CN108561358B - Differential circuit switching valve and hydraulic differential circuit - Google Patents
Differential circuit switching valve and hydraulic differential circuit Download PDFInfo
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- CN108561358B CN108561358B CN201810057475.2A CN201810057475A CN108561358B CN 108561358 B CN108561358 B CN 108561358B CN 201810057475 A CN201810057475 A CN 201810057475A CN 108561358 B CN108561358 B CN 108561358B
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- oil
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
Abstract
The invention provides a differential circuit switching valve and a differential hydraulic circuit, wherein the switching valve comprises: the valve body is sequentially provided with a first through-flow hole group communicated with an oil port A of the external valve block, a second through-flow hole group communicated with an oil port B of the external valve block and a third through-flow hole group communicated with an oil port B1 of the external valve block along the axial direction; the main valve core is connected in the valve body, and a first valve core channel and a second valve core channel are arranged on the main valve core; the first elastic component is connected to one end of the main valve core and forms a first control cavity together with the valve body and the main valve core; the first one-way valve core assembly is connected to the first valve core channel of the main valve core; and the second elastic component is connected to the other end of the main valve core and forms a second control cavity together with the valve body and the main valve core. The differential circuit switching valve can automatically realize the switching between the fast feeding and the working feeding working conditions of the differential circuit without electric control, and has more compact structure and lower cost.
Description
Technical Field
The invention relates to the technical field of valves, in particular to a differential circuit switching valve and a hydraulic differential circuit, which are mainly applied to the field of hydraulic machinery.
Background
The differential hydraulic cylinder control circuit is used as a basic hydraulic control circuit and is widely applied to the fields of industrial hydraulic pressure, engineering machinery and the like. The differential control loop of the single-piston-rod hydraulic cylinder is essentially to return the liquid discharged by the rod cavity of the hydraulic cylinder to the rodless cavity of the hydraulic cylinder, thereby increasing the flow entering the rodless cavity, correspondingly increasing the extension speed of the piston rod, and flexibly meeting the working requirements of high thrust and low speed and low thrust and high speed. The differential loop control is divided into two working conditions of fast forward and working forward, and a rod cavity and a rodless cavity of the hydraulic cylinder are communicated through a switching valve in the differential loop during the fast forward working condition so as to increase the movement speed of the hydraulic cylinder; in the working condition, the rodless cavity and the rod cavity need to be disconnected so as to increase the output force of the hydraulic cylinder. For example, patent of invention with publication number CN 104675807B, entitled "differential hydraulic control system and method, and crane", which discloses a differential hydraulic control system and method, wherein the system comprises: the hydraulic control system comprises a first reversing valve, a second reversing valve, a one-way valve, a torque limiter and a controller, wherein the first reversing valve is arranged on an oil way for communicating a rodless cavity of a differential hydraulic cylinder with an oil source and is communicated with an oil tank; the second reversing valve is respectively communicated with the first reversing valve, the rodless cavity and the rod cavity of the differential hydraulic cylinder; the one-way valve is arranged on an oil way which is communicated with the oil tank through the second reversing valve; the moment limiter is connected with the controller and transmits the detected actual hoisting weight to the controller; the controller is connected with the control end of the second reversing valve and controls the second reversing valve to reverse so as to realize the switching between the differential state and the non-differential state of the differential hydraulic cylinder. Although the invention can realize the conversion between the fast-forward working condition and the working-forward working condition of the hydraulic cylinder, the structure is more complex, the hydraulic cylinder comprises excessive valves and electronic detection and control elements, and the application cost is higher.
Disclosure of Invention
Aiming at part or all of the technical problems in the prior art, the invention provides the differential circuit switching valve which can automatically realize the switching between the fast feeding and the working feeding working conditions of the differential circuit without electric control, and has more compact structure and lower cost.
