CN109854563B - Pressure regulating and limiting combined overflow valve - Google Patents
Pressure regulating and limiting combined overflow valve Download PDFInfo
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- CN109854563B CN109854563B CN201910164757.7A CN201910164757A CN109854563B CN 109854563 B CN109854563 B CN 109854563B CN 201910164757 A CN201910164757 A CN 201910164757A CN 109854563 B CN109854563 B CN 109854563B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/024—Pressure relief valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/025—Pressure reducing valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/56—Control of an upstream pressure
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
Abstract
The invention discloses a combined overflow valve with pressure regulating and limiting functions, which belongs to the technical field of hydraulic overflow valves and comprises a valve body, a pressure regulating valve, a pilot valve, a pressure limiting valve and an electromagnetic emergency valve, wherein the valve body is provided with a flow passage, a valve element assembling cavity, a liquid inlet I, a liquid outlet I and a liquid outlet II; the pre-tightening force of the spring applied to the pilot valve can be adjusted by rotating the adjusting bolt; the pressure limiting valve is arranged above the pressure regulating valve and is coaxial with the pressure regulating valve cavity. The main valve core of the pressure limiting valve realizes balance by utilizing the hydraulic pressure at the inner side and the outer side, and once one end of the pressure limiting valve is released, the main valve core of the pressure limiting valve can be rapidly opened and released so as to ensure the safety of the system. The combined overflow valve can effectively avoid valve core resonance, automatically control pressure abnormality, has reasonable and compact valve body structure and high working stability of the pressure regulating valve.
Description
Technical Field
The invention relates to the technical field of hydraulic control valves, in particular to a pressure regulating and limiting combined overflow valve, which belongs to the range of a high-performance combined valve.
Background
Relief valves are an indispensable type of pressure control valve in hydraulic transmission systems, in which three main functions are played. And the first is a pressure regulating mechanism, so that the hydraulic system works in a constant pressure range. And secondly, a pressure limiting mechanism ensures that the hydraulic system does not exceed the highest pressure so as to ensure safety. And thirdly, a back pressure mechanism, such as a buffer brake of a hydraulic system, is used as an internal load. Pressure regulation and pressure limiting are the most important two functions of the relief valve and are an integral part of most hydraulic systems. When two overflow valves are simultaneously used for a hydraulic transmission system, one is used for regulating pressure, the other is used for limiting pressure, and as the control pressure of the two overflow valves is relatively close to each other, the spring stiffness of the two overflow valves is similar, and resonance is easy to generate, so that the normal of the hydraulic system is influenced. The common engineering solution is to stagger the mounting positions of the two relief valves, which has the disadvantage of resulting in an increased size of the hydraulic system. Therefore, it is necessary to design a combined relief valve with pressure regulating and limiting functions.
At present, the double overflow valves are combined to form a combined valve, which is simply combined with two valves for realizing the functions of multistage pressure regulation, pressure relief after pressure regulation, bidirectional pressure regulation and the like, and the combined valve is not mainly used for eliminating the resonance problem between the two valves. The most common three-purpose valve used for the single hydraulic prop of the coal mine is only provided with a sequential relation between overflow and pressure relief, and no obvious cooperative working mechanism exists between the two valves, and the three-purpose valve cannot be used for a common hydraulic system. The great-long group Ughu Xinghong hydraulic limited company provides an overflow safety valve (application number: 201610051737.5) for solving the problem of rapid overflow of a hydraulic support, and the hydraulic support does not have a pressure regulating function, and the accurate name of the patent is that the rapid overflow safety valve is more accurate. Chengshi YiKadet hydraulic pressure limited company proposes a bidirectional overflow valve (the application number is 201820164359.6) which can realize the positive and negative pressure regulation in two directions and is a simple superposition of two overflow valves.
Applicant's patent application in 2015 basically realized the function of opening the relief valve quickly when the relief valve exceeded its rated flow, but did not realize the relief valve to help its pressure stabilizing function when the relief valve was operating normally. At the same time, this patent has the following disadvantages: 1) The valve body flow passage is designed to be tortuous, the processing difficulty is high, and the process is complicated; 2) The main valve core is internally provided with a processing hole, and the processing of the hole is difficult; 3) The main valve, the pilot valve and the safety valve are arranged in parallel, and the volume of the valve body is larger; 4) The emergency procedure of example 1 and the safety procedure of example 2 are to use a manual rotation of the emergency pin to initiate the emergency procedure and the safety procedure, which may have human error; 5) The safety valve is arranged in parallel with the main valve, and the safety valve does not help the quick stability of the main valve.
