CN113738537B - Servo mechanism hydraulic motor energy matching method adapting to variable thrust working condition of engine - Google Patents
Servo mechanism hydraulic motor energy matching method adapting to variable thrust working condition of engine Download PDFInfo
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- CN113738537B CN113738537B CN202110903544.9A CN202110903544A CN113738537B CN 113738537 B CN113738537 B CN 113738537B CN 202110903544 A CN202110903544 A CN 202110903544A CN 113738537 B CN113738537 B CN 113738537B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02K—JET-PROPULSION PLANTS
- F02K9/00—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof
- F02K9/96—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof characterised by specially adapted arrangements for testing or measuring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02K—JET-PROPULSION PLANTS
- F02K9/00—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof
- F02K9/42—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof using liquid or gaseous propellants
- F02K9/44—Feeding propellants
- F02K9/56—Control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02K—JET-PROPULSION PLANTS
- F02K9/00—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof
- F02K9/42—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof using liquid or gaseous propellants
- F02K9/44—Feeding propellants
- F02K9/56—Control
- F02K9/58—Propellant feed valves
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Abstract
Adaptive hairThe method for matching the energy of the hydraulic motor of the servo mechanism under the condition of variable thrust of the motor comprises the following steps of firstly, obtaining the continuous swing speed omega of the servo mechanism, the swing arm R of the servo mechanism, the energy parameters and the structural parameters of the servo mechanism; step two, designing and selecting the displacement V 'of the hydraulic pump according to the continuous swing speed omega of the servo mechanism, the swing arm R of the servo mechanism, the energy parameter and the structural parameter of the servo mechanism obtained in the step one' p (ii) a Step three, considering the power balance relation between the output power of the hydraulic engine and the input power of the hydraulic pump, designing and selecting the displacement V 'of the hydraulic engine' m (ii) a Step four, according to the selected hydraulic pump displacement V' p And hydraulic motor displacement V' m And verifying the constant-speed function of the hydraulic motor under the condition of changing the pressure of the drainage kerosene to finish matching. The invention can quickly determine the reasonable ratio of the discharge capacities of the hydraulic pump and the hydraulic motor according to the change range of the pressure of the drainage kerosene, realize the matching of the drainage energy power and the hydraulic energy power, and keep the rotating speed of the power assembly constant through the constant-speed valve at the oil inlet of the hydraulic motor.
Description
Technical Field
The invention belongs to the field of rocket servo mechanism design, and relates to a servo mechanism hydraulic motor energy matching method adapting to a variable thrust working condition of a liquid oxygen kerosene engine.
Background
At present, liquid oxygen kerosene rockets at home and abroad adopt an engine variable thrust adjusting technology to reduce flying dynamic pressure and overload. This technique results in significant changes in kerosene pressure after the pump, which places adaptive service requirements on the associated servomechanism. For a servo mechanism scheme of a high-pressure kerosene drive actuator of a direct drainage engine, the kerosene pressure changes in a large range, so that the oil supply pressure of a servo valve deviates from the rated design working condition, and the control performance is influenced.
Disclosure of Invention
The technical problem solved by the invention is as follows: the method overcomes the defects of the prior art, provides the servo mechanism hydraulic motor energy matching method adapting to the variable thrust working condition of the engine, ensures the oil supply pressure of the servo valve to be within the rated design working condition when the thrust of the liquid oxygen kerosene engine is adjusted in a large range, and realizes the stable control of the rotating speed of a servo power assembly and the reasonable matching of the drainage energy power of the servo mechanism and the hydraulic energy power.