In order to achieve the above object, according to one aspect, the present invention provides a differential circuit switching valve having a structure including:
the valve body is sequentially provided with a first through-flow hole group communicated with an oil port A of the external valve block, a second through-flow hole group communicated with an oil port B of the external valve block and a third through-flow hole group communicated with an oil port B1 of the external valve block along the axial direction;
the main valve core is connected in the valve body, and a first valve core channel and a second valve core channel are arranged on the main valve core;
the first elastic component is connected to one end of the main valve core and forms a first control cavity together with the valve body and the main valve core;
the first one-way valve core assembly is connected to the first valve core channel of the main valve core;
the second elastic component is connected to the other end of the main valve core and forms a second control cavity together with the valve body and the main valve core; and is configured to:
when the pressure of the oil port A is low and the oil port B is fed, the oil enters the first valve core channel from at least one through hole in the second through hole group to push the first one-way valve core assembly away, and flows to the oil port A from at least one through hole in the first through hole group to realize differential motion;
when the pressure of the oil port A rises and the pressure entering the first control cavity from at least one through-flow hole in the first through-flow hole group overcomes the acting force of the second elastic assembly to push the main valve core to move towards the end where the second control cavity is located, at least one through-flow hole in the second through-flow hole group is communicated with the third through-flow hole group, and the oil liquid of the oil port B flows to the oil port B1 to realize working feeding;
when the main valve core is compressed by the oil inlet main valve core of the second control cavity to realize reversing of the main valve core, the third through hole group is communicated with at least one through hole in the second through hole group, and the second through hole group is not communicated with the first through hole group.
In the invention, three working modes of differential motion of oil from an oil port B to an oil port A, working feed from the oil port B to an oil port B1 and reset when oil is fed from an oil port B1 are realized by arranging and connecting three groups of circulation holes on the valve body, a valve core channel on the main valve core, a first elastic assembly, a first one-way valve core assembly and a second elastic assembly, and the switching between the quick feed working condition and the working feed working condition of a differential circuit can be automatically realized without electric control through the movement of the main valve core under the action of different pressures, and the structure is more compact. Meanwhile, due to the fact that other control valves and control elements are reduced, application cost is lower.
In one embodiment, the first through-flow hole group comprises a first through-flow hole and a first damping hole which are arranged on the valve body, the first damping hole is arranged below the valve body and communicated with the first control cavity, and the first through-flow hole is communicated with one end of the first valve core channel.
In one embodiment, the second flow opening set includes a second flow opening on a side of the valve body adjacent to the first flow opening and a third flow opening above the second flow opening.
In an embodiment, first case passageway is including establishing first radial through-hole, the radial through-hole of second and the first axial hole in main valve core lower part, first radial hole of first axial hole intercommunication and the radial hole of second, and when main valve core was located the meso position, first through-hole and the radial through-hole of second intercommunication, second through-hole and first radial through-hole, first one-way case subassembly from down up the joint of joint at the radial through-hole of second and first axial through-hole cuts off first through-hole and second through-hole.
In one embodiment, the first axial through hole is a stepped hole structure with a large diameter at the lower end and a small diameter at the upper end, the first one-way valve core assembly comprises a one-way valve core and a second elastic part which pushes the one-way valve core upwards, the top of the one-way valve core is of a pointed cone structure, and the lower part of the one-way valve core forms a spring seat structure.
In one embodiment, the first elastic component comprises a first elastic part and a spring seat, the spring seat is arranged at the bottom of the valve body, the lower part of the main valve core is provided with annular convex parts at two sides of the first axial through hole, the outer side of the annular convex part of the main valve core is provided with an annular concave part, and the first elastic part is sleeved on the annular convex part of the main valve core; one end of the second elastic piece is abutted against the one-way valve core, and the other end of the second elastic piece is sleeved on the spring seat.
In one embodiment, a shoulder is formed on the upper portion of the valve body, and the third through-flow hole set comprises a fourth through-flow hole arranged below the shoulder and a second damping hole communicated with a second control cavity above the shoulder; the second elastic component comprises a plug, a third elastic part and a limiting seat, the plug is fixedly connected with the upper end of the valve body, the third elastic part is pressed on the shoulder of the valve body from top to bottom by the plug, and a first through hole matched with the convex part at the upper end of the main valve core is formed in the middle of the limiting seat.
In one embodiment, the main valve spool is provided with a first annular recess and a second annular recess on the outer side of the upper portion, the first annular recess is communicated with the fourth through-flow hole and extends upward when the main valve spool is located at the neutral position, and the second annular recess is communicated with the third through-flow hole and extends downward; when the main valve core moves downwards, the third through-flow hole is communicated with the fourth through-flow hole through the first annular concave part; when the main spool moves upward, the third through-flow hole communicates with the fourth through-flow hole via the second annular recess.
