CN102022612B - Fluid flow direction control valve and valve bank system - Google Patents
Fluid flow direction control valve and valve bank system Download PDFInfo
- Publication number
- CN102022612B CN102022612B CN 201010531175 CN201010531175A CN102022612B CN 102022612 B CN102022612 B CN 102022612B CN 201010531175 CN201010531175 CN 201010531175 CN 201010531175 A CN201010531175 A CN 201010531175A CN 102022612 B CN102022612 B CN 102022612B
- Authority
- CN
- China
- Prior art keywords
- piston
- flow
- valve
- fluid
- runner
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Magnetically Actuated Valves (AREA)
Abstract
The invention discloses a fluid flow direction control valve, which comprises a valve body. A first runner and a second runner are formed in the valve body. A first piston and a second piston are arranged in each of the first and second runners. A plurality of channels communicated with the first and second runners are formed in the valve body. The first runner is symmetrically provided with a first controlled fluid outlet and a second controlled fluid outlet. Fluids in the first and second runners are pressurized stepwise to drive the first and second pistons to sequentially move and are pressurized a controlled fluid out of the first and second controlled fluid outlets. The fluid flow direction control valve provided by the invention delivers the fluid to a given position under the condition of not arranging electronic apparatuses and electromagnetic valves in the vicinity of the valve body and among a plurality of valve bodies so as to be applicable to the occasions of high temperature, high humidity, excessive dust, high corrosion and the like in which electric parts are difficult to use.
Description
Technical field
The present invention relates to a kind of direction of flow control valve and valve set system, it can be applicable to the fluid control occasion that is not easy to use electric device, especially a kind of large-scale engineering machinery that can be used for industries such as metallurgy, mine, building materials, electric power, chemical industry carries out the grease flow of centralized lubrication to the control distributing valve, such as the grease centralized lubrication that is used for casting machine etc.
Background technique
At present, in the heavy mechanical equipment of the industries such as metallurgy, mine, building materials, electric power, chemical industry, generally begin to adopt centralized lubrication, wherein, mainly comprise two kinds of distribution of lubrication oil modes of single-line type and two-wire system.
The deficiency of single-line type centralized lubrication is: as long as there is a lubricating point to stop up in the lubrication system, the circulation fuel feeding of relevant lubricating point will stop in the lubrication system, cause a plurality of lubricating points to quit work, and the position of obstruction point is difficult to find.In the situation comparatively complicated in system, that lubricating point is more, the single-line type lubrication system is easy to can't work because of the obstruction of indivedual lubricating points.
The deficiency of two-wire system centralized lubrication is: system may be because the leakage of a lubricating point, and can't set up necessary pressure reduction between two main supply oil pipes, causes whole lubrication system because can't normal commutation and cisco unity malfunction.This system also is difficult to find the obstruction of indivedual points, and when letting out in system occurs, the leak point also is difficult to find that system maintenance is poor.
The use electromagnetic valve that occurs in recent years is to the lubrication system of each point fuel feeding, and its principle is that the switch that uses PLC (programmable controller, Programmable logic Controller) to control each solenoid valve to be each lubricating point fuel feeding.Under this lubricating system, the independent controlled by solenoid valve of each point does not have association between points, and system can not form the fault chain between lubricating point, can because of the fault of a lubricating point, not cause that large-area lubricated work is undesired; , the fuel feeding situation easy to adjust to oil mass of each lubricating point can detect.Yet, to use in the lubrication system of solenoid valve, the normal open fault easily occurs in solenoid valve, and this system fuel feeding terminal has electronic equipment, can not adapt to the environment of high temperature, high humidity, high corrosion.
Summary of the invention
The technical problem to be solved in the present invention provides a kind of direction of flow control valve and valve set system, to reduce or to avoid problem noted earlier.
Specifically, the technical problem that the present invention will solve provides a kind of direction of flow control valve and valve set system, this valve adopts the mechanical-hydraulic parts to form fully, the rugged environment that can adapt to high temperature, high dust, high humility, and pipeline connects simply, the valve piece is overhauled conveniently, fault is few, the life-span is long.
Another technical problem that the present invention will solve provides a kind of direction of flow control valve and valve set system, and this valve can accurately detect, control lubricant oil (fat) amount that is fed to each lubricating point under flowmeter, pressure transducer etc. cooperate.
For solving the problems of the technologies described above, the present invention proposes a kind of direction of flow control valve, comprise a valve body, be provided with in this valve body one with the first flow of control fluid delivery pipeline UNICOM and one the second runner with controlled fluid delivery line UNICOM, respectively be provided with a first piston and second piston in described first flow and described the second runner, wherein, be provided with the passage of the described first flow of a plurality of UNICOMs and described the second runner in the described valve body, described passage is symmetric in described valve body; Described first flow has symmetrically arranged first controlled fluid outlet and the second controlled fluid outlet, by the substep pressurization to first runner and second runner inner fluid, can promote described first piston and the second piston sequential movements, and controlled fluid is extruded by described the first controlled fluid outlet and the outlet of described the second controlled fluid.
Preferably, the front end of described first piston and described the second piston is made by permeability magnetic material or magnetic material, is provided with magnet steel or permeability magnetic material that energy and described first piston and described the second piston nose produce suction in the outlet both sides of described first flow and described the second runner.
