CN111577692A - Multi-path electro-hydraulic valve with differential confluence function - Google Patents

Multi-path electro-hydraulic valve with differential confluence function Download PDF

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Publication number
CN111577692A
CN111577692A CN202010336775.1A CN202010336775A CN111577692A CN 111577692 A CN111577692 A CN 111577692A CN 202010336775 A CN202010336775 A CN 202010336775A CN 111577692 A CN111577692 A CN 111577692A
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China
Prior art keywords
electro
valve
oil
hydraulic
valve group
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CN202010336775.1A
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Chinese (zh)
Inventor
胡芳芳
陈启松
徐光德
王艳霞
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Luzhou Zhongda Science & Technology Hydraulic Parts Co ltd
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Luzhou Zhongda Science & Technology Hydraulic Parts Co ltd
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Priority to CN202010336775.1A priority Critical patent/CN111577692A/en
Publication of CN111577692A publication Critical patent/CN111577692A/en
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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
    • 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
    • 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
    • F16K31/42—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor
    • F16K31/423—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor the actuated members consisting of multiple way valves
    • F16K31/426—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor the actuated members consisting of multiple way valves the actuated valves being cylindrical sliding valves

Abstract

The invention discloses a multi-path electro-hydraulic valve with a differential confluence function, which comprises an oil inlet flow dividing valve group, a functional electro-hydraulic reversing valve group I, a functional electro-hydraulic reversing valve group II, a differential confluence valve group, a rapid electro-hydraulic reversing valve group and an oil return valve group which are connected in sequence, wherein oil inlet channels, a middle unloading channel and a common oil return channel are arranged in the valve bodies of the oil inlet flow dividing valve group, the functional electro-hydraulic reversing valve group I, the functional electro-hydraulic reversing valve group II and the rapid electro-hydraulic reversing valve group, the oil return channels of the electro-hydraulic reversing valve group are communicated with the common oil return channel in parallel, the oil inlet channels of the functional electro-hydraulic reversing valve group I and the functional electro-hydraulic reversing valve group II are communicated with an oil. The invention solves the defects of large volume, complex integrated block design, high cost, more pipeline connections, inconvenient maintenance and the like caused by a differential confluence structure form of a common electromagnetic electro-hydraulic valve group and an integrated block.

Description

Multi-path electro-hydraulic valve with differential confluence function
Technical Field
The invention relates to the technical field of hydraulic control, in particular to a multi-path electro-hydraulic valve with a differential confluence function.
Background
The hydraulic differential confluence technology is mainly used for converting the movement speed of a rodless cavity of a piston type hydraulic cylinder in a single-stage quantitative hydraulic pump system, and meets the requirement of increasing flow supply at low pressure so as to realize the quick movement of the rodless cavity of the single-stage or multi-stage hydraulic cylinder; the constant-speed feeding device supplies rated flow for a single pump under a high-pressure working condition, and meets the requirement of constant-speed feeding movement of a rodless cavity of a single-stage or multi-stage hydraulic cylinder under a high load. Its advantage is: firstly, the configuration is simplified in the quantitative pump system, and a multi-connection pump is not needed to realize the confluence function; secondly, the conversion of large flow and small flow is realized without adopting a variable hydraulic pump with high price, and particularly, the purchasing cost is obviously reduced in a medium-large flow system, so that the system structure is more reasonable. The hydraulic differential confluence technology is widely applied to compression garbage stations, compression garbage trucks, hydraulic baling presses, small and medium-sized hydraulic machines, drilling machines and various hydraulic mechanical equipment which needs to realize the function of quick feeding in medium and low pressure links at present.
The control modes of the existing hydraulic differential confluence electrohydraulic control system mainly comprise the following two modes:
(1) electric control: the differential confluence function is formed by adopting a plurality of electromagnetic valves (the flow is less than or equal to 80L/min) or a plurality of electro-hydraulic valve groups (the flow is more than 80L/min) and specially designed integrated blocks.
(2) Manual operation: a plurality of manual reversing valves and an integrated block or a plurality of manual reversing valves are connected through complex pipelines to form a differential converging function.
The two control modes have the following control problems respectively:
(1) the existing mode of adopting an electromagnetic valve or an electro-hydraulic valve and a special design integrated block has complex structure and high manufacturing and installation cost, the oil circuit of the electromagnetic valve or the electro-hydraulic valve is controlled independently, the structure volume is large, and the design and processing period of the integrated block is longer; meanwhile, system faults are easily caused due to high oil cleanliness and high electromagnetic valve current overload frequency, and maintenance is difficult.
(2) The differential confluence function is formed by connecting a plurality of manual reversing valves and integrated blocks or a plurality of manual reversing valves through pipelines, the structure is large in size, the pipeline connection is complex, the integration with other control functions is difficult, and the requirement of batch production is difficult to meet.
The multi-way valve is a combined valve with a plurality of control ends, the output end of the multi-way valve is communicated with an oil cavity of an actuating element, the actuating element is usually a hydraulic cylinder, and a rodless cavity and a rod cavity of the hydraulic cylinder are controlled by the multi-way valve to feed oil and discharge oil, so that the extension and retraction of a piston rod of the hydraulic cylinder are controlled.
In the application environment of equipment such as sanitation machinery and the like, due to the particularity of working conditions and the humanized development requirement of hydraulic machinery, the used multi-path electro-hydraulic valve needs to integrate the differential confluence function, and if the two differential confluence control modes are directly connected with the existing multi-path electro-hydraulic valve into a whole, the size of the multi-path electro-hydraulic valve is increased, and the structural complexity, the processing cost and the maintenance difficulty of the multi-path electro-hydraulic valve are also increased. Therefore, it is necessary to redesign a differential confluence valve set, and integrate the differential confluence valve set with a multi-path electro-hydraulic valve, so that the multi-path electro-hydraulic valve can be operated in a manual or electric control mode, and can be integrated with a reversing function, thereby forming a small-sized manual/electric-hydraulic control multi-path integrated valve which can realize a differential confluence function for a specific oil path.
Disclosure of Invention
The invention aims to: the utility model provides a multichannel electrohydraulic valve with differential confluence function, has solved current multichannel electrohydraulic valve and has lacked differential confluence function, and will lead to its structure complexity to increase etc. above-mentioned technical problem when directly using current differential confluence valves on multichannel electrohydraulic valve. The multi-path electro-hydraulic valve with the differential confluence function, which is designed by the invention, not only uses manual and electro-hydraulic control for controlling the multi-path electro-hydraulic valve, but also has the advantages of simple structure, low processing cost and small volume of the differential confluence valve bank. .
The technical scheme adopted by the invention is as follows:
a multi-path electro-hydraulic valve with a differential confluence function comprises an oil inlet flow dividing valve group, a functional electro-hydraulic reversing valve group I and an oil return valve group which are sequentially connected, wherein a functional electro-hydraulic reversing valve group II, a differential confluence valve group and a rapid electro-hydraulic reversing valve group are sequentially connected between the functional reversing valve group and the oil return valve group, the functional electro-hydraulic reversing valve group I and the functional electro-hydraulic reversing valve group II are three-position six-way reversing valves, the rapid electro-hydraulic reversing valve group is a two-position six-way reversing valve, and oil inlet channels, middle unloading channels and common oil return channels are respectively arranged in the oil inlet flow dividing valve group, the functional electro-hydraulic reversing valve group I, the functional electro-hydraulic reversing valve group II and the,
the oil return channels of the functional electro-hydraulic reversing valve group I, the functional electro-hydraulic reversing valve group II and the quick electro-hydraulic reversing valve group are communicated with a public oil return channel in parallel, the oil inlet channels of the functional electro-hydraulic reversing valve group I and the functional electro-hydraulic reversing valve group II are communicated with the oil outlet channel of the oil inlet flow distributing valve group in parallel, and a main oil way supplies oil to the oil inlet channel of the oil inlet flow distributing valve group 1; the functional electro-hydraulic reversing valve group I, the functional electro-hydraulic reversing valve group II and a middle unloading channel of the rapid electro-hydraulic reversing valve group are sequentially connected in series through a series oil way and communicated with a common oil return channel in an oil return valve group through the series oil way; the common oil return channel is communicated with the oil tank;
the two working oil ports of the functional electro-hydraulic reversing valve group II are respectively a working oil port A3 and a working oil port B3, the working oil port A3 and the working oil port B3 are respectively communicated with the valve cavity of the functional electro-hydraulic reversing valve group II through a working oil duct A3 and a working oil duct B3, the working oil port A3 is closed, and a working oil duct Aa communicated with the working oil duct A3 and a working oil duct Bb communicated with the working oil duct B3 are arranged on the valve body of the functional electro-hydraulic reversing valve group II;
the differential confluence valve group is provided with a working oil passage Hb and a working oil passage Ha, and a working oil port A4 and a working oil passage Hc of which one end is communicated with a working oil port A4 are arranged on the differential confluence valve group;
the working oil port of the rapid electro-hydraulic reversing valve group is closed, a working oil duct Ka, a working oil duct Kb and a working oil duct Kc which are communicated with the valve cavity of the rapid electro-hydraulic reversing valve group are arranged on the rapid electro-hydraulic reversing valve group, the working oil duct Ka is communicated with a working oil duct Aa through a working oil duct Ha, the working oil duct Kb is communicated with a working oil duct Bb through a working oil duct Hb, and the working oil duct Kc is communicated with a working oil duct Hc.