On the other hand, the invention provides a differential hydraulic circuit which comprises an oil source, an electromagnetic directional valve, a differential circuit switching valve and a hydraulic cylinder which are connected in sequence, wherein an oil port C of the electromagnetic directional valve is communicated with an oil port B1 of the differential circuit switching valve, an oil port D of the electromagnetic directional valve is communicated with an oil port A of the differential circuit switching valve, the oil port A of the differential circuit switching valve is connected with a rodless cavity of the hydraulic cylinder, and an oil port B of the differential circuit switching valve is connected with a rod cavity of the hydraulic cylinder; the differential circuit switching valve is the switching valve mentioned above.
In one embodiment, when the hydraulic cylinder is pushed to extend by oil of an oil port D of the electromagnetic directional valve, the oil of a rodless cavity of the hydraulic cylinder enters an oil port B, and a first one-way valve core assembly is pushed to flow to the oil port A from a first valve core channel of the differential circuit switching valve, so that differential quick extension of the hydraulic cylinder is realized; when the hydraulic control valve enters a working position, the load is increased to cause that the pressure of a first control cavity communicated with the oil port A of the differential circuit switching valve can overcome the acting force of the second elastic assembly, the main valve core moves upwards, and the oil port B of the differential circuit switching valve is communicated with the oil port B1 and returns to the oil port T through the oil port C of the electromagnetic directional valve; when the oil port P of the electromagnetic directional valve is communicated with the oil port C and the oil port D is communicated with the oil port T, the oil of the oil port C flows to the oil port B1 of the differential circuit switching valve to push the main valve core of the differential circuit switching valve to move downwards, the oil port B1 is communicated with the oil port B, and the oil enters the rodless cavity of the hydraulic cylinder to drive the hydraulic cylinder to retract.
Compared with the prior art, the differential hydraulic circuit has the advantages that:
the differential hydraulic circuit adopts the differential circuit switching valve and is matched with the electromagnetic directional valve to realize the automatic switching of three working conditions of hydraulic cylinder differential fast feeding, hydraulic cylinder working feeding and hydraulic cylinder retraction. When the differential fast-forward working condition is adopted, the electromagnetic directional valve is in the right position, the main valve core is in the middle position, and oil flowing out of the rod cavity pushes the one-way valve core to flow to the oil port A through the oil port B. When the hydraulic cylinder moves to a certain position, when the load rises, the pressure of the oil port A rises, the pressure of the connected first control cavity increases to push the main valve core to move upwards, and the oil of the oil port B returns to the oil tank through the oil port B1 and the right position of the electromagnetic directional valve, so that a large acting force can be output. Therefore, the switching between the fast-forward working condition and the working-feed working condition of the differential circuit can be automatically realized without electric control. Compared with the prior art, the use of control elements such as a one-way valve, a torque limiter, a controller and the like is reduced, the structure is more compact, and the cost is lower.
Drawings
Preferred embodiments of the present invention will be described in detail below with reference to the attached drawing figures, wherein:
FIG. 1 is a schematic structural diagram of one embodiment of a differential circuit switching valve of the present invention;
FIG. 2 is a schematic diagram of the differential circuit shift valve of the present invention with the main spool moving to the lower limit;
FIG. 3 is a schematic diagram of the differential circuit shift valve of the present invention with the main spool moved to the upper limit;
fig. 4 is a hydraulic schematic diagram of the differential circuit switching valve of the present invention.
Fig. 5 is a hydraulic schematic diagram of a differential hydraulic circuit including the differential circuit switching valve of the invention.
In the drawings, like parts are provided with like reference numerals. The figures are not drawn to scale.
Detailed Description
In order to make the technical solutions and advantages of the present invention more apparent, exemplary embodiments of the present invention are described in further detail below with reference to the accompanying drawings. It is clear that the described embodiments are only a part of the embodiments of the invention, and not an exhaustive list of all embodiments. And the embodiments and features of the embodiments may be combined with each other without conflict.
The inventor notices in the process of invention that although the existing hydraulic system can realize the conversion of the fast-forward working condition and the working-forward working condition of the hydraulic cylinder through the connection of the first reversing valve, the second reversing valve, the one-way valve, the torque limiter and the controller, the structure is complex, excessive valve members and electronic detection and control elements are included, and the application cost is high.