Preferably, described first piston is identical with the profile topological structure feature of described the second piston.
Preferably, a plurality of described passage that arranges in the described valve body, the width of the passway in the same runner is all identical, and the span in the same runner between the adjacent described passway is also identical.
Preferably, described first piston be connected the second piston respectively by the first I shape part that is positioned at both sides and the I shape part and connect the first I shape part and the second I shape middle brace rod partly forms of being connected; Wherein, described the first I shape part and described the second I shape part are identical, described middle brace rod is arranged in the displacement restriction passage of described first flow and described the second runner, thereby so that described first piston and described the second piston are limited in two side shiftings of described displacement restriction passage.
Preferably, described the first I shape part is comprised of larger the first H-shaped cephalic of both sides diameter and the second H-shaped cephalic and the less joint of diameter between described the first H-shaped cephalic and described the second H-shaped cephalic, wherein, described the first H-shaped cephalic is identical with size with described the second H-shaped cephalic structure, and symmetrical with respect to described joint.
Preferably, the diameter of the diameter of described the first H-shaped cephalic and described the second H-shaped cephalic and described first flow and described the second runner adapts.
In addition, the present invention also provides a kind of valve set system that is comprised of the aforesaid fluid flow direction control valve, wherein, described valve set system comprises that series connection is arranged on a plurality of described direction of flow control valve in described control fluid delivery pipeline and the described controlled fluid delivery line, by the substep pressurization to described control fluid and controlled fluid, control successively interior first piston and the second piston sequential movements of two runners of every flow direction of flow control valve in the described valve group, and controlled fluid extruded by each direction of flow control valve corresponding outlet of described the first controlled fluid or the outlet of described the second controlled fluid, be transported to each desired location, the ingress of described valve set system is provided with pressure and flow monitoring device.
Preferably, be provided with first pressure transducer in the ingress of described control fluid delivery pipeline and be provided with second pressure transducer and a flow transducer in the ingress of described controlled fluid delivery line.
Patent of the present invention provides the interlocking of a kind of two-way to flow to the control fluid valve, both two pipelines of linking valve body, and wherein the controlled fluid in the controlled fluid pipeline has two flow directions by valve body, the control that flows to controlled fluid of controlled fluid; The current intelligence of control fluid in flow direction control valve controlled by controlled fluid also.A plurality of such flow direction control valves are connected in series successively, can be by the fluid in the pipeline, direction of flow in the control another one pipeline, do not arranging between a plurality of valve bodies in the situation of electronic device, solenoid valve, controlled fluid is transported to specified position (that is: the on-the-spot mounting electrical device of manufacturing mechanism not abominable at environment, that electric device is difficult to work will be realized controlled fluid is transported to specified position simultaneously); Before fluid delivery pipeline is linked the direction of flow control valve, hold, increase flow, Pressure testing device, change of state that can the test fluid flow direction control valve, detect the controlled flow scale of construction of carrying for specified position and the obstruction leak case of detection delivery line.Because this valve can not arrange in the situation of electronic device, solenoid valve near the valve body and between a plurality of valve bodies, for specified position is carried fluid, therefore this valve is fit to be applied in the occasion that the electric components such as high temperature, high humidity, high dust, high corrosion are difficult to use, and finishes control and the detection of fluid delivery.The typical application is exactly that the flow direction with thin oil or drier oil fat control lubricating grease does not have at the main process equipment scene in the situation of electric device, realizes the site-directed quantitative supply lubricating grease to each lubricant housings of main process equipment.
Description of drawings
The following drawings only is intended to the present invention done and schematically illustrates and explain, not delimit the scope of the invention.Wherein,
Figure 1A～1E shows is workflow schematic representation according to the direction of flow control valve of a specific embodiment of the present invention;
Fig. 2 shows is valve set system schematic representation that be in series by a plurality of direction of flow control valves, that the centralized lubrication of dry oil lubrication is provided for a plurality of lubricating points according to a specific embodiment of the present invention.
Embodiment
Understand for technical characteristics of the present invention, purpose and effect being had more clearly, now contrast description of drawings the specific embodiment of the present invention.Wherein, identical parts adopt identical label.
Referring to accompanying drawing a kind of direction of flow control valve provided by the present invention is elaborated, this direction of flow control valve can be applicable to the fluid control occasion that is not easy to use electric device, especially a kind of large-scale engineering machinery that can be used for industries such as metallurgy, mine, building materials, electric power, chemical industry carries out the grease flow of centralized lubrication to the control distributing valve, such as the grease centralized lubrication that is used for casting machine etc.
Figure 1A～1E shows is workflow schematic representation according to the direction of flow control valve of a specific embodiment of the present invention, as shown in the figure, this direction of flow control valve 1 is arranged among a control fluid delivery pipeline P1 and the controlled fluid delivery line P2, in specific embodiment shown in Fig. 2 A～2E, in described control fluid delivery pipeline P1 and described controlled fluid delivery line P2, can connect a plurality of direction of flow control valves 1 are set.
