CN109506877B - Sub-span super wind tunnel 90-degree large attack angle coupling 360-degree rolling device - Google Patents
Sub-span super wind tunnel 90-degree large attack angle coupling 360-degree rolling device Download PDFInfo
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- CN109506877B CN109506877B CN201811512372.7A CN201811512372A CN109506877B CN 109506877 B CN109506877 B CN 109506877B CN 201811512372 A CN201811512372 A CN 201811512372A CN 109506877 B CN109506877 B CN 109506877B
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Abstract
The invention discloses a 90-degree large-attack-angle coupling 360-degree rolling device for a sub-span super wind tunnel, which comprises a bottom plate, a limiter, an upright post, an upper bottom plate, a servo motor speed reducer assembly, a main output gear, a large-diameter gear, a main screw rod assembly, an auxiliary screw rod assembly, a small-diameter gear, a vertical bevel gear assembly, a horizontal bevel gear assembly, a balance weight assembly, an auxiliary screw rod adapter assembly, a main screw rod adapter assembly, a pull rod, an oil cup, a pull wire sensor, a sealing plate, a pipeline assembly, a support arm, a connecting rod, a pipe joint assembly, a support section assembly, a false support rod, a linear guide rail and a slider support assembly. The invention can continuously and accurately realize the wide range of attack angle of-15 degrees to 90 degrees or even 120 degrees by utilizing the reverse motion of the eccentric crank sliding block mechanism. The length of the 1.2 m-magnitude wind tunnel model can reach 800mm, and the blockage degree is less than or equal to 3 percent. The large attack angle test capability of the wind tunnel under supersonic speed and subsonic speed conditions can be enlarged.
Description
Technical Field
The invention discloses a large-attack-angle mechanical mechanism applied to a sub-span supersonic wind tunnel, and belongs to the field of experimental aerodynamics. The pull rod is driven by the differential motion of the gear set to realize that the support section assembly rotates around the support arm to obtain different attack angles of the model on the support, the attack angle is fed back by a potentiometer of the pull wire sensor, the mechanism can accurately realize a wide attack angle range of-15 degrees to 90 degrees or even 120 degrees by utilizing the inverse motion of the eccentric crank slider mechanism, and the roll angle mechanism can realize 360-degree roll. The whole mechanism can realize the coupling simulation of an attack angle, a roll angle and a sideslip angle by additionally arranging a 0-X-degree sideslip angle joint at the front end of a support section component of the roll mechanism. The control accuracy is 3'. And can be collected in real time.
Background
With the high-speed development of military science and technology, the requirement on maneuverability is higher and higher in the design of novel missiles and airplanes, and the flight boundary of modern airplanes and missiles is expanded to meet the requirement on increased maneuverability. Achieving high maneuverability requires multi-attitude flight at large angles of attack. With the research on the design tasks of various high-maneuverability missiles and airplanes, the large-attack-angle multi-attitude-angle coupling wind tunnel test is increasingly important, and the requirements on the automation level and the precision level of equipment are higher. Accordingly, it is necessary to equip the sub-span supersonic wind tunnel with a large attack angle mechanism.
The angle of attack, also known as the angle of attack, is an important aerodynamic parameter in wind tunnel tests. The range of the angle of attack required to be measured in the conventional aircraft wind tunnel special test is as large as 90 degrees or even 180 degrees, the requirement on data accuracy is high, at present, a subcross supersonic wind tunnel angle of attack mechanism at home and abroad basically adopts a track bent knife structure, the range of the angle of attack which can be realized is-15 degrees to-30 degrees, the range of the angle of attack is small, the adjustment is difficult, the accuracy is not high, and the requirement on the large angle of attack proposed by modern aircraft design can not be met more and more. There is a strong need for a mechanism that can achieve a wide range of angles of attack.