In view of the above disadvantages, an embodiment of the present invention provides a differential circuit switching valve, which will be described below.
Fig. 1 shows one embodiment of the differential circuit switching valve 13 of the present invention. In this embodiment, the differential circuit switching valve 13 of the present invention mainly includes: the valve comprises a valve body 1, a main valve core 5, a first elastic assembly, a first one-way valve core assembly and a second elastic assembly. The valve body 1 is provided with a first through-flow hole group communicated with the oil port a of the external valve block, a second through-flow hole group communicated with the oil port B of the external valve block and a third through-flow hole group communicated with the oil port B1 of the external valve block from bottom to top in the axial direction. The main valve core 5 is connected in the valve body 1, and a first valve core passage and a second valve core passage are arranged on the main valve core 5. A first resilient member is connected to the lower end of main spool 5 and forms a first control chamber 10 with the valve body and main spool 5. And the first one-way valve core assembly is connected to the first valve core channel of the main valve core 10 from bottom to top. The second elastic component is connected to the upper end of the main valve core and forms a second control chamber 11 with the valve body and the main valve core. The external valve block is an insertion valve block into which the differential circuit switching valve 13 used in the present invention is inserted.
In one embodiment, the valve body 1, the main spool 5, the first resilient assembly, the first check spool assembly, and the second resilient assembly of the present invention are configured to: when the pressure of the oil port A is low and the oil port B is fed, the oil enters the first valve core channel from at least one through hole in the second through hole group to push the first one-way valve core assembly aside, and the differential motion is realized by the flow of the oil from at least one through hole in the first through hole group to the oil port A.
In one embodiment, when the pressure of port a rises and the pressure entering the first control chamber 10 from the at least one through-flow hole of the first through-flow hole group pushes the main valve core to move towards the end (upward in fig. 1) of the second control chamber 11 against the action force of the second elastic assembly, the at least one through-flow hole of the second through-flow hole group is communicated with the third through-flow hole group, and the oil of port B flows to port B1 to realize the working feeding.
In one embodiment, when second control chamber 11 is filled with oil and main spool 5 compresses first resilient component to reverse direction of main spool 5, third through-flow orifice set is communicated with at least one through-flow orifice in second through-flow orifice set, and second through-flow orifice set is not communicated with first through-flow orifice set.
In one embodiment, as shown in fig. 1, the first through-flow hole group essentially comprises a first through-flow hole 1.2 and a first damping hole 1.1 provided in the valve body 1. Wherein the first damping orifice 1.2 is provided below the valve body 1 and communicates with the first control chamber 10. The first through-flow opening 1.2 communicates with one end of the first valve disk channel.
In one embodiment, as shown in fig. 1, the second flow aperture group comprises essentially the second flow aperture 1.3 and the third flow aperture 1.4. The second through-flow opening 1.3 is located on the side of the valve body 1 close to the first through-flow opening 1.2, and the third through-flow opening 1.4 is located above the second through-flow opening 1.3.
In one embodiment, as shown in fig. 1, the first spool passage mainly includes a first radial through hole 5.3, a second radial through hole 5.5, and a first axial hole 5.4 provided in a lower portion of the main spool 5. Wherein the first axial bore 5.4 communicates the first radial through bore 5.3 with the second radial through bore 5.5. When the main valve element 5 is in the neutral position, the first through-opening 1.2 communicates with the second radial through-opening 5.5, and the second through-opening 1.3 communicates with the first radial through-opening 5.3, see fig. 1. The first one-way valve core assembly is clamped at the joint of the second radial through hole 5.5 and the first axial through hole 5.4 from bottom to top and separates the first through hole 1.2 and the second through hole 1.3. That is, when the oil pressure flowing from the second through-flow hole 1.3 to the first axial hole 5.4 is smaller than the opening pressure of the first check spool assembly, the first through-flow hole 1.2 is not communicated with the second through-flow hole 1.3.
In one embodiment, as shown in FIG. 1, the first axial bore 5.4 is a stepped bore configuration with a large diameter at the lower end and a small diameter at the upper end. In one embodiment, the first check spool assembly mainly includes a check spool 4 and a second resilient member 3 that urges the check spool 4 upward. The top of the one-way valve core 4 is a pointed cone structure, and the lower part of the one-way valve core 4 forms a spring seat structure.