In view of this, the main purpose of the present invention is: the cooperative work of the pressure regulating valve and the pressure limiting valve is realized (the pressure limiting valve helps the pressure regulating valve to quickly stabilize pressure during pressure regulation, and the pressure regulating valve helps the pressure regulating valve to quickly release pressure during pressure regulation), and meanwhile, the structure and the performance of the combination valve are further optimized.
Disclosure of Invention
Aiming at the defects of the prior art, the invention discloses a combined overflow valve with pressure regulating and pressure limiting functions, which can solve the resonance problem when double overflow valves coexist, and construct a cooperative working mechanism between the two, in particular a mechanism of a pressure limiting valve for assisting a pressure regulating valve to stably work, thereby further improving the pressure regulating and pressure limiting performances of the pressure regulating valve.
In order to achieve the above purpose, the invention is realized by the following technical scheme: the utility model provides a combination overflow valve with pressure regulating and pressure limiting function, includes valve body, air-vent valve, pilot valve, pressure limiting valve and electromagnetism emergency valve, the valve body have the runner, case assembly chamber, inlet I, outlet II, its characterized in that: one side of the pressure regulating valve cavity is communicated with the liquid inlet I, the other side of the pressure regulating valve cavity is connected with the pilot valve through a flow channel, the pilot valve is communicated with the liquid outlet II, and the pilot valve cavity is communicated with the pressure regulating valve spring cavity through the flow channel; the pre-tightening force of the spring applied to the pilot valve can be adjusted by rotating the adjusting bolt; the pressure limiting valve is arranged above the pressure regulating valve and is coaxial with the pressure regulating valve cavity; the pressure limiting valve is communicated with the liquid outlet II through a flow passage, a damping hole II is formed in the main valve core of the pressure limiting valve, the main valve core of the pressure limiting valve realizes balance by utilizing hydraulic pressure on the inner side and the outer side, and once one end of the pressure limiting valve is depressurized, the main valve core of the pressure limiting valve can be rapidly opened and depressurized so as to ensure the safety and stability of the system.
Preferably: the main valve core of the pressure regulating valve is provided with a conical valve core, an extension rod, a damping hole I and an annular groove, wherein the damping hole I is arranged on flanges at two sides of the main valve core of the pressure regulating valve and is symmetrical with the central line of the main valve core of the pressure regulating valve; the annular groove is arranged on the extension bar.
Preferably: the flange and the extension bar have the area A of the lower side of the flange 1 The upper side area of the flange is A 2 Area A of the extended rod end 3 ，A 1 And A is a 2 +A 3 Approximately equal, p at static pressure equilibrium 1 A 1 ＝p 2 A 2 +p 3 A 3 Hydraulic force f=p acting on the extended rod end 3 A 3 The fluctuation of the main valve core part of the pressure regulating valve can be counteracted.
Preferably: the main valve core of the pressure regulating valve is axially provided with a liquid outlet I, the cone valve core is far away from the liquid inlet I, and one end of the cone valve core is inserted into the liquid outlet I and can slide in the axial direction of the liquid outlet I.
Preferably: the pilot valve is provided with a pre-tightening mechanism which comprises a pilot spring and an adjusting bolt, wherein the adjusting bolt is used for applying pre-tightening force to the pilot spring and can axially adjust the position along the valve body.
Preferably: the pressure limiting valve comprises a pressure limiting spring and a pressure limiting valve main valve core, one end of the pressure limiting spring is in contact with the valve body, and the other end of the pressure limiting spring is connected with the pressure limiting valve main valve core; the main valve core of the pressure limiting valve is provided with a damping hole II.
Preferably: the diameter of the pressure regulating valve liquid inlet and outlet is smaller than that of the pressure limiting valve liquid inlet and outlet.
Preferably: the main valve core of the pressure regulating valve is arranged in the valve body, and the valve body is provided with an assembly cavity matched with the appearance of the main valve core of the pressure regulating valve.
Preferably: the combined overflow valve is provided with an electromagnetic emergency valve, and the electromagnetic emergency valve is arranged on a flow passage between the pressure limiting valve cavity and the liquid outlet II.
Compared with the prior art, the double-overflow valve assembly comprises the prior double-overflow valve assembly and the patent (an overflow valve with pressure regulating and safety functions, application number: 201510898227.7), and has the following beneficial effects:
1) And resonance of the valve core is effectively avoided. The main valve core spring of the pressure regulating valve and the main valve core spring of the pressure limiting valve have smaller elastic modulus, and the valve core spring of the pilot valve has larger elastic modulus, so that the valve core resonance caused by the control pressure approaching of the traditional double overflow valve is effectively avoided.