Shown in Figure 1A～1E, each direction of flow control valve 1 is provided with the first controlled fluid outlet S1 and the second controlled fluid outlet S2.During work, on same import and export direction, be pressure fluid J, the L increase pressure among fluid delivery pipeline P1, the P2 in order, so that the piston 13,13 of direction of flow control valve 1 moves in order, thereby the controlled fluid L among the controlled fluid delivery line P2 is sent by the first controlled fluid outlet S1 or the second controlled fluid outlet S2, be provided to setting position, for example each bearing of the fan-shaped section of casting machine etc.
When this patent is applied in lubricated field, it will be appreciated by those skilled in the art that the work of the control valve of direction of flow shown in the figure, need to parts such as lubricant grease fuel tank, oil pump, pressure regulator valve, electric control box, above-mentioned parts are not shown.
Shown in Figure 1A～1E, each fluid control distributing valve 1 structure is identical.Specifically, fluid control distributing valve 1 comprises a valve body 11, is illustrated as the cross-sectional schematic of valve body 11, and it is substantially a cylindrical body or cuboid.Special needs to be pointed out is, what Figure 1A～1E represented respectively is the different conditions of same direction of flow control valve, because there is more reference character, for clarity sake, only in Figure 1A, most of structure is marked, and in other accompanying drawing not to identical parts repeat mark.
Be provided with in the valve body 11 first flow 12 and second runner 12 ', first flow 12 and the second runner 12 ' interior respectively be provided with a first piston 13 and second piston 13 '.Wherein, first flow 12 and control fluid delivery pipeline P1 UNICOM, the second runner 12 ' with controlled fluid delivery line P2 UNICOM.First piston 13 and the second piston 13 ' front end are made by permeability magnetic material, first flow 12 and the second runner 12 ' the import and export both sides be provided with magnet steel 20, magnet steel 20 can be made by permanent-magnet material.Magnet steel 20 can be to first piston 13 and the second piston 13 ' generation graviational interaction.Certainly, it will be appreciated by those skilled in the art that first piston 13 and the second piston 13 ' front end also can be made by permanent-magnet material, in this case, can change magnet steel 20 into permeability magnetic material, still can obtain identical magnetic attraction.
Further be provided with in the valve body part 11 eight above-mentioned first flows 12 of UNICOM and the second runner 12 ' passage, be respectively first passage 14A, second channel 14B, third channel 14C, four-way 14D, Five-channel 14A ', the 6th passage 14B ', the 7th passage 14C ' and the 8th passage 14D '.As shown in the figure, above-mentioned eight passages are symmetric in valve body 11 entirely, and namely passage 14A, 14B, 14C, 14D and passage 14A ', 14B ', 14C ', 14D ' are the mirror image symmetry.Sectional view among Figure 1A～1E is schematic, for the position relationship that shows above-mentioned eight passages they have been drawn as plane form, in fact those skilled in the art are to be understood that, these eight passages are not in the same plane each other, but spatially mutually stagger, so that they can not intersect mutually.
Being provided with ten passwaies in the first flow 12, is respectively first passage mouth 15A, second channel mouth 15B, third channel mouth 15C, four-way road junction 15D and five-way road junction 15A ', the 6th passway 15B ', the 7th passway 15C ', the 8th passway 15D ' and aforesaid the first controlled fluid outlet S1 and the second controlled fluid outlet S2.As shown in the figure, above-mentioned ten passwaies are symmetric in valve body 11, and namely passway 15A, 15B, 15C, 15D and passway 15A ', 15B ', 15C ', 15D ' are the mirror image symmetry; The first controlled fluid outlet S1 and the second controlled fluid outlet S2 also are the mirror image symmetry.And first passage mouth 15A, second channel mouth 15B, third channel mouth 15C, four-way road junction 15D are roughly the identical and uniformly-spaced arrangement of width.Same, five-way road junction 15A ', the 6th passway 15B ', the 7th passway 15C ', the 8th passway 15D ' they also roughly are the identical and uniformly-spaced arrangements of width.
Similarly, the second runner 12 ' in be provided with the passway of eight correspondences, be respectively first passage mouth 16A, second channel mouth 16B, third channel mouth 16C, four-way road junction 16D and five-way road junction 16A ', the 6th passway 16B ', the 7th passway 16C ', the 8th passway 16D '.As shown in the figure, above-mentioned eight passwaies are symmetric in valve body 11, and namely passway 16A, 16B, 16C, 16D and passway 16A ', 16B ', 16C ', 16D ' are the mirror image symmetry.And first passage mouth 16A, second channel mouth 16B, third channel mouth 16C, four-way road junction 16D are roughly the identical and uniformly-spaced arrangement of width.Same, five-way road junction 16A ', the 6th passway 16B ', the 7th passway 16C ', the 8th passway 16D " also roughly be the identical and uniformly-spaced arrangement of width.
