to the first spring 201, the second control chamber 204 is connected to the third port C1 through the second overflow valve 205, the second control chamber 204 is connected to the fourth working port B1 through the first damping hole 206, and the second overflow valve 205 is used to normally disconnect the third port C1 from the second control chamber 204.
A second piston 207 is provided in the second control chamber 204 for urging the spool of the first direction valve 200.
Wherein the cross-section of the first control chamber 202 is smaller than the cross-section of the second control chamber 204. In other words, the cross-section of the first piston 203 is smaller than the cross-section of the second piston 207.
According to a specific example of the present invention, the second direction valve 300 further includes a second spring 301, and the second spring 301 is used for normally pushing the spool of the second direction valve 300 to make the second direction valve 300 be in the third position. The second direction valve 300 further comprises a third control cavity 302 which is coaxial with the valve hole of the second direction valve 300 and located on the opposite side of the second spring 301, the third control cavity 302 is connected with a fifth port V2 through a third overflow valve 303, the third control cavity 302 is connected with an eighth working port B2 through a second damping hole 304, and the third overflow valve 303 is used for normally disconnecting the fifth port V2 from the third control cavity 302.
The operation of a dual cylinder control system having a multi-way valve arrangement according to an embodiment of the present invention will now be briefly described.
As shown in fig. 2, in application, the third port V1 is connected to the rod cavity of the lift rod G1, the fourth port C1 is connected to the rodless cavity of the lift rod G1, the fifth port V2 is connected to the rod cavity of the reversing cylinder, the sixth port is connected to the rodless cavity of the reversing cylinder, the first port P is connected to the eleventh working port A3 of the electromagnetic directional valve 10, the second port T is connected to the twelfth working port B3 of the electromagnetic directional valve 10, the output end of the hydraulic pump 11 is connected to the ninth working port P3 of the electromagnetic directional valve 10, and the input end of the hydraulic pump 11 and the tenth working port T3 of the electromagnetic directional valve 10 are both connected to the oil tank 12.
When the electromagnetic directional valve 10 is powered off, the eleventh working oil port A3 and the twelfth working oil port B3 are both connected with the tenth working oil port T3; when the electromagnetic directional valve 10 is powered on, the ninth working oil port P3 is connected with the eleventh working oil port A3, and the tenth working oil port T3 is connected with the twelfth working oil port B3.
In the initial state, the solenoid directional valve 10 is de-energized, the hydraulic pump 11 is closed, the first directional valve 200 is in the first position, the second directional valve 300 is in the third position, and the lift lever G1 and the tumble cylinder G2 are both in the extended state.
The electromagnetic directional valve 10 is powered on and the hydraulic pump 11 is started, hydraulic oil output by the hydraulic pump 11 reaches the first oil port P through the ninth working oil port P3 and the eleventh working oil port A3, a small part of the oil enters the first control chamber 202 to push the first piston 203, so that the first piston 203 pushes the valve element of the first directional valve 200, and the first directional valve 200 is kept at the first position. Most of the oil liquid enters a rod cavity of the lifting rod G1 through the first working oil port P1, the third working oil port A1 and the third oil port V1, so that the lifting rod is retracted. The oil in the rodless cavity of the lift rod G1 passes through the fourth port C1, forcing the first relief valve 400 to open to communicate the fourth port C1 with the sixth port C2, and the oil returns to the oil tank 12 through the eighth working port B2, the sixth tenth working port T3, the second port T, the twelfth working port B3, and the tenth working port T3.
When the lift rod G1 retracts to the bottom, the pressure of the third port V1 rises rapidly, forcing the second relief valve 205 to open, and the oil enters the second control chamber 204 until the pressure inside the second control chamber 204 is equal to the pressure at the first port P. At this time, the pressure in the first control chamber 202 and the pressure in the second control chamber 204 are both equal to the pressure at the first port P, and since the cross section of the second piston 207 is greater than the cross section of the first piston 203, the thrust of the second piston 207 exerted on the first direction valve 200 is greater than the thrust of the first piston 203, so that the first direction valve 200 can be located at the second position against the elastic force of the first spring 201 (at this time, the second overflow valve 205 is already closed, and the oil can enter the second control chamber 204 through the first port P, the first working port P1, the fourth working port B1 and the first damping hole 206, so that the first direction valve 200 can be maintained at the second position). The oil liquid enters a rod cavity of the overturning cylinder G2 through a first oil port P, a first working oil port P1, a fourth working oil port B1, a fifth working oil port P2, a seventh working oil port A2 and a fifth oil port V2, so that the overturning cylinder G2 is retracted. The oil in the rodless chamber of the reversing cylinder G2 returns to the oil tank 12 through the sixth oil port C2, the eighth working oil port B2, the sixth working oil port T2, the second oil port T, the twelfth working oil port B3, and the tenth working oil port T3.