The technical scheme of the invention is as follows:
the servo mechanism hydraulic motor energy matching method adapting to the variable thrust working condition of the engine comprises the following steps:
acquiring a continuous swing speed omega of a servo mechanism, a swing force arm R of the servo mechanism, energy parameters and structural parameters of the servo mechanism; the energy parameters include the drainage kerosene pressure p m Drainage oil return pressure p m0 Rated system operating pressure p p Hydraulic pump return pressure p p0 Pressure drop delta p at fixed orifice of constant speed valve v Hydraulic motor comprehensive efficiency eta m Hydraulic motor volumetric efficiency eta mv Hydraulic pump comprehensive efficiency eta p Hydraulic pump volumetric efficiency eta pv The working speed n of the hydraulic pump p And the operating speed n of the hydraulic motor m (ii) a The structural parameters include the actuator piston area A; the constant speed valve is connected in series at an oil inlet of the hydraulic motor;
step two, calculating the displacement V of the hydraulic pump according to the continuous swing speed omega of the servo mechanism, the swing force arm R of the servo mechanism, the energy parameter and the structural parameter of the servo mechanism, which are obtained in the step one p From the design range, a hydraulic pump bank meeting the requirements is selectedMagnitude V p ′；
Displacement V of hydraulic pump p Is designed within a range of
Step three, the hydraulic motor and the hydraulic pump adopt coaxial design, namely n m ＝n p Considering the power balance relation between the output power of the hydraulic engine and the input power of the hydraulic pump, the displacement V 'of the hydraulic pump is selected according to the step two' p To calculate the displacement V of the hydraulic motor m The design range of (1), and selecting a hydraulic engine displacement value V 'meeting the requirement from the design range' m ；
Hydraulic motor displacement V m Is designed within a range of
Step four, selecting the displacement V 'of the hydraulic pump according to the step two and the step three' p Discharge V 'of hydraulic motor' m And verifying the constant speed function under the change of the drainage pressure, and completing the energy source matching of the hydraulic motor of the servo mechanism after the verification is passed.
The constant-speed valve comprises a constant-difference pressure-reducing valve and a fixed throttling hole, the fixed throttling hole is arranged at an oil outlet of the constant-difference pressure-reducing valve, and a valve core opening x of the constant-speed valve v Will follow the pressure p of the drained kerosene m And the pressure difference before and after the fixed orifice is kept constant through changing, so that the flow rate of the oil liquid is constant.
In step four, the selected hydraulic pump displacement V 'is verified using the method' p And hydraulic motor displacement V' m ：
S1, according to the selected hydraulic pump displacement V' p Discharge V 'of hydraulic motor' m Calculating the cross-sectional area A of the fixed orifice of the constant-speed valve 0 And the pressure drop Δ p over the hydraulic motor m ；
S2, utilizing pressure drop delta p on a hydraulic motor m Pressure drop delta p at the fixed orifice of the constant speed valve v And the pressure p of the drainage kerosene m Calculating the pressure drop deltap over the spool of the constant speed valve s Range of (1)；
S3, according to the cross section area A of the fixed orifice of the constant speed valve 0 And pressure drop Δ p across the spool of the constant speed valve s Calculating the constant speed valve spool opening x v ；
S4, if the calculated constant speed valve core opening x is obtained v Within a reasonable range, then verify passed, otherwise reselect the hydraulic pump displacement V' p And hydraulic motor displacement V' m 。
In the step S4, the valve core opening x of the constant speed valve v The reasonable range is 0.2-1.5 mm.
In step S1, the pressure drop Δ p across the hydraulic motor is calculated using the following formula m ；
In the formula, p v2 The pressure at the upper end of the valve core of the constant-speed valve.
In the step S1, the cross-sectional area A of the constant speed valve fixed orifice 0 Satisfies the following conditions:
wherein, C d0 To fix the flow coefficient of the orifice, ρ is the density of the tapped kerosene.
In step S3, the pressure drop Δ p across the spool of the constant speed valve is calculated using the following formula s The range of (A):
Δp s ＝p m -p m0 -Δp v -Δp m 。
in the step S3, the constant speed valve spool opening x is calculated by using the following formula v ；
Wherein, C sv Is the flow coefficient at the valve core of the constant-speed valve, W sv To be fixedThe area gradient of the orifice.
Compared with the prior art, the invention has the beneficial effects that:
(1) The method is simple, efficient and easy to implement, and can quickly determine the reasonable ratio of the displacement of the hydraulic pump and the hydraulic motor of the servo mechanism according to the variation range of the pressure of the drainage kerosene;
(2) By adopting the design method, the reasonable matching of the drainage energy power and the system hydraulic energy power under the large-range variable thrust regulation of the liquid oxygen kerosene engine can be ensured, and the margin is provided, so that the oil supply pressure of the servo valve is ensured to be within the rated design working condition, the constant rotating speed of the servo power assembly is realized, and the self-adaptive control of the servo mechanism is realized.
