CN108547821B - Integrated hydraulic steering control valve group and hydraulic steering control system - Google Patents
Integrated hydraulic steering control valve group and hydraulic steering control system Download PDFInfo
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- CN108547821B CN108547821B CN201810724787.4A CN201810724787A CN108547821B CN 108547821 B CN108547821 B CN 108547821B CN 201810724787 A CN201810724787 A CN 201810724787A CN 108547821 B CN108547821 B CN 108547821B
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- working oil
- hydraulic
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Classifications
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/08—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by type of steering valve used
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/09—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by means for actuating valves
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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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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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
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
- F15B13/0442—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with proportional solenoid allowing stable intermediate positions
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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
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
- F15B2013/0448—Actuation by solenoid and permanent magnet
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
Abstract
The invention discloses an integrated hydraulic steering control valve group and a hydraulic steering control system. The integrated hydraulic steering control valve bank integrates a valve body, a logic valve and a proportional electromagnetic directional valve, an integrated oil inlet, an integrated oil return port, a first working oil port, a second working oil port, a third working oil port and a fourth working oil port are arranged on the valve body, when the integrated hydraulic steering control valve bank is applied to a hydraulic steering control system of a vehicle, the integrated oil inlet is connected with a hydraulic pump, the integrated oil return port is connected with a hydraulic oil tank, and the first working oil port, the second working oil port, the third working oil port and the fourth working oil port are respectively connected with P, T, A, B ports of a hydraulic steering device; the oil inlet and oil return directions of the steering oil cylinder are regulated by controlling the proportional electromagnetic reversing valve, so that the steering control of the vehicle is realized, and the automatic control requirement of a hydraulic steering system of the vehicle is met; compared with the prior art, the integrated hydraulic steering control valve group has the advantages of small volume, simple structure, low manufacturing cost and more convenient installation and maintenance.
Description
Technical Field
The invention relates to a hydraulic transmission technology, in particular to an integrated hydraulic steering control valve group; in addition, the invention also relates to a hydraulic steering control system with the integrated hydraulic steering control valve group.
Background
At present, in order to realize automatic steering control of a vehicle, a mode of connecting proportional solenoid valves in parallel in an original vehicle hydraulic steering system is often adopted. The steering control of the vehicle is realized by controlling the proportional electromagnetic valve to adjust the oil inlet and oil return directions of the steering cylinder, thereby meeting the automatic control requirement of the hydraulic steering system of the vehicle and being capable of switching between automatic control and manual control.
The hydraulic automatic steering control system for a vehicle, which is now commonly used, is described as follows: the hydraulic automatic steering control system of the vehicle comprises a hydraulic oil tank, a hydraulic pump, a proportional electromagnetic directional valve, an overflow valve, a valve seat, a hydraulic steering gear, a steering oil cylinder, a steering wheel, a hydraulic pipeline and a joint, wherein all hydraulic elements are mutually independent, the hydraulic oil tank is connected with the hydraulic pump through the hydraulic pipeline and the joint, the hydraulic pump is connected with the proportional electromagnetic directional valve through the hydraulic pipeline and the joint, the proportional electromagnetic directional valve is integrated with the overflow valve and the valve seat through bolts, the proportional electromagnetic directional valve is connected with the hydraulic steering gear and the steering oil cylinder through the hydraulic pipeline and the joint, and the hydraulic steering gear is connected with the steering wheel.
The vehicle hydraulic automatic steering control system has the defects that hydraulic elements in each hydraulic system are mutually independent and are connected with other hydraulic elements through hydraulic pipelines and joints, and the structure is complex; the hydraulic elements are arranged at different positions of the vehicle and have long distances, so that the occupied space is large; the hydraulic system has more connecting joints, increases the fault risk and is difficult to overhaul; the hydraulic components are more, and the cost of the hydraulic system is higher.
The matters in the background section are only those known to the inventors and do not, of course, represent prior art in the field.
Disclosure of Invention
In view of the above, the invention provides an integrated hydraulic steering control valve group, which has smaller volume, simple structure, low manufacturing cost and more convenient installation and maintenance compared with the prior art. On the basis, the invention also provides a hydraulic steering control system with the integrated hydraulic steering control valve group.