When the reversing cylinder G2 retracts to the bottom, the pressure of the fifth port V2 rises rapidly, so that the third overflow valve 303 is forced to open, the oil enters the third control chamber 302, overcomes the elastic force of the second spring 301, and the second directional control valve 300 is located at the fourth position (at this time, the third overflow valve 303 is already closed, and the oil from the first port P enters the third control chamber 302 through the first working port P1, the fourth working port B1, the fifth working port P2, the eighth twelfth working port B3, and the second damping port 304, so that the second directional control valve 300 is kept at the fourth position). The oil liquid enters a rodless cavity of the turnover cylinder G2 through a first oil port P, a first working oil port P1, a fourth working oil port B1, a fifth working oil port P2, an eighth twelfth working oil port B3 and a sixth oil port C2 to push the turnover cylinder G2 to extend out to drive the turnover plow to turn downwards; the oil in the rod chamber of the tilting cylinder G2 returns to the oil tank 12 through the fifth oil port V2, the seventh working oil port a2, the sixth working oil port T2, the second oil port T, the twelfth working oil port B3 and the tenth working oil port T3.
When the turning cylinder G2 is fully extended, that is, the turning plow has completed the entire turning process, the pressure of the sixth port C2 rises rapidly to force the first overflow valve 400 to open, the oil enters the rodless cavity of the lift rod G1 through the first port P, the first working port P1, the fourth working port B1, the fifth working port P2, the eighth twelfth working port B3, the first overflow valve 400, and the fourth port C1, the lift rod G1 is pushed to extend out and lower the turning plow, and the oil in the rod cavity of the lift rod G1 returns to the oil tank 12 through the third port V1, the third working port a1, the second working port T1, the second working port T, the twelfth working port B3, and the tenth working port T3.
When the lift lever G1 is fully extended, the electromagnetic directional valve 10 is de-energized and the hydraulic pump 11 is turned off, the first directional valve 200 returns to the first position by the first spring 201, and the second directional valve 300 returns to the third position by the second spring 301.
Through the above description, the whole processes of retracting and lifting the lifting cylinder G1, retracting and upwards overturning the overturning cylinder G2, extending and downwards overturning the overturning cylinder G2 and extending and downwards lowering the lifting cylinder G1 can be automatically and sequentially completed only by the on/off operation of the electromagnetic directional valve 10 by a driver, the automation degree is high, and a complex electric control device is not needed.
The double-cylinder control system with the multi-way valve device has the advantages that:
(1) the structure is simple, the integration level is high, the installation is convenient, and the cost is low;
(2) the lifting and overturning control can be realized automatically and sequentially only by supplying oil, the manual operation of a driver is not needed, and the automation degree is high.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like, indicate orientations and positional relationships based on the orientations and positional relationships shown in the drawings, and are used merely for convenience in describing and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate medium. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature "under," "below," and "beneath" a second feature may be directly or obliquely under the first feature or may simply mean that the first feature is at a lesser elevation than the second feature.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Although the embodiments of the present invention have been shown and described, it is understood that the embodiments are illustrative and not restrictive, and that those skilled in the art may make changes, modifications, substitutions and alterations to the embodiments without departing from the scope of the present invention.
Claims (6)
1. A dual cylinder control system having a multi-way valve apparatus, comprising:
a multiple way valve apparatus, comprising: the valve body, the first reversing valve, the second reversing valve and the first overflow valve; the valve body is provided with a first oil port, a second oil port, a third oil port, a fourth oil port, a fifth oil port and a sixth oil port; the first reversing valve is provided with a first working oil port, a second working oil port, a third working oil port and a fourth working oil port, the first working oil port is connected with the first oil port, the second working oil port is connected with the second oil port, the third working oil port is connected with the third oil port, and the first reversing valve can be switched between a first position and a second position; the second reversing valve is provided with a fifth working oil port, a sixth working oil port, a seventh working oil port and an eighth working oil port, the fifth working oil port is connected with the fourth working oil port, the sixth working oil port is connected with the second oil port, the seventh working oil port is connected with the fifth oil port, the eighth working oil port is connected with the sixth oil port, the second reversing valve is switchable between a third position and a fourth position, the first end of the first overflow valve is connected with the fourth oil port, the second end of the first overflow valve is connected with the sixth oil port, and the first overflow valve is used for normally breaking the connection between the fourth oil port and the sixth oil port;
a rod cavity of the lifting rod is connected with the third oil port, and a rodless cavity of the lifting rod is connected with the fourth oil port;
a rod cavity of the turning cylinder is connected with the fifth oil port, and a rodless cavity of the turning cylinder is connected with the sixth oil port;
the electromagnetic reversing valve is provided with a ninth working oil port, a tenth working oil port, an eleventh working oil port and a twelfth working oil port, the eleventh working oil port is connected with the first oil port, the twelfth working oil port is connected with the second oil port, and when the electromagnetic reversing valve is powered off, the eleventh working oil port and the twelfth working oil port are both connected with the tenth working oil port; when the electromagnetic directional valve is electrified, the ninth working oil port is connected with the eleventh working oil port, and the tenth working oil port is connected with the twelfth working oil port;
the output end of the hydraulic pump is connected with the ninth working oil port;
the oil tank is respectively connected with the input end of the hydraulic pump and the tenth working oil port;
the first direction valve further includes a first spring for normally urging a spool of the first direction valve to place the first direction valve in the first position, the first direction valve further including: the first control cavity is coaxial with the valve hole of the first reversing valve and is arranged on the same side of the first spring, and the first control cavity is connected with the first oil port; the first piston is arranged in the first control cavity and used for pushing a valve core of the first reversing valve; the second control cavity is coaxial with the valve hole of the first reversing valve and is arranged on the opposite side of the first spring, the second control cavity is connected with the third oil port through a second overflow valve, the second control cavity is connected with the fourth working oil port through a first damping hole, and the second overflow valve is used for normally disconnecting the third oil port from the second control cavity; the second piston is arranged in the second control cavity and used for pushing the valve core of the first reversing valve; wherein the cross-section of the first control chamber is smaller than the cross-section of the second control chamber;
the second reversing valve further comprises a second spring, the second spring is used for normally pushing a valve core of the second reversing valve to enable the second reversing valve to be located at the third position, the second reversing valve further comprises a third control cavity which is coaxial with a valve hole of the second reversing valve and located on the opposite side of the second spring, the third control cavity is connected with the fifth oil port through a third overflow valve and is connected with the eighth working oil port through a second damping hole, and the third overflow valve is used for normally disconnecting the fifth oil port from the third control cavity.