Drawings
FIG. 1 is a schematic diagram of the operation of a hydraulic motor drainage type servo mechanism;
FIG. 2 is a simplified schematic diagram of a servo energy apparatus;
fig. 3 is a flow chart of the energy matching method of the present invention.
Detailed Description
The invention is further elucidated with reference to the drawing.
The invention provides a servo mechanism hydraulic motor energy matching method by adopting a hydraulic motor drainage engine high-pressure kerosene scheme so as to adapt to the variable thrust working condition of an engine.
The invention adopts a constant-speed hydraulic motor drainage scheme, reasonably matches the power of drainage energy and system hydraulic energy, quickly determines the displacement of a hydraulic pump and the hydraulic motor, and keeps the rotating speed of a power assembly constant through a constant-speed valve so as to adapt to the large-range change of the kerosene pressure after the pump caused by the thrust adjustment of an engine.
The working principle diagram of the hydraulic motor flow-guiding type servo mechanism is shown in figure 1. High-pressure kerosene enters the hydraulic motor 1 through a hose, a drainage high-pressure kerosene filter 6 and a constant-speed valve 5 after a primary pump of the engine, the hydraulic motor 1 is driven to rotate, and the constant-speed valve 5 maintains the constant output of the rotating speed of the hydraulic motor 1. The hydraulic motor 1 drives the motor 2 to rotate through the overrunning clutch 4, and then drives the hydraulic pump 3 to rotate at a high speed, so that hydraulic energy required by the actuator is generated. The kerosene which has done work is discharged from the oil outlet of the hydraulic motor and returns to the front of the engine pump through the return oil low-pressure kerosene oil filter 7 and the hose.
Under the thrust adjusting working condition of the liquid oxygen kerosene engine, the kerosene pressure after the primary pump is obviously reduced, and for a liquid engine running constantly, the input power of the liquid oxygen kerosene engine is also reduced. In order to maintain the stable operation of the servo mechanism energy system under the minimum throttling condition, the matching relationship between the input energy and the system hydraulic energy power needs to be adjusted. A simplified servo energy device model is shown in fig. 2. During flight, the motor is not operated, and is omitted here.
Acquiring a continuous swing speed omega of a servo mechanism, a swing force arm R of the servo mechanism, energy parameters and structural parameters of the servo mechanism; wherein the energy parameter comprises the pressure p of the drainage kerosene m Drainage oil return pressure p m0 Rated system operating pressure p p Hydraulic pump return pressure p p0 Pressure drop delta p at fixed orifice of constant speed valve v Hydraulic motor comprehensive efficiency eta m Hydraulic motor volumetric efficiency eta mv Hydraulic pump comprehensive efficiency eta p Hydraulic pump volumetric efficiency eta pv The working speed n of the hydraulic pump p And the operating speed n of the hydraulic motor m (ii) a The structural parameters include the actuator piston area a.
Output power P of hydraulic motor m With the pressure p of kerosene drained by hydraulic motor m The relationship (c) is shown in the formula (1).
Throttling operation of engine, guiding kerosene pressure p m Will decrease, therefore, the output power P of the hydraulic motor m Will be reduced.
The power of the hydraulic energy source is determined by the power of the hydraulic pump. Input power P of hydraulic pump of servo mechanism p Determined by equation (2).
Considering the power balancing relationship and preserving the design margin is:
P m ≥P p (3)
the hydraulic motor and the hydraulic pump are designed coaxially, so that the hydraulic motor and the hydraulic pump have the following structure:
n m ＝n p (4)
the relationship between the displacement of the hydraulic pump and the displacement of the hydraulic motor obtained by the joint type (1) to the formula (4) is shown as the formula (5):
V p is the displacement of a hydraulic pump, V m Is the displacement of the hydraulic motor.
According to the formula (5), the matching of the input energy and the hydraulic power of the hydraulic motor can adapt to the large-range change of the diversion pressure and the thrust of the engine only by properly taking the displacement ratio of the hydraulic pump and the hydraulic motor according to the thrust adjusting working condition.