Furthermore, the stations of the reversing main valve cores of the functional electro-hydraulic reversing valve group I, the functional electro-hydraulic reversing valve group II and the quick electro-hydraulic reversing valve group are controlled by an electro-hydraulic control system, the electro-hydraulic control system comprises a flow dividing sequence valve and a plurality of reversing control components which are respectively fixed on the lower side of a valve body of an electro-hydraulic reversing valve group, the reversing control assembly comprises a pilot electromagnetic valve and a pilot oil cylinder, wherein oil passages of the pilot electromagnetic valve and the pilot oil cylinder are communicated with each other, the tail end of a piston rod of the pilot oil cylinder is coaxially connected with one end of a reversing main valve core of the corresponding electro-hydraulic reversing valve group, the flow dividing sequence valve is arranged in an oil inlet channel of the oil inlet flow dividing valve group, the liquid inlet port and the main liquid outlet port are respectively communicated with the main oil inlet path and the oil inlet channel of the oil inlet flow distributing valve group, the auxiliary liquid outlet port of the electro-hydraulic reversing valve group is communicated with the valve cavity of each pilot electromagnetic valve after passing through the pilot oil passage and the shunt oil passage on the side surface of each electro-hydraulic reversing valve group in sequence;
the reversing of the valve core of the pilot electromagnetic valve can be controlled by controlling the electrification and the outage of the electromagnet of the pilot electromagnetic valve, so that the movement direction of the piston rod of the pilot oil cylinder is controlled, and the station of the main valve core is controlled to be reversed.
Furthermore, the reversing control assembly also comprises a return spring which is used for moving the reversing main valve core to a neutral position when both cavities of the pilot oil cylinder are in an unloading state.
Further, the pilot electromagnetic valve arranged below the functional electro-hydraulic reversing valve group is a first pilot electromagnetic valve which is a three-position four-way electromagnetic valve, and the pilot electromagnetic valve arranged below the rapid electro-hydraulic reversing valve group is a second pilot electromagnetic valve which is a two-position four-way electromagnetic valve.
Furthermore, the other end of the reversing main valve core of the electro-hydraulic reversing valve group is connected with a handle rod for manually operating the station where the reversing main valve core is located.
Furthermore, a pilot overflow valve is connected into the pilot oil passage.
Furthermore, the functional electro-hydraulic reversing valve group II is an O-shaped functional electro-hydraulic reversing valve group.
Furthermore, the functional electro-hydraulic reversing valve group I comprises one or more than one, and the functional electro-hydraulic reversing valve group I comprises the following types: the hydraulic reversing valve set comprises a Y-shaped functional electro-hydraulic reversing valve set, an O-shaped functional electro-hydraulic reversing valve set, a C-shaped functional electro-hydraulic reversing valve set and a K-shaped functional electro-hydraulic reversing valve set.
Further, couple together the valve body of each valves through coupling assembling, coupling mechanism includes double threaded screw, nut and packing ring all be provided with the connecting hole of mutual correspondence on the valve body of oil feed reposition of redundant personnel valves, electricity liquid switching-over valves I, electricity liquid switching-over valves II, differential confluence valves, quick electricity liquid switching-over valves and oil return valves, the one end of double threaded screw passes in proper order behind each connecting hole and a packing ring and screws up with a nut, the other end of double threaded screw passes behind another packing ring and nut threaded connection.
Furthermore, four connecting holes are formed in the valve body of each valve group, the connecting holes in two adjacent valve bodies are in one-to-one correspondence, and the connecting mechanisms are provided with four groups.
Due to the adoption of the technical scheme, the invention has the beneficial effects that:
1. the invention relates to a multi-path electro-hydraulic valve with a differential confluence function, which solves the defects of large volume, complex integrated block design, high cost, multiple pipeline connections, inconvenient maintenance and the like caused by a differential confluence structural form of a common electromagnetic electro-hydraulic valve group and an integrated block; in the invention, the valve group for forming the differential confluence function has a simple structure, and is integrated with the multi-path electro-hydraulic valve, so that the multi-path electro-hydraulic valve can realize the differential confluence function for a specific oil path, and the control function of the multi-path electro-hydraulic valve is further perfected; the multi-path electro-hydraulic valve designed by the invention has small volume, only a plurality of valve groups are added, and the oil passages in each valve group are utilized to realize the confluence function of pressure oil, so that the multi-path electro-hydraulic valve has a simple structure and is convenient to maintain, and the manufacturing and maintenance cost is reduced;
2. according to the multi-path electro-hydraulic valve with the differential confluence function, the shunting sequence valve is arranged between the main oil inlet path and the oil inlet channel of the oil inlet shunting valve group, so that the working position of a piston rod of a pilot oil cylinder is adjusted through pilot control oil, then the reversing main valve cores of all electro-hydraulic reversing valve groups are adjusted to move to the required working position, and then preparation is made for related control operation of the multi-path electro-hydraulic valve; after the preparation is finished, the pressure oil output by the flow dividing sequence valve is used as control oil to open the flow dividing overflow valve through the control oil duct, so that a main oil inlet path is communicated with oil inlet channels of the oil inlet flow dividing valve blocks, and main flow is sent to each valve block to perform related control operation; a flow dividing sequence valve is arranged between a main oil inlet path and an oil inlet channel of an oil inlet flow dividing valve bank, so that before the reversing main valve cores of all the valve banks are adjusted to required stations, pressure oil does not enter the valve banks, and the working stability of the multi-path electro-hydraulic valve bank is guaranteed.
3. The invention relates to a multi-path electro-hydraulic valve with a differential confluence function, which is used for controlling pressure oil of an electro-hydraulic control system of a station where a reversing main valve core of a functional electro-hydraulic reversing valve group and a reversing main valve core of a quick electro-hydraulic reversing valve group are located, wherein the pressure oil is from oil at a P port of a main oil inlet, the structure of the electro-hydraulic control system is simplified, the working state of a pilot oil cylinder can be controlled by utilizing the pressure oil pumped by an oil pump of the valve group, an oil pump for the electro-hydraulic control system is not required to be additionally arranged, the control mode and the number of components of the electro-hydraulic control system are simplified, the length of the oil passage of the electro-hydraulic control system is shortened, and therefore, the volume of the multi.
4. According to the multi-path electro-hydraulic valve with the differential confluence function, due to the arrangement of the return spring, the operation of returning the reversing main valve core to the neutral position can be simplified, pressure oil is not required to be pumped to a pilot oil cylinder additionally, and the energy urgently needed by the deformation of the return spring caused by the movement of the main valve core of the reversing valve in the previous step is directly utilized to return the reversing main valve core to the neutral position, so that an electro-hydraulic control system is further simplified, the control reliability of the electro-hydraulic control system is improved, the manufacturing cost is reduced, and the maintenance is convenient; meanwhile, when two cavities of the pilot oil cylinder are in an unloading state, the reversing main valve core is reset through the reset spring, and the working stability is guaranteed.
5. The multi-path electro-hydraulic valve with the differential confluence function not only realizes the reversing of the reversing main valve element of each valve group through the electro-hydraulic control system, but also realizes the reversing of the reversing main valve element of each valve group through the manual operation handle rod, thereby improving the application environment of the multi-path electro-hydraulic valve and facilitating the later maintenance, overhaul and the like; in addition, the differential confluence function and the manual and electric control are integrated, so that the reliability and the feedback sensitivity of the hydraulic system are improved, and the system configuration cost is reduced;
6. the invention relates to a multi-path electro-hydraulic valve with a differential confluence function, which organically integrates pilot control of internal control and internal discharge, electro-hydraulic and manual operation modes and the differential confluence function into a whole, improves the reliability and feedback sensitivity of a hydraulic system, and reduces the configuration cost of the system. The invention can realize remote or PLC (when the pilot electromagnetic valve is a pressure-reducing proportional electromagnetic valve) control of the hydraulic actuating element, and electronic devices such as a pressure sensor are connected with controllers such as the PLC and the like for transmitting working signals, thereby facilitating subsequent related operation and control operation according to programs; and when the electro-hydraulic control fails, the control requirement is realized or potential safety hazards are eliminated by adopting manual control. The invention can be widely applied to various environmental sanitation machines, packaging machines, drilling machines and the like of which the hydraulic cylinders need to move in an accelerated manner.
7. The invention relates to a multi-path electro-hydraulic valve with a differential confluence function, which overcomes the defects of large volume, complex integrated block design, high cost, multiple pipeline connections, inconvenient maintenance and the like caused by a differential confluence structural form of a common electromagnetic electro-hydraulic valve group and an integrated block.
8. The invention relates to a multi-path electro-hydraulic valve with a differential confluence function, wherein an auxiliary valve jack and a flow channel, a main reversing valve hole and a flow channel and a pilot control flow channel are integrated into a multi-layer design on the same valve body, so that the valve body is more optimized in oil path, small in pressure loss, compact in structure and convenient and fast in integration of different functional valve groups.
9. The invention relates to a multi-path electro-hydraulic valve with a differential confluence function, which can be plugged with auxiliary valves such as an overload valve, an oil supplementing valve, a hydraulic lock, a balance valve, a pressure sensor and the like according to functional requirements.
10. The invention relates to a multi-path electro-hydraulic valve with a differential confluence function, which can be combined in one to eight links and meet the operating requirements of single operation or multi-mechanism linkage of various actuating elements.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the embodiments are briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention, and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without creative efforts, and the proportional relationship of each component in the drawings in the present specification does not represent the proportional relationship in the actual material selection design, and is only a schematic diagram of the structure or the position, in which:
FIG. 1 is a schematic view of the profile structure of the invention;
FIG. 2 is a cross-sectional view A-A of FIG. 1;
FIG. 3 is a cross-sectional view B-B of FIG. 1;
FIG. 4 is a view from direction F-F of FIG. 1;
FIG. 5 is a view from the direction G-G of FIG. 3;
FIG. 6 is a view from D-D of FIG. 1;
FIG. 7 is a view from the C-C of FIG. 1;
fig. 8 is a hydraulic schematic of the invention.