On the one hand, the invention provides an integrated hydraulic steering control valve bank, which is provided with a valve body, wherein an integrated oil inlet, an integrated oil return port, a first working oil port, a second working oil port, a third working oil port and a fourth working oil port are arranged on the valve body, a logic element pressure compensator and a proportional electromagnetic directional valve are also arranged on the integrated hydraulic steering control valve bank, and the logic element pressure compensator and the proportional electromagnetic directional valve are integrated into a single integral structural member in the valve body.
Further, a fifth working oil port, a sixth working oil port and a pressure measuring port are formed in the valve body, a two-position two-way power-on reversing valve, a first one-way valve, a damping hole, an overflow valve, a pressure compensation flow regulating valve, a hydraulic lock, a second one-way valve and a third one-way valve are integrated in the valve body of the integrated hydraulic steering control valve group, and the integrated oil inlet is connected with the pressure measuring port, a logic element pressure compensator P port and a first one-way valve outlet; the integrated oil return port is connected with a fourth working oil port, a first one-way valve inlet, an overflow valve outlet, a pressure compensation flow regulating valve outlet and a proportional electromagnetic reversing valve T port; the first working oil port is connected with an A port of the logic element pressure compensator; the third working oil port is connected with the fifth working oil port and the hydraulic lock A2 port; the fourth working oil port is connected with the sixth working oil port and the hydraulic lock B2 port; the port B of the logic element pressure compensator is connected with the inlet of the two-position two-way electromagnetic reversing valve; the outlet of the two-position two-way electromagnetic reversing valve is connected with the P port of the proportional electromagnetic reversing valve; the damping hole inlet is connected with an oil drain port of the logic element pressure compensator, and the damping hole outlet is connected with the overflow valve inlet, the pressure compensation flow regulating valve inlet, the second one-way valve outlet and the third one-way valve outlet; the port A of the proportional electromagnetic directional valve is connected with the port A1 of the hydraulic lock, and the port B of the proportional electromagnetic directional valve is connected with the port B1 of the hydraulic lock.
Further, the logic element pressure compensator is a hydraulic control two-position three-way valve, a hydraulic control port of the logic element pressure compensator is connected with a B port of the logic element pressure compensator and an inlet of a two-position two-way electromagnetic reversing valve, and when a valve core of the logic element pressure compensator is positioned at an upper position, a P port is communicated with an A port; when the valve core of the logic element pressure compensator is positioned at the lower position, the P port and the B port are communicated.
Further, the two-position two-way electromagnetic reversing valve is an electric control two-position two-way valve, when the two-position two-way electromagnetic reversing valve is electrified, the valve core of the two-position two-way electromagnetic reversing valve is positioned at the upper position, and the inlet and the outlet are communicated; when the two-position two-way electromagnetic reversing valve loses power, the valve core of the two-position two-way electromagnetic reversing valve is positioned at the lower position, and the inlet and the outlet are cut off.
Further, the proportional electromagnetic directional valve is a three-position four-way valve, and when the valve core of the proportional electromagnetic directional valve is positioned at the left position, the port P is communicated with the port B, and the port A is communicated with the port T; when the valve core is positioned in the middle position, the port P is cut off, and the port A, the port B and the port T are communicated; when the valve core is positioned at the right position, the port P is communicated with the port A, and the port T is communicated with the port B.
The integrated hydraulic steering control valve group provided by the invention is integrated with a logic element pressure compensator, a two-position two-way electromagnetic reversing valve, a first one-way valve, a second one-way valve, a third one-way valve, a damping hole, an overflow valve, a pressure compensation flow regulating valve, a hydraulic lock and a proportional electromagnetic reversing valve, when the integrated hydraulic steering control valve group is applied to a hydraulic steering control system of a vehicle, an integrated oil inlet is connected with a pressure oil source of the hydraulic system of the vehicle, an integrated oil return port is connected with an oil tank of the hydraulic system of the vehicle, a first working oil port, a second working oil port, a third working oil port and a fourth working oil port are respectively connected with P, T, A, B ports of a hydraulic steering device, and a fifth working oil port and a sixth working oil port are respectively connected with a steering oil cylinder; the oil inlet and oil return directions of the steering oil cylinder are regulated by controlling the proportional electromagnetic reversing valve, so that the steering control of the vehicle is realized, and the automatic control requirement of a hydraulic steering system of the vehicle is met; compared with the prior art, the integrated hydraulic steering control valve group has the advantages of small volume, simple structure, low manufacturing cost and more convenient installation and maintenance.