The method for keeping the rotating speed of the power assembly constant is to serially connect a constant speed valve at an oil inlet of the hydraulic motor, wherein the constant speed valve consists of a fixed differential pressure reducing valve and a fixed throttling orifice, and the fixed differential pressure reducing valve keeps the front and back pressure difference of the fixed throttling orifice constant, so that the flow speed of oil is constant. If the kerosene pressure p is introduced m Decreasing, the pressure p at the lower end of the valve core of the constant speed valve v1 Will be reduced therewith, the pressure p at the lower end of the valve core v1 With the pressure p at the upper end of the spool v2 The difference in (c) decreases. Under the action of spring, the whole valve body moves downwards, and the valve core is opened x v Increased flow rate Q through the constant speed valve m Increase, in turn, p v1 Increase, p v1 And p v2 The difference in (c) is reduced and a new equilibrium is reached and vice versa.
The characteristic functions of the constant-speed valve are as equations (6) to (8).
A s (p v1 -p v2 )＝K s x s +F f (x v ) (8)
Wherein A is s Cross-sectional area of constant-speed valve spool, K s Constant velocity valve internal spring rate, x s For constant rate of pre-compression of the valve spring, F f (x v ) Is the hydraulic power at the valve core of the constant speed valve. C d0 To fix the flow coefficient of the orifice, ρ is the density of the bleed kerosene. C sv Is the flow coefficient at the valve core of the constant-speed valve, W sv Is a fixed orifice area gradient. A. The 0 The cross-sectional area of the orifice is fixed for the constant speed valve.
Equation (6) represents the flow rate from the engine into the constant speed valve spool, and equation (7) represents the flow rate through the fixed orifice. Pressure drop delta p at a fixed orifice of a constant speed valve v Substantially unchanged, and can be regarded as a constant, the flow Q in the formula (7) m Is a constant. To ensure the flow Q in formula (6) m Constant rate valve spool opening x v Will follow the pressure p of the drained kerosene m And (4) changing.
Equation (8) is a force balance equation at both sides of the constant speed valve spool. Generally, the spring force is much greater than the hydraulic force F at the spool f (x v ) The pressure drop deltap at the fixed orifice of the constant-speed valve v Can be approximated by equation (9), the pressure drop Δ p over the spool s As equation (10), the pressure drop Δ p over the hydrostatic machine m As shown in formula (11).
Thus diverting the high pressure kerosene pressure p m Can be expressed as:
as can be seen from equation (12), only the high pressure kerosene pressure p is directed m And constant speed valve spool opening x v For variable quantities, i.e. constant speed valves, the change in the pilot pressure can be accommodated by adjusting the spool opening.
As shown in fig. 3, the energy matching method of the present invention comprises the following steps:
acquiring a continuous swing speed omega of a servo mechanism, a swing force arm R of the servo mechanism, energy parameters and structural parameters of the servo mechanism; the energy parameters comprise the pressure p of the drainage kerosene m Drainage oil return pressure p m0 Rated system operating pressure p p Hydraulic pump return pressure p p0 Pressure drop delta p at the fixed orifice of the constant speed valve v Hydraulic motor comprehensive efficiency eta m Hydraulic motor volumetric efficiency eta mv Hydraulic pump comprehensive efficiency eta p Hydraulic pump volumetric efficiency eta pv The working speed n of the hydraulic pump p Working speed n of hydraulic motor m (ii) a The structural parameters include the actuator piston area A;
step two, calculating the displacement V of the hydraulic pump according to the continuous swing speed index omega of the servo mechanism, the swing force arm R of the servo mechanism, the energy parameter and the structural parameter of the servo mechanism, which are obtained in the step one p Is selected to meet a required hydraulic pump displacement V p ', a certain margin can be reserved;
displacement V of hydraulic pump p Satisfy the requirements of
Step three, the hydraulic motor and the hydraulic pump adopt coaxial design, namely n m ＝n p And considering the power balance relation between the output power of the hydraulic motor and the input power of the hydraulic pump, selecting the displacement V 'of the hydraulic pump according to the step two' p To calculate the displacement V of the hydraulic motor m Is selected as a minimum design value of (1), and one hydraulic motor displacement V 'meeting the requirement is selected from the minimum design values' m A certain margin can be reserved;
displacement V of hydraulic motor m Satisfy the requirement of
Step four, selecting the displacement V 'of the hydraulic pump according to the step two and the step three' p And hydraulic motor displacement V' m And verifying the constant speed function under the change of the drainage pressure, and if the constant speed function passes the change of the drainage pressure, finishing the energy matching.