In one embodiment, as shown in fig. 1, the first elastic assembly mainly includes a first elastic member 2 and a spring seat 9. Wherein, the spring seat 9 is arranged at the bottom of the valve body 1. The lower part of the main valve core 5 is provided with annular convex parts at two sides of the first axial through hole 5.4, the main valve core 5 is provided with an annular concave part at the outer side of the annular convex part, and the first elastic part 2 is sleeved on the annular convex part of the main valve core 5 or is abutted against the annular concave part of the main valve core 5. The upper end of the second elastic element 2 is abutted against the one-way valve core 4, and the lower end of the second elastic element 2 is sleeved and abutted against the spring seat 9.
In one embodiment, as shown in fig. 1, a shoulder is formed at the upper end of the valve body 1, and the third through-flow hole set includes a fourth through-flow hole 1.6 provided below the shoulder and a second orifice 1.5 communicating with the second control chamber 11 above the shoulder at the upper end of the valve body 1. The second elastic component mainly comprises a plug 8, a third elastic piece 7 and a limiting seat 6. Wherein, plug 8 and the upper end fixed connection of valve body 1, plug 8 from the top down with third elastic component 7 through spacing seat 6 crimping in the shoulder of valve body 1. Preferably, the middle of the limiting seat 6 is provided with a first through hole 6.1 which is matched with the upper end convex part of the main valve core 5, as can be seen in fig. 1 to 3.
In one embodiment, as shown in fig. 1, the upper outer side of the main spool 5 is provided with a first annular recess 5.1 and a second annular recess 5.2. When the main valve element 5 is in the middle position, the first annular recess 5.1 communicates with the fourth through-flow opening 1.6 and extends upwards. The second annular recess 5.2 communicates with the third through-flow aperture 1.4 and extends downwardly. When the main valve element 5 is moved downwards, the third through-opening 1.4 communicates with the fourth through-opening 1.6 via the first annular recess 5.1, as shown in fig. 2. When the main valve element 5 is moved upwards, the third flow opening 1.4 communicates with the fourth flow opening 1.6 via the second annular recess 5.2, as shown in fig. 3. The first annular recess 5.1 communicates with the second damping orifice 1.5.
On the other hand, fig. 5 shows a specific embodiment of the differential hydraulic circuit including the differential circuit switching valve 13 of the invention. In this embodiment, the differential hydraulic circuit mainly includes an oil source (not shown in fig. 5), a solenoid directional valve 12, a differential circuit switching valve 13, and a hydraulic cylinder 14, which are connected in this order. The port C of the electromagnetic directional valve 12 is communicated with the port B1 of the differential circuit switching valve 13, the port D of the electromagnetic directional valve 12 is communicated with the port a of the differential circuit switching valve 13, the port a of the differential circuit switching valve 13 is connected to the rodless cavity of the hydraulic cylinder 14, and the port B of the differential circuit switching valve 13 is connected to the rod cavity of the hydraulic cylinder 14. The differential circuit switching valve 13 is a switching valve as described above, and the hydraulic cylinder 14 is a differential hydraulic cylinder.
In one embodiment, as shown in fig. 5, when the hydraulic cylinder 14 is pushed to extend by the oil from the oil port D of the electromagnetic directional valve 12, the oil from the rodless chamber of the hydraulic cylinder 14 enters the oil port B, and pushes the first check valve core assembly away from the first valve core channel of the differential circuit switching valve 13 to flow to the oil port a, so as to achieve differential rapid extension of the hydraulic cylinder. When the hydraulic jack is in working process and the pressure of the first control chamber 10 communicated with the oil port a of the differential circuit switching valve 13 is increased to overcome the acting force of the second elastic component due to the load increase, the main valve spool 5 moves upwards, the oil port B of the differential circuit switching valve 13 is communicated with the oil port B1 (specifically, refer to the right working position in fig. 4), and returns to the oil port T through the oil port C of the electromagnetic directional valve 12 (the electromagnetic directional valve 12 is switched to the right position in fig. 5). When the oil port P of the electromagnetic directional valve is communicated with the oil port C and the oil port D is communicated with the oil port T (at this time, the electromagnetic directional valve in fig. 5 is switched to the left position), the oil of the oil port C flows to the oil port B1 of the differential circuit switching valve 13 to push the main valve core of the differential circuit switching valve to move downward, the oil port B1 is communicated with the oil port B, and the oil enters the rodless cavity of the hydraulic cylinder to drive the hydraulic cylinder to retract (refer to the left working position of the differential circuit switching valve 13 in fig. 4).