On the other hand, the invention also provides a hydraulic steering control system, which is provided with a hydraulic pump, a hydraulic oil tank, a hydraulic steering device, a steering oil cylinder and the integrated hydraulic steering control valve group, wherein the hydraulic pump is connected with an integrated oil inlet of the integrated hydraulic steering control valve group, the hydraulic oil tank is connected with an integrated oil return port, a P, T, A, B port of the hydraulic steering device is respectively connected with a first working oil port, a second working oil port, a third working oil port and a fourth working oil port, and the steering oil cylinder is connected with a fifth working oil port and a sixth working oil port.
Obviously, by utilizing the integrated hydraulic steering control valve group, the hydraulic steering control system can realize the automatic control requirement of the hydraulic steering system of the vehicle, can enable the steering of the vehicle to be mutually converted between automatic control and manual control, and can also facilitate the installation and maintenance of the hydraulic steering control system.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
FIG. 1 is one of the structural schematic diagrams of an integrated hydraulic steering control valve block according to an embodiment of the present invention;
FIG. 2 is one of the structural schematics of a hydraulic steering control system having an integrated hydraulic steering control valve set of the type shown in FIG. 1, in accordance with an embodiment of the present invention;
reference numerals illustrate:
1-Integrated oil inlet
2-integrated oil return port
3-first working oil port
4-second working oil port
5-third working oil port
6-fourth working oil port
7-fifth working oil port
8-sixth working oil port
9-pressure measuring port
10-valve body
11-logic element pressure compensator
12-two-position two-way electromagnetic reversing valve
13-first one-way valve
14-damping hole
15-overflow valve
16-pressure compensation flow regulating valve
17-hydraulic lock
18-second one-way valve
19-third one-way valve
20-proportion electromagnetic reversing valve
21-hydraulic pump
22-hydraulic oil tank
23-hydraulic steering gear
24-steering cylinder
Detailed Description
Hereinafter, only certain exemplary embodiments are briefly described. As will be recognized by those of skill in the pertinent art, the described embodiments may be modified in various different ways without departing from the spirit or scope of the present invention. Accordingly, the drawings and description are to be regarded as illustrative in nature and not as restrictive.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more of the described features. In the description of the present invention, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be fixedly connected, detachably connected, or integrally connected, and may be mechanically connected, electrically connected, or may communicate with each other, for example; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present invention, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is less level than the second feature.
The following disclosure provides many different embodiments, or examples, for implementing different features of the invention. In order to simplify the present disclosure, components and arrangements of specific examples are described below. They are, of course, merely examples and are not intended to limit the invention. Furthermore, the present invention may repeat reference numerals and/or letters in the various examples, which are for the purpose of brevity and clarity, and which do not themselves indicate the relationship between the various embodiments and/or arrangements discussed. In addition, the present invention provides examples of various specific processes and materials, but one of ordinary skill in the art will recognize the application of other processes and/or the use of other materials.
The preferred embodiments of the present invention will be described below with reference to the accompanying drawings, it being understood that the preferred embodiments described herein are for illustration and explanation of the present invention only, and are not intended to limit the present invention.
Specific embodiments of the present invention will be described in detail below with reference to fig. 1 and 2. FIG. 1 illustrates an integrated hydraulic steering control valve set 100 according to one embodiment of the present invention. As shown in fig. 1, the integrated hydraulic steering control valve group 100 is provided with a valve body 10, an integrated oil inlet 1, an integrated oil return port 2, a first working oil port 3, a second working oil port 4, a third working oil port 5 and a fourth working oil port 6 are arranged on the valve body 10, a logic valve (preferably a logic element pressure compensator) 11 and a proportional electromagnetic directional valve 20 are also arranged on the integrated hydraulic steering control valve group, and the logic element pressure compensator 11 and the proportional electromagnetic directional valve 20 are integrated into the valve body 10 as a single integral structural member respectively.