In step four, the selected hydraulic pump displacement V 'is verified using the following method' p And hydraulic motor displacement V' m Whether it is appropriate:
s1, according to the selected hydraulic pump displacement V' p Discharge V 'of hydraulic motor' m Calculating the cross-sectional area A of the fixed orifice of the constant-speed valve 0 And the pressure drop Δ p across the hydraulic motor m ；
S2, setting the pressure drop delta p at the fixed throttle of the constant-speed valve v =2MPa, pressure of the kerosene introduced p m Is in the range of 19 to 24MPa, and the pressure drop deltap on the hydraulic motor obtained by combining S1 m Calculating the pressure drop Deltap on the spool of the constant speed valve s A range of (a);
Δp s ＝p m -p m0 -Δp v -Δp m
s3, fixing the cross section area A of the throttling hole according to the constant speed valve 0 And pressure drop Δ p across the spool of the constant speed valve s Calculating the constant speed valve spool opening x v A range of (d);
s4, if the valve core opening x of the constant speed valve obtained in the S3 v Is within a reasonable range of 0.2-1.5 mm, the selected hydraulic pump displacement V is considered to be p ' and hydraulic motor displacement V m ' proper, otherwise, reselection is required.
The embodiment is as follows:
the design of the displacement of the hydraulic pump and the displacement of the hydraulic motor and the matching calculation flow of the drainage pressure and the opening of the valve core of the constant-speed valve are shown in figure 3. The main design parameters of the servo mechanism under the thrust adjusting working condition of the engine are shown in the table 1.
TABLE 1 Servo mechanism Main design parameters
According to different drainage kerosene pressures, the internal parameters of the hydraulic motor are calculated, and the results are shown in the table 2. It can be clearly seen that the constant speed valve can adjust the pressure drop at the valve body by changing the opening of the valve core to adapt to different pressures of the drained kerosene.
TABLE 2 Main calculation parameters of hydraulic motor
Experiments prove that the parameter design can adapt to the pressure change of the drainage kerosene, the reasonable matching of the power of the hydraulic energy and the power of the kerosene energy is realized, the oil supply pressure of the servo valve is ensured to be in a rated design working condition, and the constant rotating speed of the power assembly can be kept.
The invention can quickly determine the reasonable ratio of the discharge capacities of the hydraulic pump and the hydraulic motor according to the variation range of the pressure of the drainage kerosene, ensure that the oil supply pressure of the servo valve is in a rated design working condition, realize the matching of the drainage energy power and the hydraulic energy power, and keep the rotating speed of the power assembly constant through the constant-speed valve at the oil inlet of the hydraulic motor.
Those skilled in the art will appreciate that the invention may be practiced without these specific details.
Claims (7)
1. A servo mechanism hydraulic motor energy matching method adapting to the variable thrust working condition of an engine is characterized in that:
high-pressure kerosene enters the hydraulic motor through a hose, a drainage high-pressure kerosene filter and a constant-speed valve after a primary pump of the engine, the hydraulic motor is driven to rotate, and the constant-speed valve maintains the constant output of the rotating speed of the hydraulic motor; the hydraulic motor drives the motor to rotate through the overrunning clutch and then drives the hydraulic pump to rotate at a high speed to generate hydraulic energy required by the actuator; the kerosene which has done work is discharged from an oil outlet of the hydraulic engine and returns to the front of the engine pump through an oil return low-pressure kerosene filter and a hose;
the method comprises the following steps:
acquiring a continuous swing speed omega of a servo mechanism, a swing force arm R of the servo mechanism, energy parameters and structural parameters of the servo mechanism; the energy parameters include the drainage kerosene pressure p m Drainage oil return pressure p m0 Rated system operating pressure p p Hydraulic pump return pressure p p0 Pressure drop delta p at fixed orifice of constant speed valve v Hydraulic motor comprehensive efficiency eta m Hydraulic motor volumetric efficiency eta mv Hydraulic pump comprehensive efficiency eta p Hydraulic pump volumetric efficiency eta pv The working speed n of the hydraulic pump p And the operating speed n of the hydraulic motor m (ii) a The structural parameters comprise the area A of the piston of the actuator; the constant speed valve is connected in series at an oil inlet of the hydraulic motor;