In one embodiment, as shown in fig. 1 to 5, the differential hydraulic circuit of the present invention operates as follows:
as shown in fig. 5, when the electromagnet on the right side of the electromagnetic directional valve 12 is energized, the electromagnetic directional valve 12 works in the right position, the hydraulic oil of the oil port P is communicated with the oil port D, and the hydraulic oil of the oil port C is communicated with the oil port T, so that the hydraulic oil of the oil port P reaches the oil port a of the differential circuit directional valve 13 of the present invention through the oil port D and simultaneously enters the rodless cavity of the hydraulic cylinder, the hydraulic oil of the oil port a enters the first control cavity 10 through the first damping hole 1.1, if the load of the hydraulic cylinder is lower at this time, the pressure of the oil port a is also lower, the thrust generated when the hydraulic oil pressure of the first control cavity 10 acts on the main valve core 5 is insufficient to overcome the acting force of the third elastic element 7, and at this time, the differential circuit directional valve 13 of the present. The oil in the oil port D of the electromagnetic directional valve 12 pushes the hydraulic cylinder 14 to move leftwards, the oil in the rod cavity of the hydraulic cylinder 14 enters the oil port B of the differential circuit switching valve 13, the oil in the oil port B enters the first radial through hole 5.3 and the first axial through hole 5.4 from the second through hole 1.3 and then acts on the one-way valve core 4 to overcome the acting force of the second elastic element 3 to move downwards, the oil flows into the second radial through hole 5.5 through the first axial through hole 5.4 and then flows to the oil port A, the differential function is realized, and the outward extending speed of the hydraulic cylinder 14 is very high. When the hydraulic cylinder 14 enters a working state, i.e. a load is large, the pressure of the port a rises, and the pressure of the first control chamber 10 rises, and when the thrust generated by the pressure of the first control chamber 10 acting on the main valve element 5 is sufficient to overcome the force generated by the third elastic element 7, the main valve element 5 moves upward and enters the position shown in fig. 3. At this time, the oil liquid of the oil port B enters the second annular concave portion 5.2 through the first through-flow hole 1.4, and then enters the oil port B1 through the fourth through-flow hole 1.6, the oil liquid of the oil port B1 returns to the oil port T through the oil port C of the electromagnetic directional valve 12, and the rodless cavity and the rod cavity of the hydraulic cylinder 14 are not communicated any more, so that a large output force is ensured.
When the left electromagnet of the electromagnetic directional valve 12 in fig. 5 is energized, the electromagnetic directional valve 12 works in the left position, the hydraulic oil of the oil port P is communicated with the oil port C, and the hydraulic oil of the oil port D is communicated with the oil port T, so that the hydraulic oil of the oil port P reaches the oil port B1 of the differential circuit switching valve 13 of the present invention through the oil port C, and the hydraulic oil of the oil port B1 enters the second control chamber 11 through the second damping hole 1.5, and acts on the main valve element 5 to push the main valve element 5 to move downward to the state shown in fig. 2 by overcoming the acting force of the first elastic element 2 and the second elastic element 3. Here, the oil from the port B1 enters the port B through the fourth through-flow hole 1.6, the first annular recess 5.1, and the third through-flow hole 1.4, and the port a is blocked, so that the hydraulic cylinder 14 is retracted. In the differential circuit switching valve 13 of the present invention, the acting force of the third elastic element 7 is much larger than the acting forces of the first elastic element 2 and the second elastic element 3, because the switching pressure entering the working process is relatively high, for example, 15-20 MPA. When hydraulic cylinder 14 is retracted, first elastic member 2 and the second elastic member may function, so that the pressure required for retraction of hydraulic cylinder 14 is not high.
While preferred embodiments of the present invention have been described, additional variations and modifications in those embodiments may occur to those skilled in the art once they learn of the basic inventive concepts. Therefore, the appended claims are intended to be construed to include preferred embodiments and all such changes and/or modifications as fall within the scope of the invention, and all such changes and/or modifications as are made to the embodiments of the present invention are intended to be covered by the scope of the invention.