According to a preferred embodiment of the present invention, the first working port 3 is connected to port a (first oil outlet) of the logic element pressure compensator 11, the second working port 4 is connected to the integrated oil return port 2, and the fourth working port 6 is connected to the integrated oil return port 2.
According to a preferred embodiment of the present invention, the valve body 10 is further provided with a fifth working oil port 7, and the integrated hydraulic steering control valve group further includes a hydraulic lock 17 integrated inside the valve body 10, wherein the third working oil port 5 is connected to the fifth working oil port 7 and an A2 port of the hydraulic lock 17.
According to a preferred embodiment of the invention, the valve body 10 of the integrated hydraulic steering control valve block is provided with a sixth working oil port 8 and a pressure measuring port 9; the valve body 10 is internally integrated with a two-position two-way electromagnetic reversing valve 12, a first one-way valve 13, a damping hole 14, an overflow valve 15, a pressure compensation flow regulating valve 16, a second one-way valve 18 and a third one-way valve 19; the integrated oil inlet 1 is respectively connected with the pressure measuring port 9, the P port of the logic element pressure compensator 11 and the outlet of the first one-way valve 13; the integrated oil return port 2 is respectively connected with the fourth working oil port 6, the inlet of the first one-way valve 13, the outlet of the overflow valve 15, the outlet of the pressure compensation flow regulating valve 16 and the T port of the proportional electromagnetic directional valve 20; the first working oil port 3 is connected with an A port of the logic element pressure compensator 11; the third working oil port 5 is respectively connected with the fifth working oil port 7 and an A2 port of the hydraulic lock 7; the fourth working oil port 6 is respectively connected with the sixth working oil port 8 and a port B2 of the hydraulic lock 17; the port B of the logic element pressure compensator 11 is connected with the inlet of the two-position two-way power-on reversing valve 12; the outlet of the two-position two-way electromagnetic reversing valve 12 is connected with the P port of the proportional electromagnetic reversing valve 20; the inlet of the damping hole 14 is connected with an oil drain port of the logic element pressure compensator 11, and the outlet of the damping hole 14 is respectively connected with the inlet of the overflow valve 15, the inlet of the pressure compensation flow regulating valve 16, the outlet of the second one-way valve 18 and the outlet of the third one-way valve 19; the port A of the proportional electromagnetic directional valve 20 is connected with the port A1 of the hydraulic lock 17, and the port B of the proportional electromagnetic directional valve 20 is connected with the port B1 of the hydraulic lock 17.
The logic element pressure compensator 11 is a hydraulic control two-position three-way valve, a hydraulic control port of the logic element pressure compensator 11 is respectively connected with a port B (second oil outlet) of the logic element pressure compensator 11 and an inlet of the two-position two-way electromagnetic reversing valve 12, and when a valve core of the logic element pressure compensator 11 is positioned at an upper position, a port P (oil inlet) is communicated with a port A (first oil outlet); when the valve core of the logic element pressure compensator 11 is positioned at the lower position, the port P is communicated with the port B; the two-position two-way electromagnetic reversing valve 12 is an electric control two-position two-way valve, when the two-position two-way electromagnetic reversing valve 12 is powered on, the valve core of the two-position two-way electromagnetic reversing valve 12 is positioned at the upper position, and the inlet and the outlet are communicated; when the two-position two-way electromagnetic reversing valve 12 is powered off, the valve core of the two-position two-way electromagnetic reversing valve 12 is positioned at the lower position, and the inlet and the outlet are cut off; the proportional electromagnetic directional valve 20 is a three-position four-way valve, when the valve core of the proportional electromagnetic directional valve 20 is positioned at the left position, the port P (oil inlet) is communicated with the port B (second oil outlet), and the port A (first oil outlet) is communicated with the port T (oil return port); when the valve core is positioned in the middle position, the port P is cut off, and the port A, the port B and the port T are communicated; when the valve core is positioned at the right position, the port P is communicated with the port A, and the port T is communicated with the port B.
Fig. 2 is a schematic illustration of a hydraulic steering control system provided with an integrated hydraulic steering control valve set as described above, which may be used in a vehicle steering system to achieve automatic control requirements of the vehicle hydraulic steering system, enabling the vehicle steering to be switched between automatic and manual control. The working principle of the integrated hydraulic steering control valve set is described below in connection with the working process of the hydraulic steering control system.