In addition, many sets of supporting rods are designed for the roll angle mechanism of the sub-span supersonic wind tunnel at home and abroad, and key grooves or wedge holes with different roll angles are formed in the supporting rods in the circumferential direction to realize the roll angle. The roll angles are discontinuously arranged according to a certain difference value, and the discontinuity is discontinuous; the design of the supporting rod needs a plurality of sets, the design and processing period is long, and the model needs to be assembled and disassembled again when the roll angle is replaced every time. The use efficiency is low, needs artifical dismouting, and automation level and accuracy are all on the low side.
A90-degree attack angle mechanism of a domestic 1.2 m-magnitude wind tunnel FL-24 wind tunnel adopts a single-arm tail support structure, the mechanism rotates around a fixed point to realize an attack angle of-5-60 degrees, and a 55-degree joint is replaced to realize an attack angle of 50-115 degrees. When the model attack angle alpha is less than or equal to 60 degrees, the model length LB is less than or equal to 0.6m, the model attack angle alpha is greater than 60 degrees, and the model length LB is less than or equal to 0.4 m. When the attack angle of 90 degrees is realized, 55-degree joints need to be replaced, and the realization is realized in sections; the efficiency is low, and the data are deviated around the 60-degree attack angle of the connecting point.
A90-degree attack angle mechanism of a domestic 2.4 m-magnitude wind tunnel FL-26 wind tunnel adopts a joint type tail support structure, and the attack angle range is-6-96 degrees. The length LB of the model with the attack angle alpha less than or equal to 60 degrees is less than or equal to 1 m; the attack angle alpha is more than 60 degrees, and the model LB is less than or equal to 0.6 m. Although the structure can continuously realize an attack angle of 90 degrees, the structure of a plurality of joints is complex, and the joints and the arc-shaped bent cutter tail support occupy large space, so that the blockage ratio is large, and the length of a test model is smaller than the size of a test section.
FL-24 and FL-26 wind tunnels can realize the coupled simulation of an attack angle and a sideslip angle, and cannot realize the simulation of a continuous 90-degree attack angle and a continuous 360-degree rolling angle.
In summary, a wind tunnel test mechanism capable of continuously realizing continuous coupling simulation of a large-range attack angle of 90 degrees, a large model size, a small blockage degree, a large attack angle of 90 degrees and a roll angle of 360 degrees is urgently needed.
Disclosure of Invention
The technical problems solved by the invention are as follows: the invention overcomes the defects of the prior art, provides a 90-degree large-attack-angle coupling 360-degree rolling device for a sub-span super wind tunnel, and can continuously and accurately realize a large-range attack angle range of-15 degrees to 90 degrees or even 120 degrees by utilizing the reverse motion of an eccentric crank slider mechanism. The length of the 1.2 m-magnitude wind tunnel model can reach 800mm, and the blockage degree is less than or equal to 3 percent. The large attack angle test capability of the wind tunnel under supersonic speed and subsonic speed conditions can be enlarged.
The technical solution of the invention is as follows: a90-degree large-attack-angle coupling 360-degree rolling device for a sub-span super wind tunnel comprises a bottom plate, a limiter, an upright post, an upper bottom plate, a servo motor speed reducer assembly, a main output gear, a large-diameter gear, a main lead screw assembly, an auxiliary lead screw assembly, a small-diameter gear, a vertical bevel gear assembly, a horizontal bevel gear assembly, a counterweight assembly, an auxiliary lead screw adapter assembly, a main lead screw adapter assembly, a pull rod, an oil cup, a pull wire sensor, a sealing plate, a pipeline assembly, a support arm, a connecting rod, a pipe joint assembly, a support section assembly, a false support rod, a linear guide rail and a slider support assembly;
the lower bottom plate is connected with the upper bottom plate through the upright post; limiting devices are arranged at the upper and lower stroke limits of the upright column to limit the up-and-down movement of the counterweight component;
the servo motor speed reducer assembly, the main output gear, the large-diameter gear, the main screw nut assembly, the auxiliary screw nut assembly, the small-diameter gear, the vertical bevel gear assembly, the horizontal bevel gear assembly and the counterweight assembly are all arranged on the upper base plate; the vertical bevel gear component and the horizontal bevel gear component are mutually vertical to form a hand-operated mechanism;