2) The structure is reasonable and compact. Because the pressure regulating valve, the pressure limiting valve and the pilot valve are integrated together, the pilot valve and the pressure limiting valve are arranged in parallel and are respectively arranged on the left side and the upper side of the main valve core of the pressure regulating valve, the middle is communicated through the flow passage, and the pressure regulating valve and the pilot valve share one liquid inlet, so that the structure is more reasonable and compact.
3) And automatically controlling the pressure abnormality. The combined overflow valve is provided with the electromagnetic emergency valve, the electromagnetic emergency valve can be started under emergency conditions to ensure the safety of the system pressure, compared with manual rotation of the emergency pin, the manual operation error is reduced, the safer, faster and more accurate starting of the emergency valve is achieved, the pressure relief is carried out, the system pressure is stabilized, and the safety and the stability of the system pressure are ensured.
4) The pressure regulating stability is high. The pressure with the same fluctuation or fluctuation is applied to the two ends of the main valve core of the pressure regulating valve, so that the stability of the main valve core of the pressure regulating valve is improved, the flow impact of the pilot valve is reduced, and the pressure regulating stability is improved. The area of the lower side of the flanges at the two sides of the main valve core of the pressure regulating valve is A 1 The upper side area of the flange is A 2 The area of the lengthened rod end is A 3 The following equilibrium relationship exists: a is that 1 >A 2 And A is 1 ＝A 2 +A 3 The liquid in the pressure limiting valve cavity is applied to the area A of the lengthened rod end of the main valve core of the pressure regulating valve 3 The hydraulic pressure of (c) can help to improve the steady state performance of the main valve element of the pressure regulating valve and to stabilize rapidly when the pressure regulating valve core is in operation.
Drawings
In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only embodiments of the invention and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a front view of embodiment 1 of the present invention;
FIG. 2 is a cross-sectional view at A-A in FIG. 1;
FIG. 3 is a cross-sectional view at B-B in FIG. 1;
FIG. 4 is a cross-sectional view at C-C in FIG. 1;
FIG. 5 is a top view of invention example 1;
FIG. 6 is a cross-sectional view at D-D in FIG. 5;
FIG. 7 is a state diagram of the relief valve during the pressure limiting process of example 1;
FIG. 8 is an enlarged view of a portion of FIG. 7 at Q;
fig. 9 is a perspective view of the valve body of embodiment 1;
FIG. 10 is a cross-sectional view of a main valve spool of the pressure regulating valve;
FIG. 11 is a pressure chart of the main valve element of the pressure regulating valve;
FIG. 12 is a perspective view of a main valve core of the pressure regulating valve;
FIG. 13 is a top view of example 2;
FIG. 14 is a cross-sectional view taken at E-E of FIG. 13;
fig. 15 is a front view of embodiment 2;
FIG. 16 is a cross-sectional view taken at F-F in FIG. 15;
in the figure, 1, a valve body, 2, a pressure regulating valve, 3, a pilot valve, 4, a pressure limiting valve, 5, an electromagnetic emergency valve, 11, a liquid inlet I, 12, a flow passage I, 13, a liquid outlet I, 14, a flow passage II, 15, a flow passage III, 16, a flow passage IV, 17, a liquid outlet II, 18, a flow passage V, 121, an oil cavity, 122, a liquid inlet II, 123, a liquid outlet III, 21, a pressure regulating valve main valve core, 22, a pressure regulating spring, 23, a damping hole I, 24, an annular groove, 31, a pilot valve core, 32, a pilot spring, 33, an adjusting bolt, 41, a pressure limiting valve main valve core, 42, a damping hole II, 43, a pressure limiting spring, 44, a plug, 51, an electromagnetic valve core, 52 and a solenoid valve spring.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. All other embodiments, which can be made by one of ordinary skill in the art without inventive effort, are intended to be within the scope of the present invention, based on the embodiments herein.