As shown in fig. 2, the hydraulic steering control system is provided with a hydraulic pump 21, a hydraulic oil tank 22, a hydraulic steering gear 23, a steering oil cylinder 24 and one of the integrated hydraulic steering control valve groups, wherein the hydraulic pump 21 is connected with an integrated oil inlet 1 of the integrated hydraulic steering control valve group, the hydraulic oil tank 22 is connected with an integrated oil return port 2, P, T, A, B ports of the hydraulic steering gear 23 are respectively connected with a first working oil port 3, a second working oil port 4, a third working oil port 5 and a fourth working oil port 6, and the steering oil cylinder 24 is connected with a fifth working oil port 7 and a sixth working oil port 8.
When the two-position two-way electromagnetic reversing valve 12 loses electricity, the valve core of the two-way electromagnetic reversing valve 12 is positioned at the lower position, the inlet and the outlet are cut off, hydraulic oil is sucked out from the hydraulic oil tank 22 by the hydraulic steering control system hydraulic pump 21, enters the P port of the logic element pressure compensator 11 through the integrated oil inlet 1, the valve core of the logic element pressure compensator 11 is positioned at the lower position, the P port is communicated with the B port, the pressure oil enters the inlet of the two-position two-way electromagnetic reversing valve 12 from the B port of the logic element pressure compensator 11, the inlet and the outlet are cut off due to the fact that the valve core of the two-position two-way electromagnetic reversing valve 12 is positioned at the lower position, the pressure oil is enabled to rise, the pressure oil enters the logic element pressure compensator 11 through the control pipeline, the valve core of the logic element pressure compensator 11 is positioned at the upper position, the P port is communicated with the A port, the system pressure oil enters the P port of the hydraulic steering oil tank 23 through the first working oil port 3, the steering oil cylinder 24 is driven to steer the vehicle, and then flows out of the hydraulic oil tank 22 through the integrated oil return port 2 from the T port of the hydraulic steering device 23, and manual control of the hydraulic steering control system is achieved.
When the two-position two-way electromagnetic reversing valve 12 is electrified, the valve core of the two-way electromagnetic reversing valve 12 is positioned at an upper position, the inlet is communicated with the outlet, hydraulic oil is sucked out of the hydraulic oil tank 22 by the hydraulic steering control system hydraulic pump 21, enters the P port of the logic element pressure compensator 11 through the integrated oil inlet 1, the valve core of the logic element pressure compensator 11 is positioned at a lower position, the P port is communicated with the B port, pressure oil enters the inlet of the two-position two-way electromagnetic reversing valve 12 from the B port of the logic element pressure compensator 11, the inlet is communicated with the outlet because the valve core of the two-way electromagnetic reversing valve 12 is positioned at an upper position, system pressure oil enters the P port of the proportional electromagnetic reversing valve 20 through the outlet of the two-way electromagnetic reversing valve 12, the proportional electromagnetic reversing valve 20 is a three-way valve, when the valve core of the proportional electromagnetic reversing valve 20 is positioned at a left position, the P port is communicated with the B port, the A port is communicated with the T port, the system pressure oil enters the B1 port of the hydraulic lock 17 through the B port of the proportional electromagnetic reversing valve 20, flows out of the B2 port of the hydraulic lock 17 into the steering oil cylinder 24, drives the vehicle to steer, and then enters the A2 port of the hydraulic lock 17, and flows out of the hydraulic lock 17 through the proportional electromagnetic reversing valve 20A 2 through the electromagnetic reversing valve 20 through the proportional electromagnetic reversing valve 20; when the valve core of the proportional electromagnetic directional valve 20 is positioned in the middle position, the port P is cut off, the port A, the port B and the port T are communicated, the steering oil cylinder 24 does not enter oil or return oil, and the direction of the vehicle is kept unchanged; when the valve core of the proportional electromagnetic directional valve 20 is positioned at the right position, the port P is communicated with the port A, the port T is communicated with the port B, system pressure oil enters the port A1 of the hydraulic lock 17 through the port A of the proportional electromagnetic directional valve 20, flows out of the port A2 of the hydraulic lock 17 and enters the steering cylinder 24 to drive the vehicle to steer, then enters the port B2 of the hydraulic lock 17, enters the port B of the proportional electromagnetic directional valve 20 from the port B1 of the hydraulic lock 17, flows out of the port T of the proportional electromagnetic directional valve 20 and returns to the hydraulic oil tank 22 through the integrated oil return port 2, and automatic control of a hydraulic steering control system is realized.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the invention.