Reference numerals in the drawings indicate:
1-an oil inlet flow dividing valve group, 2-a functional electro-hydraulic reversing valve group I, 3-a functional electro-hydraulic reversing valve group II, 4-a differential confluence valve group, 5-a rapid electro-hydraulic reversing valve group, 6-an oil return valve group, 7-a flow dividing sequence valve, 8-a one-way valve, 9-a pilot overflow valve, 10-an overload valve, 11-a main overflow valve, 12-a double-head screw, 13-a nut and a gasket, 14-a pressure relay I, 15-a pressure relay II, 16-an oil inlet channel, 17-a middle unloading oil channel, 18-a common oil channel, 19-a pilot oil inlet channel, 20-a pilot oil channel, 21-a pilot reversing oil channel, 22-a pilot reversing channel, 23-a first electromagnetic valve, 24-a second electromagnetic valve and 25-a reversing main valve, 26-pilot oil cylinder, 27-handle rod, 28-working oil passage Bb, 29-working oil passage Aa, 30-working oil passage Hb, 31-working oil passage Ha, 32-working oil passage Hc, 33-working oil passage Ka, 34-working oil passage Kb, 35-pilot oil passage and 36-control oil passage.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
The term "connection" in the present invention is not particularly limited, and may be any conventional connection means such as a pipe thread connection, a hydraulic passage connection, etc., and the specific connection means is preferably adapted according to the conventional technical knowledge in the art. All of the features disclosed in this specification, or all of the steps in any method or process so disclosed, may be combined in any combination, except combinations of features and/or steps that are mutually exclusive.
The present invention will be described in detail with reference to fig. 1 to 8.
Example 1
As shown in fig. 1 to 8, the multi-path electrohydraulic valve with differential confluence function of the invention comprises an oil inlet flow dividing valve group 1, a functional electrohydraulic reversing valve group i 2 and an oil return valve group 6 which are connected in sequence, wherein a functional electrohydraulic reversing valve group ii 3, a differential confluence valve group 4 and a fast electrohydraulic reversing valve group 5 are sequentially connected between the functional electrohydraulic reversing valve group and the oil return valve group 6, the functional electrohydraulic reversing valve group i 2 and the functional electrohydraulic reversing valve group ii 3 are three-position six-way reversing valves, the fast electrohydraulic reversing valve group 5 is a two-position six-way reversing valve, oil inlet channels 16, a middle unloading channel 17 and a common oil return channel 18 are respectively arranged in valve bodies of the oil inlet flow dividing valve group 1, the functional electrohydraulic reversing valve group i 2, the functional electrohydraulic reversing valve group ii 3 and the fast electrohydraulic reversing valve group 5,
the oil return channels of the functional electro-hydraulic reversing valve group I2, the functional electro-hydraulic reversing valve group II 3 and the quick electro-hydraulic reversing valve group 5 are communicated with a public oil return channel 18 in parallel, the oil inlet channels 16 of the functional electro-hydraulic reversing valve group I2 and the functional electro-hydraulic reversing valve group II 3 are communicated with the oil outlet channel of the oil inlet flow dividing valve group in parallel, and a main oil way supplies oil to the oil inlet channel 16 of the oil inlet flow dividing valve group 1; the functional electro-hydraulic reversing valve group I2, the functional electro-hydraulic reversing valve group II 3 and the middle unloading channel 19 of the quick electro-hydraulic reversing valve group 5 are sequentially connected in series through a series oil way and communicated with a common oil return channel 18 in the oil return valve group 6 through the series oil way; the common oil return channel 18 is communicated with an oil tank;
the two working oil ports of the functional electro-hydraulic reversing valve group II 3 are respectively a working oil port A3 and a working oil port B3, the working oil port A3 and the working oil port B3 are respectively communicated with the valve cavity of the functional electro-hydraulic reversing valve group II 3 through a working oil duct A3 and a working oil duct B3, the working oil port A3 is closed, and a valve body of the functional electro-hydraulic reversing valve group II 3 is provided with a working oil duct Aa29 communicated with the working oil duct A3 and a working oil duct Bb28 communicated with a working oil duct B3;
the differential confluence valve group 4 is provided with a working oil passage Hb30 and a working oil passage Ha31, and is provided with a working oil port A4 and a working oil passage Hc32, one end of which is communicated with the working oil port A4;
the working oil ports of the rapid electro-hydraulic reversing valve group 5 are all closed, a working oil duct Ka33, a working oil duct Kb34 and a working oil duct Kc which are all communicated with the valve cavity of the rapid electro-hydraulic reversing valve group are arranged on the rapid electro-hydraulic reversing valve group, the working oil duct Ka33 is communicated with a working oil duct Aa29 through a working oil duct Ha31, the working oil duct Kb34 is communicated with a working oil duct Bb28 through a working oil duct Hb30, and the working oil duct Kc is communicated with a working oil duct Hc 32.
When the hydraulic cylinder is used, the working oil port B3 and the working oil port A4 are respectively connected into two chambers of an actuating element, the actuating element is preferably a hydraulic cylinder, the working oil port B3 is communicated with a rodless cavity of the hydraulic cylinder, the working oil port A4 is communicated with a rod cavity of the hydraulic cylinder, the working oil port B3 sends pressure oil to the hydraulic cylinder, and a piston rod extends outwards; the working oil port A4 sends pressure oil to the hydraulic cylinder, and the piston rod retracts.
The functional electro-hydraulic reversing valve group II 3 is preferably an O-shaped functional electro-hydraulic reversing valve group.
The functional electro-hydraulic reversing valve group I is 1-8 so as to meet the operating requirements of single operation or multi-mechanism linkage of various executing elements, and the functional electro-hydraulic reversing valve group I comprises the following types: the number of the functional electro-hydraulic reversing valve groups I is 1 in the embodiment, and the functional electro-hydraulic reversing valve group I is preferably a Y-shaped functional electro-hydraulic reversing valve group.
The functional electro-hydraulic reversing valve group II 3 is a three-position six-way reversing valve, and is in an O-shaped functional state, namely when the functional electro-hydraulic reversing valve group is in an original position, a main reversing valve core of the functional electro-hydraulic reversing valve group is in a middle position, namely in an unloading state.
The working condition I is as follows: retracting the piston rod of the hydraulic cylinder
At this time, when the reversing main valve element of the functional electro-hydraulic reversing valve group II 3 is at the left station, namely the left station of the functional electro-hydraulic reversing valve group II 3 in FIG. 8 is connected into the oil path, at this time, the oil path leading to the rear valve group on the neutral unloading channel 17 of the O-shaped functional electro-hydraulic reversing valve group 3 is cut off, and at this time, the fast electro-hydraulic reversing valve 5 is in the original state shown in FIG. 8, and at this time, the working oil path Ka33 is communicated with the working oil path Kc through the reversing main valve element of the fast electro-hydraulic reversing valve 5.
The reversing main valve core 25 of the O-shaped electro-hydraulic reversing valve group 3 is positioned at a left station, oil enters from a port P, the oil enters into an oil inlet channel 16 of the O-shaped electro-hydraulic reversing valve group 3, then enters into a working oil channel A3 through the guiding of the reversing main valve core 25, a working oil port A3 is sealed, so the oil in the working oil channel A3 enters into a working oil channel Aa29 communicated with the oil channel A29, the working oil channel Aa29 is communicated with a working oil channel Ha31 on the differential confluence valve group, the oil in the working oil channel Aa29 flows into a working oil channel Ka33 of the rapid electro-hydraulic reversing valve group 5 through the working oil channel Ha31, then flows into a working oil channel Kc through a valve cavity of the rapid electro-hydraulic reversing valve group 5, then flows into a working oil channel Hc32 of the differential confluence valve group 4, and finally flows into a working oil port A4 through the working oil channel Hc32, and particularly the working oil port A4 outputs pressure oil to an execution, preferably working in the rod chambers of the hydraulic cylinders. And meanwhile, the return oil of the rodless cavity of the hydraulic cylinder flows to an oil return port T from a working oil port B3, an oil return channel of the functional electro-hydraulic reversing valve group II 3 and the common oil return channel 18, so that the return oil enters the oil tank, and at the moment, an actuating element, namely a piston rod of the hydraulic cylinder, generates contraction motion.
Working conditions are as follows: by extending the piston rod of a hydraulic cylinder
At this time, when the reversing main valve element of the functional electro-hydraulic reversing valve group II 3 is located at the right station, namely the right station of the functional electro-hydraulic reversing valve group II 3 in FIG. 8 is connected into the oil way, the oil way leading to the rear valve group on the neutral unloading channel 17 of the O-shaped functional electro-hydraulic reversing valve group 3 is cut off, the left station of the rapid electro-hydraulic reversing valve 5 is connected into the oil way, and the working oil duct Kb34 is communicated with the working oil duct Kc through the reversing main valve element of the rapid electro-hydraulic reversing valve 5.