Example 1
As shown in fig. 2, fig. 3, fig. 4, fig. 6 and fig. 11, the combined overflow valve with the functions of pressure regulation and pressure limiting according to the embodiment of the invention is composed of five parts: the valve body 1, the pressure regulating valve 2, the pilot valve 3, the pressure limiting valve 4 and the electromagnetic emergency valve 5 are formed, one side of the pressure regulating valve 2 is communicated with the liquid inlet I, the other side of the pressure regulating valve 2 is connected with the pilot valve 3 through a flow passage II, the pilot valve 3 is communicated with the liquid outlet II, and the pilot valve cavity is communicated with the spring cavity of the pressure regulating valve through the flow passage; the pre-tightening force of the spring applied to the pilot valve 3 can be adjusted by rotating the adjusting bolt; the pressure limiting valve 4 is arranged above the pressure regulating valve 2 and is coaxial with the main valve cavity of the pressure regulating valve; the pressure limiting valve 4 is communicated with the liquid outlet II through a flow passage, a damping hole II is formed in a main valve core of the pressure limiting valve, and the main valve core of the pressure limiting valve realizes balance by utilizing hydraulic pressure on the inner side and the outer side. The method can be divided into three working processes of a pressure regulating process, a pressure limiting process and an emergency pressure releasing process.
The working principle of the pressure regulating process is as follows:
(1) the pressure goes from zero to the pre-opening stage of the pilot valve.
The fluid flows into the valve body 1 from the liquid inlet I11 and then is divided into two paths, one path enters the lower cavity of the flange of the main valve core 21 of the pressure regulating valve to form the pressure p 1 ，p 1 Acting on the lower side of the flange of the main valve core 21 of the pressure regulating valve, the acting area is A 1 The method comprises the steps of carrying out a first treatment on the surface of the Then the fluid enters the upper cavity of the flange of the main valve core 21 of the pressure regulating valve through the damping hole I23 to form the pressure p 2 ，p 2 Acting on the upper side of the flange of the main valve core 21 of the pressure regulating valve, the acting area is A 2 . The other path of fluid enters the spring cavity of the pressure limiting valve through the damping hole II 42 to form the pressure p 3 The pressure at the liquid inlet I11 is lower in the initial stage, at the moment, the pressure limiting valve is not opened, the fluid is in a static state, static pressure is formed at the inner side and the outer side of the main valve core 41 of the pressure limiting valve, the main valve core 41 of the pressure limiting valve is kept closed under the action of the static pressure and the pressure limiting spring 43, and the pressure p in the spring cavity of the pressure limiting valve 3 ，p 3 The lengthened rod end acts on the main valve core 21 of the pressure regulating valve, and the acting area is A 3 . The pressure at the liquid inlet I11 in the initial stage is lower, fluid in the upper cavity of the flange of the main valve core 21 of the pressure regulating valve acts on the pilot valve core 31 through the flow passage II 14, the hydraulic pressure acting on the pilot valve core 31 is smaller than the designated pressure of the pilot spring 32 at the moment, the pilot valve core 31 keeps a closed state under the action of the spring force, and fluid at the upper side and the lower side of the flange of the main valve core 21 of the pressure regulating valve is static fluid at the moment, so the static pressure p is high 2 ＝p 3 . The pressure regulating valve main spool 21 is operated at the hydraulic pressure f=p 3 A 3 Pressure regulating spring force F t And the liquid outlet I13 is kept in a closed state under the action of dead weight and is not opened.
The balance of the main valve core 21 of the pressure regulating valve is different from that of a common pilot relief valve, as shown in fig. 6, 11 and 12, the area of the lower side of the flange of the main valve core of the pressure regulating valve is A 1 Static pressure is p 1 The area of the lower side of the flange is A 2 Static pressure is p 2 The area of the lengthened rod end of the main valve core of the pressure regulating valve is A 3 Static pressure is p 3 The main valve core of the pressure regulating valve receives 3 end face hydrostatic pressures p 1 A 1 、p 2 A 2 、p 3 A 3 And pressure regulating spring force F t The static equilibrium equation is: p is p 1 A 1 ＝p 2 A 2 +p 3 A 3 +F t . Due to the end face A 3 Hydraulic pressure p on 3 And inlet pressure p 1 The pressure regulating and limiting combined overflow valve has the same fluctuation rule, can partially offset the fluctuation of inlet pressure, and improves the pressure stabilizing performance of the pressure regulating and limiting combined overflow valve.
(2) And a stage after the pilot valve is opened.