Finally, it should be noted that: the foregoing description is only a preferred embodiment of the present invention, and the present invention is not limited thereto, but it is to be understood that modifications and equivalents of some of the technical features described in the foregoing embodiments may be made by those skilled in the art, although the present invention has been described in detail with reference to the foregoing embodiments. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (9)
1. An integrated hydraulic steering control valve set, comprising:
the valve comprises a valve body (10), wherein an integrated oil inlet (1), an integrated oil return port (2), a first working oil port (3), a second working oil port (4), a third working oil port (5) and a fourth working oil port (6) are arranged on the valve body (10);
a logic valve (11); and
a proportional electromagnetic directional valve (20),
wherein the logic valve (11) and the proportional electromagnetic directional valve (20) are integrated into the valve body (10) to form an integral structural part;
the valve body (10) is further provided with a sixth working oil port (8) and a pressure measuring port (9), a two-position two-way electromagnetic reversing valve (12), a first one-way valve (13), a damping hole (14), an overflow valve (15), a pressure compensation flow regulating valve (16), a hydraulic lock (17), a second one-way valve (18) and a third one-way valve (19) are integrated in the valve body (10), and the integrated oil inlet (1) is connected with the pressure measuring port (9), the P port of the logic valve (11) and the outlet of the first one-way valve (13); the integrated oil return port (2) is connected with the fourth working oil port (6), the inlet of the first one-way valve (13), the outlet of the overflow valve (15), the outlet of the pressure compensation flow regulating valve (16) and the T port of the proportional electromagnetic directional valve (20); the first working oil port (3) is connected with an A port of the logic valve (11); the fourth working oil port (6) is connected with the sixth working oil port (8) and the port B2 of the hydraulic lock (17); the port B of the logic valve (11) is connected with the inlet of the two-position two-way electromagnetic reversing valve (12); the outlet of the two-position two-way electromagnetic reversing valve (12) is connected with the P port of the proportional electromagnetic reversing valve (20); the inlet of the damping hole (14) is connected with an oil drain port of the logic valve (11), and the outlet of the damping hole (14) is connected with the inlet of the overflow valve (15), the inlet of the pressure compensation flow regulating valve (16), the outlet of the second one-way valve (18) and the outlet of the third one-way valve (19); the port A of the proportional electromagnetic directional valve (20) is connected with the port A1 of the hydraulic lock (17), and the port B of the proportional electromagnetic directional valve (20) is connected with the port B1 of the hydraulic lock (17).
2. The integrated hydraulic steering control valve group according to claim 1, characterized in that the first working oil port (3) is connected with an a port of a logic valve (11), the second working oil port (4) is connected with the integrated oil return port (2), and the fourth working oil port (6) is connected with the integrated oil return port (2).
3. The integrated hydraulic steering control valve group according to claim 1 or 2, characterized in that a fifth working oil port (7) is further arranged on the valve body (10), the integrated hydraulic steering control valve group further comprises a hydraulic lock (17) integrated inside the valve body (10), wherein the third working oil port (5) is connected with the fifth working oil port (7) and an A2 port of the hydraulic lock (17).
4. The integrated hydraulic steering control valve group according to claim 1, wherein the logic valve (11) is a hydraulically controlled two-position three-way valve, a hydraulic control port of the logic valve (11) is connected with a port B of the logic valve (11) and an inlet of the two-position two-way electromagnetic reversing valve (12), and when a valve core of the logic valve (11) is located at an upper position, a port P is communicated with a port a; when the valve core of the logic valve (11) is positioned at the lower position, the port P and the port B are communicated.
5. The integrated hydraulic steering control valve set according to any one of claims 1-2, wherein the proportional electromagnetic directional valve (20) is a three-position four-way valve, and when a valve core of the proportional electromagnetic directional valve (20) is located at a left position, a port P and a port B are communicated, and a port a and a port T are communicated; when the valve core is positioned in the middle position, the port P is cut off, and the port A, the port B and the port T are communicated; when the valve core is positioned at the right position, the port P is communicated with the port A, and the port T is communicated with the port B.