Except the first controlled fluid outlet S1 and the second controlled fluid outlet S2, first flow 12 and the second runner 12 ' the external form topological structure identical.Usually, first flow 12 and the second runner 12 ' in each passway be full symmetrical configuration, namely, the size of each passway all is identical, about each passway, position, the left and right sides also all is the mirror image symmetry, namely as shown in the figure, not only passway 15A, 15B, 15C, 15D and passway 15A ', 15B ', 15C ', 15D ' are the mirror image symmetry, and passway 16A, 16B, 16C, 16D and passway 16A ', 16B ', 16C ', 16D ' are the mirror image symmetry; And passway 15A, 15B, 15C, 15D and passway 16A, 16B, 16C, 16D and passway 15A ', 15B ', 15C ', 15D ' and passway 16A ', 16B ', 16C ', 16D ' also be the mirror image symmetry,
In addition, the second channel mouth 15B in the first flow 12 by third channel 14C and the second runner 12 ' in the 8th passway 16D ' UNICOM; Accordingly, the second runner 12 ' in second channel mouth 16B by the 8th passway 15D ' UNICOM in four-way 14D and the first flow 12.Similarly, the 6th passway 15B ' in the first flow 12 by the 7th passage 14C ' and the second runner 12 ' in four-way road junction 16D UNICOM; Accordingly, the second runner 12 ' in the 6th passway 16B ' by the four-way road junction 15D UNICOM in the 8th passage 14D ' and the first flow 12.
In addition, the 9th passway in the first flow 12 is exactly the first controlled fluid outlet S1; The tenth passway in the runner 12 is exactly the second controlled fluid outlet S2.
As shown in Figure 1B, first piston 13 is comprised of with the middle brace rod 133 of being connected I shape part 132 and connect the first I shape part 131 and the second I shape part 132 the first I shape part 131 that is positioned at both sides; Wherein, the first I shape part 131 and the second I shape part 132 are identical.Middle brace rod 133 is arranged in the displacement restriction passage 134 of first flow 12, thereby so that first piston 13 is limited in two side shiftings of displacement restriction passage 134, as shown in the figure.Therefore the second piston 13 ' identical with topological structure, the forms of motion of first piston 13 is no longer to the second piston 13 ' be further described.
The first I shape part 131 is comprised of larger the first H-shaped cephalic 1311 of both sides diameter and the second H-shaped cephalic 1312 and the less joint 1313 of diameter between the first H-shaped cephalic 1311 and the second H-shaped cephalic 1312, wherein, the first H-shaped cephalic 1311 is identical with size with the second H-shaped cephalic 1312 structures, and with respect to joint 1313 symmetries; Usually, the width of the first H-shaped cephalic 1311, the second H-shaped cephalic 1312 and joint 1313 is roughly the same, as shown in the figure.
The diameter of the first H-shaped cephalic 1311 and the second H-shaped cephalic 1312 and the diameter of first flow 12 adapt.
Usually, the width of the first H-shaped cephalic 1311 is substantially equal to the width sum at the interval between two passwaies that second channel mouth 15B and second channel mouth 15B be adjacent; Usually, the width of the first H-shaped cephalic 1311 is substantially equal to the width sum at the interval between two passwaies that third channel mouth 15C and third channel mouth 15C be adjacent; Usually, the width of joint 1313 is substantially equal to the width sum at third channel mouth 15C, four-way road junction 15D and the interval between the two.
Because the width of the first H-shaped cephalic 1311, the second H-shaped cephalic 1312 and joint 1313 is basic identical, therefore, the width of the first H-shaped cephalic 1311, the second H-shaped cephalic 1312 and joint 1313 equals the width of three times of aforementioned channels mouths substantially, as shown in the figure.
The second I shape part 132 and the first I shape part 131 are identical, therefore no longer the second I shape part 132 are further described.
Describe the workflow of the direction of flow control valve of present embodiment in detail below with reference to Figure 1A～1E.
Shown in Figure 1A, when initial, controlled fluid L in the controlled fluid delivery line P2 stops from the diagram left side mobile one-way valve 141 that is arranged on the second channel 14B to the right, pressure rises gradually, but its pressure still can not overcome second piston 13 of 20 pairs of the second runners 12 of magnet steel ' interior ' graviational interaction, therefore the second piston 13 ' still be in the second runner 12 ' the left side.
Pressure fluid J among the control fluid delivery pipeline P1 successively by first passage mouth 15A, first passage 14A in the first flow 12, the second runner 12 ' in third channel mouth 16C, four-way road junction 16D, the 7th passage 14C ', first fluid in 15B ' outflows diagram left side, the 6th passway in the first flow 12 control distributing valve 1, enter other fluid control distributing valves 1 that arrange thereafter, for example, shown in Fig. 2 A～2E.
As shown in Figure 1B, along with the controlled fluid L in the controlled fluid delivery line P2 is pressurizeed, the pressure rise of controlled fluid L, when this pressure is increased to design load, controlled fluid L to the second runner 12 ' interior the second piston 13 ' thrust overcome 20 pairs of the second pistons of magnet steel, 13 ' gravitation, promote the second piston 13 ' move right, and arrive next settling position, as shown in Figure 1B.
At this moment, controlled fluid L successively by the second runner 12 ' in second channel mouth 16B, four-way 14D, the 8th passway 15D ' in the first flow 12, the second controlled fluid outlet S2 flow out, and be introduced to definite outer portion (that is: carrying target for of controlled fluid).And the control fluid J of this moment because the second piston 13 ' change in location, path is cut off, and can not flow out by the passage in first flow 12 and the valve body 11 again.