When the pressure of the upper side fluid pressure on the flange of the main valve core 21 of the pressure regulating valve is larger than the designated pressure of the pilot valve 3 spring and smaller than the pressure limiting pressure when the pressure of the liquid inlet I11 is increased, the pilot valve core 31 is opened under the action of hydraulic pressure against the designated pressure of the pilot spring 32, the upper side fluid on the flange of the main valve core 21 of the pressure regulating valve enters the pilot valve spring cavity, the pressure regulating valve spring cavity and the liquid outlet II 17 through the flow channel 14 and flows into the oil tank, and at the moment, the upper side fluid pressure p on the flange of the main valve core 21 of the pressure regulating valve is under the blocking action of the damping hole I23 on the main valve core 21 of the pressure regulating valve 2 Reducing below flange-lower fluid pressure p 1 The pressure difference deltap is formed on the upper side and the lower side of the flange of the pressure regulating valve main valve core 21, and the pressure regulating valve main valve core 21 overcomes the lengthened rod end hydraulic pressure f=p of the pressure regulating valve main valve core under the action of the pressure difference deltap 3 A 3 Pressure regulating spring force F t And the self-weight opening is carried out, the liquid outlet I13 is opened, and fluid flows into the oil tank from the liquid outlet I13, so that a pressure regulating mechanism is realized. At this time, the opening of the main valve core 21 of the pressure regulating valve is smaller, the annular groove 24 of the lengthened rod of the main valve core of the pressure regulating valve does not form a channel with the valve body 1, and the pressure limiting valve spring cavity and the pressure regulating valve spring cavity are not communicated. At this stage, no matter how the inlet pressure fluctuates, the regulator valve main spool 21 can adjust the valve port opening by the pressure difference, thereby maintaining the stability of the outlet pressure due to the end face a 3 Hydraulic pressure p on 3 Pressure p below the flange of main valve core of pressure regulating valve 1 Has the following characteristics ofThe same fluctuation rule can partially offset the fluctuation of inlet pressure, and the stability of the main valve core of the pressure regulating valve is improved.
The pressure limiting process comprises the following steps: when the pressure of the liquid inlet I11 reaches the specified pressure of the pressure limiting valve, the main valve core 21 overcomes the hydraulic force F=p of the lengthened rod end of the main valve core under the action of hydraulic force 3 A 3 Pressure regulating spring force F t And dead weight moves to the uppermost end, the annular groove 24 on the extension rod of the pressure regulating valve main valve core 21 and the valve body 1 form a channel, so that the pressure limiting valve spring cavity is communicated with the pressure regulating valve spring cavity, fluid in the pressure limiting valve spring cavity enters the pressure regulating valve spring cavity through the annular groove 24 and flows to the pilot valve spring cavity and then flows out of the liquid outlet II 17 to the oil tank, and under the blocking effect of the damping hole II 42 on the pressure limiting valve main valve core 41, the fluid pressure p at the inner side of the pressure limiting valve main valve core 41 3 Reducing the pressure p of the fluid at the inlet I11 of the main valve core 41 of the pressure limiting valve to be lower than the low pressure 1 The pressure difference is formed on the inner side and the outer side of the main valve core 41 of the pressure limiting valve, and the main valve core 41 of the pressure limiting valve overcomes the pressure limiting spring force F under the action of the pressure difference t1 And the valve is opened, the fluid at the inlet of the main valve core 41 of the pressure limiting valve flows into the pilot valve cavity through the flow channel III 15 and then flows into the oil tank through the liquid outlet II 17, the main valve core 41 of the pressure limiting valve is opened rapidly and depressurized, the safety and the stability of the system are ensured, and the pressure limiting mechanism is realized.
In the emergency pressure relief process, when the pressure of the inlet of the system is overlarge and exceeds the pressure relief range of the overflow valve or emergency occurs, the electromagnetic emergency valve 5 can be started to enable the pressure limiting valve spring cavity to be communicated with the flow passage of the liquid outlet II 17, the fluid in the pressure limiting valve spring cavity flows into the oil tank through the liquid outlet II 17 via the flow passage, and under the blocking effect of the damping hole II 42 on the pressure limiting valve main valve core 41, the fluid pressure p at the inner side of the pressure limiting valve main valve core 41 3 Reducing the pressure p of the fluid at the inlet I11 of the main valve core 41 of the pressure limiting valve to be lower than the low pressure 1 The pressure difference is formed on the inner side and the outer side of the main valve core 41 of the pressure limiting valve, and the main valve core 41 of the pressure limiting valve overcomes the pressure limiting spring force F under the action of the pressure difference t1 The valve is opened, the fluid at the inlet of the main valve core of the pressure limiting valve flows into the pilot valve cavity through the flow passage III 15 and then flows into the oil tank through the liquid outlet II 17, so that the aim of quick pressure relief is fulfilled, the phenomenon that the pressure of the combined overflow valve system is continuously increased is prevented, and the aim ofThe emergency protection function, and then the safety and stability of the overflow valve are better protected.