an output shaft of the servo motor speed reducer assembly is fixedly connected with the main output gear; the large-diameter gear is fixedly connected with a nut seat of the main screw rod nut component; the main screw nut component is fixedly connected with the support arm through a main screw adapter component; the small-diameter gear is fixedly connected with a nut seat of the auxiliary lead screw assembly; the auxiliary lead screw assembly is fixedly connected with the pull rod through an auxiliary lead screw adapter assembly; the pull rod and the support rod, the support rod and the support section, and the support arm and the support section are connected through a needle bearing to form relative rotation, so that the pull rod, the support arm, the support rod and the support section form an eccentric crank slider mechanism;
the oil cup is fixedly arranged on the baffle of the support arm;
one end of a stay wire of the stay wire sensor is fixedly connected with the support arm, and the other end of the stay wire sensor is fixed on the lower bottom plate;
the sealing plate is fixed on the lower bottom plate;
one end of the pipeline component is connected with the tail end of the supporting section, and the other end is fixed on the lower bottom plate
The linear guide rail fixed on the support arm and the sliding block component fixed on the lower bottom plate realize vertical relative movement;
the motion process is as follows: the power of the mechanism adopts a servo motor speed reducer component as a drive and is transmitted by a speed reduction gear set consisting of a main output gear, a large-diameter gear and a small-diameter gear; the large-diameter gear drives the support arm through the main lead screw nut component, and the small-diameter gear drives the pull rod through the auxiliary lead screw component; the pull rod, the support arm, the support rod and the support section form an eccentric crank sliding block mechanism; the relative motion is realized through the differential motion between the pull rod and the support arm, the relative motion distances are different, so that the model support rod balance assembly arranged on the support section is raised and lowered to form a positive attack angle and a negative attack angle, and the models at all the attack angles are uniformly distributed between the upper wall plate and the lower wall plate of the test section; the attack angle of the mechanism ranges from minus 15 degrees to 90 degrees, the gear ratio is changed by replacing the main output gear and the large-diameter gear and the small-diameter gear, and the length of the diagonal draw bar and the deflection angle of the support section of the mechanism are changed, so that the attack angle can be enlarged to 120 degrees; the large attack angle test capability of the wind tunnel under supersonic speed and subsonic speed conditions can be enlarged.
The attack angle feedback system of the wind measurement and control system measures the actual rotating angle of a false strut arranged on a supporting section by using an external quadrant, simultaneously measures and uses a potentiometer of a pull wire sensor arranged on a supporting arm to obtain the corresponding relation between the attack angle degree and the feedback voltage of the potentiometer, and obtains the fitting relational expression of the attack angle and the potential of minus 15-90 degrees or even 120 degrees for feedback control.
The support arm realizes vertical motion through a linear guide rail and a sliding block component arranged on the bottom plate; the support arm is made of 30CrMnSiA and is divided into an upper part, a middle part and a lower part, the cross section of the upper part is of a structure with a rectangular groove, and the groove is provided with a fixed linear guide rail; the cross section of the middle part is of a pointed wedge-shaped structure with an included angle of 45 degrees, the longitudinal section of the lower part is of a pointed structure with a front end of 15 degrees and a rear end of 60 degrees.
The supporting section is a crank joint with a pre-deflection of 30 degrees; the pre-deflection angle of the supporting section is from 0 degree to 60 degrees, and the whole mechanism realizes an attack angle of 60 degrees to 120 degrees; the material of the supporting section is 30 CrMnSiA.
And key slots and wedge holes of 0-360 degrees are machined on the periphery of the external support rod connected with the support section assembly.
The front end of the supporting section component is additionally provided with a sideslip angle beta joint of 0-X degrees.
The front end of the supporting section component is additionally provided with a sideslip angle beta joint, and the supporting section component is additionally provided with a key groove of 0-360 degrees and a wedge hole.
The external balance, the external support rod or the side slip angle beta joint connected with the support section assembly, the support section and the central axis of the wind tunnel are on the same axis.