6. The integrated hydraulic steering control valve group according to claim 1, wherein the two-position two-way electromagnetic directional valve (12) is an electric control two-position two-way valve, when the two-position two-way electromagnetic directional valve (12) is powered on, a valve core of the two-position two-way electromagnetic directional valve (12) is positioned at an upper position, and an inlet and an outlet are communicated; when the two-position two-way electromagnetic reversing valve (12) is powered off, the valve core of the two-position two-way electromagnetic reversing valve (12) is positioned at the lower position, and the inlet and the outlet are cut off.
7. Integrated hydraulic steering control valve group according to any of claims 1-2, characterized in that the logic valve (11) is a logic element pressure compensator.
8. A hydraulic steering control system, comprising: the integrated hydraulic steering control valve group according to any one of claims 1 to 7, wherein the hydraulic pump (21), the hydraulic oil tank (22), the hydraulic steering gear (23), the steering oil cylinder (24) and the integrated oil inlet (1) of the integrated hydraulic steering control valve group are connected, the hydraulic oil tank (22) is connected with the integrated oil return port (2), P, T, A, B ports of the hydraulic steering gear (23) are respectively connected with the first working oil port (3), the second working oil port (4), the third working oil port (5) and the fourth working oil port (6), and the steering oil cylinder (24) is connected with the fifth working oil port (7) and the sixth working oil port (8).
9. A method of controlling the hydraulic steering control system of claim 8, comprising:
when the hydraulic steering control system is required to be manually operated, the two-position two-way electromagnetic reversing valve (12) is powered off;
when the hydraulic steering control system is required to be automatically operated, the two-position two-way electromagnetic reversing valve (12) is electrified.
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| CN201810724787.4A CN108547821B (en) | 2018-07-04 | 2018-07-04 | Integrated hydraulic steering control valve group and hydraulic steering control system |
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| CN201810724787.4A CN108547821B (en) | 2018-07-04 | 2018-07-04 | Integrated hydraulic steering control valve group and hydraulic steering control system |
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| CN108547821B true CN108547821B (en) | 2023-08-01 |
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| CN109747708B (en) * | 2019-03-13 | 2020-08-21 | 合肥工业大学 | Full-hydraulic synchronous steering system for low-speed heavy-load vehicle and control method thereof |
| CN109899329B (en) * | 2019-03-29 | 2021-05-18 | 潍柴动力股份有限公司 | Load sensitive control mechanism and hydraulic system |
| CN110712735B (en) * | 2019-08-29 | 2021-06-01 | 武汉船用机械有限责任公司 | Hydraulic control system for a water jet propulsion device |
| CN112443527B (en) * | 2020-12-10 | 2023-11-07 | 徐州阿马凯液压技术有限公司 | High-flow-precision flow amplifying valve |
| CN114278696A (en) * | 2021-12-27 | 2022-04-05 | 湖南联诚轨道装备有限公司 | Steering damper of railway vehicle bogie |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| IT1230619B (en) * | 1987-11-09 | 1991-10-28 | Rexroth Mannesmann Gmbh | HYDROSTATIC POWER STEERING FOR VEHICLES |
| CN102923188B (en) * | 2012-11-27 | 2015-07-22 | 徐州重型机械有限公司 | Electrically controlled multi-mode steering valve, steering hydraulic control system and wheeled crane |
| CN105134678A (en) * | 2015-08-26 | 2015-12-09 | 徐工集团工程机械股份有限公司科技分公司 | Pilot control valve block, core opening and closing hydraulic system and engineering machine |
| CN206246446U (en) * | 2016-11-11 | 2017-06-13 | 三一汽车制造有限公司 | Integrated hydraulic valve group and the fluid power system and concrete pump of the valve group are set |
| CN108100033A (en) * | 2018-01-10 | 2018-06-01 | 西安合众思壮导航技术有限公司 | Turn to fluid distributor |
| CN208885671U (en) * | 2018-07-04 | 2019-05-21 | 北京奥腾岩石科技有限公司 | Integrated hydraulic course changing control valve group and fluid-link steering control system |
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