Example 2
Fig. 6 and 13 are two different implementation modes of the pressure regulating and limiting combined relief valve and the basic idea is the same, and the opening of the pressure limiting valve is controlled by the displacement of the main valve core of the pressure regulating valve.
As shown in fig. 11, 13, 14 and 15, the combined overflow valve with the pressure regulating and limiting functions according to the embodiment of the invention is composed of five parts: the electromagnetic emergency valve comprises a valve body, a pressure regulating valve, a pilot valve, a pressure limiting valve and an electromagnetic emergency valve, wherein a pressure limiting valve main valve core 41 and a pressure regulating valve main valve core 21 are vertically arranged, the valve body is provided with a liquid inlet I11, a liquid inlet II 122, a liquid outlet I13, a liquid outlet II 17 and a liquid outlet III 123, and the electromagnetic emergency valve 5 is arranged between an oil cavity 121 and the liquid outlet III 123. The pilot valve 3 is communicated with a liquid outlet II 17, and the pressure limiting valve 4 is communicated with a liquid outlet III 123. The method can be divided into three working processes of a pressure regulating process, a pressure limiting process and an emergency pressure releasing process.
The working principle of the pressure regulating process is as follows:
(1) the pressure goes from zero to the pre-opening stage of the pilot valve.
Fluid enters the lower cavity of the flange of the main valve core 21 of the pressure regulating valve from the liquid inlet I11 to form the pressure p 1 ，p 1 Acting on the lower side of the flange of the main valve core 21 of the pressure regulating valve, the acting area is A 1 The method comprises the steps of carrying out a first treatment on the surface of the Then the fluid enters the upper cavity of the flange of the main valve core 21 of the pressure regulating valve through the damping hole I23 to form the pressure p 2 ，p 2 Acting on the upper side of the flange of the main valve core 21 of the pressure regulating valve, the acting area is A 2 . Fluid enters the pressure limiting valve cavity from the liquid inlet II 122 through the damping hole II 42 to form the pressure p 3 The pressure at the liquid inlet II 122 in the initial stage is lower, at the moment, the pressure limiting valve is not opened, the fluid is in a static state, static pressure is formed at the inner side and the outer side of the main valve core 41 of the pressure limiting valve, the main valve core 41 of the pressure limiting valve is kept closed under the action of the static pressure and the pressure limiting spring 43, and the pressure p in the spring cavity of the pressure limiting valve 3 ，p 3 The lengthened rod end acts on the main valve core 21 of the pressure regulating valve, and the acting area is A 3 . The pressure at the position of the liquid inlet I11 in the initial stage is lower, and the fluid in the upper cavity of the flange of the main valve core 21 of the pressure regulating valve passes through the flow passage II14 act on the pilot valve core 31, at this time, the fluid pressure acting on the pilot valve core 31 is smaller than the designated pressure of the pilot spring 32, the pilot valve core 31 is kept in a closed state under the action of the spring force, at this time, the fluid at the upper and lower sides of the flange of the pressure regulating valve main valve core 21 is static fluid, so the static pressure p is 2 ＝p 3 . Pressure regulating valve main spool 21 lengthens rod end hydraulic pressure f=p at pressure regulating valve main spool 21 3 A 3 Pressure regulating spring force F t And the liquid outlet I13 is kept in a closed state under the action of dead weight and is not opened.
The balance of the main valve core 21 of the pressure regulating valve is different from that of a common pilot relief valve, as shown in fig. 6, 11 and 12, the area of the lower side of the flange of the main valve core of the pressure regulating valve is A 1 Static pressure is p 1 The area of the lower side of the flange is A 2 Static pressure is p 2 The area of the lengthened rod end of the main valve core of the pressure regulating valve is A 3 Static pressure is p 3 The main valve core of the pressure regulating valve receives 3 end face hydrostatic pressures p 1 A 1 、p 2 A 2 、p 3 A 3 And pressure regulating spring force F t The static equilibrium equation is: p is p 1 A 1 ＝p 2 A 2 +p 3 A 3 +F t . Due to the end face A 3 Hydraulic pressure p on 3 And inlet pressure p 1 The pressure regulating and limiting combined overflow valve has the same fluctuation rule, can partially offset the fluctuation of inlet pressure, and improves the pressure stabilizing performance of the pressure regulating and limiting combined overflow valve.
(2) And a stage after the pilot valve is opened.
When the pressure of the liquid inlet I11 is increased, and the pressure of the liquid on the flange upper side of the main valve core 21 of the pressure regulating valve is larger than the opening pressure of the pilot valve 3 and smaller than the pressure limiting pressure, the pilot valve core 31 is opened under the action of hydraulic pressure, the liquid on the upper side of the flange upper side of the flow channel 14 and the main valve core of the pressure regulating valve flows into the oil tank from the liquid outlet II 17, and the pressure p of the liquid on the flange upper side of the main valve core 21 of the pressure regulating valve is reduced under the action of the obstruction of the damping hole I23 on the main valve core 21 of the pressure regulating valve 2 Reducing below flange-lower fluid pressure p 1 The pressure difference deltap is formed on the upper side and the lower side of the flange of the pressure regulating valve main valve core 21, and the pressure regulating valve main valve core 21 overcomes the lengthened rod end hydraulic pressure f=p of the pressure regulating valve main valve core 21 under the action of the pressure difference deltap 3 A 3 Pressure regulating spring force F t And the liquid outlet I13 is opened under the action of dead weight, and fluid flows into the oil tank from the liquid outlet I13, so that a pressure regulating mechanism is realized. At this time, the opening degree of the main valve core 21 of the pressure regulating valve is smaller, the annular groove 24 on the extension rod of the main valve core 21 of the pressure regulating valve does not form a channel with the valve body 1, and the oil cavity 121 is not communicated with the spring cavity of the pressure regulating valve. At this stage, the regulator valve main spool 21 can adjust the valve port opening by the pressure difference regardless of fluctuation of the inlet pressure, thereby maintaining the stability of the outlet pressure.
The pressure limiting process comprises the following steps: when the pressure of the liquid inlet is higher than the pressure limiting pressure, the main valve core 21 of the pressure regulating valve moves to the highest position, the annular groove 24 on the extension rod of the main valve core 21 of the pressure regulating valve forms a channel with the valve body 1, the fluid in the oil cavity 121 enters the spring cavity of the pressure regulating valve through the annular groove 24 and then flows into the oil tank from the liquid outlet II 17 through the flow channel 18, and the fluid pressure p at the inner side of the main valve core 41 of the pressure limiting valve is under the blocking effect of the damping hole II 42 on the main valve core 41 of the pressure limiting valve 3 Reducing the fluid pressure p at the inlet II 122 of the main valve core 41 of the pressure limiting valve to be lower than the low pressure 1 The pressure difference is formed on the inner side and the outer side of the main valve core 41 of the pressure limiting valve, and the main valve core 41 of the pressure limiting valve overcomes the pressure limiting spring force F under the action of the pressure difference t1 And the opening is carried out, the fluid of the liquid inlet II 122 flows out rapidly through the liquid outlet III 123, the main valve core 41 of the pressure limiting valve is opened rapidly and depressurized, the safety and stability of the system are ensured, and the pressure limiting mechanism is realized.
During emergency pressure relief, when the pressure at the inlet of the system is too high and exceeds the pressure relief range of the overflow valve or emergency occurs, the electromagnetic emergency valve 5 can be opened to open a flow passage between the oil cavity 121 and the liquid outlet III 123, so that the fluid in the oil cavity 121 and the spring cavity of the pressure limiting valve flows into the oil tank from the liquid outlet III 123, and at the moment, under the blocking effect of the damping hole II 42 on the main valve core 41 of the pressure limiting valve, the fluid pressure p at the inner side of the main valve core 41 of the pressure limiting valve 3 Reducing the fluid pressure p at the inlet II 122 of the main valve core 41 of the pressure limiting valve to be lower than the low pressure 1 The pressure difference is formed on the inner side and the outer side of the main valve core 41 of the pressure limiting valve, and the main valve core 41 of the pressure limiting valve overcomes the pressure limiting spring force F under the action of the pressure difference t1 The opening is carried out, the fluid in the liquid inlet II 122 flows out rapidly through the liquid outlet III 123, the purpose of rapid pressure relief is achieved, and the pressure of the overflow valve system is prevented from continuously risingThe phenomenon occurs, and the safety and stability of the overflow valve system are better protected.
Claims (6)
1. The utility model provides a combination overflow valve with pressure regulating and pressure limiting function, includes valve body (1), air-vent valve (2), pilot valve (3), pressure limiting valve (4) and electromagnetism emergency valve (5), valve body (1) have the runner, case assembly chamber, inlet I (11), liquid outlet I (13), liquid outlet II (17), its characterized in that: one side of the pressure regulating valve (2) is communicated with the liquid inlet I (11), the other side of the pressure regulating valve is connected with the pilot valve (3) through a flow passage II (14), the pilot valve (3) is communicated with the liquid outlet II (17), and the pilot valve cavity is communicated with the pressure regulating valve spring cavity through the flow passage; the spring pretightening force applied to the pilot valve (3) can be adjusted by rotating the adjusting bolt (33); the pressure limiting valve (4) is arranged above the pressure regulating valve (2) and is coaxial with the main valve cavity of the pressure regulating valve; the pressure limiting valve is communicated with the liquid outlet II (17) through a flow passage, a damping hole II is formed in a main valve core (41) of the pressure limiting valve, and the main valve core (41) of the pressure limiting valve realizes balance by utilizing hydraulic pressure on the inner side and the outer side; the pressure regulating valve main valve core (21) is provided with a conical valve core, flanges, an extension rod, damping holes I (23) and annular grooves (24), wherein the damping holes I (23) are arranged on the flanges on two sides of the pressure regulating valve main valve core (21) and are symmetrical relative to the central line of the pressure regulating valve main valve core (21); the annular groove (24) is arranged on the extension bar; the flange and the extension bar have the following areasA 1 The upper side area of the flange isA 2 Area of the extended rod endA 3 ，A 1 And (3) withA 2 +A 3 Approximately equal, when static pressure is balancedp 1 A 1 ＝p 2 A 2 +p 3 A 3 Hydraulic power acting on the extended rod endF＝p 3 A 3 The fluctuation of the main valve core part of the pressure regulating valve can be counteracted; the electromagnetic emergency valve (5) is arranged on a flow passage between the pressure limiting valve cavity and the liquid outlet II (17).
2. The combined relief valve with pressure regulating and limiting functions according to claim 1, wherein: the pressure regulating valve main valve core (21) is axially provided with a liquid outlet I (13), the cone valve core is far away from the liquid inlet I (11), and one end of the cone valve core is inserted into the liquid outlet I (13) and can slide in the axial direction of the liquid outlet I (13).
3. The combined relief valve with pressure regulating and limiting functions according to claim 1, wherein: the pilot valve (3) is provided with a pre-tightening mechanism which comprises a pilot spring (32) and an adjusting bolt (33) which is used for exerting pre-tightening force on the pilot spring (32) and can axially adjust the position along the valve body (1).
4. The combined relief valve with pressure regulating and limiting functions according to claim 1, wherein: the pressure limiting valve (4) comprises a pressure limiting spring (43) and a pressure limiting valve main valve core (41), one end of the pressure limiting spring (43) is in contact with the valve body (1), and the other end of the pressure limiting spring is connected with the pressure limiting valve main valve core (41).
5. A combined relief valve with pressure regulating and limiting functions according to claim 3, characterized in that: the pressure limiting valve cavity and the pressure regulating valve spring cavity are coaxial and are communicated up and down through a flow passage; the pressure limiting valve cavity is communicated with the electromagnetic emergency valve (5) through a flow passage to form a liquid outlet II (17).
6. The combined relief valve with pressure regulating and limiting function according to claim 5, wherein: the pressure regulating valve main valve core (21) is arranged in the valve body (1), and the valve body (1) is provided with an assembling cavity matched with the shape of the pressure regulating valve main valve core (21).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910164757.7A CN109854563B (en) | 2019-03-05 | 2019-03-05 | Pressure regulating and limiting combined overflow valve |
| LU101583A LU101583B1 (en) | 2019-03-05 | 2019-12-30 | Combined overflow valve with pressure regulating and limiting functions |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910164757.7A CN109854563B (en) | 2019-03-05 | 2019-03-05 | Pressure regulating and limiting combined overflow valve |
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| Publication Number | Publication Date |
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| CN109854563A CN109854563A (en) | 2019-06-07 |
| CN109854563B true CN109854563B (en) | 2023-08-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910164757.7A Active CN109854563B (en) | 2019-03-05 | 2019-03-05 | Pressure regulating and limiting combined overflow valve |
Country Status (2)
| Country | Link |
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| CN (1) | CN109854563B (en) |
| LU (1) | LU101583B1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113236622B (en) * | 2021-05-28 | 2023-05-30 | 北京天玛智控科技股份有限公司 | Constant-difference overflow valve and intelligent power generation hydraulic system |
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| Publication number | Publication date |
|---|---|
| CN109854563A (en) | 2019-06-07 |
| LU101583B1 (en) | 2020-09-18 |
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