The reduction ratio i of the large-diameter gear to the small-diameter gear is as follows: ((L)Z+LM)sinαmax+Lx)/((LZ+LM)sinαmax) (ii) a In the formula: l isZIs the length of the strut, LMFor external test model length, αmaxAnd Lx is the maximum angle of attack and the length of the connecting rod.
The counterweight component comprises a guide wheel, a guide wheel supporting component, a steel wire rope clamp, a counterweight block and a connecting pin; the guide wheel is arranged on the guide wheel supporting assembly, the steel wire rope is wound in a groove of the guide wheel, one end of the steel wire rope is connected with the main screw rod adapter assembly through a connecting pin, and the other end of the steel wire rope is connected with the balancing weight; the steel wire rope clamp is used for fixing the steel wire rope.
The vertical bevel gear component comprises a straight gear, a support, a shaft, paired conical roller bearings and a bevel gear; the straight gear is arranged at one end of the shaft, the bevel gear is arranged at the other end of the shaft, and the shaft is connected with the support through paired tapered roller bearings; the horizontal bevel gear component comprises a bevel gear, a shaft, a support, paired tapered roller bearings and a crank; the bevel gear is arranged at one end of the shaft, the crank is arranged at the other end of the shaft, and the shaft is connected with the support through paired tapered roller bearings.
The balance model strut assembly and the dummy strut are connected by 1: the cone of 10 fits over the support section.
The supporting section assembly can realize high-precision large-torque 360-degree rolling. The hollow servo motor harmonic reducer comprises a rectifying cone, a straight support, a hollow shaft, a high-strength bearing, an external shaft, a bearing cover, a motor base, a hollow servo motor harmonic reducer assembly and the like. The hollow servo motor harmonic speed reducer assembly is installed on the motor base, the motor base is fixed on the rear end of the straight support, and the external shaft is installed on the hollow servo motor harmonic speed reducer assembly. The hollow shaft is connected with the external shaft through a key, the hollow shaft and the straight support are connected through paired high-strength needle roller bearings to rotate relatively, and two ends of the bearings are fixed through bearing covers. The fairing cone is arranged at the front end of the straight support. The hollow servo motor harmonic speed reducer component drives a dummy support rod connected with the hollow shaft or an external balance model support rod component to realize 360-degree rolling. The control precision of the rolling angle can reach +/-3'.
The 90-degree attack angle mechanism and the 360-degree rolling mechanism operate independently.
Any angle of attack α, sideslip angle β of the model may be changed by an angle of attack mechanism αmAnd a rolling mechanism gamma. The solving formula is as follows:
tanα＝cosγ·tanαm
sinβ＝sinγ·sinαm
the front end of the supporting section component is additionally provided with a beta joint with a sideslip angle of 22 degrees, so that three-degree-of-freedom multi-attitude coupling simulation of a 90-degree or even attack angle, a 360-degree roll angle and a 22-degree sideslip angle can be realized.
Compared with other technologies, the invention has the advantages that:
1. the large-attack-angle mechanism disclosed by the invention has a large attack angle range.
The invention overcomes the defect that the conventional sub-span supersonic wind tunnel attack angle mechanism only adopts a track bent blade structure to realize an attack angle range of-15-30 degrees and cannot meet the requirement of a large attack angle provided by modern aircraft design, and provides a 90-degree large attack angle mechanical mechanism applied to a sub-span supersonic wind tunnel, which can continuously realize an attack angle of-15-90 degrees at one time, change the gear ratio by replacing a main output gear, a large-diameter gear and a small-diameter gear, and enlarge the attack angle to 120 degrees by changing the length of a diagonal draw bar and the deflection angle of a support section of the mechanism. The large attack angle test capability of the wind tunnel under supersonic speed and subsonic speed conditions can be enlarged.