Claims (10)
1. A differential circuit switching valve, comprising:
the valve body is sequentially provided with a first through-flow hole group communicated with an oil port A of the external valve block, a second through-flow hole group communicated with an oil port B of the external valve block and a third through-flow hole group communicated with an oil port B1 of the external valve block along the axial direction;
the main valve core is connected in the valve body, and a first valve core channel and a second valve core channel are arranged on the main valve core;
the first elastic component is connected to one end of the main valve core and forms a first control cavity together with the valve body and the main valve core;
the first one-way valve core assembly is connected to the first valve core channel of the main valve core;
the second elastic component is connected to the other end of the main valve core and forms a second control cavity together with the valve body and the main valve core; and is configured to:
when the pressure of the oil port A is lower than the set pressure of the second elastic assembly, and the oil port B is used for feeding oil, the oil enters the first valve core channel from at least one through hole in the second through hole group to push the first one-way valve core assembly away, and flows to the oil port A from at least one through hole in the first through hole group to realize differential motion;
when the pressure of the oil port A rises and the pressure entering the first control cavity from at least one through-flow hole in the first through-flow hole group overcomes the acting force of the second elastic assembly to push the main valve core to move towards the end where the second control cavity is located, at least one through-flow hole in the second through-flow hole group is communicated with the third through-flow hole group, and the oil liquid of the oil port B flows to the oil port B1 to realize working feeding;
when the second control cavity is filled with oil and pushes the main valve core to compress the first elastic assembly to realize the reversing of the main valve core, the third through-flow hole group is communicated with at least one through-flow hole in the second through-flow hole group, and the second through-flow hole group is not communicated with the first through-flow hole group.
2. The switching valve of claim 1, wherein the first through-flow hole set includes a first through-flow hole provided in the valve body and a first orifice hole provided below the valve body and communicating with the first control chamber, the first through-flow hole communicating with one end of the first spool passage.
3. The switching valve of claim 2, wherein the second flow aperture set includes a second flow aperture on a side of the valve body adjacent the first flow aperture and a third flow aperture above the second flow aperture.
4. The switching valve according to claim 3, wherein the first spool passage includes a first radial through hole, a second radial through hole and a first axial hole, the first radial through hole and the second radial through hole are arranged at a lower portion of the main spool, the first axial hole communicates with the first radial through hole and the second radial through hole, when the main spool is located at a middle position, the first through hole communicates with the second radial through hole, the second through hole communicates with the first radial through hole, and the first check spool assembly is clamped at a joint of the second radial through hole and the first axial hole from bottom to top to block the first through hole and the second through hole.
5. The switching valve according to claim 4, wherein the first axial hole has a stepped hole structure with a large diameter at a lower end and a small diameter at an upper end, the first check valve core assembly includes a check valve core and a second elastic member for pushing the check valve core upward, a top portion of the check valve core has a pointed cone-shaped structure, and a lower portion of the check valve core forms a spring seat structure.
6. The switching valve according to claim 5, wherein the first elastic member includes a first elastic member and a spring seat, the spring seat is provided at a bottom of the valve body, a lower portion of the main spool is formed with annular protrusions on both sides of the first axial hole, an annular recess is formed on an outer side of the annular protrusion of the main spool, and the first elastic member is fitted over the annular protrusion of the main spool; one end of the second elastic piece is abutted against the one-way valve core, and the other end of the second elastic piece is sleeved on the spring seat.
7. The switching valve according to claim 6, wherein the valve body is formed at an upper portion thereof with a shoulder, and the third through-flow hole group includes a fourth through-flow hole provided below the shoulder and a second orifice communicating with the second control chamber above the shoulder; the second elastic component comprises a plug, a third elastic part and a limiting seat, the plug is fixedly connected with the upper end of the valve body, the third elastic part is pressed on the shoulder of the valve body from top to bottom by the plug, and a first through hole matched with the convex part at the upper end of the main valve core is formed in the middle of the limiting seat.
8. The switching valve of claim 7, wherein the main spool has a first annular recess and a second annular recess on an upper outer side thereof, the first annular recess communicating with the fourth through-flow hole and extending upwardly and the second annular recess communicating with the third through-flow hole and extending downwardly when the main spool is in the neutral position; when the main valve core moves downwards, the third through-flow hole is communicated with the fourth through-flow hole through the first annular concave part; when the main spool moves upward, the third through-flow hole communicates with the fourth through-flow hole via the second annular recess.