Shown in Fig. 1 C, under the state that control fluid J is blocked, inflow along with control fluid J, the pressure of control fluid J becomes large gradually, when being increased to design load, the thrust that first piston 13 is subject to overcomes the gravitation of magnet steel 20, promotes first piston 13 and moves right, and arrive next settling position, shown in Fig. 1 C.
At this moment, change in location along with first piston 13, can be by the reversal of direction of flow of extra control mechanism control controlled fluid L and control fluid J, controlled fluid L will by the second runner 12 ', the 4th passage 14D, the 6th passage 14B ' in the valve body 11, again through the second runner 12 ' rear end effluent fluid flow direction control valve 1.Under this state, for control fluid J and controlled fluid L, valve body 11 is suitable one section carrying path only, by the control fluid J behind the valve body 11 and controlled fluid L, can operate next direction of flow control valve through identical step, be reached for next target of carrying target to supply with controlled fluid, shown in Fig. 1 D.
When valve body 11 in state lower time shown in Fig. 1 D, L flows into from the right side along with controlled fluid, the second runner 12 ' right side in the described valve body 11 increases pressure, then when pressure is elevated to certain value, thrust greater than 20 pairs of the second pistons 13 of the right magnet steel ' suction, the second piston 13 sound are moved left, and reach the limit of settling position, shown in Fig. 1 D.
At this moment, controlled fluid L will be by described valve body 11 internal paths, and S1 flows out from the outlet of the first controlled fluid, and are introduced to definite outer portion (that is: carrying target for of controlled fluid).
Shown in Fig. 1 E, J flows into from the right side along with the control fluid, the pressure of controlled fluid J in the described first flow 12 increases, when pressure is increased to certain value, the thrust that first piston 13 is subject to overcomes the gravitation of magnet steel 20, promote first piston 13 and be moved to the left, and arrive next settling position, shown in Fig. 1 E.
At this moment, change in location along with first piston 13, can again reverse by the flow direction of extra control mechanism control controlled fluid L and control fluid J, controlled fluid L will by the second runner 12 ', the 8th passage 14D ', the 2nd passage 14B in the valve body 11 be again through the second runner 12 ' front end effluent fluid flow direction control valve 1.
The direction of flow control valve of this moment has returned to again original state, can again repeat the operation that begins shown in Figure 1A.
In fact, Figure 1A～1E only is illustrated single fluid control distributing valve 1, with a plurality of above-mentioned direction of flow control valve 1 order serial connections, just can form a valve set system, and controlled fluid is transported to a plurality of conveying targets.After being equipped with time-controlling arrangement, pressure and flow monitoring device for valve set system, just can be desired location in the time of setting, provide the controlled fluid of set amount, and whether normal the fluid that can detect in the whole system is carried.
For example, being in series by four direction of flow control valves 1 shown in Fig. 2 A～2E, provide for a plurality of lubricating points in the valve set system of centralized lubrication of dry oil lubrication, the ingress of (that is control fluid delivery pipeline P1) is provided with first a pressure transducer M1 on control oil delivery pipe road, ingress at lubricant grease delivery line (that is controlled fluid delivery line P2) is provided with second a pressure transducer M2 and a flow transducer M3, thereby can be implemented in electronic device is not set between a plurality of valve bodies, in the situation of solenoid valve, regularly, quantitatively lubricating grease is transported to specified position, and can detects obstruction or the leakage fault that any one lubricating point occurs by real-time online.
The concrete control flow of this valve set system can referring to accompanying drawing 2A～2E, be described in detail as follows:
For the ease of narration, special explanation: in the concrete example application of following direction of flow control valve 1, fluid control distributing valve, pressure fluid J, lubricant grease L, the first/the second lubricant grease outlet S1/S2 correspond respectively to direction of flow control valve, control fluid, controlled fluid, the first/the second controlled fluid outlet S1/S2 of aforementioned part, pressure fluid J wherein can be same lubricating grease with lubricant grease L both, also can be fully different, for example, pressure fluid J can be the hydraulic pressure wet goods.
Be the working condition of every flow direction of flow control valve among clear performance Fig. 2 A～2E, simplify for some the fluid control distributing valve 1 among each figure, omitted parameatal sectional structure, so that those skilled in the art's understanding.For example, each fluid control distributing valve 1 parameatal structure has just dispensed among Fig. 2 A, and first fluid control distributing valve 1 parameatal structure is not omitted among Fig. 2 B, represents that it is in slave mode.
Under state shown in Fig. 2 A, pressure fluid J can flow into from the entrance of first fluid control distributing valve 1, directly arrives the outlet of last fluid control distributing valve 1 by its latter linked pipeline and each fluid control distributing valve 1; And lubricant grease L is blocked in first fluid control distributing valve 1.