The reversing main valve core 25 of the O-shaped functional electro-hydraulic reversing valve group 3 is positioned at a left station, oil enters from a port P, enters into an oil inlet channel 16 of the O-shaped functional electro-hydraulic reversing valve group 3, then enters into a working oil channel B3 through the guiding of the reversing main valve core 25, enters into an execution element through a working oil channel B3, specifically enters into a rodless cavity of a hydraulic cylinder, works, pushes a piston of the hydraulic cylinder, and extends out the piston rod. The piston sends oil with a rod cavity into a working oil passage Hc through a working oil port A4, then the oil enters a valve cavity of the rapid electro-hydraulic directional control valve 5 through a working oil passage Kc, then the oil enters a working oil passage Bb28 after passing through the working oil passage Kb34 and a working oil passage Hb30, and finally the oil enters a working oil passage B3, and the oil enters a rodless cavity of the hydraulic cylinder along with the oil in the original working oil passage B3, so that the oil discharged by the hydraulic cylinder is converged into an oil passage of liquid inlet, and the differential converging function of the multi-path electro-hydraulic valve is realized.
At the moment, the unloaded oil in the rod cavity of the hydraulic cylinder enters the rodless cavity of the hydraulic cylinder together with the oil from the port P in the working oil passage B3 to push the piston rod to extend outwards, and the stress area of the rodless cavity of the hydraulic cylinder is larger than that of the rod cavity of the hydraulic cylinder, so that the piston rod of the hydraulic cylinder continues to extend out and differential speed-increasing motion is realized under the condition of equal pressure values. The differential flow rate increase value is the ratio of the stress area of the rod cavity to the stress area of the rodless cavity, and the effective working thrust of the rodless cavity is (the stress area of the rodless cavity-the stress area of the rod cavity) multiplied by the working pressure Mpa.
In conclusion, the invention solves the defects of large volume, complex integrated block design, high cost, more pipeline connections, inconvenient maintenance and the like caused by the differential confluence structural form of the electromagnetic electro-hydraulic valve group and the integrated block which is usually adopted. In the multi-path electro-hydraulic valve with the differential confluence function, the valve group for forming the differential confluence function has a simple structure, and is integrated with the multi-path electro-hydraulic valve into a whole, so that the multi-path electro-hydraulic valve can realize the differential confluence function on a specific oil path, and the control function of the multi-path electro-hydraulic valve is further perfected; the multi-channel electro-hydraulic valve designed by the invention has small volume, only a plurality of valve groups are added, the oil passage in each valve group is utilized to realize the confluence function of pressure oil, the structure is simple, the maintenance is convenient, and the manufacturing and maintenance cost is reduced.
Example 2
The embodiment is based on embodiment 1, and explains the station control of the reversing main valve element of the electro-hydraulic reversing valve group.
As shown in fig. 8, in the present invention, the positions of the reversing main valve cores 25 of the functional electro-hydraulic reversing valve group i 2, the functional electro-hydraulic reversing valve group ii 3 and the fast electro-hydraulic reversing valve group 5 are controlled by an electro-hydraulic control system, the electro-hydraulic control system includes a flow dividing sequence valve 7 and a plurality of reversing control assemblies respectively fixed on the lower side of the valve body of one electro-hydraulic reversing valve group, the reversing control assemblies include a pilot electromagnetic valve and a pilot oil cylinder 26, the ends of the piston rods of the pilot oil cylinders 26 are coaxially connected with one end of the reversing main valve core 25 of the corresponding electro-hydraulic reversing valve group, the flow dividing sequence valve 7 is disposed in the oil inlet channel of the oil inlet flow dividing valve group 1, the liquid inlet port and the main liquid outlet port of the flow dividing valve group are respectively communicated with the main oil inlet channel and the oil inlet, The split oil passage on the side surface of each electro-hydraulic reversing valve group is communicated with the valve cavity of each pilot electromagnetic valve;
the reversing of the spool of the pilot solenoid valve can be controlled by controlling the electrification and the outage of the electromagnet of the pilot solenoid valve, and further the movement direction of the piston rod of the pilot oil cylinder 26 is controlled, so that the station of the main spool 25 is controlled to be reversed.
When oil entering from the port P enters the flow dividing sequence valve 7, a small part of pressure oil enters a working chamber of the corresponding pilot oil cylinder through the auxiliary liquid outlet port of the pressure-reducing throttling auxiliary oil passage in the flow dividing sequence valve 7, the pilot oil passage and the corresponding pilot electromagnetic valve to apply work so as to control the piston rod of the pilot oil cylinder to extend or retract, and thus, the station of the reversing main valve cores 25 of the electro-hydraulic reversing valve groups is adjusted. After the pilot pressure is formed in the pilot oil passage, a part of pressure oil is output through the auxiliary oil passage and opens the main oil passage sealed inside the flow dividing sequence valve 7 through the control oil passage 38 inside the flow dividing sequence valve 7, so that the main oil passage is communicated with the oil inlet passage 16 of the oil inlet flow dividing valve group 1, and oil is fed into a subsequent valve group.
The pilot electromagnetic valve arranged below the functional electro-hydraulic reversing valve group is a first pilot electromagnetic valve 23 which is a three-position four-way electromagnetic valve, and the pilot electromagnetic valve arranged below the rapid electro-hydraulic reversing valve group is a second pilot electromagnetic valve 24 which is a two-position four-way electromagnetic valve. The quick electro-hydraulic reversing valve group is of a two-position six-way structure, so that the corresponding installation of a two-position four-way electromagnetic valve can complete related control operation; the functional electro-hydraulic reversing valve group is of a three-position six-way structure, so that the corresponding three-dimensional four-way electromagnetic valve can complete related control operation.
Preferably, a pilot relief valve 9 is connected to the pilot oil passage 25. The starting pressure of the pilot overflow valve 9 can be adjusted, so that the pressure value of the pressure oil received by each pilot electromagnetic valve is controlled, and the requirements of all working conditions are met. Specifically, the oil pressure of the pressure oil required by the pilot solenoid valve is 1.5-2.5MPa conventionally, and the working oil pressure required by each valve bank is not more than 31.5MPa, because the starting oil pressure of the pilot overflow valve 9 can be adjusted no matter how the oil pressure of the pressure oil required by each valve bank is increased, the pressure stability of the pressure oil required by the pilot solenoid valve is ensured, and the influence of the oil pressure entering from the P port is avoided.
Firstly, controlling the electrification and the outage of an electromagnet of a pilot solenoid valve according to the direction in which a reversing main valve element 25 of each electro-hydraulic reversing valve group needs to move, for example, when the reversing main valve element 25 needs to move rightwards, a piston rod of a corresponding pilot oil cylinder 26 needs to extend outwards to push the reversing main valve element 25 to move rightwards, so that a rodless cavity of the pilot oil cylinder 26, namely a left cavity shown in fig. 8 needs to be filled with pressure oil, in order to fill the left cavity with the pressure oil, a pilot oil duct 35 needs to be communicated with the left cavity through the pilot solenoid valve, therefore, the left end of the pilot solenoid valve needs to be electrified, the valve element of the pilot solenoid valve needs to move rightwards, and therefore, the pilot oil duct 35 is communicated with the left cavity of the pilot oil cylinder, the piston; on the contrary, when the reversing main valve element 25 needs to be moved leftward, the right end of the pilot solenoid valve needs to be electrified, and the valve element of the pilot solenoid valve moves leftward, so that the pilot oil duct 35 is communicated with the right cavity, the piston rod of the pilot oil cylinder retracts, and the reversing main valve element correspondingly moves leftward.
As shown in fig. 8, the left side in fig. 8 is an unloading end communicated with the oil return port T, and the right side is an oil inlet end communicated with the oil inlet P; then pumping pressure oil from a main oil inlet P port through an oil pump, firstly shunting a small amount of pressure oil by a shunting sequence valve 7, and feeding the small amount of pressure oil shunted by the shunting sequence valve 7 into a pilot oil duct, wherein the pressure oil is defined as pilot control oil, the flow rate of the pressure oil is low, and the flow rate is mainly controlled to be 1-2L/min; the pilot control oil respectively enters the functional electro-hydraulic reversing valve group and the shunt oil passage on the side face of the rapid electro-hydraulic reversing valve group 5 through the pilot oil passage 35, and then simultaneously enters the oil inlet passage of the pilot electromagnetic valve, the oil inlet passage of the pilot electromagnetic valve is defined as a pilot oil passage 19, specifically, the shunt oil passage on the side face of the functional electro-hydraulic reversing valve group enters the pilot oil passage 19 of the pilot electromagnetic valve fixed on the lower side of the valve body of the functional electro-hydraulic reversing valve group, and the shunt oil passage on the side face of the rapid electro-hydraulic reversing valve group 5 enters the pilot oil passage 19 of the pilot electromagnetic valve; on the basis of controlling the reversing of the valve core of the pilot electromagnetic valve by combining the power-on and power-off of an electromagnet controlling the pilot electromagnetic valve, hydraulic oil is introduced into a chamber corresponding to the pilot oil cylinder 26 through the pilot electromagnetic valve, so that the movement direction of a piston rod of the pilot oil cylinder 26 coaxially connected with the reversing main valve cores 25 of all the electro-hydraulic reversing valve groups is controlled, the reversing main valve cores are driven to required stations, and the adjustment of the stations of the valve cores of all the electro-hydraulic reversing valve groups is completed.
Meanwhile, after the pilot pressure is formed in the pilot oil duct 35, a part of pressure oil which is split by the split sequence valve 7 is used as control oil of an internal overflow valve, and is communicated with a control oil duct of a split valve core in the split sequence valve 7 through a control oil duct 36, so that a main oil path in the split sequence valve 7 is in a passage state, and main flow pressure oil which enters from a port P and is split enters the functional electro-hydraulic directional valve set and a subsequent valve set to perform related operations.
In the invention, the flow dividing sequence valve 7 is arranged between the main oil inlet path and the oil inlet channel 16 of the oil inlet flow dividing valve group 1, so that the working position of a piston rod of a pilot oil cylinder is firstly adjusted through pilot control oil, and then the reversing main valve cores 25 of all electro-hydraulic reversing valve groups are adjusted to move to the required working position, thereby preparing for the relevant control operation of all multi-path electro-hydraulic valves; after preparation, the closed main oil path inside the flow dividing sequence valve 7 is opened through the control oil duct 36, so that the main oil inlet path is communicated with the oil inlet channel of the oil inlet flow dividing valve group 1, and the divided main flow is sent to each valve group for relevant control operation.
Set up reposition of redundant personnel sequence valve 7 between the oil feed passageway of main oil inlet way and oil feed reposition of redundant personnel valves 1, guaranteed before the required station is adjusted to the switching-over main valve core 25 of each valves, the inside obstructed pressure oil that goes into of each valves, guaranteed the stability of multichannel electricity liquid valves work then.
In summary, in the present invention, the pressure oil of the electro-hydraulic control system for controlling the station where the reversing main valve element 25 of the functional electro-hydraulic reversing valve group and the fast electro-hydraulic reversing valve group 5 are located comes from the oil of the main oil inlet P, so that the structure of the electro-hydraulic control system is simplified, the working state of the pilot oil cylinder can be controlled by the pressure oil pumped by the oil pump of the valve group, an additional oil pump for the electro-hydraulic control system is not needed, the control mode and the number of components of the electro-hydraulic control system are simplified, and the length of the oil passage of the electro-hydraulic control system is shortened, thereby reducing the volume of the multi-path electro-hydraulic valve, reducing the manufacturing and installation cost, and facilitating the later maintenance. Meanwhile, in the invention, the flow dividing sequence valve 7 arranged between the main oil inlet path and the oil inlet channel of the oil inlet flow dividing valve group 1 is used for ensuring that the main oil inlet path is communicated with the oil inlet channel of the oil inlet flow dividing valve group 1 only by the flow dividing sequence valve 7 after the piston rods of the oil cylinders are driven in place, namely the reversing main valve cores 25 of the valve groups move in place, and the oil can be fed into the valve groups, thereby ensuring the working stability of the invention after the structure of the electro-hydraulic control system is simplified.
Example 3
The present embodiment is further described with reference to embodiment 2.
As shown in fig. 8, the reversing control assembly of the present invention further includes a return spring for moving the reversing main spool 25 to the neutral position when both chambers of the pilot cylinder are in the unloaded state.
The return spring is a spiral cylindrical compression spring, and the telescopic direction of the return spring is parallel to the axis of the pilot oil cylinder 26.
The neutral position of the reversing main valve element 25 is the state that each valve group does not work, namely the position that the port P is communicated with the oil tank through each valve group.
The reset spring can be directly arranged on the outer side of the pilot oil cylinder 26, one end of the reset spring is fixed on the valve body, and the other end of the reset spring is connected with a piston rod of the pilot oil cylinder 26 or the reversing main valve core 25; the return spring can also be arranged in a left cavity or a right cavity of the pilot oil cylinder 26, one end of the return spring is connected with the end part of the cylinder body of the pilot oil cylinder, the other end of the return spring is connected with the piston, and the restoring force of the stretched return spring is utilized to drive the reversing main valve core to move to the neutral position; the return spring can also be fixed directly in the chamber, with one end connected to the end of the piston or cylinder and the other end in a free state, using the return force of the return spring after it has been compressed to move the reversing main valve 25 to the neutral position.
When the oil paths of the two cavities of the pilot oil cylinder 26 are communicated with the oil tank through the pilot electromagnetic valve, namely, when the two cavities of the pilot oil cylinder 26 are in an unloading state, the oil does not work on the piston, and the reversing main valve element 25 returns to the neutral position under the action of the restoring force of the compressed or stretched return spring to prepare for the next operation of the multi-path electro-hydraulic valve.
The arrangement of the return spring can simplify the operation of returning the reversing main valve element 25 to the neutral position, does not need to pump pressure oil for a pilot oil cylinder additionally, and directly utilizes the energy urgently needed by the deformation of the return spring caused by moving the reversing valve main valve element 25 in the previous step to reset the reversing main valve element 25 to the neutral position, thereby further simplifying the electro-hydraulic control system, improving the control reliability, reducing the manufacturing cost and facilitating the maintenance; meanwhile, when the two cavities of the pilot oil cylinder 26 are in an unloading state, the main valve element 25 is reset through the reset spring, and the working stability is ensured.
Example 4
This embodiment is further explained by the control of the main spool 25 based on embodiment 2.
As shown in fig. 1 to 8, in the present invention, the other end of the reversing main valve 25 of the electro-hydraulic reversing valve set is connected to a handle lever 27 for manually operating the station where the reversing main valve 25 is located.
The handle rod 27 is used for manual operation or fault removal in the event of an electrical control fault, and particularly, when a pilot control oil path has a fault, the externally connected handle rod can be operated to realize the reversing function of the valve bank.
In the invention, the reversing of the reversing main valve cores 25 of all the valve groups is realized by an electro-hydraulic control system, and the reversing of the reversing main valve cores 25 of all the valve groups can be realized by manually operating the handle rod, so that the application environment of the invention is improved, and the later maintenance, overhaul and the like are facilitated; in addition, the invention integrates the differential confluence function and the manual and electric control, improves the reliability and the feedback sensitivity of the hydraulic system, and reduces the configuration cost of the system.
Example 5
The present embodiment is described with respect to the fixation of the valve body of each valve block.
In the invention, as shown in fig. 1, the valve bodies of the valve groups are connected through a connecting assembly, the connecting mechanism comprises a double-headed screw 12, a nut 13 and a gasket, connecting holes corresponding to each other are formed in the valve bodies of the oil inlet flow dividing valve group 1, the electro-hydraulic reversing valve group I2, the electro-hydraulic reversing valve group II 3, the differential confluence valve group 4, the fast electro-hydraulic reversing valve group 5 and the oil return valve group 6, one end of the double-headed screw 12 sequentially penetrates through each connecting hole and one gasket and then is screwed with one nut 13, and the other end of the double-headed screw 12 penetrates through the other gasket and then is in threaded connection with.
Furthermore, four connecting holes are formed in the valve body of each valve group, the connecting holes in two adjacent valve bodies are in one-to-one correspondence, and the connecting mechanisms are provided with four groups.
The connecting mechanism can also adopt a clamping device and the like, and the specific embodiment is not limited.
The connecting mechanism designed by the invention is convenient for disassembling and assembling each valve group, is convenient for early-stage installation and later-stage maintenance, improves the maintenance convenience and reduces the maintenance cost.
Example 6
As shown in fig. 8, a main overflow valve 11 is connected to the oil return channel of the oil inlet flow distribution valve bank 1, and when the working pressure or hydraulic impact pressure of the subsequent reversing valve bank is greater than the set pressure value of the main overflow valve 11, the main overflow valve 11 is opened, so that pressure unloading is directly performed, and impact damage to a hydraulic system when the oil pressure is too large is prevented.
And check valves 8 are arranged in oil inlet channels 16 of the electro-hydraulic reversing valve group.
The functional electro-hydraulic reversing valve group II 3 is an O-shaped functional electro-hydraulic reversing valve group 3, and the functional electro-hydraulic reversing valve group I is a Y-shaped functional electro-hydraulic reversing valve group 2.
Each pilot electromagnetic valve [23, 24] is internally provided with a pilot oil inlet channel 19, a pilot oil return channel 20, a pilot reversing oil channel 21 and a pilot reversing channel 22. One part of oil entering from the port P passes through a small amount of pressure oil at the shunting position of a shunting sequence valve 7 inserted in the oil inlet shunting valve bank 1 to be used as pilot oil (for example, the pilot flow is 2L/min), simultaneously enters a pilot oil inlet channel 19 of pilot electromagnetic valves [23, 24] arranged at the lower part of the valve bank through shunting oil channels on the side surfaces of the electro-hydraulic reversing valve banks [2, 3, 5], and can realize the reversing of the pilot electromagnetic valve cores by controlling the electrification and the outage of electromagnets of the pilot electromagnetic valves [23, 24], thereby controlling the movement direction of a pilot oil cylinder 26 coaxially connected with the main valve cores 25 of the electro-hydraulic reversing valve banks. The return oil of the pilot oil cylinder 26 returns to the common oil return channel 18 through the pilot oil return channels 20 of the pilot electromagnetic valves [23 and 24] to form a complete pilot control oil path. (pilot pressure is 1.5-2.5 Mpa); the oil entering from the P port enters an oil inlet channel 16 of the electro-hydraulic reversing valve banks [2, 3] adopting parallel oil paths and a middle unloading channel 17 of the electro-hydraulic reversing valve banks [2, 3, 5] adopting serial oil paths and the differential confluence valve bank 4 after the residual main flow is divided by the dividing sequence valve 7 and passes through a liquid inlet port of the dividing sequence valve 7. The working oil path of the main valve core 25 can be switched by controlling the reversing of the pilot oil cylinder 26, so that the pressure oil of the main flow enters each executing element to do work. The working pressure of the main oil circuit of the hydraulic system can be changed by adjusting the main overflow valve 11 inserted in the oil inlet flow dividing valve group 1.