9. The differential hydraulic circuit is characterized by comprising an oil source, an electromagnetic directional valve, a differential circuit switching valve and a hydraulic cylinder which are sequentially connected, wherein an oil port C of the electromagnetic directional valve is communicated with an oil port B1 of the differential circuit switching valve, an oil port D of the electromagnetic directional valve is communicated with an oil port A of the differential circuit switching valve, the oil port A of the differential circuit switching valve is connected with a rodless cavity of the hydraulic cylinder, and the oil port B of the differential circuit switching valve is connected with a rod cavity of the hydraulic cylinder; the differential circuit switching valve is the switching valve according to any one of claims 1 to 8.
10. The circuit of claim 9, wherein when the hydraulic cylinder is pushed to extend by the oil from the oil port D of the electromagnetic directional valve, the oil in the rod chamber of the hydraulic cylinder enters the oil port B, and pushes the first check valve core assembly to flow to the oil port a from the first valve core channel of the differential circuit switching valve, so as to realize differential rapid extension of the hydraulic cylinder; when the hydraulic control valve enters a working position, the load is increased to cause that the pressure of a first control cavity communicated with the oil port A of the differential circuit switching valve can overcome the acting force of the second elastic assembly, the main valve core moves upwards, and the oil port B of the differential circuit switching valve is communicated with the oil port B1 and returns to the oil port T through the oil port C of the electromagnetic directional valve; when the oil port P of the electromagnetic directional valve is communicated with the oil port C and the oil port D is communicated with the oil port T, the oil of the oil port C flows to the oil port B1 of the differential circuit switching valve to push the main valve core of the differential circuit switching valve to move downwards, the oil port B1 is communicated with the oil port B, and the oil enters the rod cavity of the hydraulic cylinder to drive the hydraulic cylinder to retract.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810057475.2A CN108561358B (en) | 2018-01-22 | 2018-01-22 | Differential circuit switching valve and hydraulic differential circuit |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810057475.2A CN108561358B (en) | 2018-01-22 | 2018-01-22 | Differential circuit switching valve and hydraulic differential circuit |
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| CN108561358A CN108561358A (en) | 2018-09-21 |
| CN108561358B true CN108561358B (en) | 2020-05-08 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108953633B (en) * | 2018-09-27 | 2019-08-23 | 上海江浪科技股份有限公司 | A kind of screw-in cartridge valve |
| CN110878779B (en) * | 2019-11-28 | 2021-07-23 | 浙江万得凯流体设备科技股份有限公司 | Pressure reducing valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2804096B2 (en) * | 1989-07-17 | 1998-09-24 | 住友重機械工業株式会社 | Hydraulic circuit in mold clamping device |
| CN1182849A (en) * | 1996-03-10 | 1998-05-27 | 三星重工业(株) | Mobno-block control valve with regeneration conduit |
| JP3942840B2 (en) * | 2001-04-20 | 2007-07-11 | 株式会社カワサキプレシジョンマシナリ | Hydraulic differential |
| CN104196775A (en) * | 2014-09-05 | 2014-12-10 | 酒泉奥凯种子机械股份有限公司 | Hydraulic control system with load feedback function |
| CN104358902B (en) * | 2014-10-15 | 2016-09-28 | 浙江华益精密机械股份有限公司 | A kind of pressure safety valve |
| CN104675807B (en) * | 2015-03-12 | 2017-01-04 | 徐州重型机械有限公司 | Differential hydraulic control system and method and crane |
| CN106438521A (en) * | 2016-11-11 | 2017-02-22 | 徐工消防安全装备有限公司 | Hydraulic circuit of the differential telescopic system and aerial work platform using hydraulic circuit of the differential telescopic system |
| CN107461516A (en) * | 2017-08-02 | 2017-12-12 | 北京航空航天大学 | A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve |
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Effective date of registration: 20200413 Address after: 264200 west of Ludong village, Yangting Town, Huancui District, Weihai City, Shandong Province (factory building of Weihai Luxing welding equipment factory) Applicant after: Weihai Yuhui Machinery Co., Ltd Address before: 315000 No. 510 Chuangyuan Road, Ningbo National High-tech Zone, Zhejiang Province Applicant before: Shao Likun |
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