At this moment, the import of described valve group pressure fluid J and outlet are communicated with, pressure fluid J delivery line is in the pressure release state, allow M1 raise, can't produce enough large pressure reduction at first piston 13 two ends of first fluid control distributing valve 1 for pressure fluid J pressurization, thereby first fluid first piston 13 of controlling distributing valve 1 can not overcome magnet steel suction and move to right under pressure fluid J thrust to the right; The carrying path of lubricant grease L is blocked in first fluid control distributing valve 1, thereby can be from the importer of lubricant grease L delivery line to the lubricating grease pressure M2 that increases lubricant grease L delivery line, when pressure M2 be elevated to design load, lubricant grease L the second piston piston 13 of first fluid control distributing valve 1 ' the right and left when producing enough large differential pressure, lubricant grease L will promote this second piston 13 ' move right to the second piston 13 thrust to the right, and arrive next settling position (Fig. 2 B).The sign that arrives this position is: M2 reaches normal grease lubrication pressure, M3 can be metered into lubricant grease and pass through.
Under state shown in Fig. 2 B, continuation is from the importer of lubricant grease L delivery line to force feed lubricant grease L, lubricant grease L will discharge from the lubricant grease outlet S2 of first fluid control distributing valve 1, and to the lubricant housings of setting, the lubricant housings that is setting provides lubricant grease L.The amount of the lubricating grease that provides can predict by M3; Oil feed line pressure when lubricated can predict by M2.
Under state shown in Fig. 2 B, the passage of pressure fluid J is interior by the second piston 13 ' blocking-up at first fluid control distributing valve 1, this moment is from the importer of pressure fluid J delivery line to the pressure M1 that increases pressure fluid J delivery line, when pressure is elevated to design load, pressure fluid J when the right and left of the first piston 13 of first fluid control distributing valve 1 produces enough large differential pressure, pressure fluid J will overcome magnet steel suction, promote this first piston 13 and move right first piston 13 thrust to the right, and arrive next settling position (Fig. 2 C).The sign that reaches this position is: the M1 fast reducing that is raising is reduced to approach and reveals pressure; Before M2 is elevated to design load, M3 almost can't detect lubricant grease and flow through.
During to state shown in Fig. 2 C, first piston 13 has changed the flow direction of lubricant grease L under Fig. 2 B state, lubricant grease L has been guided to the outlet of first fluid control distributing valve 1, make it the import of second fluid control of flow valves group distributing valve 1, and the carrying path of lubricant grease L is blocked in second fluid control distributing valve 1; And pressure fluid J again can from the outlet of the import of valve set system, first fluid control distributing valve 1, to second fluid control distributing valve 1 entrance ... until the outlet of whole valve set system, so the delivery line of pressure fluid J is in the pressure release state.
More than the change procedure of first fluid control distributing valve 1 state from Fig. 2 A, Fig. 2 B to Fig. 2 C, can know by the first pressure transducer M1, the second pressure transducer M2 and flow transducer M3 monitoring.
Successively, under state shown in Fig. 2 D and the 2E, can by second fluid control of valve set system distributing valve 1 is adopted same control, realize answering lubricant grease L to desired location from the S2 confession of second fluid control of valve group distributing valve 1.
Second fluid control of valve group distributing valve 1 can be known by the first pressure transducer M1, the second pressure transducer M2 and flow transducer M3 monitoring equally finishing to the change of state in the desired location fuel feeding process, to flow, the pressure condition of desired location supplying lubricating oil fat L.
Carry out successively, can finish all fluids control distributing valves 1 in the valve set system are gone out lubricant grease L to the setting lubricating point of correspondence from S2 confession separately.
Each fluid control distributing valve 1 of valve group is finished the change of state in the desired location fuel feeding process, flow to desired location supplying lubricating oil fat L, pressure condition, all can pass through the first pressure transducer M1, the second pressure transducer M2 and flow transducer M3 monitoring are known, that is to say: by to lubricating pipe pressure, the detection that flow parameter changes, can clearly know the state of current controlled fluid control distributing valve 1, can know clearly that current valve group is to be the lubricating point fuel feeding of which setting, and clearly know the pressure to the lubrication oil supply process, the flow situation.
Similarly, working procedure as the single fluid control distributing valve 1 shown in Fig. 1 D and the 1E, oppositely pressurize from the outlet of described valve set system, can be by order from back to front, one by one lubricant grease L is gone out lubricating point to correspondence from the S1 confession of each fluid control distributing valve 1, and by the detection to pipeline pressure, flow, control to the lubricants capacity of lubricating point, the obstruction that detects each lubricating point lubricating oil path, leak condition.
As a supplement explanation, the obstruction of lubricating point lubricating oil path, to reveal fault be to judge like this: when for the S1 mouth of certain fluid control distributing valve 1 or S2 confession oil, the value of M2 should be the normal feed speed of lubricant oil for the normal value of lubrication pressure, M3.If this moment, the checkout value of M3 is 0 or near 0, has stopped up with regard to showing corresponding lubricating point; If this moment, the checkout value of M3 is more than or equal to normal value, and M2 is significantly on the low side, is lower than the normal lubricated back pressure that needs, and has revealed with regard to showing corresponding lubricating point.After in time finding fault, just can provide caution by warning.