According to the invention, the control oil path of the auxiliary valve jack, the main reversing valve hole and the electromagnetic pilot valve of the electro-hydraulic reversing valve group is divided into an upper layer, a middle layer, a lower layer and a4 layer integrated design, and the manual control mechanism, the main reversing valve core and the piston rod of the pilot oil cylinder are designed into a coaxial connecting body, so that the structure is more compact, the oil path of the valve body is more optimized, and the auxiliary valve is more convenient to combine. The nominal drift diameter of flashlight liquid integrated valve has: 15mm, 18mm and 22mm, and the nominal flow rates are respectively as follows: 80L/min, 120L/min, 200L/min, nominal pressure: 31.5MPa, pilot flow of 1-2L/min and pilot control pressure of 1.5-2.5 MPa.
In the invention, the Y-shaped electro-hydraulic reversing valve group 2 is provided with two working output ports, namely a working oil port A2 and a working oil port B2, and an overload valve 10 is inserted in an oil way communicated with the working oil port A2 and the working oil port B2; the O-shaped electro-hydraulic reversing valve group 3 is provided with two working output ports, namely a working oil port A3 and a working oil port B3, and the working oil port A3 is closed; the differential confluence valve group 4 is provided with a working output which is a working oil port A4; the quick electro-hydraulic reversing valve group 5 is provided with two working output ports, namely a working oil port A5 and a working oil port B5, which are closed. The pilot cylinder 26 corresponding to each electro-hydraulic directional valve block [2, 3, 5] is preferably mounted in the end cap of the corresponding valve block, as shown in fig. 3.
Regarding the electro-hydraulic reversing valve group 3 of the O-shaped function: as shown in fig. 8, an external working oil port A3 of the "O" type functional electro-hydraulic directional valve set 3 is closed, and a working oil passage A3 communicated with the working oil port A3 is communicated with a working oil passage Ha31 of the differential confluence valve set 4 through a working oil passage Aa29 on the side surface of the valve body; a working oil passage B3 communicated with the working oil port B3 is communicated with a working oil passage Hb30 of the differential confluence valve group 4 through a working oil passage Bb28 on the side surface of the valve body; an overload valve 10 and a pressure relay II 15 are inserted into an oil cavity of the working oil port B3, and another overload valve 10 is inserted into an oil cavity A3; the working oil port B3 is connected with the components required to be operated and controlled by the invention, namely is communicated with the rodless cavity of the hydraulic cylinder.
Regarding the differential confluence valve group 4: as shown in fig. 8, the other side surface of the valve body of the differential confluence valve group 4 is respectively communicated with a working oil passage Ka33 and a working oil passage Kb34 corresponding to the valve body of the fast electro-hydraulic directional valve group 5 through a working oil passage Ha31 and a working oil passage Hb30 which penetrate through the valve body, and a working oil port a4 communicated with the valve cavity of the differential confluence valve group 4 is arranged at the upper part of the valve body of the differential confluence valve group.
Regarding the fast electro-hydraulic directional valve set 5: as shown in fig. 8, the working oil port a5 and the working oil port B5 of the quick electro-hydraulic directional valve group 5 are closed, and a pressure relay i 14 is inserted into a differential oil path communicated with the working oil port B5.
The working principle of each electro-hydraulic reversing valve group is as follows:
one and Y-shaped function electro-hydraulic reversing valve group 2
Reverse main spool 25 to move leftward
A power supply at the right end of a pilot electromagnetic valve 23 arranged on a valve body of the Y-shaped electro-hydraulic reversing valve group 2 is connected, a valve core of the pilot electromagnetic valve 23 moves to the left, oil enters from a main oil inlet P, a small amount of pressure oil is firstly branched by a flow-dividing sequence valve 7 to serve as pilot control oil, the pilot control oil firstly enters a flow-dividing oil passage on the side surface of the Y-shaped electro-hydraulic reversing valve group 2 through a pilot oil passage 35, then flows out of the flow-dividing oil passage and enters a right cavity of a pilot oil cylinder 26 positioned in an end cover of the electro-hydraulic reversing valve group 2 through a pilot reversing channel 22 of the pilot electromagnetic valve 23 to push a piston of the pilot oil cylinder 26 to move to the left, a reversing main valve core 25 coaxially connected with the piston rod moves synchronously along with the piston rod, the reversing main valve core 25 moves to the left, and.
The return oil in the left cavity of the pilot oil cylinder 26 sequentially enters the common oil return passage 18 from the pilot reversing oil passage 21 of the pilot electromagnetic valve 23, the internal oil return passage of the pilot electromagnetic valve 23 and the pilot oil return passage 20 of the pilot electromagnetic valve 23, and finally returns to the oil tank through the common oil return passage 18.
At this time, the residual main flow after being split by the split sequence valve 7 entering from the oil inlet split valve set 1 enters the oil inlet channel 16 of the "Y" type electro-hydraulic directional valve set 2, then the check valve 8 installed in the oil inlet channel 16 is opened, then the return oil enters one cavity of the execution element from the working oil port a2 through the opening between the main valve core 25 and the main valve hole of the "Y" type electro-hydraulic directional valve set 2 to do work, the return oil of the other cavity of the execution element returns to the common oil return channel 18 through the working oil port B2, and finally returns to the oil tank.
(II) reverse main spool 25 to move rightwards
The left end power supply of a pilot electromagnetic valve 23 arranged on a valve body of the Y-shaped functional electro-hydraulic directional valve group 2 is switched on, a valve core of the pilot electromagnetic valve 23 moves to the right, pilot control oil enters a left cavity of a pilot oil cylinder 26 through a pilot directional oil passage 22 of the pilot electromagnetic valve 23, a piston of the pilot oil cylinder 26 is pushed to move to the right, a directional main valve core 25 coaxially connected with the piston rod moves synchronously along with the piston rod, the directional main valve core 25 moves to the left in place, and at the moment, an oil way leading to a rear valve group on a neutral unloading passage 17 of the Y-shaped functional electro-hydraulic directional valve group 2.
The return oil in the right chamber of the pilot oil cylinder 26 returns to the oil tank from the pilot reversing channel 21 of the pilot electromagnetic valve 23, the internal oil return channel of the pilot electromagnetic valve 23, the pilot oil return channel 20 and the common oil return channel 18 in sequence.
At this time, after the residual main flow which enters from the oil inlet flow distribution valve bank 1 and is divided by the flow distribution sequence valve 7 enters the oil inlet channel 16 of the Y-shaped functional electro-hydraulic reversing valve bank 2, the check valve 8 arranged in the valve body is opened, enters one cavity of the executing element from the oil port B2 through the opening between the reversing main valve core 25 and the main valve hole for doing work, and the return oil of the other cavity of the executing element returns to the oil tank through the oil port A2 to the public return oil channel 18.
(III) automatic Return of main spool 25
When the two ends of the pilot electromagnetic valve 23 integrated at the lower part of the "Y" type electro-hydraulic directional valve set 2 are powered off, and the spool of the pilot electromagnetic valve 23 is at the neutral position as shown in fig. 8, the oil inlet p of the pilot electromagnetic valve 23 is closed, and the oil passages leading to the two cavities of the pilot oil cylinder 26 are both communicated with the pilot oil return passage 20 and are in the unloading state. Because no pressure oil is applied to the two cavities of the pilot oil cylinder 26, the deformed return spring starts to act due to the movement of the reversing main valve element 25, the reversing main valve element 25 returns to the neutral position under the restoring force action of the return spring, as shown in fig. 8, the oil inlet channel 16 is closed, the working oil ports a2 and B2 which are communicated with the working cavities at the two ends of the execution element are communicated with the common oil return channel 18 through the inner flow channel of the reversing main valve element 25 to unload, at the moment, the two working cavities of the execution element are both in an unloading working condition, and the execution element is in a floating state; the overload valve 10 inserted in the oil passage communicated with the working oil port A2 and the working oil port B2 is adjusted, so that pressure overload protection can be realized or the working pressure of an output oil passage can be adjusted, and the overload protection oil passage is used for preventing the pressure of the oil passage from being overloaded or adjusting the working pressure required by different execution elements; it is not necessary to insert the overload valve 10 when this function is not required.
When the pilot control oil path is in failure, the handle rod 27 connected with the outside of the Y-shaped functional electro-hydraulic reversing valve bank 2 is operated to realize the normal reversing function of the valve bank.
Two and O-shaped functional electro-hydraulic reversing valve group 3
An external working oil port A3 of the O-shaped functional electro-hydraulic reversing valve group 3 is closed, and a working oil passage Aa29 and a working oil passage Bb28 on the side surface of the valve body are respectively communicated with a working oil passage Ha31 and a working oil passage Hb30 on the adjacent side surface of the differential confluence valve group 4.
Reverse main spool 25 to move leftward
A power supply at the right end of a pilot electromagnetic valve 23 arranged on a valve body of the O-shaped functional electro-hydraulic reversing valve group 3 is switched on, a valve core of the pilot electromagnetic valve 23 moves to the left, pilot control oil enters a right cavity of a pilot oil cylinder 26 positioned in an end cover of the O-shaped functional electro-hydraulic reversing valve group 3 after passing through a pilot oil duct and a pilot reversing channel 22 of the pilot electromagnetic valve 23, so that a piston of the pilot oil cylinder 26 is pushed to move to the left, a reversing main valve core 25 coaxially connected with the piston rod moves synchronously along with the piston rod, the reversing main valve core 25 moves to the left in place, and at the moment, an oil path leading to a rear valve group on a neutral unloading channel 17 of the.
The return oil in the left cavity of the pilot oil cylinder 26 returns to the oil tank through the common oil return passage 18 from the pilot reversing passage 22 of the pilot electromagnetic valve 23, the internal oil return passage of the pilot electromagnetic valve 23 and the pilot oil return passage 20 of the pilot electromagnetic valve 23 in sequence.
Because the reversing main valve core 25 of the O-shaped functional electro-hydraulic reversing valve group 3 is positioned at the left station, oil enters from a port P, enters the oil flow dividing valve group 1, the residual main flow after being divided by the flow dividing sequence valve 7 flows into the oil inlet channel 16 of the O-shaped functional electro-hydraulic reversing valve group 3, the check valve 8 arranged in the oil inlet channel 16 is opened, and then enters the oil channel A3 through the guidance of the reversing main valve core 25, the working oil port A3 is closed, so that the oil in the working oil channel A3 enters the working oil channel Aa29 communicated with the working oil channel Aa29, the working oil channel Aa29 is communicated with the working oil channel Ha31 on the differential confluence valve group, the oil in the working oil channel Aa29 flows into the working oil channel Ka33 of the rapid electro-hydraulic reversing valve group 5 through the working oil channel Ha31, then flows into the working oil channel Kc of the rapid electro-hydraulic reversing valve group 5, and then flows into the working oil channel Hc32 of the differential confluence valve group 4, and finally, the pressure oil flows into a working oil port A4 through a working oil passage Hc32, and specifically, the working oil port A4 outputs the pressure oil to an actuating element, namely, a rod cavity of the hydraulic cylinder does work. Meanwhile, the return oil of the rodless cavity of the hydraulic cylinder flows to an oil return port T from a working oil port B3, an oil return channel of the O-shaped functional electro-hydraulic reversing valve group 3 and the common oil return channel 18, so that the return oil enters the oil tank, and at the moment, an actuating element, namely a piston rod of the hydraulic cylinder, generates contraction motion.
(II) reverse main spool 25 to move rightwards
The left end power supply of a pilot electromagnetic valve 23 arranged on a valve body of the O-shaped functional electro-hydraulic reversing valve group 3 is switched on, a valve core of the pilot electromagnetic valve 23 moves to the right, pilot control oil enters a left cavity of a pilot oil cylinder 26 positioned in an end cover of the O-shaped functional electro-hydraulic reversing valve group 3 after passing through a pilot oil duct and a pilot reversing channel 22 of the pilot electromagnetic valve 23, so that a piston of the pilot oil cylinder 26 is pushed to move to the right, a reversing main valve core 25 coaxially connected with the piston rod moves synchronously along with the piston rod, the reversing main valve core 25 moves to the right in place, and at the moment, an oil path leading to a rear valve group on a neutral unloading channel 17 of the O-shaped.
The return oil in the right cavity of the pilot oil cylinder 26 returns to the oil tank through the common oil return passage 18 from the pilot reversing passage 22 of the pilot electromagnetic valve 23, the internal oil return passage of the pilot electromagnetic valve 23 and the pilot oil return passage 20 of the pilot electromagnetic valve 23 in sequence.
Because the reversing main valve core 25 of the O-shaped functional electro-hydraulic reversing valve group 3 is positioned at the right station, oil enters from the P port, enters into the oil distribution valve group 1, flows into the oil inlet channel 16 of the O-shaped functional electro-hydraulic reversing valve group 3 through the main flow left after being distributed by the distribution sequence valve 7, opens the check valve 8 arranged in the oil inlet channel 16, then enters into the oil channel of the working oil port B3 through the guidance of the reversing main valve core 25, and enters into the rodless cavity of the hydraulic cylinder of the executing element from the working oil port B3 to do work. Meanwhile, the return oil of the rod cavity of the hydraulic cylinder of the actuating element sequentially enters a working oil port A4, a working oil passage Hc32, a working oil passage Kc of the rapid electro-hydraulic directional valve group 5, a main directional valve core of the rapid electro-hydraulic directional valve group 5, a working oil passage Kb34, a working oil passage Hb30 and a working oil passage Bb28 of the differential confluence valve group 4, finally enters a working oil passage B3, and enters the rodless cavity of the oil cylinder along with the oil in the original working oil passage B3, so that the oil discharged from the oil cylinder is converged into the oil passage of the inlet liquid, and the differential confluence function of the multi-path electro-hydraulic valve is realized.
(III) automatic Return of main spool 25
When two ends of a pilot electromagnetic valve 23 integrated at the lower part of the O-shaped functional electro-hydraulic directional valve group 3 are powered off, an electromagnetic valve core is in a neutral position. At this time, the oil inlet of the pilot electromagnetic valve 23 is closed, and the oil passages leading to the two cavities of the pilot oil cylinder 26 are communicated with the pilot oil return passage 20 and are in an unloading state. Because no pressure oil is applied to the two cavities of the pilot cylinder 26, the return spring deformed due to the movement of the reversing main valve element 25 starts to act, the reversing main valve element 25 returns to the neutral position under the restoring force of the return spring, as shown in fig. 8, the oil inlet passage 16 is closed, the working oil port a3 and the working oil port B3 are both cut off by the reversing main valve element 25 and are not communicated with the oil return port T, and the hydraulic cylinder is in a static state.
The overload valves 10 inserted in the oil cavities A3 and B3 are respectively adjusted, so that pressure overload protection can be realized or the working pressure of an output oil way can be adjusted. When this function is not required, it is not necessary to insert an overload valve.
And the pressure relay II 15 inserted in the B3 oil way of the electro-hydraulic reversing valve group 3 is used for outputting a signal to reverse the electro-hydraulic reversing valve group 3 after the set highest working pressure is reached, so that the hydraulic pump station stops working after the hydraulic cylinder returns to the initial working position. When this function is not required or other control methods are used, it is not necessary to plug in the pressure relay ii 15.
When the pilot control oil path is in failure, the handle rod 27 connected externally is operated to realize the normal reversing function of the valve group.
Three, differential confluence valve group 4
The differential confluence valve group 4 is combined between the O-shaped functional electro-hydraulic reversing valve group 3 and the rapid electro-hydraulic reversing valve group 6, a working oil passage Hc32 of the differential confluence valve group is communicated with a main oil inlet passage, namely a working oil passage Kc, on the adjacent side surface of the rapid electro-hydraulic reversing valve group 5 except that the communication of a flow passage with the O-shaped functional electro-hydraulic reversing valve group 3 is realized, and the upper part of the valve body is provided with an external oil port A4 which is used for connecting a rodless cavity of a hydraulic cylinder of an executing element.
The actuator is an element operated by the present invention, and is usually a hydraulic cylinder.
Four, quick electro-hydraulic reversing valve group 5
The quick electro-hydraulic reversing valve group 5 is preferably a C-shaped quick electro-hydraulic reversing valve group. The C-shaped rapid electro-hydraulic reversing valve group 5 is a two-position six-way reversing valve group, a two-position four-way pilot solenoid valve 24 is arranged at the lower part of the valve group, and the valve group has only two working positions.
When the valve group is in a neutral position, the reversing function of the front end electro-hydraulic reversing valve group 3 is not changed, only a working channel of oil is provided, and the pushing oil cylinder is in a normal working speed state; when an electromagnet power supply at the left end of the pilot electromagnetic valve 24 of the valve group is switched on, the valve core of the pilot electromagnetic valve 24 moves to the right, and pilot control oil enters a left cavity of a pilot oil cylinder 26 in the end cover of the electro-hydraulic reversing valve group 5 through a pilot oil passage and a pilot reversing passage 22 to push a reversing main valve core 25 to move to the right. In the oil cylinder of the actuating element connected with the working oil port a4, return oil of a rod cavity of the oil cylinder enters a working oil passage Hc32 from the working oil port a4 of the differential confluence valve group 4, then enters a working oil passage Kc, a valve cavity of the rapid electro-hydraulic directional valve 5, a working oil passage Kb34, a working oil passage Hb30 of the differential confluence valve group 4, then enters a working oil passage Bb of the "O" -type functional electro-hydraulic directional valve group 3, and then enters a rodless cavity of the oil cylinder together with pressure oil which is originally led to the oil port B3 of the O "-type functional electro-hydraulic directional valve group 3 in a confluence manner so as to realize a confluence function.
The pressure relay I14 arranged in the differential oil circuit of the electro-hydraulic reversing valve group 5 outputs an electric signal to cut off the power supply of the pilot electromagnetic valve 24 when the oil pressure reaches a preset value, so that the electro-hydraulic reversing valve group 5 returns to a neutral position, and at the moment, the passage of differential confluence is cut off, and the hydraulic cylinder recovers to a normal running speed.
A pressure relay can be inserted into an oil cavity of a port B5 of the two-position six-way quick electro-hydraulic reversing valve set, when the differential confluence pressure reaches a set pressure value, an electric signal is output to cut off the power supply of a pilot electromagnetic valve of the valve set, and the differential confluence function is not executed any more.
When the pilot control oil path is in failure, the handle rod 27 connected externally is operated to realize the normal reversing function of the valve group.
According to the invention, the auxiliary valve jack and the flow channel, the main reversing valve hole and the flow channel and the pilot control flow channel are designed into a multi-layer integrated structure on the same valve body, so that the valve body oil path is more optimized, the pressure loss is small, the structure is compact, and different functional valve groups are conveniently integrated. Meanwhile, auxiliary valves such as an overload valve, an oil supplementing valve, a hydraulic lock, a balance valve, a pressure sensor and the like can be inserted according to functional requirements.