2. The dual cylinder control system with a multiplex valve apparatus as defined in claim 1 wherein said first working port is in communication with said third working port and said second working port is in communication with said fourth working port when said first directional control valve is in said first position; when the first reversing valve is located at the second position, the first working oil port is communicated with the fourth working oil port, and the second working oil port is communicated with the third working oil port; when the second reversing valve is located at the third position, the fifth working oil port is communicated with the seventh working oil port, and the sixth working oil port is communicated with the eighth working oil port; and when the second reversing valve is located at the fourth position, the fifth working oil port is communicated with the eighth working oil port, and the sixth working oil port is communicated with the seventh working oil port.
3. The dual cylinder control system having a multiplex valve apparatus as defined in claim 2 wherein said first port is in communication with said third port and said fourth port is in communication with said second port when said first directional valve is in said first position and said second directional valve is in said third position.
4. The dual cylinder control system having a multiplex valve apparatus as defined in claim 2 wherein said first port is in communication with said fifth port and said fifth port is in communication with said second port when said first directional valve is in said second position and said second directional valve is in said third position.
5. The dual cylinder control system having a multiplex valve apparatus as defined in claim 2 wherein said first port is in communication with said sixth port and said fifth port is in communication with said second port when said first directional valve is in said second position and said second directional valve is in said fourth position.
6. The dual cylinder control system having a multiplex valve apparatus as defined in claim 2 wherein said first port is in communication with said fourth port and said third port is in communication with said second port when said first directional valve is in said second position and said second directional valve is in said third position.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810480550.6A CN108612693B (en) | 2018-05-18 | 2018-05-18 | Double-cylinder control system with multi-way valve device |
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| CN201810480550.6A CN108612693B (en) | 2018-05-18 | 2018-05-18 | Double-cylinder control system with multi-way valve device |
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| CN108612693A CN108612693A (en) | 2018-10-02 |
| CN108612693B true CN108612693B (en) | 2020-10-20 |
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Citations (5)
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|---|---|---|---|---|
| DE3908985A1 (en) * | 1989-03-18 | 1990-09-27 | Integral Hydraulik Co | Hydraulic circuit for a mounted half-turn plough |
| FR2720123A1 (en) * | 1994-05-19 | 1995-11-24 | France Power Packer Sa | Automated hydraulic control for semi-rotating plough share |
| EP1371855A1 (en) * | 2002-06-11 | 2003-12-17 | Actuant Corporation | Plough-turning device |
| CN204985138U (en) * | 2015-09-25 | 2016-01-20 | 湖州生力液压有限公司 | Take sequence action valve of load feedback |
| CN106499688A (en) * | 2016-12-20 | 2017-03-15 | 湖南鸿辉科技有限公司 | A kind of garbage-compressing control integral multitandem valve and control method |
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2018
- 2018-05-18 CN CN201810480550.6A patent/CN108612693B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3908985A1 (en) * | 1989-03-18 | 1990-09-27 | Integral Hydraulik Co | Hydraulic circuit for a mounted half-turn plough |
| FR2720123A1 (en) * | 1994-05-19 | 1995-11-24 | France Power Packer Sa | Automated hydraulic control for semi-rotating plough share |
| EP1371855A1 (en) * | 2002-06-11 | 2003-12-17 | Actuant Corporation | Plough-turning device |
| CN204985138U (en) * | 2015-09-25 | 2016-01-20 | 湖州生力液压有限公司 | Take sequence action valve of load feedback |
| CN106499688A (en) * | 2016-12-20 | 2017-03-15 | 湖南鸿辉科技有限公司 | A kind of garbage-compressing control integral multitandem valve and control method |
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|---|---|
| CN108612693A (en) | 2018-10-02 |
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