Set each pressure transducer M1, M2, flow transducer M3 all is arranged on the starting end of pressure fluid J delivery line and lubricant grease L delivery line among the present invention, away from each control terminal---and fluid control distributing valve.Corresponding control unit, such as PLC, relief valve, pressure regulator valve, switch valve etc. is arranged on again oil pump and enters before each pressure, the flow transducer, specific pressure, flow transducer are further from the scene that fluid control distributing valve has been installed, and fluid control distributing valve of the present invention is a kind of pressure controlled valve, do not comprise any electronic component, thereby failure rate is low, environment-adapting ability is strong, be not afraid of high temperature, be particularly useful for the centralized lubrication of casting machine.
The present invention has adopted pressure fluid that every flow direction of flow control valve is carried out sequence control, need not complicated electronic equipment or solenoid valve etc., and pilot line is simple in structure, complex environment strong adaptability, long service life, be difficult for blocking, be not afraid of high temperature, failure rate is low.
This patent is applied in the grease concentrating lubricating system, can finishes the timing to each lubricating point, quantitative fuel feeding in the production scene of high temperature, high humidity, high dust, high radiation, and can in time find the leak stopping fault of lubricating point.
Although it will be appreciated by those skilled in the art that the present invention is that mode according to a plurality of embodiments is described, and is not that each embodiment only comprises an independently technological scheme.Narration like this only is for the sake of clarity in the specification; those skilled in the art should make specification as a wholely to be understood, and regard technological scheme related among each embodiment as the mode that can mutually be combined into different embodiments understand protection scope of the present invention.
The above only is the schematic embodiment of the present invention, is not to limit scope of the present invention.Any those skilled in the art, the equivalent variations of doing under the prerequisite that does not break away from design of the present invention and principle, modification and combination all should belong to the scope of protection of the invention.
Claims (9)
1. direction of flow control valve, comprise a valve body, be provided with in this valve body one with the first flow of control fluid delivery pipeline UNICOM and one the second runner with controlled fluid delivery line UNICOM, respectively be provided with a first piston and second piston in described first flow and described the second runner, it is characterized in that, be provided with the passage of the described first flow of a plurality of UNICOMs and described the second runner in the described valve body, described passage is symmetric in described valve body; Described first flow has symmetrically arranged first controlled fluid outlet and the second controlled fluid outlet, by the substep pressurization to first runner and second runner inner fluid, can promote described first piston and the second piston sequential movements, and controlled fluid is extruded by described the first controlled fluid outlet and the outlet of described the second controlled fluid.
2. direction of flow control valve according to claim 1, it is characterized in that, the front end of described first piston and described the second piston is made by permeability magnetic material or magnetic material, is provided with magnet steel or permeability magnetic material that energy and described first piston and described the second piston nose produce suction in the outlet both sides of described first flow and described the second runner.
3. direction of flow control valve according to claim 2 is characterized in that, described first piston is identical with the profile topological structure feature of described the second piston.
4. direction of flow control valve according to claim 3 is characterized in that, a plurality of described passage that arranges in the described valve body, and the width of the passway in the same runner is all identical, and the span in the same runner between the adjacent described passway is also identical.
5. direction of flow control valve according to claim 4, it is characterized in that, described first piston be connected the second piston respectively by the first I shape part that is positioned at both sides and the I shape part and connect the first I shape part and the second I shape middle brace rod partly forms of being connected; Wherein, described the first I shape part and described the second I shape part are identical, described middle brace rod is arranged in the displacement restriction passage of described first flow and described the second runner, thereby so that described first piston and described the second piston are limited in two side shiftings of described displacement restriction passage.
6. direction of flow control valve according to claim 5, it is characterized in that, described the first I shape part is comprised of larger the first H-shaped cephalic of both sides diameter and the second H-shaped cephalic and the less joint of diameter between described the first H-shaped cephalic and described the second H-shaped cephalic, wherein, described the first H-shaped cephalic is identical with size with described the second H-shaped cephalic structure, and symmetrical with respect to described joint.
7. direction of flow control valve according to claim 6 is characterized in that, the diameter of the diameter of described the first H-shaped cephalic and described the second H-shaped cephalic and described first flow and described the second runner adapts.
8. valve set system that is formed by the described direction of flow control valve of one of claim 1-7, it is characterized in that, described valve set system comprises that series connection is arranged on a plurality of described direction of flow control valve in described control fluid delivery pipeline and the described controlled fluid delivery line, by the substep pressurization to described control fluid and controlled fluid, control successively interior first piston and the second piston sequential movements of two runners of every flow direction of flow control valve in the described valve group, and controlled fluid extruded by each direction of flow control valve corresponding outlet of described the first controlled fluid or the outlet of described the second controlled fluid, be transported to each desired location, the ingress of described valve set system is provided with pressure and flow monitoring device.