When the pilot electromagnetic valve is replaced by the pressure reducing proportional electromagnetic valve, the reversing and the speed control of the main reversing valve core can be controlled through the PLC programming function, and the automatic control program of the hydraulic system is realized.
The invention organically integrates the pilot control of internal control and internal row, the electro-hydraulic and manual operation modes and the differential confluence function into a whole, and is a manual and electric hydraulic multi-path integrated valve which is exquisite, compact, high in integration level, light in operation and convenient to maintain and has a manual and electric integrated function and a differential function. The invention can realize remote or PLC (when the pilot electromagnetic valve is a pressure-reducing proportional electromagnetic valve) control of the hydraulic actuating element, and electronic devices such as a pressure sensor are connected with controllers such as the PLC and the like for transmitting working signals, thereby facilitating subsequent related operation and control operation according to programs; and when the electro-hydraulic control fails, the control requirement is realized or potential safety hazards are eliminated by adopting manual control. The invention can be widely applied to various environmental sanitation machines, packaging machines, drilling machines and the like of which the hydraulic cylinders need to move in an accelerated manner.
The above description is only a preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be made by those skilled in the art without inventive work within the technical scope of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope defined by the claims.

Claims (10)

1. The utility model provides a multichannel electro-hydraulic valve with differential confluence function, includes oil feed reposition of redundant personnel valves (1), functional electro-hydraulic reversing valve group I (2) and oil return valves (6) that connect gradually, its characterized in that: an organic function electro-hydraulic reversing valve group II (3), a differential confluence valve group (4) and a quick electro-hydraulic reversing valve group (5) are sequentially connected between the function electro-hydraulic reversing valve group and the oil return valve group (6), the function electro-hydraulic reversing valve group I (2) and the function electro-hydraulic reversing valve group II (3) are three-position six-way reversing valves, the quick electro-hydraulic reversing valve group (5) is a two-position six-way reversing valve, and an oil inlet channel (16), a middle unloading channel (17) and a public oil return channel (18) are respectively arranged in valve bodies of the oil inlet flow dividing valve group (1), the function electro-hydraulic reversing valve group I (2), the function electro-hydraulic reversing valve group II (3) and the quick electro-hydraulic reversing valve,
oil return channels of the functional electro-hydraulic reversing valve group I (2), the functional electro-hydraulic reversing valve group II (3) and the quick electro-hydraulic reversing valve group (5) are communicated with a public oil return channel (18) in parallel, and oil inlet channels (16) of the functional electro-hydraulic reversing valve group I (2) and the functional electro-hydraulic reversing valve group II (3) are communicated with an oil outlet channel of the oil inlet flow dividing valve group (1) in parallel; the functional electro-hydraulic reversing valve group I (2), the functional electro-hydraulic reversing valve group II (3) and a middle unloading channel (19) of the quick electro-hydraulic reversing valve group (5) are sequentially connected in series through a series oil way and communicated with a public oil return channel (18) in an oil return valve group (6) through the series oil way; the common oil return channel (18) is communicated with the oil tank;
two working oil ports of the functional electro-hydraulic reversing valve group II (3) are respectively a working oil port A3 and a working oil port B3, the working oil port A3 and the working oil port B3 are respectively communicated with a valve cavity of the functional electro-hydraulic reversing valve group II (3) through a working oil duct A3 and a working oil duct B3, the working oil port A3 is closed, and a working oil duct Aa (29) communicated with the working oil duct A3 and a working oil duct Bb (28) communicated with the working oil duct B3 are arranged on a valve body of the functional electro-hydraulic reversing valve group II (3);
the differential confluence valve group (4) is provided with a working oil passage Hb (30) and a working oil passage Ha (31), and a working oil port A4 and a working oil passage Hc (32) with one end communicated with a working oil port A4 are arranged on the differential confluence valve group;
the working oil ports of the rapid electro-hydraulic reversing valve group (5) are closed, a working oil passage Ka (33), a working oil passage Kb (34) and a working oil passage Kc which are communicated with the valve cavity of the rapid electro-hydraulic reversing valve group are arranged on the rapid electro-hydraulic reversing valve group, the working oil passage Ka (33) is communicated with a working oil passage Aa (29) through a working oil passage Ha (31), the working oil passage Kb (34) is communicated with a working oil passage Bb (28) through a working oil passage Hb (30), and the working oil passage Kc is communicated with a working oil passage Hc (32).
2. A multi-way electro-hydraulic valve with differential confluence function as claimed in claim 1, wherein: the work stations of reversing main valve cores (25) of the functional electro-hydraulic reversing valve group I (2), the functional electro-hydraulic reversing valve group II (3) and the quick electro-hydraulic reversing valve group (5) are controlled by an electro-hydraulic control system, the electro-hydraulic control system comprises a flow distribution sequence valve (7) and a plurality of reversing control assemblies which are respectively fixed on the lower side of a valve body of one electro-hydraulic reversing valve group, each reversing control assembly comprises a pilot electromagnetic valve and a pilot oil cylinder (26) with oil passages communicated with each other, the tail end of a piston rod of each pilot oil cylinder (26) is coaxially connected with one end of the corresponding reversing main valve core (25) of the electro-hydraulic reversing valve group, the flow distribution sequence valve (7) is arranged in an oil inlet channel of the oil inlet flow distribution valve group (1), a liquid inlet port and a main liquid outlet port of the flow distribution valve group are respectively communicated with an oil inlet channel of the main oil inlet, The split oil passage on the side surface of each electro-hydraulic reversing valve group is communicated with the valve cavity of each pilot electromagnetic valve;
the reversing of the valve core of the pilot electromagnetic valve can be controlled by controlling the electrification and the outage of the electromagnet of the pilot electromagnetic valve, so that the movement direction of the piston rod of the pilot oil cylinder (26) is controlled, and the station of the reversing main valve core (25) is controlled.
3. A multi-way electro-hydraulic valve with differential confluence function as claimed in claim 2, wherein: the reversing control assembly further comprises a return spring which is used for moving the reversing main valve core (25) to a neutral position when two cavities of the pilot oil cylinder are in an unloading state.
4. A multi-way electro-hydraulic valve with differential confluence function as claimed in claim 2, wherein: the pilot electromagnetic valve arranged below the functional electro-hydraulic reversing valve group is a first pilot electromagnetic valve (23) which is a three-position four-way electromagnetic valve, and the pilot electromagnetic valve arranged below the rapid electro-hydraulic reversing valve group is a second pilot electromagnetic valve (24) which is a two-position four-way electromagnetic valve.
5. A multi-way electro-hydraulic valve with differential confluence function as claimed in claim 2, wherein: and the other end of the reversing main valve core (25) of the electro-hydraulic reversing valve group is connected with a handle rod (27) for manually operating the station where the reversing main valve core (25) is located.
6. A multi-way electro-hydraulic valve with differential confluence function as claimed in claim 2, wherein: a pilot overflow valve (9) is connected into the pilot oil passage (25).
7. A multi-way electro-hydraulic valve with differential confluence function as claimed in claim 1, wherein: the functional electro-hydraulic reversing valve group II (3) is an O-shaped functional electro-hydraulic reversing valve group.
8. A multi-way electro-hydraulic valve with differential confluence function as claimed in claim 1, wherein: the functional electro-hydraulic reversing valve set I comprises 1-8 functional electro-hydraulic reversing valve sets, and includes but is not limited to the following models: the hydraulic reversing valve set comprises a Y-shaped functional electro-hydraulic reversing valve set, an O-shaped functional electro-hydraulic reversing valve set, a C-shaped functional electro-hydraulic reversing valve set and a K-shaped functional electro-hydraulic reversing valve set.
9. The multi-way electro-hydraulic valve with a differential confluence function according to any one of claims 1 to 8, wherein: couple together the valve body of each valves through coupling assembling, coupling mechanism includes double threaded screw (12), nut (13) and packing ring all be provided with the connecting hole that corresponds each other on the valve body of oil feed reposition of redundant personnel valves (1), electricity liquid switching-over valves I (2), electricity liquid switching-over valves II (3), differential confluence valves (4), quick electricity liquid switching-over valves (5) and oil return valves (6), the one end of double threaded screw (12) is passed in proper order behind each connecting hole and a packing ring and is screwed up with a nut (13), the other end of double threaded screw (12) pass behind another packing ring with nut (13) threaded connection.
10. A multi-way electro-hydraulic valve with differential confluence function as claimed in claim 9, wherein: every all be provided with four connecting holes on the valve body of valves, the connecting hole one-to-one on two adjacent valve bodies, just coupling mechanism has four groups.
CN202010336775.1A 2020-04-26 2020-04-26 Multi-path electro-hydraulic valve with differential confluence function Pending CN111577692A (en)

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Application Number Priority Date Filing Date Title
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Application Number Priority Date Filing Date Title
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112780628A (en) * 2021-03-03 2021-05-11 徐州威世泽机电设备有限公司 Reversing valve structure and multi-way valve
CN113175455A (en) * 2021-04-26 2021-07-27 江苏汇智高端工程机械创新中心有限公司 Multi-way valve confluence control structure of hydraulic excavator

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112780628A (en) * 2021-03-03 2021-05-11 徐州威世泽机电设备有限公司 Reversing valve structure and multi-way valve
CN113175455A (en) * 2021-04-26 2021-07-27 江苏汇智高端工程机械创新中心有限公司 Multi-way valve confluence control structure of hydraulic excavator
CN113175455B (en) * 2021-04-26 2024-04-02 江苏汇智高端工程机械创新中心有限公司 Multi-way valve confluence control structure of hydraulic excavator

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