step two, calculating the discharge volume V of the hydraulic pump according to the continuous swing speed omega of the servo mechanism, the swing force arm R of the servo mechanism, the energy parameter and the structural parameter of the servo mechanism obtained in the step one p Is selected from the design range, and one hydraulic pump displacement value V 'meeting the requirement is selected from the design range' p ；
Displacement V of hydraulic pump p Is designed within a range of
Step three, the hydraulic motor and the hydraulic pump adopt a coaxial design, namely n m ＝n p Considering the power balance relation between the output power of the hydraulic engine and the input power of the hydraulic pump, the displacement V 'of the hydraulic pump is selected according to the step two' p To calculate the displacement V of the hydraulic motor m The design range of (1), and selecting a hydraulic engine displacement value V 'meeting the requirement from the design range' m ；
Hydraulic motor displacement V m Is designed within a range of
Step four, selecting the displacement V 'of the hydraulic pump according to the step two and the step three' p And hydraulic motor displacement V' m Verifying the constant speed function under the change of the drainage pressure, and completing the energy source matching of the hydraulic motor of the servo mechanism after the verification is passed;
verifying the selected hydraulic pump displacement V 'with' p And hydraulic motor displacement V' m ：
S1, according to the selected hydraulic pump displacement V' p Discharge V 'of hydraulic motor' m Calculating the cross-sectional area A of the fixed orifice of the constant-speed valve 0 And the pressure drop Δ p over the hydraulic motor m ；
S2, utilizing pressure drop delta p on hydraulic motor m Pressure drop delta p at fixed orifice of constant speed valve v And the pressure p of the drainage kerosene m Calculating the pressure drop deltap over the spool of the constant speed valve s A range of (d);
s3, fixing the cross section area A of the throttling hole according to the constant speed valve 0 And pressure drop Δ p across the spool of the constant speed valve s Calculating the constant speed valve spool opening x v ；
S4, if the calculated constant speed valve core opening x is obtained v Within a reasonable range, then verify passed, otherwise reselect the hydraulic pump displacement V' p And hydraulic motor displacement V' m 。
2. A method as claimed in claim 1The servo mechanism hydraulic motor energy matching method adapting to the variable thrust working condition of the engine is characterized in that: the constant-speed valve comprises a constant-difference pressure-reducing valve and a fixed throttling hole, the fixed throttling hole is arranged at an oil outlet of the constant-difference pressure-reducing valve, and a valve core opening x of the constant-speed valve v Will follow the pressure p of the drained kerosene m And the pressure difference before and after the fixed orifice is kept constant through changing, so that the flow rate of the oil liquid is constant.
3. The servo mechanism hydraulic motor energy matching method adapting to the variable thrust working condition of the engine as claimed in claim 1, characterized in that: in the step S4, the valve core opening x of the constant speed valve v The reasonable range is 0.2-1.5 mm.
4. The servo mechanism hydraulic motor energy matching method adapting to the variable thrust working condition of the engine as claimed in claim 1, characterized in that: in step S1, the pressure drop Δ p across the hydraulic motor is calculated using the following formula m ；
In the formula, p v2 The pressure at the upper end of the valve core of the constant-speed valve.
5. The servo mechanism hydraulic motor energy matching method adapting to the variable thrust working condition of the engine as claimed in claim 4, characterized in that: in the step S1, the cross-sectional area A of the constant speed valve fixed orifice 0 Satisfies the following conditions:
wherein, C d0 To fix the flow coefficient of the orifice, ρ is the density of the tapped kerosene.
6. The servo mechanism hydraulic motor adapting to variable thrust working condition of engine according to claim 1The energy matching method is characterized in that: in the step S3, the pressure drop Δ p on the spool of the constant speed valve is calculated by using the following formula s In the following range:
Δp s ＝p m -p m0 -Δp v -Δp m 。
7. the servo mechanism hydraulic motor energy matching method adapting to the variable thrust working condition of the engine as claimed in claim 1, characterized in that: in the step S3, the constant speed valve spool opening x is calculated by using the following formula v ；
Wherein, C sv Is the flow coefficient at the valve core of the constant-speed valve, W sv Is a fixed orifice area gradient.
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| CN106500992B (en) * | 2016-09-21 | 2018-10-09 | 北京精密机电控制设备研究所 | A kind of drainage engine kerosene servo mechanism ground experiment method |
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