9. valve set system according to claim 8, it is characterized in that, be provided with first pressure transducer in the ingress of described control fluid delivery pipeline, be provided with second pressure transducer and a flow transducer in the ingress of described controlled fluid delivery line.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010531175 CN102022612B (en) | 2010-11-03 | 2010-11-03 | Fluid flow direction control valve and valve bank system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010531175 CN102022612B (en) | 2010-11-03 | 2010-11-03 | Fluid flow direction control valve and valve bank system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102022612A CN102022612A (en) | 2011-04-20 |
| CN102022612B true CN102022612B (en) | 2013-04-03 |
Family
ID=43864234
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201010531175 Expired - Fee Related CN102022612B (en) | 2010-11-03 | 2010-11-03 | Fluid flow direction control valve and valve bank system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102022612B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2947211B1 (en) | 2013-01-18 | 2018-09-26 | Volvo Construction Equipment AB | Flow control device and flow control method for construction machine |
| KR101763282B1 (en) | 2013-02-05 | 2017-07-31 | 볼보 컨스트럭션 이큅먼트 에이비 | Construction equipment pressure control valve |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2834433A (en) * | 1954-02-26 | 1958-05-13 | Tanway Ltd | Lubricating systems |
| US3409104A (en) * | 1965-06-11 | 1968-11-05 | Eaton Yale & Towne | Dual pressure progressive valve structure |
| US4712649A (en) * | 1985-12-04 | 1987-12-15 | Joseph Vogele Ag | Progressive distributor for lubricants |
| US7380571B2 (en) * | 2003-08-27 | 2008-06-03 | Koganei Corporation | Directional control valve |
| CN101251225A (en) * | 2008-04-09 | 2008-08-27 | 义小毛 | Hydraulic pressure regulating automatic reversing combined valve for double-line grease lubricating system |
| CN201215243Y (en) * | 2008-07-04 | 2009-04-01 | 段修英 | Oil and gas lubricant distributor |
-
2010
- 2010-11-03 CN CN 201010531175 patent/CN102022612B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2834433A (en) * | 1954-02-26 | 1958-05-13 | Tanway Ltd | Lubricating systems |
| US3409104A (en) * | 1965-06-11 | 1968-11-05 | Eaton Yale & Towne | Dual pressure progressive valve structure |
| US4712649A (en) * | 1985-12-04 | 1987-12-15 | Joseph Vogele Ag | Progressive distributor for lubricants |
| US7380571B2 (en) * | 2003-08-27 | 2008-06-03 | Koganei Corporation | Directional control valve |
| CN101251225A (en) * | 2008-04-09 | 2008-08-27 | 义小毛 | Hydraulic pressure regulating automatic reversing combined valve for double-line grease lubricating system |
| CN201215243Y (en) * | 2008-07-04 | 2009-04-01 | 段修英 | Oil and gas lubricant distributor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102022612A (en) | 2011-04-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101864965B (en) | Pressure flow rate composite synchronization control energy-saving type shield propelling system | |
| CN102042217B (en) | Piston lubricating system of concrete cylinder | |
| CN103032397B (en) | Multi-degree-of-freedom parallel tube segment assembling and locating electrohydraulic control system and method thereof | |
| CZ297720B6 (en) | Valve system central block and valve block of two- or three-way valve and use thereof | |
| CN105134684B (en) | Logic oil duct control system with electromagnetic switch valves and failure autodiagnosis method | |
| CN102213201B (en) | High-efficiency concrete or coal slurry conveying system, control method thereof, and two-position three-way hydraulically-controlled directional control valve applied to high-efficiency concrete or coal slurry conveying system | |
| CN204163138U (en) | Super-tonnage excavator straight line moving hydraulic system | |
| CN102220863B (en) | Valve-controlled automatic confluence hydraulic system for horizontal directional drilling machine | |
| CN102022612B (en) | Fluid flow direction control valve and valve bank system | |
| CN215174031U (en) | Heavy lubricating arrangement of intelligence | |
| CN102667015B (en) | Pump control running system for construction machinery | |
| CN103343741A (en) | Hydraulic oil replacement control method for double-cylinder pumping device, double-cylinder pumping device and equipment | |
| CN103010069A (en) | Electric-hydraulic control system for lifting bucket trolley | |
| CN202731325U (en) | Synchronous jacking-up translation system | |
| CN102287418B (en) | Hydraulic cylinder control device capable of realizing accurate half-way stoppage | |
| CN209704966U (en) | A kind of split type shield machine hydraulic drive control valve group convenient for assembling | |
| CN104481944B (en) | Depressurizing system and engineering machinery | |
| CN103982489B (en) | The modular control apparatus tested for hydraulic pump and hydraulic motor | |
| CN206655852U (en) | Work connection, load sensing multi-way valve and engineering machinery | |
| KR101331612B1 (en) | Apparatus for converting railroad able to power compensating following the change of load | |
| CN102937074B (en) | Continuous material feeding system and control method and elevating platform fire truck thereof | |
| WO2020113952A1 (en) | Pumping mechanical hydraulic system | |
| CN109226113B (en) | Hydraulic pipeline flushing oil supply channel and flow control method thereof | |
| CN101876314A (en) | Engineering machinery and multi-path synchronous lubricating device thereof | |
| CN203529814U (en) | Variable amplitude control system for fixed fly jib of crane |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Application publication date: 20110420 Assignee: JIAOZUO SHENGJING TECHNOLOGY CO., LTD. Assignor: Zhang Weihua Contract record no.: 2013410000032 Denomination of invention: Fluid flow direction control valve and valve bank system Granted publication date: 20130403 License type: Exclusive License Record date: 20130424 |
|
| LICC | Enforcement, change and cancellation of record of contracts on the licence for exploitation of a patent or utility model | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130403 Termination date: 20181103 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |