CN112879193B - Method and device for analyzing motion of valve rod of motion sealing coupling part - Google Patents

Method and device for analyzing motion of valve rod of motion sealing coupling part Download PDF

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Publication number
CN112879193B
CN112879193B CN202110126373.3A CN202110126373A CN112879193B CN 112879193 B CN112879193 B CN 112879193B CN 202110126373 A CN202110126373 A CN 202110126373A CN 112879193 B CN112879193 B CN 112879193B
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valve rod
pressure
valve
force
fuel
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CN112879193A (en
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张可
周明
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Tsinghua University
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Tsinghua University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The present disclosure relates to a method and a device for analyzing the movement of a valve rod of a moving sealing coupling part, wherein the method comprises the following steps: determining the clamping stagnation state of the valve rod according to the working condition of the engine; determining the one-dimensional axial force axially applied to the valve rod according to the clamping stagnation state of the valve rod, the working condition of the engine, the structural information of the valve rod and the performance parameters of fuel oil; and determining the driving force required for axially moving the valve rod according to the one-dimensional axial force. According to the motion analysis method for the valve rod of the motion sealing coupling part, the multidimensional and mutually coupled force borne by the valve rod can be fitted into a one-dimensional stress, so that the analysis of the motion process of the valve rod is greatly simplified, the occupation of operation resources is reduced, the efficiency of the motion analysis of the valve rod is improved, and the motion analysis method can adapt to the scenes of motion analysis and motion control of the valve rod under complex working conditions.

Description

Method and device for analyzing motion of valve rod of motion sealing coupling part
Technical Field
The present disclosure relates to the field of computer technologies, and in particular, to a method and an apparatus for analyzing a valve rod motion.
Background
The dynamic characteristics of the electric control high-pressure fuel injection system refer to the characteristics and basic rules of the electric control high-pressure fuel injection system in the dynamic working process, and mainly comprise the dynamic response characteristics of a system electromagnetic valve, the dynamic hydraulic characteristics of a high-pressure and low-pressure hydraulic system, the dynamic motion characteristics of high-speed motion sealing coupling parts such as an electromagnetic valve rod/a control piston/a needle valve and the like. Good dynamic characteristics determine the flexibility, sensitivity, adjustability, stability and consistency of the dynamic control of the system. How to obtain the dynamic characteristics of the system which meet the use requirements, including the dynamic response characteristics of a driving mechanism (such as a solenoid valve, a piezoelectric crystal actuator or a hydraulic mechanism and the like), the dynamic hydraulic characteristics of a hydraulic system and the dynamic motion characteristics of a high-speed motion sealing coupling part, is a key technical problem for designing an electric control high-pressure fuel injection system.
The dynamic response process of the electric control high-pressure fuel injection system is a complex coupling process involving electromagnetic force, static hydraulic pressure, dynamic hydraulic damping force and structural power. There are complex coupling relationships for several major forces that affect the dynamic response process: the electromagnetic force is coupled with the peak current; peak current is coupled to the magnetic field and peak voltage; valve stem velocity and valve stem displacement coupling; the dynamic hydraulic damping force is coupled with the valve rod speed; the static hydraulic pressure is coupled with the displacement of the valve rod; friction force is coupled with static hydraulic pressure; the spring force is coupled with the valve rod displacement; the impact force is coupled with the valve stem velocity.
Due to the coupling effect of the multidimensional acting forces in the moving process of the valve rod, many difficulties exist in the aspect of controlling the valve rod to move, for example, the calculation amount for analyzing the multidimensional acting forces is huge, the processing resources are more occupied, the requirement on the calculation force is high, the multidimensional acting forces are difficult to analyze through an onboard processing device of an engine or a vehicle-mounted ECU (Electronic Control Unit), and further the scheme for controlling the valve rod to move is difficult to realize.
Disclosure of Invention
The present disclosure provides a method and a device for analyzing the motion of a valve rod of a motion sealing coupling.
According to an aspect of the present disclosure, there is provided a method for analyzing motion of a valve stem of a kinematic seal coupling, including: determining the clamping stagnation state of the valve rod according to the working condition of the engine; determining a one-dimensional axial force axially applied to the valve rod according to the clamping stagnation state of the valve rod, the working condition of an engine, the structural information of the valve rod and the performance parameters of fuel oil, wherein the one-dimensional axial force comprises the friction force applied to the valve rod; and determining the driving force required for axially moving the valve rod according to the one-dimensional axial force.
In a possible implementation manner, the one-dimensional axial force includes a spring force, wherein the determination of the one-dimensional axial force applied to the valve rod in the axial direction according to the clamping stagnation state of the valve rod, the engine operating condition, the structural information of the valve rod, and the performance parameter of the fuel includes: and determining the spring force according to the performance parameters of the spring and the valve rod lift.
In one possible implementation manner, the one-dimensional axial force includes a flow field pressure, the flow field pressure includes a high-pressure hydraulic pressure, the engine operating condition includes a cam lift, a cam rotation angle, a cam rotation speed, and an ambient pressure, the structural information of the valve rod includes a plunger diameter, a valve port sealing surface ring surface diameter, an electromagnetic valve port gap, a valve port half-cone angle, a valve port flow coefficient, and a maximum total volume of the high-pressure chamber, and the performance parameter of the fuel includes a fuel density, where the one-dimensional axial force applied to the valve rod in the axial direction is determined according to a clamping stagnation state of the valve rod, the engine operating condition, the structural information of the valve rod, and the performance parameter of the fuel, and the one-dimensional axial force includes: determining the high-pressure fuel inlet flow of the valve rod according to the cam lift, the cam rotation angle, the cam rotation speed and the plunger diameter; determining the outlet flow of the high-pressure fuel according to the pressure of the high-pressure fuel and the pressure of the external environment; determining the fuel pressure in the high-pressure cavity according to the high-pressure fuel outlet flow, the high-pressure fuel inlet flow, the valve port outlet flow, the maximum total volume of the high-pressure cavity, the diameter of the plunger and the cam lift; and determining the high-pressure liquid pressure according to the gap of the valve port of the electromagnetic valve, the diameter of the ring surface of the sealing surface of the valve port, the fuel pressure in the high-pressure cavity, the fuel density of the high-pressure cavity, the flow coefficient of the valve port and the half cone angle of the valve.
In one possible implementation manner, the one-dimensional axial force includes a flow field pressure, the flow field pressure includes a low-pressure hydraulic pressure, and determining the one-dimensional axial force axially applied to the valve rod according to a clamping stagnation state of the valve rod, an engine operating condition, structural information of the valve rod, and a performance parameter of fuel includes: and determining the low-pressure hydraulic pressure according to the low-pressure fuel pressure and the action area of the low-pressure fuel.
In one possible implementation manner, the one-dimensional axial force includes a viscous damping force, the structural information of the valve rod includes a gap width of a valve rod guide sealing section, a length of the valve rod guide sealing section, and a diameter of the valve rod guide sealing section, and the performance parameters of the fuel include a viscosity coefficient and a dynamic viscosity of the fuel, where the one-dimensional axial force received by the valve rod in the axial direction is determined according to a clamping state of the valve rod, an engine operating condition, structural information of the valve rod, and the performance parameters of the fuel, and the method includes: determining the sealing gap flow of the valve rod according to the gap width of the valve rod guide sealing section, the length of the valve rod guide sealing section, the viscosity coefficient of the fuel oil of the diameter of the valve rod guide sealing section and the dynamic viscosity; and determining the viscous damping force according to the flow of the sealing gap.
In one possible implementation manner, the one-dimensional axial force includes squeeze film resistance, the engine operating condition includes a valve rod movement speed and a valve rod stroke, and the structural information of the valve rod includes an armature maximum air gap, where the one-dimensional axial force received in the axial direction of the valve rod is determined according to a clamping state of the valve rod, an engine operating condition, the structural information of the valve rod, and a performance parameter of fuel, and the one-dimensional axial force includes: and determining the squeeze film resistance according to the valve rod movement speed, the valve rod stroke and the armature maximum air gap.
In one possible implementation manner, the one-dimensional axial force includes a collision force, the engine operating condition includes a relative initial speed between a valve rod and a plug and a lift of the valve rod, and the structural information of the valve rod includes a maximum stroke and a valve half cone angle of the valve rod, wherein the one-dimensional axial force axially applied to the valve rod is determined according to a clamping stagnation state of the valve rod, the engine operating condition, the structural information of the valve rod, and a performance parameter of fuel, and the one-dimensional axial force includes: and determining the collision force according to the relative initial speed between the valve rod and the plug, the stroke of the valve rod, the maximum stroke of the valve rod and the valve half-cone angle.
In one possible implementation manner, the one-dimensional axial force includes an inertial force, the structural information of the valve rod includes a total mass and a spring mass of a moving part of the valve rod, and the engine operating condition includes a stroke of the valve rod, wherein the one-dimensional axial force axially applied to the valve rod is determined according to a clamping state of the valve rod, the engine operating condition, the structural information of the valve rod, and a performance parameter of fuel, and the one-dimensional axial force includes: the inertial force is determined from the total mass of the moving parts of the valve stem, the spring mass and the stroke of the valve stem.
In a possible implementation manner, determining a one-dimensional axial force applied to the valve rod in the axial direction according to a clamping stagnation state of the valve rod, an engine working condition, structural information of the valve rod, and a performance parameter of fuel, includes: under the condition that a valve rod is clamped, three-dimensional motion analysis is carried out on the valve rod according to the working condition of the engine, the structural information of the valve rod, the performance parameters of the fuel oil and the motion parameters of the valve rod, and the radial load of the valve rod is obtained; determining the static friction coefficient of the valve rod and the valve body according to the performance parameters of the valve rod and the valve body and the radial load; and determining the maximum static friction force of the valve rod according to the static friction coefficient and the radial load.
In a possible implementation manner, determining a one-dimensional axial force applied to the valve rod in the axial direction according to a clamping stagnation state of the valve rod, an engine working condition, structural information of the valve rod, and a performance parameter of fuel, includes: and under the condition that the valve rod is not clamped, determining the dynamic friction force of the valve rod according to the dynamic friction coefficient between the valve rod and the valve body and the radial load of the valve rod.
According to an aspect of the present disclosure, there is provided a motion analysis apparatus for a valve stem of a kinematic seal coupling, comprising: the clamping stagnation state module is used for determining the clamping stagnation state of the valve rod according to the working condition of the engine; the axial force module is used for determining one-dimensional axial force axially applied to the valve rod according to the clamping stagnation state of the valve rod, the working condition of an engine, the structural information of the valve rod and the performance parameters of fuel oil, and the one-dimensional axial force comprises friction force applied to the valve rod; and the driving force module is used for determining the driving force required by the axial movement of the valve rod according to the one-dimensional axial force.
In one possible implementation, the one-dimensional axial force includes a spring force, wherein the axial force module is further to: and determining the spring force according to the performance parameters of the spring and the valve rod lift.
In one possible implementation manner, the one-dimensional axial force includes a flow field pressure, the flow field pressure includes a high-pressure hydraulic pressure, the engine operating condition includes a cam lift, a cam rotation angle, a cam rotation speed, and an ambient pressure, the structural information of the valve rod includes a plunger diameter, a valve port sealing surface ring surface diameter, an electromagnetic valve port gap, a valve port half-cone angle, a valve port flow coefficient, and a maximum total volume of the high-pressure chamber, and the performance parameter of the fuel includes a fuel density, where the axial force module is further configured to: determining the high-pressure fuel inlet flow of the valve rod according to the cam lift, the cam rotation angle, the cam rotation speed and the plunger diameter; determining the outlet flow of the high-pressure fuel according to the pressure of the high-pressure fuel and the pressure of the external environment; determining the fuel pressure in the high-pressure cavity according to the high-pressure fuel outlet flow, the high-pressure fuel inlet flow, the valve port outlet flow, the maximum total volume of the high-pressure cavity, the diameter of the plunger and the cam lift; and determining the high-pressure liquid pressure according to the gap of the valve port of the electromagnetic valve, the diameter of the ring surface of the sealing surface of the valve port, the fuel pressure in the high-pressure cavity, the fuel density of the high-pressure cavity, the flow coefficient of the valve port and the half cone angle of the valve.
In one possible implementation, the one-dimensional axial force comprises a flow field pressure, the flow field pressure comprises a low pressure hydraulic force, and the axial force module is further configured to: and determining the low-pressure hydraulic pressure according to the low-pressure fuel pressure and the action area of the low-pressure fuel.
In one possible implementation manner, the one-dimensional axial force includes a viscous damping force, the structural information of the valve rod includes a valve rod guide sealing section gap width, a valve rod guide sealing section length, and a valve rod guide sealing section diameter, and the performance parameters of the fuel include a viscosity coefficient and a dynamic viscosity of the fuel, where the axial force module is further configured to: determining the sealing gap flow of the valve rod according to the gap width of the valve rod guide sealing section, the length of the valve rod guide sealing section, the viscosity coefficient of the fuel oil of the diameter of the valve rod guide sealing section and the dynamic viscosity; and determining the viscous damping force according to the flow of the sealing gap.
In one possible implementation, the one-dimensional axial force comprises squeeze film resistance, the engine operating condition comprises valve stem movement speed and valve stem travel, the valve stem structural information comprises armature maximum air gap, and the axial force module is further configured to: and determining the squeeze film resistance according to the valve rod movement speed, the valve rod stroke and the armature maximum air gap.
In one possible implementation, the one-dimensional axial force includes an impact force, the engine operating condition includes a relative initial velocity between the valve stem and the plug and a lift of the valve stem, the structural information of the valve stem includes a maximum stroke and a valve half-cone angle of the valve stem, and the axial force module is further configured to: and determining the collision force according to the relative initial speed between the valve rod and the plug, the stroke of the valve rod, the maximum stroke of the valve rod and the valve half-cone angle.
In one possible implementation, the one-dimensional axial force includes an inertial force, the structural information of the valve stem includes a total mass and a spring mass of a moving part of the valve stem, and the engine operating condition includes a stroke of the valve stem, wherein the axial force module is further configured to: the inertial force is determined from the total mass of the moving parts of the valve stem, the spring mass and the stroke of the valve stem.
In one possible implementation, the axial force module is further configured to: under the condition that a valve rod is clamped, three-dimensional motion analysis is carried out on the valve rod according to the working condition of the engine, the structural information of the valve rod, the performance parameters of the fuel oil and the motion parameters of the valve rod, and the radial load of the valve rod is obtained; determining the static friction coefficient of the valve rod and the valve body according to the performance parameters of the valve rod and the valve body and the radial load; and determining the maximum static friction force of the valve rod according to the static friction coefficient and the radial load.
In one possible implementation, the axial force module is further configured to: and under the condition that the valve rod is not clamped, determining the dynamic friction force of the valve rod according to the dynamic friction coefficient between the valve rod and the valve body and the radial load of the valve rod.
According to an aspect of the present disclosure, there is provided an electronic device including: a processor; a memory for storing processor-executable instructions; wherein the processor is configured to invoke the memory-stored instructions to perform the above-described method.
According to an aspect of the present disclosure, there is provided a computer readable storage medium having stored thereon computer program instructions which, when executed by a processor, implement the above-described method.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the disclosure. Other features and aspects of the present disclosure will become apparent from the following detailed description of exemplary embodiments, which proceeds with reference to the accompanying drawings.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the disclosure.
FIG. 1 illustrates a flow chart of a method of motion analysis of a moving seal couple valve stem according to an embodiment of the present disclosure;
FIG. 2 shows a schematic diagram of a monoblock pump according to an embodiment of the present disclosure;
FIG. 3 shows a schematic diagram of a unit pump solenoid valve arrangement according to an embodiment of the present disclosure;
FIG. 4 illustrates a schematic view of a valve stem of a unit pump solenoid valve arrangement according to an embodiment of the present disclosure;
5A, 5B, 5C, 5D show schematic views of a valve stem of a monoblock pump solenoid valve device according to an embodiment of the present disclosure;
FIG. 6 illustrates a schematic of a one-dimensional axial force experienced by a valve stem according to an embodiment of the present disclosure;
FIG. 7 shows a schematic diagram of a drive cam causing movement of a plunger according to an embodiment of the present disclosure;
FIGS. 8A and 8B show schematic diagrams of squeeze film resistance according to embodiments of the present disclosure;
FIG. 9 is a schematic diagram illustrating an application of a method for motion analysis of a moving seal couple valve stem according to an embodiment of the present disclosure;
FIG. 10 shows a block diagram of a kinematic sealing coupling valve stem motion analysis apparatus according to an embodiment of the present disclosure;
FIG. 11 shows a block diagram of an electronic device according to an embodiment of the present disclosure;
fig. 12 illustrates a block diagram of an electronic device in accordance with an embodiment of the disclosure.
Detailed Description
Various exemplary embodiments, features and aspects of the present disclosure will be described in detail below with reference to the accompanying drawings. In the drawings, like reference numbers can indicate functionally identical or similar elements. While the various aspects of the embodiments are presented in drawings, the drawings are not necessarily drawn to scale unless specifically indicated.
The word "exemplary" is used exclusively herein to mean "serving as an example, embodiment, or illustration. Any embodiment described herein as "exemplary" is not necessarily to be construed as preferred or advantageous over other embodiments.
The term "and/or" herein is merely an association describing an associated object, meaning that three relationships may exist, e.g., a and/or B, may mean: a exists alone, A and B exist simultaneously, and B exists alone. In addition, the term "at least one" herein means any one of a plurality or any combination of at least two of a plurality, for example, including at least one of A, B, C, and may mean including any one or more elements selected from the group consisting of A, B and C.
Furthermore, in the following detailed description, numerous specific details are set forth in order to provide a better understanding of the present disclosure. It will be understood by those skilled in the art that the present disclosure may be practiced without some of these specific details. In some instances, methods, means, elements and circuits that are well known to those skilled in the art have not been described in detail so as not to obscure the present disclosure.
Fig. 1 shows a flow chart of a method for analyzing the movement of a valve stem of a kinematic seal coupling according to an embodiment of the present disclosure, as shown in fig. 1, the method includes:
in step S11, determining the clamping stagnation state of the valve rod according to the working condition of the engine;
in step S12, determining a one-dimensional axial force applied to the valve rod in the axial direction according to the clamping stagnation state of the valve rod, the engine operating condition, the structural information of the valve rod, and the performance parameter of the fuel oil, where the one-dimensional axial force includes a friction force applied to the valve rod;
in step S13, a driving force required to axially move the valve stem is determined based on the one-dimensional axial force.
According to the valve rod motion analysis method disclosed by the embodiment of the disclosure, multidimensional and mutually coupled forces borne by the valve rod can be fitted into a one-dimensional stress, so that the analysis of the valve rod motion process is greatly simplified, the occupation of operation resources is reduced, the efficiency of valve rod motion analysis is improved, and the method can adapt to the scenes of motion analysis and motion control of the valve rod under complex working conditions.
In one possible implementation, the valve stem motion analysis method may be performed by an electronic device such as a terminal device or a server, the terminal device may be a User Equipment (UE), a mobile device, a User terminal, a cellular phone, a cordless phone, a Personal Digital Assistant (PDA), a handheld device, a computing device, a vehicle-mounted device, a wearable device, or the like, and the method may be implemented by a processor calling a computer readable instruction stored in a memory. Alternatively, the method may be performed by a server.
In a possible implementation mode, the valve rod can be used for an electric control high-pressure fuel injection system, and the high-speed motion sealing matching part of the electric control high-pressure fuel injection system mainly comprises a high-pressure oil pump plunger matching part, a monoblock pump high-speed powerful electromagnetic valve rod matching part, an electric control fuel injector control piston matching part, an electric control fuel injector needle valve matching part and the like. The valve rod of the solenoid valve device of the monoblock pump is stressed complexly and moves at a high speed under the action of electromagnetic force, hydraulic pressure, spring force, friction force and the like.
FIG. 2 shows a schematic diagram of a monoblock pump according to an embodiment of the present disclosure. The unit pump electromagnetic valve device shown in fig. 2 mainly comprises a valve rod, an electromagnet, an armature and the like, and can directly control the pressure of high-pressure oil and indirectly control the oil injection time by controlling the adsorption action of the electromagnet and the armature through current. The valve rod of the electromagnetic valve is positioned in a high-pressure flow field, is acted by three paths of high-pressure oil pressure of oil inlet, oil injection and oil drainage, and has a plurality of stress surfaces and a plurality of stress directions, and the stressed pressure changes along with the rotating speed and the closing and opening time of the valve port. The dynamic hydraulic characteristic fluctuation of the unit pump electromagnetic valve device is severe, the stress condition of the high-speed motion sealing matching part is complex, and the motion control difficulty of the valve rod is large.
FIG. 3 shows a schematic diagram of a unit pump solenoid valve arrangement according to an embodiment of the present disclosure. As shown in fig. 3, the solenoid valve device of the unit pump may include an electromagnet, an armature, a spring pad, a valve rod, a valve body, a plug, and the like. The gap between the electromagnet and the armature is a working air gap, fuel oil flows due to system oil supply and system oil return, the working air gap is immersed in a low-pressure flow field formed by the fuel oil flow to form a damping oil film, and the working air gap forms a low-pressure cavity of the unit pump electromagnetic valve device. In addition, the spring and the plug are also immersed in the low-pressure flow field, and a cavity for placing the spring in the cavity and a plug cavity form a low-pressure cavity of the unit pump electromagnetic valve device.
FIG. 4 shows a schematic view of a valve stem of a unit pump solenoid valve arrangement according to an embodiment of the present disclosure. As shown in fig. 4, the valve stem may include a valve port, a stem high pressure section, a pilot seal section, a spring mounting section, an armature mounting section, and a low pressure balancing bore. The guide sealing section is positioned in a guide hole in the valve body, the spring mounting end is used for mounting a spring, the diameter of the valve rod high-pressure section is smaller than that of the guide sealing section and the valve port, and a cavity between the valve rod high-pressure section and the valve body is a high-pressure cavity. When the plunger generates pressure on the fuel, the fuel pressure in the high pressure chamber increases.
Fig. 5A shows a schematic view of a valve stem of a unit pump solenoid valve device according to an embodiment of the present disclosure. As shown in fig. 5, in the figure, 1 is a low pressure chamber, 2 is a plug, 3 is a valve body, 4 is a high pressure chamber, 5 is a high pressure oil passage, 6 is a valve rod high pressure section, 7 is a valve rod guide sealing section, 8 is a spring, 9 is a spring mounting section, 10 is an armature, 11 is an electromagnet, and 12 is a valve port.
In a possible realization mode, when the electromagnet does not work, no magnetic force is generated, the valve port is contacted with the plug due to the spring force of the spring, and the high-pressure cavity is connected with the low-pressure cavity (the valve port is in an opening state). When the electromagnet works, if the electromagnetic force generated by the electromagnet can overcome the acting forces such as spring force, friction force and the like, the armature is adsorbed to the electromagnet, a gap is generated between the valve port and the plug, so that the low-pressure cavity is connected with the inner cavity of the valve rod, and the high-pressure cavity is sealed by the valve port, namely, the connection between the high-pressure cavity and the low-pressure cavity is disconnected (the valve port is in a closed state).
Fig. 5B shows a schematic view of a valve stem of a unit pump solenoid valve device according to an embodiment of the present disclosure. When the electromagnet does not work, no magnetic force is generated, and the valve port is in an opening state at the moment, namely, the high-pressure cavity is connected with the low-pressure cavity. At the moment, the plunger moves upwards, upward oil pressure is generated in the high-pressure oil duct, the pressure in the high-pressure cavity rises, but the valve port is opened at the moment, the fuel oil in the high-pressure cavity flows to the low-pressure cavity, and the low-pressure cavity is connected with the system oil return oil duct to generate a low-pressure oil duct. At this time, the pressure in the high-pressure cavity only rises to a small extent due to the pressure relief effect of the valve port. In this case, the electromagnet may be caused to operate, for example, by applying a voltage or a current through a drive circuit of the electromagnet, so that the electromagnet establishes a magnetic field to generate an electromagnetic force (attraction force) on the armature. If the electromagnet can overcome acting forces such as spring force, friction force and the like, the armature can drive the valve rod to move towards the direction that the working air gap is reduced, namely, the armature and the valve rod are adsorbed to the electromagnet by the electromagnet. At the moment, the valve port is gradually closed, the connecting channel between the high-pressure cavity and the low-pressure cavity is gradually reduced, the outflow of fuel flowing from the high-pressure cavity to the low-pressure cavity is reduced, the pressure relief effect of the low-pressure cavity is reduced, and the pressure rising speed in the high-pressure cavity is accelerated.
Fig. 5C shows a schematic view of a valve stem of a unit pump solenoid valve device according to an embodiment of the present disclosure. The electromagnet can work continuously, so that the valve port is closed completely, the high-pressure cavity and the low-pressure cavity are disconnected completely, fuel in the high-pressure cavity cannot flow into the low-pressure cavity, and the pressure relief effect disappears completely. At this time, if the plunger continues to move upward, that is, the pressure in the high-pressure oil passage continues to increase, the pressure in the high-pressure chamber may be caused to rise sharply. The high-pressure oil duct above can be connected with an oil nozzle, when the pressure in the high-pressure cavity exceeds the starting pressure of the oil nozzle, the needle valve of the oil injector is opened to start oil injection, so that the engine piston works. The pressure in the high-pressure chamber decreases as the injection process progresses. But the pressure in the high pressure chamber is still greater than the pressure in the low pressure chamber.
Fig. 5D shows a schematic view of a valve stem of a unit pump solenoid valve device according to an embodiment of the present disclosure. The electromagnet may be deactivated, for example, by stopping the application of the driving current or voltage to the electromagnet, the electromagnetic field and force of the electromagnet being lost, i.e. the electromagnet no longer exerts an attractive force on the ramp, at which point the valve stem begins to return under the action of the spring force, i.e. to move in a direction in which the working air gap of the armature increases. The valve port is gradually opened (not yet reaching a complete opening state), at this time, the pressure in the high-pressure cavity is still larger, the pressure in the high-pressure cavity is larger than the pressure in the low-pressure cavity and larger than the starting pressure of the fuel injection nozzle, the fuel in the high-pressure cavity and the fuel in the high-pressure oil duct simultaneously flow out from two channels of the fuel injection nozzle and the valve port, namely, the fuel in the high-pressure cavity flows to the low-pressure cavity while the fuel injection nozzle continues to inject fuel. In this case, if the plunger is in the upward state, when the flow rate of the fuel flowing out from the fuel injection nozzle and the valve port is larger than the upward pressurizing flow rate of the plunger, the pressure in the high-pressure chamber still keeps rising, but the rising speed is slower than that when the valve port is closed. When the flow of fuel oil flowing out from the fuel injection nozzle and the valve port is smaller than the flow of upward pressurization of the plunger, the pressure in the high-pressure cavity can be reduced. If the plunger is in a descending state, the pressure in the high-pressure cavity is reduced rapidly.
In one possible implementation, when the valve rod moves to a state that the valve port is completely opened, the connecting channel between the high-pressure cavity and the low-pressure cavity is completely opened, the pressure in the high-pressure cavity and the high-pressure oil way is rapidly reduced, and the oil injection nozzle stops injecting oil when the pressure is reduced to be lower than the injection starting pressure of the oil injection nozzle. At this time, the pressure in the high-pressure chamber fluctuates depending on the state of the plunger, but the pressure in the high-pressure chamber does not rapidly increase regardless of the upward or downward movement of the plunger. For example, when the plunger starts to suck oil downward after reaching the top dead center, the fuel in the high-pressure chamber and the low-pressure chamber can flow into the high-pressure oil path, that is, the movable chamber (plunger chamber) of the plunger.
In summary, the movement process of the valve rod can be subjected to various acting forces such as flow field pressure, friction force, spring force, electromagnetic force and the like of the fuel, and the acting forces can change along with the working period of oil injection. In addition, although the acting force applied on the valve rod is axial one-dimensional acting force theoretically, the valve rod can be subjected to the action of radial load because a sealing gap exists between the guide sealing section of the valve rod and the guide hole of the valve body. And under the action of the coupling force of multi-dimensional negative pressure, the valve rod can move laterally, swing and the like in a small scale in a radial direction in a three-dimensional gap space between the valve rod and the guide hole, so that a non-axisymmetric motion attitude can be caused, and the attitude can feed back and influence the complex coupling force borne by the valve rod, so that a complex dynamic motion process can be caused. When the position of the valve rod deviates from a balance point, the hydraulic distribution in the sealing gap is changed, the imbalance of radial force is further intensified, and the valve rod is collided under partial conditions, so that the friction force distribution is changed.
In a possible implementation mode, the real motion process is a three-dimensional complex coupling dynamic process which relates to dynamic electromagnetic force, fluid motion and damping force and structural dynamics, but under the constraint action of a valve body guide hole, a valve rod mainly carries out one-dimensional axial motion, and the processing resource occupation amount for analyzing the three-dimensional complex coupling dynamic motion process is large and is not suitable for being analyzed in an embedded processor configured for the engine, so that the three-dimensional complex coupling dynamic process carried out by the valve rod can be fitted into the one-dimensional dynamic process to adapt to the actual use scene of the engine.
In the example, under the limiting effect of the valve body guide hole, the motion mode of the valve rod is mainly axial motion, the valve rod is slightly radially deviated and deflected in the gap of the guide sealing hole, and the direction of the radial motion is mainly in the direction of the oil inlet and outlet high-pressure oil passage, so that the deviation motion of the valve rod can be simplified into a two-dimensional plane motion model, and the influence of radial load generated by the radial deviation in the two-dimensional plane direction on the friction force in the one-dimensional axial direction can be determined. That is, fitting a complex kinetic process to a one-dimensional kinetic process can be achieved by fitting three dimensions to two dimensions and one dimension.
In one possible implementation, the force to which the valve stem is subjected may vary with the duty cycle of the injection, as described above. Therefore, the working period of oil injection can be determined based on the working conditions and other parameters of the engine, and the acting force borne by the valve rod can be further determined.
And in the first stage, before the plunger begins to compress the oil supply, the valve rod is in a static state with balanced stress.
And in the second stage, after the plunger starts to compress the fuel supply, the valve rod deflects and deflects under the action of static hydraulic pressure on the valve port and the high-pressure section of the valve rod due to the jet impact force and the bypass pressure difference of the high-pressure fuel oil moving at high speed on the valve rod.
And in the third stage, when the valve rod deviates and deflects, the valve rod guide sealing section and the fuel oil in the sealing gap move relatively to generate dynamic hydraulic pressure, and meanwhile, the three-dimensional static hydraulic pressure in the inclined sealing gap also changes. The time required by the valve rod to deflect and collide with the valve body can be determined, and whether the valve body is collided and clamped or not can be judged by comparing the time required by closing the valve port with the time required by closing the valve port. In addition, the valve rod and the valve body may collide and contact with each other when the valve rod is subjected to random factors such as high-temperature and high-pressure deformation, machining errors, mechanical failures and the like.
And stage four, when the valve rod is collided and clamped with the valve body, the hydraulic pressure received by the valve port and the high-pressure section of the valve rod forms moment to the center of the valve rod, the hydraulic pressure received by the guide sealing section forms another moment, and the cooperation of the moments makes the valve rod have two possible motions: one is that the valve stem is impacted against the valve sleeve and is reacted by the valve sleeve. The other is that the valve stem is rotated parallel to the valve body, the deflection angle is reduced and stabilized at an angle, or parallel against the valve sleeve.
And step five, when the valve rod collides with the valve body and abuts against the valve sleeve, determining the pressure between the valve rod and the valve sleeve according to the balanced force system. Whether the contact point is elastically or plastically deformed can be judged according to the magnitude of the pressure, and the static friction coefficient and the maximum static friction force can be determined.
And stage six, the valve rod is required to overcome the maximum static friction force when the valve rod starts to move, and the sliding friction force is required to be overcome during the movement process. The electromagnetic force required for closing the valve port against the friction force can be determined according to the friction force.
In one possible implementation, the valve rod undergoes the above six stages during the movement of the valve rod during the injection cycle, and the movement of the valve rod can be analyzed based on the above six stages.
In one possible implementation, to determine the one-dimensional axial force (including friction) experienced by the valve stem, it is first determined whether the valve stem is stuck, i.e., in the case of sticking, the static friction force to be overcome for the valve stem movement is different from the sliding friction force to be overcome without sticking.
In one possible implementation, in step S11, it may be determined whether the valve stem is stuck. When the plunger starts to compress the fuel supply, the valve rod is subjected to jet impact force and bypass pressure difference of high-pressure fuel on the valve rod, so that the valve rod deflects and deflects. At this time, the three-dimensional static hydraulic pressure in the sealing gap is changed due to the deviation and deflection of the valve rod, so that the valve rod and the valve body are possibly collided and clamped, and the valve body is possibly abutted against the valve sleeve. The process of abutting can cause the radial load to change, so that the friction force borne by the valve rod changes. At the moment, the friction force borne by the valve rod when the valve rod does not move in the axial direction is not ordinary static friction force, but is static friction force after clamping, the static friction coefficient of the valve rod when the valve rod is subjected to the static friction force during clamping can be determined, and the static friction force at the moment can be determined. Therefore, when determining the friction force applied to the valve rod, whether the valve rod is blocked or not can be determined firstly, if the valve rod is blocked, the friction force can be determined through the radial load and the static friction coefficient when the valve rod is blocked, and if the valve rod is not blocked, the friction force can be determined through the radial load and the dynamic friction coefficient when the valve rod is not blocked.
In one possible implementation, the determination of whether the valve stem is stuck may be based on a parameter of engine operating conditions. In one example, the high pressure fuel pressure may be determined by engine operating conditions and compared to a theoretical pressure based on actual pressure sensed by a sensor, and if the two pressures differ significantly, the valve stem may become stuck. In addition, under the condition that the valve rod is subjected to random factors such as high-temperature and high-pressure deformation, machining errors and mechanical faults, the valve rod and the valve body can be in collision contact, and clamping stagnation is generated.
In the example, when the valve rod is not filled with oil, the two-dimensional motion of the valve rod only has driving force, no damping force exists, the state and the position can be changed rapidly, and the valve rod is easy to collide and block with the valve body before the valve port is seated.
In the example, the clamping stagnation can be reduced under the condition that the processing precision of the valve rod is high, the collision clamping stagnation of the valve rod can be reduced by properly increasing the length of the sealing section, but the weight and the processing deformation quantity of the valve rod can be influenced, the responsiveness of the valve rod is reduced, and the manufacturing cost of the valve rod is increased.
In one possible implementation, in step S12, a one-dimensional axial force that needs to be overcome by the valve stem in the movement, i.e., the force that the valve stem is subjected to during the axial movement, may be determined. As described above, the acting force of the valve rod in motion is related to the injection period, that is, related to the operating condition of the engine, and the one-dimensional axial force of the valve rod in the axial direction can be determined based on the operating condition of the engine, and the structural information (for example, parameters such as size and material) of the valve rod itself and the performance parameters (for example, parameters such as dynamic viscosity and density) of the fuel oil itself, where the one-dimensional axial force includes friction force, and the friction force can be related to the stuck state of the valve rod, that is, when the valve rod is stuck, the static friction force is large, so that the valve rod is difficult to move, and in the case of the stuck state, if the static friction force is to be overcome, a larger driving force (for example, electromagnetic force) is required to move.
FIG. 6 is a schematic diagram illustrating one-dimensional axial forces on a valve stem according to an embodiment of the disclosure, as shown in FIG. 6, the one-dimensional axial forces on the valve stem may include an electromagnetic force FmegAnd the friction force F between the guide sealing section valve rod and the guide hole of the valve bodyfricAnd also includes spring force FsprFlow field pressure (including high pressure fluid pressure F)hpAnd low pressure fluid force Flp) Viscous damping force FviscDamping oil resistance F generated by hindering armature movementwindAnd the impact force F between the valve stem and the plug or the valve seatbAnd the inertial force F of the valve-stem movementinertia. The one-dimensional axial force may vary during a fuel injection cycle, for example, the spring force may vary during the fuel injection cycle as a result of compression of the spring due to movement of the valve stem caused by attraction of the armature by an electromagnetic force that varies during the fuel injection cycle, thereby causing the spring force to vary during the fuel injection cycle. There is a correspondence between the stages of the injection cycle and the movement of the valve stem, so that the position of the valve stem, and hence the spring force, can be determined based on the injection cycle. Other one-dimensional axial forces may also have a corresponding relationship with the injection period. Go toThe injection period is related to the operating period of the engine, and thus, the injection period, and thus the one-dimensional axial force, may be determined based on the engine operating conditions. Further, the above-mentioned one-dimensional axial force has a coupling relationship, for example, the relationship between the spring force and the electromagnetic force as described above, and for example, the spring force and the friction force are forces that hinder the working air gap of the armature from decreasing, and during the movement of the valve stem toward the direction of decreasing working air gap, the spring force and the friction force also affect the inertia force of the valve stem during the movement. Due to the fact that the coupling relation exists, when the one-dimensional axial force borne by the valve rod is determined, the oil injection period can be determined according to the working condition of the engine, and then the magnitude of each acting force in the determined period is determined.
In one possible implementation, the one-dimensional axial force comprises a spring force FsprWherein step S12 includes: and determining the spring force according to the performance parameters of the spring and the valve rod lift.
In one possible implementation, the spring force FsprMay be determined by the precompression stroke of the spring, the lift of the valve stem, and a performance parameter of the spring (e.g., stiffness or spring rate). During engine operation, the valve stem may move according to a fuel injection cycle, and therefore, the valve stem travel may be determined based on the fuel injection cycle (which may include, for example, the direction of valve stem movement, i.e., whether the valve stem moves in a direction toward an increasing working air gap or a decreasing working air gap, and the position of the valve stem, i.e., the position the valve stem is currently in). Further, the pre-compression stroke of the spring may form the pre-load force of the spring. Furthermore, the elastic contact between the plug and the valve stem causes the valve stem to deform, which in turn affects the precompression stroke of the spring, which can therefore be corrected.
In an example, the spring force of the spring may be determined by the following equation (1):
Figure BDA0002924157150000081
wherein, Fspr0For spring pre-tension, ksprIs the spring rate, kbcapAnd s is the valve rod lift, which is the collision stiffness of the plug.
In one possible implementation, the one-dimensional axial force comprises a flow field pressure. The flow field pressure includes a high pressure hydraulic pressure and a low pressure hydraulic pressure. In the injection period, the pressure in the high-pressure cavity is changed along with the movement of the plunger, the acting force of the pressure in the high-pressure cavity on the valve rod is high-pressure hydraulic pressure, the magnitude of the high-pressure hydraulic pressure can be determined by the movement of the plunger, namely, the injection period, further, the injection period can be determined by the working condition of the engine, namely, the high-pressure hydraulic pressure can be determined by the working condition of the engine. The low pressure hydraulic pressure is caused by the action of the pressure in the low pressure cavity on the valve rod, and the pressure in the low pressure cavity and the pressure in the high pressure cavity have a certain relation, for example, when the valve port is opened, the high pressure cavity is communicated with the low pressure cavity, and the high pressure cavity releases pressure to the low pressure cavity, so that the pressure in the low pressure cavity can be changed.
In one possible implementation, when determining the high pressure hydraulic pressure, the high pressure hydraulic pressure may be calculated by engine operating conditions. The engine operating conditions may include cam lift, cam angle, cam speed, ambient pressure (i.e., fuel pressure within the high pressure chamber), etc. Furthermore, the structure information of the valve rod can be used for determining the high-pressure liquid pressure, and the structure information of the valve rod comprises the diameter of a plunger, the diameter of a ring surface of a valve port sealing surface, the gap of a valve port of the electromagnetic valve, the half cone angle of the valve port, the flow coefficient of the valve port and the maximum total volume of the high-pressure cavity. The high pressure hydraulic force is the force that the pressure of the fuel within the high pressure chamber exerts on the valve stem, and therefore, the high pressure hydraulic force may also be calculated based on the performance parameters of the fuel, which may include the fuel density within the high pressure chamber.
In one possible implementation, step S12 may include: determining the high-pressure fuel inlet flow of the valve rod according to the cam lift, the cam rotation angle, the cam rotation speed and the plunger diameter; determining the outlet flow of the high-pressure fuel according to the pressure of the high-pressure fuel and the pressure of the external environment; determining the fuel pressure in the high-pressure cavity according to the high-pressure fuel outlet flow, the high-pressure fuel inlet flow, the valve port outlet flow, the maximum total volume of the high-pressure cavity, the diameter of the plunger and the cam lift; and determining the high-pressure liquid pressure according to the gap of the valve port of the electromagnetic valve, the diameter of the ring surface of the sealing surface of the valve port, the fuel pressure in the high-pressure cavity, the fuel density of the high-pressure cavity, the flow coefficient of the valve port and the half cone angle of the valve.
In one possible implementation, the high-pressure hydraulic pressure in the high-pressure cavity is jointly determined by the plunger inlet flow, the valve port outlet flow and the fuel injector outlet flow. That is, the increase of the inlet flow of the plunger can increase the hydraulic pressure in the high-pressure cavity, and the outlet flow of the valve port and the outlet flow of the fuel injector can reduce the hydraulic pressure in the high-pressure cavity.
Fig. 7 shows a schematic diagram of a drive cam causing movement of a plunger according to an embodiment of the present disclosure. As shown in fig. 7, the driving cam can drive the plunger to move, for example, when the plunger moves upwards, the pressure in the plunger cavity increases, when the valve port is not closed, the pressure in the high-pressure cavity can be relieved through the valve port (at the oil inlet valve), and if the fuel injector (at the oil outlet valve) injects fuel, the pressure relief effect can also be achieved.
In one possible implementation, the inlet fuel flow to the plunger section may be determined first, followed by the outlet flow to the valve port and fuel injector. And then determining the fuel pressure in the high-pressure cavity according to the flow, and further determining the acting force of the fuel pressure on the valve rod, namely the high-pressure hydraulic pressure.
In one possible implementation mode, the inlet fuel flow of the plunger end face of the valve rod can be determined according to parameters such as cam lift, cam rotation angle, cam rotation speed and plunger diameter. The operating state of the cam can be determined according to the engine working condition parameters, and then the moving state of the plunger caused by the cam is determined, so that the inlet fuel flow of the end face of the plunger is determined.
In an example, the plunger end face inlet fuel flow may be determined according to the following equation (2):
Figure BDA0002924157150000091
wherein Q isin_pFor inlet of fuel flow to the end face of the plunger, dpIn order to be the diameter of the plunger,
wherein the cam lift may be determined by the following equation (3):
SCamProfile＝fCamProfile(θcam/6ncam) (3)
wherein S isCamProfileFor cam lift, θcamIs the cam angle in units of DEG PT, ncamIs the camshaft speed.
In one possible implementation, high pressure fuel may flow out of the high pressure chamber through the valve port and the fuel injector, and thus, the high pressure fuel outlet flow includes a valve port outlet flow and a fuel injector outlet flow.
In one possible implementation, when the fuel in the high pressure chamber flows out through the valve port, the fuel can flow to the low pressure chamber, therefore, the external environment pressure can include the fuel pressure of the low pressure chamber, and the valve port outlet flow of the valve rod can be determined according to the diameter of the valve port sealing surface ring surface, the gap of the electromagnetic valve port, the valve half-cone angle, the high pressure fuel pressure and the low pressure fuel pressure.
In an example, the valve port outlet flow may be determined according to the following equation (4):
Figure BDA0002924157150000092
wherein Q isout_mIs the valve port outlet flow, CvThe valve-port flow coefficient, e.g. 0.8, dmouthThe diameter of the annulus of the valve port sealing face, deltamouthIs the gap of the valve port of the electromagnetic valve, beta is the half cone angle of the valve, P0At low fuel pressure, PsIs the fuel pressure of the high pressure chamber.
Wherein, the valve port clearance of the electromagnetic valve can be determined according to the following formula (5):
Figure BDA0002924157150000101
where t is the operating time of the camshaft, t1Time of energization of the solenoid valve, t2Is the valve stem seating time, t3At the moment when the solenoid valve is de-energized, t4The moment when the solenoid valve is fully opened again. a isvalve_closeFor valve port closing acceleration, avalve_openAcceleration for opening the valve port.
In one possible implementation, assuming that the valve port opening and closing operation time period is constant and has a constant acceleration, the valve port closing acceleration and the valve port opening acceleration may be determined by the following equation (6):
Figure BDA0002924157150000102
wherein, TcloseTime consuming closing of the solenoid valve, TopenIt takes time for the solenoid valve to open. Deltamouth-maxThe maximum opening clearance of the valve port.
In one possible implementation, fuel may flow to the cylinder as it exits through the fuel injector, and thus, the external ambient pressure may comprise in-cylinder pressure. The outlet flow of the oil injector can be determined according to the number of the spray holes of the oil injector, the flow coefficient of the spray holes of the oil injector, the diameter of the spray holes of the oil injector, the outlet flow of a valve port, the oil injection pressure of the oil injector and the pressure in an air cylinder. In an example, the injector outlet flow may be determined according to equation (7) below:
Figure BDA0002924157150000103
wherein Q isout_iIs the outlet flow of the oil injector, i is the number of spray holes of the oil injector, Cv_iIs the flow coefficient of the injector orifice, diIs the diameter of the injector orifice, PiFor fuel injection pressure of fuel injector, Pcρ is the fuel density for the in-cylinder pressure.
Wherein the fuel density can be determined according to the following equation (8):
Figure BDA0002924157150000104
wherein T is the fuel temperature. Fuel pressure rho in a high pressure cavity can be determined based on real-time fuel temperatures。
In one possible implementation, the fuel pressure in the high-pressure chamber may be determined according to the fuel injector outlet flow, the plunger section inlet fuel flow, the valve port outlet flow, the maximum total volume of the high-pressure chamber, and the plunger diameter.
In one possible implementation, the equation of state of the fuel in the high pressure chamber may be determined by the following equation (9):
Figure BDA0002924157150000111
wherein K is the modulus of elasticity, V, of the fuelsIs the volume of the high pressure chamber.
Wherein the elastic modulus K of the fuel can be determined by the following formula (10):
K＝34.74(P+111061456.8-469742T)0.947 (10)
wherein P is the fuel pressure.
In one possible implementation, the fuel pressure in the high pressure chamber may be determined using equation (9) and the fuel injector outlet flow, plunger cross-section inlet fuel flow, and valve port outlet flow described above. In an example, the fuel pressure in the high pressure chamber may be determined according to the following equation (11):
Figure BDA0002924157150000112
wherein, VmaxIs the maximum total volume of the high pressure chamber.
In one possible implementation, after determining the fuel pressure in the high-pressure chamber, the force exerted on the valve stem by the fuel pressure in the high-pressure chamber, i.e., the high-pressure hydraulic pressure, may be determined. The high-pressure hydraulic pressure can be determined according to the gap of the valve port of the electromagnetic valve, the diameter of the ring surface of the sealing surface of the valve port, the fuel pressure in the high-pressure cavity, the fuel density of the high-pressure cavity, the flow coefficient of the valve port and the half cone angle of the valve.
In one possible implementation, the high pressure hydraulic forces to which the high pressure section of the valve stem is subjected are axially balanced. During the opening process of the valve port, the high-pressure section of the valve rod is subjected to unbalanced axial hydraulic pressure. For example, in the early stage of the opening stage of the valve port, the high pressure unbalanced force ratio is large because the fuel flowing out from the valve port is very high in speed and flow rate, the pressure drop at the valve port is large, and the reaction force of the movement of the high pressure fuel, namely the high pressure hydraulic force, is also large.
In one possible implementation, the high pressure hydraulic force may be determined kinematically, as the valve stem is subjected to the high pressure hydraulic force while moving (i.e., while the valve port is open). In an example, the high pressure hydraulic force may be determined by the following equation (12):
Figure BDA0002924157150000113
wherein the content of the first and second substances,
Figure BDA0002924157150000116
for valve port fuel mass flow, vfuelThe valve port fuel injection rate. In one example, the port fuel injection rate may be determined by equation (13) below:
Figure BDA0002924157150000115
in one possible implementation, the flow field pressure may also include a low pressure hydraulic force FlpStep S12 may include: and determining the low-pressure hydraulic pressure according to the low-pressure fuel pressure and the action area of the low-pressure fuel.
In the example, through the balanced design, there is the axis through-hole in the valve rod center, and is equipped with low pressure balance hole radially, can effectively restrain the influence of low pressure oil circuit pressure to the valve rod effect. Thus, the low pressure hydraulic force may be zero.
In one possible implementationIn this manner, the one-dimensional axial force may include a viscous damping force FviscThe gap between the guide sealing section of the valve rod and the guide hole of the valve body forms a circular seam, the circular seam can be soaked by fuel oil, and when the valve rod moves, the fuel oil in the circular seam can apply viscous damping force to the valve rod. The viscous damping force is related to the annular seam, namely, the structural information such as the size of the valve rod and the like, and is also related to performance parameters such as the viscosity of fuel oil and the like.
In a possible implementation manner, the one-dimensional axial force includes a viscous damping force, the structural information of the valve stem includes a valve stem guide sealing section gap width, a valve stem guide sealing section length, and a valve stem guide sealing section diameter, and the performance parameter of the fuel includes a viscosity coefficient and a dynamic viscosity of the fuel, where step S12 includes: determining the sealing gap flow of the valve rod according to the gap width of the valve rod guide sealing section, the length of the valve rod guide sealing section, the viscosity coefficient of the fuel oil of the diameter of the valve rod guide sealing section and the dynamic viscosity; and determining the viscous damping force according to the flow of the sealing gap.
In one possible implementation, the seal clearance flow may be determined first. Due to the pressure difference of the fuel oil in the high-pressure cavity and the low-pressure cavity, the fuel oil flows in the cavity. The fuel oil flows into the annular gap to form a sealing gap flow. In an example, the seal clearance flow may be determined by the following equation (14):
Figure BDA0002924157150000121
wherein d is the diameter of the valve rod guide sealing section, L is the length of the valve rod guide sealing section, mu is the viscosity coefficient of the fuel oil, and nu is the dynamic viscosity of the fuel oil.
In a possible implementation manner, the viscous damping force of the fuel in the seal clearance can be approximately solved according to the flow of the seal clearance, and the viscous damping force is determined. In an example, the viscous damping force F may be determined according to equation (15) belowvisc：
Figure BDA0002924157150000122
In one possible implementation, the one-dimensional axial force comprises squeeze film resistance Fwind。
Fig. 8A and 8B show schematic diagrams of squeeze film resistance with a working air gap between the electromagnet and the armature, as shown in fig. 8A, as the armature moves away from the electromagnet, the working air gap increases and fuel flows into the working air gap through the gap between the armature and the air gap adjustment block, which flow creates squeeze film resistance, i.e., squeeze film resistance is also overcome as the armature moves away from the electromagnet. As shown in fig. 8B, as the armature approaches the electromagnet, fuel in the working air gap is forced out of the working air gap through the gap between the armature and the air gap adjustment block, causing fuel flow, creating squeeze film resistance that needs to be overcome by the squeeze film resistance of the fuel in the working air gap.
In one possible implementation, the squeeze film resistance is related to the movement state of the valve stem, i.e. to the injection period, and also to the operating conditions of the engine, since the squeeze film resistance is generated during the movement of the valve stem. In an example, the engine operating conditions may include valve stem movement speed and valve stem travel. Further, squeeze film resistance is also related to structural information of the valve stem, such as the maximum air gap of the armature.
In one possible implementation, step S12 may include: and determining the squeeze film resistance according to the valve rod movement speed, the valve rod stroke and the armature maximum air gap. In an example, the squeeze film resistance can be determined according to the following equation (16):
Figure BDA0002924157150000123
wherein, deltamegIs armature air gap, δmaxIs the maximum air gap of the armature, u is the valve rod movement speed,shapeis in the shape of armature, B is the damping coefficient of the armature, and the damping coefficient can be matched with the performance of fuel oilThe values of B can be obtained by fitting, and m and n are also fitting parameters and can be obtained by fitting.
In the example, m has a value of 0.5, n has a value of 0.5, and B has a value of-1.7713 during opening of the valve port (i.e., decreasing working air gap), and m has a value of 0.5, n has a value of 0.5, and B has a value of 3.0466 during closing of the valve port (i.e., increasing working air gap). The present disclosure does not limit the acquisition methods and values of m, n, and B.
In one possible implementation, the one-dimensional axial force includes a collision force F between the valve stem and the plug or the valve seatb. The in-process that the valve port was opened can bump with the end cap, and the in-process that the valve port was closed can bump with the disk seat. The force generated during the collision is the collision force Fb. The impact force is related to the state of motion of the valve stem, e.g., to the stroke, velocity, etc. of the valve stem. In addition, the collision force is also related to structural information of the valve stem, such as the maximum stroke of the valve stem (the maximum stroke is long, the distance available for acceleration is long, resulting in a large velocity at the time of collision, thus causing a large collision force), a valve half-cone angle, and the like.
In one possible implementation, step S12 may include: and determining the collision force according to the relative initial speed between the valve rod and the plug, the stroke of the valve rod, the maximum stroke of the valve rod and the valve half-cone angle. In an example, the impact force may be determined according to equation (17) below:
Figure BDA0002924157150000131
wherein k isbvalveStiffness of collision between valve stem and valve seat, kbcapIs the collision stiffness between the valve rod and the plug, smaxThe maximum stroke of the valve stem. ξ is the damping constant, which can be determined by the following equation (18):
Figure BDA0002924157150000132
wherein k isbFor crash stiffness, k may be includedbcapOr kbvalveE is a collision velocity recovery coefficient, u0Is the relative initial velocity of the collision.
In one possible implementation, the one-dimensional axial force comprises an inertial force F of the valve stem movementinertia. The inertial force is a force generated by a speed and acceleration change caused by the relative motion of the valve rod and the spring in the motion process, and therefore, the inertial force is related to the structural information of the valve rod, such as the total mass of the moving parts of the valve rod, the mass of the spring and the like. Further, the movement of the valve stem is related to the injection period, i.e., related to engine operating conditions, and the travel of the valve stem may be determined based on the engine operating conditions, and the velocity and acceleration, and thus the inertial force, may be determined from the travel of the valve stem.
In one possible implementation, step S11 may include: the inertial force is determined from the total mass of the moving parts of the valve stem, the spring mass and the stroke of the valve stem. In the example, the inertial force FinertiaCan be determined according to the following equation (19):
Figure BDA0002924157150000133
where m is the mass of the moving part of the valve stem, msprIs the mass of the spring.
In one possible implementation, through the above analysis steps, the acting force of the valve rod in one-dimensional axial force can be determined except for the friction force and the electromagnetic force. The radial load borne by the valve rod can be further analyzed, and the friction force borne by the valve rod is further determined according to the clamping stagnation state. Further, after the friction force is determined, the electromagnetic force required for controlling the movement of the valve rod can be determined based on the friction force and the one-dimensional axial force, so that the movement control of the valve rod is realized.
In one possible implementation, the stem may be stuck if it collides with the valve body and plastically deforms under the impact of the fuel flow, and the coefficient of friction of the stem is different from that without sticking when the stem is stuck, in which case the coefficient of friction is not a definite value but a value related to the performance parameters of the stem and the valve body (e.g., hardness, modulus of elasticity, etc.) and the radial load (e.g., the greater the load, the greater the plastic deformation, which in turn affects the coefficient of friction).
In one possible implementation, step S12 may include: under the condition that a valve rod is clamped, three-dimensional motion analysis is carried out on the valve rod according to the working condition of the engine, the structural information of the valve rod, the performance parameters of the fuel oil and the motion parameters of the valve rod, and the radial load of the valve rod is obtained; determining the static friction coefficient of the valve rod and the valve body according to the performance parameters of the valve rod and the valve body and the radial load; and determining the maximum static friction force of the valve rod according to the static friction coefficient and the radial load.
In a possible implementation mode, due to the fact that a gap exists between the valve rod and the valve body, acting force is generated on the valve rod by fuel oil in the gap, the valve rod is stressed in a radial direction to be three-dimensional acting force, however, analysis of the three-dimensional acting force is difficult to achieve in an embedded system (such as an on-board computer and the like), therefore, the three-dimensional acting force can be simplified, and the valve rod can be fitted into radial one-dimensional acting force according to radial movement of the valve rod.
In one possible implementation, the radial load of the valve rod can comprise the radial load of the valve port and the valve rod high-pressure section, and the radial load of the valve port and the valve rod high-pressure section can be simplified. For example, a theoretical value of the one-dimensional radial load of the high-pressure section of the valve port and the valve rod can be determined through fuel performance parameters, engine working conditions and the like, and the theoretical value does not take the influence of axial flow of a closed space into consideration, so that the theoretical value has errors and needs to be corrected.
In a possible implementation mode, three-dimensional modeling can be performed on the valve port and the valve rod high-pressure section, the stress of each position of the valve port and the valve rod high-pressure section is analyzed by using a three-dimensional model, three-dimensional resultant force borne by the valve port and the valve rod high-pressure section is determined, further, the three-dimensional resultant force and a theoretical value of radial load can be fitted, and a three-dimensional numerical simulation correction coefficient is determined. The theoretical value of the one-dimensional radial load corrected by the coefficient is close to the three-dimensional resultant force determined by three-dimensional modeling, so that the more accurate radial load on the valve port and the valve rod high-pressure section can be determined under the condition of greatly reducing calculation consumption. In an example, the modified radial load of the valve port and stem high pressure section may be determined by the following equation (20):
Figure BDA0002924157150000141
wherein, F'y1Radial force on the valve port and the high-pressure section of the valve rod, Fy1The theoretical value of the jet impact force borne by the high-pressure section of the valve port and the valve rod is rho, the fuel density and the U∞For the oil flow rate of the plunger cavity, d is the diameter of the high-pressure section of the valve rod, l is the axial action length of the jet flow in the high-pressure section of the valve rod, and the action length can be equal to the diameter of the oil outlet flow passage of the plunger cavity, CaFor three-dimensional numerical simulation of correction coefficients, in the example, Ca＝1.7052，CDIs the streaming coefficient.
In one possible implementation, the radial load of the valve stem may include the radial load of the pilot seal segment, which may be simplified. For example, a theoretical value of the one-dimensional radial load of the pilot seal segment can be determined through fuel performance parameters, engine operating conditions, fuel pressure and the like, and the theoretical value does not take the influence of circumferential flow of fluid due to pressure difference into consideration, so that the theoretical value has errors and needs to be corrected.
In a possible implementation mode, three-dimensional modeling can be performed on the guide sealing section, the stress of each position of the guide sealing section is analyzed by using a three-dimensional model, the three-dimensional resultant force applied to the valve port and the valve rod high-pressure section is determined, and further, the three-dimensional resultant force and the theoretical value of the radial load can be fitted to determine the three-dimensional numerical simulation correction coefficient. The theoretical value of the one-dimensional radial load corrected by the coefficient is close to the three-dimensional resultant force determined by three-dimensional modeling, so that the more accurate radial load applied to the guide sealing section can be determined under the condition of greatly reducing calculation consumption. In an example, the corrected radial load of the pilot seal segment may be determined by the following equation (21):
Figure BDA0002924157150000151
wherein, Fy2In order to obtain the theoretical value of the radial force applied to the guide sealing section, theta is the deflection angle of the central axis of the valve rod relative to the central axis of the valve body, R is the radius of the cross section of the guide sealing hole of the valve body, R is the radius of the cross section of the guide sealing section of the valve rod, and CbFor three-dimensional numerical simulation of correction coefficients, in the example, Cb＝1/1.39。
In summary, the radial load experienced by the valve stem may be determined as | F'y1+F’y2|。
In one possible implementation, the radial loads of the high-pressure section of the valve port and the valve rod and the radial load of the guide sealing section of the valve rod can not be all included. For example, if a valve stem of some sort has only a pilot seal segment, the radial load experienced by the valve stem may include only the radial load of the pilot seal segment of the valve stem.
In one possible implementation, the static coefficient of friction may be determined based on the radial load and performance parameters of the valve stem and valve body in the event of a stem jam.
In an example, the performance parameter comprises a poisson ratio of the valve stem and the valve body, and the hardness factor K is determined to be 0.454+0.41 upsilon according to the poisson ratio of the valve stem and the valve body.
In an example, the performance parameter includes a yield strength Y of the valve stem and the valve body, from which a hardness H of 2.8Y may be determined.
In an example, a Hertzian critical load F for converting elastic deformation into elastic-plastic deformation of a valve body is determined according to a hardness factor, the hardness of a valve rod and a valve body and the Hertzian elastic modulus E of the valve rod and the valve bodycFor example, the hertzian critical load for elastoplastic deformation may be determined according to the following equation (22):
Figure BDA0002924157150000152
in an example, the static coefficient of friction may be determined based on a hertzian critical load at which the valve body is transformed from elastic deformation to elastoplastic deformation and the radial load. In an example, the static coefficient of friction μ at stem sticking may be determined according to equation (23) belowT：
Figure BDA0002924157150000153
Wherein, F'y＝|F’y1+F’y2The radial load of the contact point of the valve rod and the valve body is |; omega is the contact deformation of the valve bodycIs Hertz critical contact deformation of the valve body, F'y/Fc＝1.03(ω/ωc)1.425。
Wherein the Hertz critical contact deformation omega of the valve bodycCan be determined by the following equation (24):
Figure BDA0002924157150000161
in one possible implementation, after determining the sticking friction coefficient, the maximum static friction force of the valve stem may be determined based on the static friction coefficient at the time of sticking and the radial load. In an example, a three-dimensional simulated one-dimensional modified theoretical value of the maximum static friction force of the valve stem can be determined by the following equation (25):
Figure BDA0002924157150000162
in one possible implementation, it may be determined whether the valve stem is stuck according to the method described above, and if the valve stem is not stuck, the coefficient of dynamic friction and the coefficient of static friction of the valve stem may be determined values. Step S12 may include: and under the condition that the valve rod is not clamped, determining the dynamic friction force of the valve rod according to the dynamic friction coefficient between the valve rod and the valve body and the radial load of the valve rod.
In one possible implementation, the valve stem is subjected to static friction before axial sliding begins and to sliding friction after the valve stem begins to slide. In an example, the friction experienced by the valve stem without the valve stem jamming may be determined according to the following equation (26):
Figure BDA0002924157150000163
wherein, FdynTo sliding friction, FstatIs static friction force, ustribeckSpeed threshold, μ, for conversion of static friction to kinetic frictiondynIs a coefficient of dynamic friction, Fy＝|F’y1+F’y2L, radial load of the contact point of the valve stem and the valve body, mustatThe coefficient of static friction was obtained without occurrence of seizure.
In one possible implementation, the coefficient of dynamic friction is μ after the valve stem begins to move, regardless of whether the valve stem is stuck before moving or notdynSliding friction is Fdyn。
In one possible implementation manner, in step S13, based on the one-dimensional axial force and the friction force obtained above, the axial force may be analyzed to determine the driving force required to drive the valve rod. The driving force may be an electromagnetic force, for example, an electromagnetic force generated by a solenoid valve. The source of the driving force may also be other mechanisms, such as a piezoelectric crystal actuator or a driving cam, etc., and the present disclosure does not limit the type of the driving force. Taking electromagnetic force as an example, the axial stress analysis of the valve rod is carried out as follows:
in an example, force analysis may be performed according to the following equation (27) to determine the electromagnetic force F required to drive the movement of the valve stemmeg：
Fmeg+Fspr+Flp+Fhp+Fvisc+Fwind+Ffric+Fb+Finertia＝0 (27)
In one possible implementation, the electromagnetic force required to overcome the one-dimensional axial force and the friction force in the case of force balance can be determined according to equation (27). For example, if the valve rod is accelerated when moving the valve rod towards the direction of decreasing armature air gap, the required electromagnetic force is larger than the electromagnetic force determined according to the formula (27), and the speed and acceleration of the valve rod can be further determined through parameters such as the stroke of the valve rod and the movement time of the valve rod, so as to determine the electromagnetic force.
In one possible implementation, the magnetic field, and thus the electromagnetic force, may be generated by applying a current or voltage to an electromagnet, which may be determined, in an example, by the following equation (28):
Figure BDA0002924157150000171
wherein, mu0For vacuum permeability, AeffThe effective action area of the electromagnet magnetic field on the armature, I is the electromagnet current, N is the number of turns of the electromagnet, and deltamegIs the armature air gap. Wherein the armature air gap may be determined according to the following equation (29):
δmeg＝δmax-s (29)
wherein, deltamaxAnd s is the valve rod lift.
In an example, the current required to generate the electromagnetic force can be determined by equations (28) - (29) above.
According to the valve rod motion analysis method disclosed by the embodiment of the disclosure, the multidimensional and mutually coupled force borne by the valve rod can be fitted into a radial one-dimensional stress, so that the friction force is determined, the analysis on the valve rod motion process is greatly simplified, the occupation of operation resources is reduced, the valve rod motion analysis efficiency is improved, and the method can be suitable for the scenes of motion analysis and motion control on the valve rod under complex working conditions. Further, the axial stress of the valve rod can be determined based on the determined friction force, so that the valve rod can be subjected to motion analysis, and the control accuracy of controlling the motion of the valve rod can be improved.
Fig. 9 is a schematic diagram illustrating an application of a method for analyzing the movement of a valve stem of a kinematic seal coupling according to an embodiment of the present disclosure. As shown in FIG. 9, the valve stemThe analysis method is complex and occupies large computational resources due to various acting forces in the three-dimensional dynamic flow field, and the analysis is difficult to be carried out in actual scenes such as vehicles. The multiple acting forces of the valve rod in the three-dimensional dynamic flow field can be fitted into one-dimensional axial acting force, such as electromagnetic force FmegFrictional force FfricSpring force FsprFlow field pressure (including high pressure fluid pressure F)hpAnd low pressure fluid force Flp) Viscous damping force FviscSqueeze film resistance FwindCollision force FbAnd inertial force Finertia。
In one possible implementation, the flow field pressure, viscous damping force FviscSqueeze film resistance FwindCollision force FbAnd inertial force FinertiaThe axial forces are one-dimensional axial forces, and can be calculated according to the working condition of the engine, the structural information of the valve rod and the performance parameters of the fuel.
In one possible implementation, the friction force F is determinedfricDuring the process, because the friction force needs to be solved through the friction coefficient and the radial load, various acting forces in the dimensional dynamic flow field received by the valve rod can be simplified into two-dimensional stress in the axial direction and the radial direction, namely, the valve rod can receive the axial force in the axial direction and can receive the radial load in the radial direction.
In a possible implementation manner, the valve rod may be subjected to three-dimensional motion analysis according to the engine operating condition, structural information of the valve rod, a performance parameter of fuel oil, and a motion parameter of the valve rod, and a theoretical value of the radial force applied to the valve rod is corrected, for example, the theoretical value of the radial force applied to the guide sealing section is corrected, and the theoretical values of the radial forces applied to the valve port and the valve rod high-pressure section are corrected, so as to determine the radial load applied to the valve rod.
In one possible implementation, the friction force experienced by the valve stem may be determined after the radial load of the valve stem is obtained. Whether the valve rod is blocked or not can be determined according to the working condition of the engine, if the valve rod is blocked, the blocked friction coefficient can be determined by using the corrected radial load and the performance parameters of the valve body, and then the blocked friction force is determined. If the electromagnetic force can overcome the clamping friction force to move the valve rod, the friction force borne by the valve rod after the movement is dynamic friction force.
In one possible implementation, if the valve stem is not stuck, the static friction experienced when the valve stem is at rest and the dynamic friction experienced when the valve stem is moving may be determined according to equation (26).
In a possible implementation, the force analysis can be carried out in one-dimensional axial direction, determining the electromagnetic force F required to drive the movement of the valve stemmegThe speed and the acceleration of the valve rod can be further determined through parameters such as the stroke of the valve rod, the movement time of the valve rod and the like, and then the specific numerical value of the electromagnetic force is determined so as to apply current or voltage and generate the electromagnetic force to control the valve rod.
Fig. 10 shows a block diagram of a kinematic sealing couple valve stem motion analysis apparatus according to an embodiment of the present disclosure, which, as shown in fig. 10, includes: the clamping stagnation state module 11 is used for determining the clamping stagnation state of the valve rod according to the working condition of the engine; the axial force module 12 is configured to determine a one-dimensional axial force applied to the valve rod in the axial direction according to a clamping stagnation state of the valve rod, an engine working condition, structural information of the valve rod, and a fuel performance parameter, where the one-dimensional axial force includes a friction force applied to the valve rod; and the driving force module 13 is used for determining the driving force required by the axial movement of the valve rod according to the one-dimensional axial force.
In one possible implementation, the one-dimensional axial force comprises a spring force, wherein the axial force module is further configured to: and determining the spring force according to the performance parameters of the spring and the valve rod lift.
In one possible implementation manner, the one-dimensional axial force includes a flow field pressure, the flow field pressure includes a high-pressure hydraulic pressure, the engine operating condition includes a cam lift, a cam rotation angle, a cam rotation speed, and an ambient pressure, the structural information of the valve rod includes a plunger diameter, a valve port sealing surface ring surface diameter, an electromagnetic valve port gap, a valve port half-cone angle, a valve port flow coefficient, and a maximum total volume of the high-pressure chamber, and the performance parameter of the fuel includes a fuel density, where the axial force module is further configured to: determining the high-pressure fuel inlet flow of the valve rod according to the cam lift, the cam rotation angle, the cam rotation speed and the plunger diameter; determining the outlet flow of the high-pressure fuel according to the pressure of the high-pressure fuel and the pressure of the external environment; determining the fuel pressure in the high-pressure cavity according to the high-pressure fuel outlet flow, the high-pressure fuel inlet flow, the valve port outlet flow, the maximum total volume of the high-pressure cavity, the diameter of the plunger and the cam lift; and determining the high-pressure liquid pressure according to the gap of the valve port of the electromagnetic valve, the diameter of the ring surface of the sealing surface of the valve port, the fuel pressure in the high-pressure cavity, the fuel density of the high-pressure cavity, the flow coefficient of the valve port and the half cone angle of the valve.
In one possible implementation, the one-dimensional axial force comprises a flow field pressure, the flow field pressure comprises a low pressure hydraulic force, and the axial force module is further configured to: and determining the low-pressure hydraulic pressure according to the low-pressure fuel pressure and the action area of the low-pressure fuel.
In one possible implementation manner, the one-dimensional axial force includes a viscous damping force, the structural information of the valve rod includes a valve rod guide sealing section gap width, a valve rod guide sealing section length, and a valve rod guide sealing section diameter, and the performance parameters of the fuel include a viscosity coefficient and a dynamic viscosity of the fuel, where the axial force module is further configured to: determining the sealing gap flow of the valve rod according to the gap width of the valve rod guide sealing section, the length of the valve rod guide sealing section, the viscosity coefficient of the fuel oil of the diameter of the valve rod guide sealing section and the dynamic viscosity; and determining the viscous damping force according to the flow of the sealing gap.
In one possible implementation, the one-dimensional axial force comprises squeeze film resistance, the engine operating condition comprises valve stem movement speed and valve stem travel, the valve stem structural information comprises armature maximum air gap, and the axial force module is further configured to: and determining the squeeze film resistance according to the valve rod movement speed, the valve rod stroke and the armature maximum air gap.
In one possible implementation, the one-dimensional axial force includes an impact force, the engine operating condition includes a relative initial velocity between the valve stem and the plug and a lift of the valve stem, the structural information of the valve stem includes a maximum stroke and a valve half-cone angle of the valve stem, and the axial force module is further configured to: and determining the collision force according to the relative initial speed between the valve rod and the plug, the stroke of the valve rod, the maximum stroke of the valve rod and the valve half-cone angle.
In one possible implementation, the one-dimensional axial force includes an inertial force, the structural information of the valve stem includes a total mass and a spring mass of a moving part of the valve stem, and the engine operating condition includes a stroke of the valve stem, wherein the axial force module is further configured to: the inertial force is determined from the total mass of the moving parts of the valve stem, the spring mass and the stroke of the valve stem.
In one possible implementation, the axial force module is further configured to: under the condition that a valve rod is clamped, three-dimensional motion analysis is carried out on the valve rod according to the working condition of the engine, the structural information of the valve rod, the performance parameters of the fuel oil and the motion parameters of the valve rod, and the radial load of the valve rod is obtained; determining the static friction coefficient of the valve rod and the valve body according to the performance parameters of the valve rod and the valve body and the radial load; and determining the maximum static friction force of the valve rod according to the static friction coefficient and the radial load.
In one possible implementation, the axial force module is further configured to: and under the condition that the valve rod is not clamped, determining the dynamic friction force of the valve rod according to the dynamic friction coefficient between the valve rod and the valve body and the radial load of the valve rod.
It is understood that the above-mentioned method embodiments of the present disclosure can be combined with each other to form a combined embodiment without departing from the logic of the principle, which is limited by the space, and the detailed description of the present disclosure is omitted. Those skilled in the art will appreciate that in the above methods of the specific embodiments, the specific order of execution of the steps should be determined by their function and possibly their inherent logic.
In addition, the present disclosure also provides a motion analysis device for a valve rod of a kinematic seal coupling, an electronic device, a computer-readable storage medium, and a program, which can be used to implement any one of the motion analysis methods for a valve rod of a kinematic seal coupling provided by the present disclosure, and the corresponding technical solutions and descriptions and corresponding descriptions of the method sections are not repeated.
In some embodiments, functions of or modules included in the apparatus provided in the embodiments of the present disclosure may be used to execute the method described in the above method embodiments, and specific implementation thereof may refer to the description of the above method embodiments, and for brevity, will not be described again here.
Embodiments of the present disclosure also provide a computer-readable storage medium having stored thereon computer program instructions, which when executed by a processor, implement the above-mentioned method. The computer readable storage medium may be a non-volatile computer readable storage medium.
An embodiment of the present disclosure further provides an electronic device, including: a processor; a memory for storing processor-executable instructions; wherein the processor is configured to invoke the memory-stored instructions to perform the above-described method.
The disclosed embodiments also provide a computer program product comprising computer readable code, when the computer readable code runs on a device, a processor in the device executes instructions for implementing the method for analyzing the motion of the valve rod of the moving sealing coupling provided in any one of the above embodiments.
Embodiments of the present disclosure also provide another computer program product for storing computer readable instructions, which when executed, cause a computer to perform the operations of the method for analyzing the motion of a valve stem of a moving seal coupling provided in any of the embodiments.
The electronic device may be provided as a terminal, server, or other form of device.
Fig. 11 illustrates a block diagram of an electronic device 800 in accordance with an embodiment of the disclosure. For example, the electronic device 800 may be a mobile phone, a computer, a digital broadcast terminal, a messaging device, a game console, a tablet device, a medical device, a fitness device, a personal digital assistant, or the like terminal.
Referring to fig. 11, electronic device 800 may include one or more of the following components: processing component 802, memory 804, power component 806, multimedia component 808, audio component 810, input/output (I/O) interface 812, sensor component 814, and communication component 816.
The processing component 802 generally controls overall operation of the electronic device 800, such as operations associated with display, telephone calls, data communications, camera operations, and recording operations. The processing components 802 may include one or more processors 820 to execute instructions to perform all or a portion of the steps of the methods described above. Further, the processing component 802 can include one or more modules that facilitate interaction between the processing component 802 and other components. For example, the processing component 802 can include a multimedia module to facilitate interaction between the multimedia component 808 and the processing component 802.
The memory 804 is configured to store various types of data to support operations at the electronic device 800. Examples of such data include instructions for any application or method operating on the electronic device 800, contact data, phonebook data, messages, pictures, videos, and so forth. The memory 804 may be implemented by any type or combination of volatile or non-volatile memory devices such as Static Random Access Memory (SRAM), electrically erasable programmable read-only memory (EEPROM), erasable programmable read-only memory (EPROM), programmable read-only memory (PROM), read-only memory (ROM), magnetic memory, flash memory, magnetic or optical disks.
The power supply component 806 provides power to the various components of the electronic device 800. The power components 806 may include a power management system, one or more power supplies, and other components associated with generating, managing, and distributing power for the electronic device 800.
The multimedia component 808 includes a screen that provides an output interface between the electronic device 800 and a user. In some embodiments, the screen may include a Liquid Crystal Display (LCD) and a Touch Panel (TP). If the screen includes a touch panel, the screen may be implemented as a touch screen to receive an input signal from a user. The touch panel includes one or more touch sensors to sense touch, slide, and gestures on the touch panel. The touch sensor may not only sense the boundary of a touch or slide action, but also detect the duration and pressure associated with the touch or slide operation. In some embodiments, the multimedia component 808 includes a front facing camera and/or a rear facing camera. The front camera and/or the rear camera may receive external multimedia data when the electronic device 800 is in an operation mode, such as a shooting mode or a video mode. Each front camera and rear camera may be a fixed optical lens system or have a focal length and optical zoom capability.
The audio component 810 is configured to output and/or input audio signals. For example, the audio component 810 includes a Microphone (MIC) configured to receive external audio signals when the electronic device 800 is in an operational mode, such as a call mode, a recording mode, and a voice recognition mode. The received audio signals may further be stored in the memory 804 or transmitted via the communication component 816. In some embodiments, audio component 810 also includes a speaker for outputting audio signals.
The I/O interface 812 provides an interface between the processing component 802 and peripheral interface modules, which may be keyboards, click wheels, buttons, etc. These buttons may include, but are not limited to: a home button, a volume button, a start button, and a lock button.
The sensor assembly 814 includes one or more sensors for providing various aspects of state assessment for the electronic device 800. For example, the sensor assembly 814 may detect an open/closed state of the electronic device 800, the relative positioning of components, such as a display and keypad of the electronic device 800, the sensor assembly 814 may also detect a change in the position of the electronic device 800 or a component of the electronic device 800, the presence or absence of user contact with the electronic device 800, orientation or acceleration/deceleration of the electronic device 800, and a change in the temperature of the electronic device 800. Sensor assembly 814 may include a proximity sensor configured to detect the presence of a nearby object without any physical contact. The sensor assembly 814 may also include a light sensor, such as a CMOS or CCD image sensor, for use in imaging applications. In some embodiments, the sensor assembly 814 may also include an acceleration sensor, a gyroscope sensor, a magnetic sensor, a pressure sensor, or a temperature sensor.
The communication component 816 is configured to facilitate wired or wireless communication between the electronic device 800 and other devices. The electronic device 800 may access a wireless network based on a communication standard, such as WiFi, 2G or 3G, or a combination thereof. In an exemplary embodiment, the communication component 816 receives a broadcast signal or broadcast related information from an external broadcast management system via a broadcast channel. In an exemplary embodiment, the communication component 816 further includes a Near Field Communication (NFC) module to facilitate short-range communications. For example, the NFC module may be implemented based on Radio Frequency Identification (RFID) technology, infrared data association (IrDA) technology, Ultra Wideband (UWB) technology, Bluetooth (BT) technology, and other technologies.
In an exemplary embodiment, the electronic device 800 may be implemented by one or more Application Specific Integrated Circuits (ASICs), Digital Signal Processors (DSPs), Digital Signal Processing Devices (DSPDs), Programmable Logic Devices (PLDs), Field Programmable Gate Arrays (FPGAs), controllers, micro-controllers, microprocessors or other electronic components for performing the above-described methods.
In an exemplary embodiment, a non-transitory computer-readable storage medium, such as the memory 804, is also provided that includes computer program instructions executable by the processor 820 of the electronic device 800 to perform the above-described methods.
Fig. 12 shows a block diagram of an electronic device 1900 according to an embodiment of the disclosure. For example, the electronic device 1900 may be provided as a server. Referring to fig. 12, electronic device 1900 includes a processing component 1922 further including one or more processors and memory resources, represented by memory 1932, for storing instructions, e.g., applications, executable by processing component 1922. The application programs stored in memory 1932 may include one or more modules that each correspond to a set of instructions. Further, the processing component 1922 is configured to execute instructions to perform the above-described method.
The electronic device 1900 may also include a power component 1926 configured to perform power management of the electronic device 1900, a wired or wireless network interface 1950 configured to connect the electronic device 1900 to a network, and an input/output (I/O) interface 1958. The electronic device 1900 may operate based on an operating system, such as Windows Server, stored in memory 1932TM，Mac OS XTM，UnixTM,LinuxTM，FreeBSDTMOr the like.
In an exemplary embodiment, a non-transitory computer readable storage medium, such as the memory 1932, is also provided that includes computer program instructions executable by the processing component 1922 of the electronic device 1900 to perform the above-described methods.
The present disclosure may be systems, methods, and/or computer program products. The computer program product may include a computer-readable storage medium having computer-readable program instructions embodied thereon for causing a processor to implement various aspects of the present disclosure.
The computer readable storage medium may be a tangible device that can hold and store the instructions for use by the instruction execution device. The computer readable storage medium may be, for example, but not limited to, an electronic memory device, a magnetic memory device, an optical memory device, an electromagnetic memory device, a semiconductor memory device, or any suitable combination of the foregoing. More specific examples (a non-exhaustive list) of the computer readable storage medium would include the following: a portable computer diskette, a hard disk, a Random Access Memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), a Static Random Access Memory (SRAM), a portable compact disc read-only memory (CD-ROM), a Digital Versatile Disc (DVD), a memory stick, a floppy disk, a mechanical coding device, such as punch cards or in-groove projection structures having instructions stored thereon, and any suitable combination of the foregoing. Computer-readable storage media as used herein is not to be construed as transitory signals per se, such as radio waves or other freely propagating electromagnetic waves, electromagnetic waves propagating through a waveguide or other transmission medium (e.g., optical pulses through a fiber optic cable), or electrical signals transmitted through electrical wires.
The computer-readable program instructions described herein may be downloaded from a computer-readable storage medium to a respective computing/processing device, or to an external computer or external storage device via a network, such as the internet, a local area network, a wide area network, and/or a wireless network. The network may include copper transmission cables, fiber optic transmission, wireless transmission, routers, firewalls, switches, gateway computers and/or edge servers. The network adapter card or network interface in each computing/processing device receives computer-readable program instructions from the network and forwards the computer-readable program instructions for storage in a computer-readable storage medium in the respective computing/processing device.
The computer program instructions for carrying out operations of the present disclosure may be assembler instructions, Instruction Set Architecture (ISA) instructions, machine-related instructions, microcode, firmware instructions, state setting data, or source or object code written in any combination of one or more programming languages, including an object oriented programming language such as Smalltalk, C + + or the like and conventional procedural programming languages, such as the "C" programming language or similar programming languages. The computer-readable program instructions may execute entirely on the user's computer, partly on the user's computer, as a stand-alone software package, partly on the user's computer and partly on a remote computer or entirely on the remote computer or server. In the case of a remote computer, the remote computer may be connected to the user's computer through any type of network, including a Local Area Network (LAN) or a Wide Area Network (WAN), or the connection may be made to an external computer (for example, through the Internet using an Internet service provider). In some embodiments, the electronic circuitry that can execute the computer-readable program instructions implements aspects of the present disclosure by utilizing the state information of the computer-readable program instructions to personalize the electronic circuitry, such as a programmable logic circuit, a Field Programmable Gate Array (FPGA), or a Programmable Logic Array (PLA).
Various aspects of the present disclosure are described herein with reference to flowchart illustrations and/or block diagrams of methods, apparatus (systems) and computer program products according to embodiments of the disclosure. It will be understood that each block of the flowchart illustrations and/or block diagrams, and combinations of blocks in the flowchart illustrations and/or block diagrams, can be implemented by computer-readable program instructions.
These computer-readable program instructions may be provided to a processor of a general purpose computer, special purpose computer, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions/acts specified in the flowchart and/or block diagram block or blocks. These computer-readable program instructions may also be stored in a computer-readable storage medium that can direct a computer, programmable data processing apparatus, and/or other devices to function in a particular manner, such that the computer-readable medium storing the instructions comprises an article of manufacture including instructions which implement the function/act specified in the flowchart and/or block diagram block or blocks.
The computer readable program instructions may also be loaded onto a computer, other programmable data processing apparatus, or other devices to cause a series of operational steps to be performed on the computer, other programmable apparatus or other devices to produce a computer implemented process such that the instructions which execute on the computer, other programmable apparatus or other devices implement the functions/acts specified in the flowchart and/or block diagram block or blocks.
The flowchart and block diagrams in the figures illustrate the architecture, functionality, and operation of possible implementations of systems, methods and computer program products according to various embodiments of the present disclosure. In this regard, each block in the flowchart or block diagrams may represent a module, segment, or portion of instructions, which comprises one or more executable instructions for implementing the specified logical function(s). In some alternative implementations, the functions noted in the block may occur out of the order noted in the figures. For example, two blocks shown in succession may, in fact, be executed substantially concurrently, or the blocks may sometimes be executed in the reverse order, depending upon the functionality involved. It will also be noted that each block of the block diagrams and/or flowchart illustration, and combinations of blocks in the block diagrams and/or flowchart illustration, can be implemented by special purpose hardware-based systems which perform the specified functions or acts, or combinations of special purpose hardware and computer instructions.
The computer program product may be embodied in hardware, software or a combination thereof. In an alternative embodiment, the computer program product is embodied in a computer storage medium, and in another alternative embodiment, the computer program product is embodied in a Software product, such as a Software Development Kit (SDK), or the like.
Having described embodiments of the present disclosure, the foregoing description is intended to be exemplary, not exhaustive, and not limited to the disclosed embodiments. Many modifications and variations will be apparent to those of ordinary skill in the art without departing from the scope and spirit of the described embodiments. The terminology used herein is chosen in order to best explain the principles of the embodiments, the practical application, or improvements made to the technology in the marketplace, or to enable others of ordinary skill in the art to understand the embodiments disclosed herein.

Claims (13)

1. A method for analyzing the motion of a valve rod of a motion sealing coupling part is characterized by comprising the following steps:
determining the clamping stagnation state of the valve rod according to the working condition of the engine;
determining a one-dimensional axial force axially applied to the valve rod according to the clamping stagnation state of the valve rod, the working condition of an engine, the structural information of the valve rod and the performance parameters of fuel oil, wherein the one-dimensional axial force comprises friction force, spring force, flow field pressure, viscous damping force, squeeze oil film resistance, collision force and inertia force applied to the valve rod, and the flow field pressure comprises high-pressure liquid pressure and low-pressure liquid pressure;
and determining the driving force required for axially moving the valve rod according to the one-dimensional axial force.
2. The method of claim 1, wherein the one-dimensional axial force comprises a spring force,
wherein, according to the jamming state of valve rod, the engine operating mode, the structural information of valve rod and the performance parameter of fuel, confirm the one-dimensional axial force that the axial of valve rod received, include:
and determining the spring force according to the performance parameters of the spring and the valve rod lift.
3. The method of claim 1, wherein the one-dimensional axial force comprises a flow field pressure, the flow field pressure comprises a high pressure hydraulic pressure, the engine operating conditions comprise a cam lift, a cam rotation angle, a cam rotation speed, an ambient pressure, the valve stem structural information comprises a plunger diameter, a valve port sealing surface annulus diameter, a valve port gap, a valve port half cone angle, a valve port flow coefficient, and a high pressure chamber maximum total volume, the fuel performance parameter comprises a fuel density,
wherein, according to the jamming state of valve rod, the engine operating mode, the structural information of valve rod and the performance parameter of fuel, confirm the one-dimensional axial force that the axial of valve rod received, include:
determining the high-pressure fuel inlet flow of the valve rod according to the cam lift, the cam rotation angle, the cam rotation speed and the plunger diameter;
determining the outlet flow of the high-pressure fuel according to the pressure of the high-pressure fuel and the pressure of the external environment;
determining the fuel pressure in the high-pressure cavity according to the high-pressure fuel outlet flow, the high-pressure fuel inlet flow, the valve port outlet flow, the maximum total volume of the high-pressure cavity, the diameter of the plunger and the cam lift;
and determining the high-pressure liquid pressure according to the valve port clearance, the diameter of the valve port sealing surface ring surface, the fuel pressure in the high-pressure cavity, the fuel density of the high-pressure cavity, the valve port flow coefficient and the valve port half-cone angle.
4. The method of claim 1, wherein the one-dimensional axial force comprises a flow field pressure, the flow field pressure comprises a low pressure hydraulic force,
wherein, according to the jamming state of valve rod, the engine operating mode, the structural information of valve rod and the performance parameter of fuel, confirm the one-dimensional axial force that the axial of valve rod received, include:
and determining the low-pressure hydraulic pressure according to the low-pressure fuel pressure and the action area of the low-pressure fuel.
5. The method of claim 1, wherein the one-dimensional axial force comprises a viscous damping force, the valve stem structural information comprises a valve stem guide seal segment gap width, a valve stem guide seal segment length, a valve stem guide seal segment diameter, the fuel performance parameters comprise a viscosity coefficient and a kinematic viscosity of the fuel,
wherein, according to the jamming state of valve rod, the engine operating mode, the structural information of valve rod and the performance parameter of fuel, confirm the one-dimensional axial force that the axial of valve rod received, include:
determining the sealing gap flow of the valve rod according to the gap width of the valve rod guide sealing section, the length of the valve rod guide sealing section, the viscosity coefficient of the fuel oil of the diameter of the valve rod guide sealing section and the dynamic viscosity;
and determining the viscous damping force according to the flow of the sealing gap.
6. The method of claim 1, wherein the one-dimensional axial force comprises squeeze film resistance, the engine operating condition comprises valve stem movement speed and valve stem travel, the valve stem configuration information comprises armature maximum air gap,
wherein, according to the jamming state of valve rod, the engine operating mode, the structural information of valve rod and the performance parameter of fuel, confirm the one-dimensional axial force that the axial of valve rod received, include:
and determining the squeeze film resistance according to the valve rod movement speed, the valve rod stroke and the armature maximum air gap.
7. The method of claim 1, wherein the one-dimensional axial force comprises an impact force, the engine operating condition comprises an initial relative velocity between the stem and plug and a lift of the stem, the structural information of the stem comprises a maximum stroke and a valve half-cone angle of the stem,
wherein, according to the jamming state of valve rod, the engine operating mode, the structural information of valve rod and the performance parameter of fuel, confirm the one-dimensional axial force that the axial of valve rod received, include:
and determining the collision force according to the relative initial speed between the valve rod and the plug, the stroke of the valve rod, the maximum stroke of the valve rod and the valve half-cone angle.
8. The method of claim 1, wherein the one-dimensional axial force comprises an inertial force, the structural information of the valve stem comprises a total mass and a spring mass of a moving part of the valve stem, the engine operating condition comprises a stroke of the valve stem,
wherein, according to the jamming state of valve rod, the engine operating mode, the structural information of valve rod and the performance parameter of fuel, confirm the one-dimensional axial force that the axial of valve rod received, include:
the inertial force is determined from the total mass of the moving parts of the valve stem, the spring mass and the stroke of the valve stem.
9. The method of claim 1, wherein determining the one-dimensional axial force applied to the valve rod in the axial direction according to the clamping stagnation state of the valve rod, the engine working condition, the structural information of the valve rod and the performance parameters of the fuel comprises:
under the condition that a valve rod is clamped, three-dimensional motion analysis is carried out on the valve rod according to the working condition of the engine, the structural information of the valve rod, the performance parameters of the fuel oil and the motion parameters of the valve rod, and the radial load of the valve rod is obtained;
determining the static friction coefficient of the valve rod and the valve body according to the performance parameters of the valve rod and the valve body and the radial load;
and determining the maximum static friction force of the valve rod according to the static friction coefficient and the radial load.
10. The method of claim 1, wherein determining the one-dimensional axial force applied to the valve rod in the axial direction according to the clamping stagnation state of the valve rod, the engine working condition, the structural information of the valve rod and the performance parameters of the fuel comprises:
and under the condition that the valve rod is not clamped, determining the dynamic friction force of the valve rod according to the dynamic friction coefficient between the valve rod and the valve body and the radial load of the valve rod.
11. A kinematic seal coupling valve stem kinematic analysis apparatus, comprising:
the clamping stagnation state module is used for determining the clamping stagnation state of the valve rod according to the working condition of the engine;
the axial force module is used for determining one-dimensional axial force axially applied to the valve rod according to the clamping stagnation state of the valve rod, the working condition of an engine, the structural information of the valve rod and the performance parameters of fuel oil, wherein the one-dimensional axial force comprises friction force, spring force, flow field pressure, viscous damping force, squeeze oil film resistance, collision force and inertia force applied to the valve rod, and the flow field pressure comprises high-pressure liquid pressure and low-pressure liquid pressure;
and the driving force module is used for determining the driving force required by the axial movement of the valve rod according to the one-dimensional axial force.
12. An electronic device, comprising:
a processor;
a memory for storing processor-executable instructions;
wherein the processor is configured to invoke the memory-stored instructions to perform the method of any one of claims 1 to 10.
13. A computer readable storage medium having computer program instructions stored thereon, which when executed by a processor implement the method of any one of claims 1 to 10.
CN202110126373.3A 2021-01-29 2021-01-29 Method and device for analyzing motion of valve rod of motion sealing coupling part Active CN112879193B (en)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1181458B1 (en) * 1999-05-28 2004-02-25 Bosch Rexroth AG Hydraulic drive with several hydraulic consumers also comprising a differential cylinder
KR20050006734A (en) * 2003-07-10 2005-01-17 현대자동차주식회사 an unexpected start protecting device for vehiclels
CN102465806A (en) * 2010-11-08 2012-05-23 胡建华 Internal combustion engine
CN104632317A (en) * 2015-01-30 2015-05-20 哈尔滨工程大学 Vent valve device for high-power low-speed marine diesel engine
CN211951649U (en) * 2020-02-26 2020-11-17 苏州纽威阀门股份有限公司 Valve rod sealing structure and valve
CN112065795A (en) * 2020-09-03 2020-12-11 上海豪高机电科技有限公司 Threaded cartridge valve group

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1181458B1 (en) * 1999-05-28 2004-02-25 Bosch Rexroth AG Hydraulic drive with several hydraulic consumers also comprising a differential cylinder
KR20050006734A (en) * 2003-07-10 2005-01-17 현대자동차주식회사 an unexpected start protecting device for vehiclels
CN102465806A (en) * 2010-11-08 2012-05-23 胡建华 Internal combustion engine
CN104632317A (en) * 2015-01-30 2015-05-20 哈尔滨工程大学 Vent valve device for high-power low-speed marine diesel engine
CN211951649U (en) * 2020-02-26 2020-11-17 苏州纽威阀门股份有限公司 Valve rod sealing structure and valve
CN112065795A (en) * 2020-09-03 2020-12-11 上海豪高机电科技有限公司 Threaded cartridge valve group

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