2. The invention discloses a large attack angle mechanism, and provides a new principle design method for realizing an ultra-large attack angle by adopting the principle of inverse motion of an eccentric crank slide block. The traditional attack angle method mainly comprises the following steps: a curved knife structure, a pole changing and model changing, a joint type tail support and the like. The angle of attack range is small by the curved cutter structure, the method of changing the strut and changing the model can not realize continuous angle of attack, and the manufacturing cost is high and the efficiency is low; the articulated tail branch has the defects of complex control, large blockage degree and small test model; the angle of attack designed by adopting the principle of the inverse motion of the eccentric crank sliding block can reach 90 degrees or even 120 degrees, the range of the angle of attack is large, the angle of attack can be continuously realized, the larger the angle of attack is, the smaller the blockage degree of the mechanism is, and the 90-degree angle of attack of the model in the wind tunnel with the magnitude of 1.2m can reach 800 mm. And the model length is only 600mm when the articulated tail support structure of the wind tunnel with the magnitude of 2.4m has an attack angle of 90 degrees. In conclusion, the principle design principle of the reverse motion of the eccentric crank sliding block has obvious advantages in various aspects.
3. The large-attack-angle mechanism disclosed by the invention has no jumping point in a full-attack-angle range and does not need data correction. The mechanism can continuously realize the attack angle of-15-90 degrees at one time by using the same-size model, and the size of the model and the structure position of the supporting rod do not need to be changed, so that the test data does not need to be corrected due to the change of the supporting rod and the model, and the test data is smooth and has no jumping points.
4. The degree of blockage of the angle of attack mechanism is smaller than that of the conventional angle of attack mechanism. The blocking degree of the attack angle mechanism is less than or equal to 3.9 percent at 0 degree, and the blocking degree of the attack angle mechanism is only 0.8 percent at 90 degrees. The larger the angle of attack mechanism, the less the jamming of the mechanism itself. The interference caused by the large-attack-angle mechanism of 90 degrees is reduced to the minimum. The problem that the larger the attack angle of the conventional attack angle mechanism is, the larger the mechanism blockage degree is, the mechanism interference amount is equivalent to the unsteady measurement amount at the attack angle of 90 degrees is solved.
5. The 360-degree rolling angle mechanism disclosed by the invention can continuously realize the accurate control of 360-degree high-precision large-torque load. The problems of discontinuous rolling angle and low use efficiency of the conventional method for realizing the rolling angle by matching a plurality of support rods with key slot holes are solved.
6. The invention can solve the model attack angle and the sideslip angle through the attack angle mechanism and the roll angle mechanism of the device. The front end of the roll angle mechanism is additionally provided with a beta joint with a sideslip angle of 22 degrees, so that three-degree-of-freedom multi-attitude coupling simulation of a continuous 90-degree or even 120-degree attack angle, a 360-degree roll angle and a 22-degree sideslip angle can be realized. The development of the large attack angle mechanism enables various flight attitudes of an aircraft in air to be successfully simulated in a wind tunnel, and particularly solves the problem of simulation of the coupled flight attitudes of a large attack angle and a plurality of attitude angles.
7. The large-attack-angle mechanism is convenient, quick and efficient to adjust compared with a conventional mechanism. A conventional test attack angle mechanism is installed on a wind tunnel body, and a wind tunnel test cannot be carried out by replacing a model during test preparation. The blowing time of the wind tunnel body test is occupied, and the efficiency is low; the 90-degree attack angle mechanism is combined with a special test section for use. The whole system modularization is fixed on a positioning platform on the special test section through a plurality of groups of bolts for the lower bottom plate, the dismounting and the mounting are very convenient, and the next test can be carried out by removing the special test section and the 90-degree mechanism. The test preparation and the evacuation do not occupy the blowing time of the wind tunnel body. Not influence each other, improved efficiency of blowing and experimental efficiency of preparing.
Drawings
FIG. 1 is a diagram of a 90-degree large-attack-angle coupling 360-degree rolling device
FIG. 2 is a detailed view of the driving part of the 90-degree large-attack-angle coupling 360-degree rolling device
FIG. 3 is a detailed view of the attack angle portion of a 90-degree large attack angle coupled 360-degree rolling device
FIG. 4 is a schematic diagram of a main screw assembly of a 90-degree large-attack-angle coupling 360-degree rolling device
FIG. 5 is a diagram of a support arm structure of a 90-degree large-attack-angle coupling 360-degree rolling device
FIG. 6 is a structural diagram of a hand-operated mechanism assembly of a 90-degree large-attack-angle coupling 360-degree rolling device
FIG. 7 is a schematic view of a counterweight assembly of a 90 DEG high-angle-of-attack coupled 360 DEG roll-over device
FIG. 8 is a 360-degree rolling configuration diagram of a 90-degree large angle of attack coupling 360-degree rolling device support segment assembly
FIG. 9 is a schematic structural diagram of a 120-degree large-attack-angle coupled 360-degree rolling device
FIG. 10 is a detailed view of the angle of attack portion of a 120 large angle of attack coupled 360 roll device
FIG. 11 is a schematic view of an angle of attack mechanism of a 90-degree large angle of attack coupling 360-degree rolling device
FIG. 12 is a structure view of a beta joint with a sideslip angle of-2 to 22 DEG
FIG. 13 is a schematic view of an installation of a 90-degree large-attack-angle coupled 360-degree rolling device
Detailed Description
The invention is described in further detail below with reference to the following figures and specific examples: the examples are not intended to limit the invention. Those skilled in the art will appreciate that those matters not described in detail in the present specification are well known in the art.
As shown in fig. 1-3, a 90 ° large attack angle coupling 360 ° rolling device includes a lower base plate 1, a stopper 2, an upright post 3, an upper base plate 4, a servo motor reducer assembly 5, a main output gear 6, a large diameter gear 7, a main screw assembly 8, an auxiliary screw assembly 9, a small diameter gear 10, a vertical bevel gear assembly 11, a horizontal bevel gear assembly 12, a counterweight assembly 13, an auxiliary screw adapter assembly 14, a main screw adapter assembly 15, a pull rod 16, an oil cup 17, a pull wire sensor 18, a seal plate 19, a pipeline assembly 20, a support arm 21, a connecting rod 22, a pipe joint assembly 23, a support section assembly 24, a dummy support rod 25, a linear guide rail assembly 26, and a slider support assembly 27.
The servo motor speed reducer component 5, the main output gear 6, the large-diameter gear 7, the main screw component 8, the auxiliary screw component 9, the small-diameter gear 10, the bevel gear component 11, the bevel gear component 12, the counterweight component 13 and the like are all installed and fixed on the upper base plate 4 through bolts, screws and the like. The upper bottom plate 4 is fixed with the lower bottom plate 1 through the upright post 3. The lengths of the steel wire ropes of the upright post 3, the main lead screw component 8, the auxiliary lead screw component 9 and the counterweight component 13 are all determined by the maximum stroke of the system movement.
The main lead screw assembly 8 is connected to the arm 21 by a main lead screw adapter assembly 15. The auxiliary lead screw assembly 9 is connected to a tie rod 16 by an auxiliary lead screw adapter assembly 14. The arm 21, the link 22, the coupling joint assembly 23, and the support section assembly 24 are coupled to each other by high-strength needle bearings.
The main lead screw assembly 8 is shown in fig. 4. The device mainly comprises a high-precision lead screw 8-1, a tapered roller bearing 8-2, an outer sleeve 8-3, an inner sleeve 8-4, a small cover plate 8-5 and a large cover plate 8-6. A nut of the high-precision lead screw 8-1 is fixedly connected with the gear 7 through a screw, the rotary motion of the gear 7 is converted into the linear motion of the lead screw, and the lead screw drives the support arm 21 to vertically and linearly move through the main lead screw adapter assembly 15.
The structure form of the auxiliary screw rod component 9 is the same as that of the main screw rod component 8, and the description is omitted.
The support arm 21 is constructed as shown. The arm 21 is vertically moved up and down with high accuracy by a high-accuracy linear guide 26 and a slider assembly 27 mounted on the base plate 1. The support arm is made of 30CrMnSiA, so that the rigidity and the strength of the system are enhanced. The support arm 21 is divided into an upper part, a middle part and a lower part, the cross section of the upper part is of a structure with a rectangular groove, and a fixed linear guide rail 26 is arranged in the groove; the cross section of the middle part is of a pointed wedge-shaped structure with an included angle of 45 degrees, the cross section of the front end of the supporting arm is of the pointed wedge-shaped structure with the included angle of 45 degrees in the range between the upper wall plate and the lower wall plate of the test section in the whole attack angle operation range, and the supporting arm is prevented from generating extra shock waves at supersonic speed relative to a rectangular structure. The stable area of the flow field is enlarged. The longitudinal section of the lower part is a sharp-angled structure with the front end of 15 degrees and the rear end of 60 degrees. The included angle between the front end of the longitudinal section and the horizontal line is 15 degrees, the included angle between the rear end of the longitudinal section and the horizontal line is 60 degrees, and the uniqueness of the structural rigidity, the structural strength and the operational relation angle of the support arm is ensured.
The vertical bevel gear assembly 11 and the horizontal bevel gear assembly 12 which are perpendicular to each other form a hand-operated mechanism, as shown in fig. 6. The rotation around the Y axis is converted into the rotation around the X axis, so that manual hand-cranking debugging is facilitated. The vertical bevel gear assembly 11 is composed of a straight gear 11-1, a support 11-2, a shaft 11-3, a pair of tapered roller bearings 11-4, a bevel gear 11-5 and the like. The straight gear 11-1 is arranged at one end of the shaft 11-3, the bevel gear 11-5 is arranged at the other end of the shaft 11-3, and the shaft 11-3 is connected with the support 11-2 through the paired tapered roller bearings 11-4. The horizontal bevel gear assembly 12 is composed of a bevel gear 12-1, a shaft 12-2, a support 12-3, a pair of tapered roller bearings 12-4, a crank 12-5 and the like. The bevel gear 12-1 is arranged at one end of the shaft 12-2, the crank 12-5 is arranged at the other end of the shaft 12-2, and the shaft 11-3 is connected with the support 12-2 through a pair of tapered roller bearings 12-4.
The weight assembly 13 is shown in fig. 7. The device comprises guide wheels 13-1, guide wheel supporting components 13-2, steel wire ropes 13-3, steel wire rope clamps 13-4, balancing weights 13-5, connecting pins 13-6 and the like. The guide wheel 13-1 is arranged on the guide wheel supporting component 13-2, the steel wire rope 13-3 is wound in a groove of the guide wheel 13-1, one end of the steel wire rope is connected with the main screw rod adapter component 15 through the connecting pin 13-6, and the other end of the steel wire rope is connected with the balancing weight 13-5. The wire rope clamp 13-4 is used for fixing the wire rope. The balancing weight is used for balancing the mass of the support arm. And the useless power of the servo motor is reduced. And the starting impact load of the structure is reduced. The structure mass is lightened.
The oil cup 17 is fixedly arranged on the baffle plate of the support arm 21. For lubricating the arm 21 and the pull rod 16.
The stay wire sensor 18 has one end of the stay wire fixed to the support arm 21 and the other end fixed to the lower base plate 1. And the actual attack angle is obtained through mathematical calculation by feeding back the position of the support arm.
The sealing plate 19 is fixed on the lower bottom plate 1 through bolts, and through tolerance fit with the support arm 21, the air leakage is reduced while the support arm is ensured to run stably up and down, and dynamic sealing is used for sealing.
The pipeline assembly 20 is connected at one end to the rear end of the support section 24 and is fixed at one end to the lower base plate 1. The device is used for protecting a balance measurement control circuit and avoiding being blown off by sub-span supersonic airflow.
The high-precision linear guide rail 26 fixed on the support arm 21 and the slide block assembly 27 fixed on the lower base plate 1 can realize high-precision vertical up-and-down relative movement.
The connecting rod 22 is connected to the tie rod 16 and the support segment assembly 24, respectively, by tapered roller bearings.
The coupling assembly 23 is used to couple the line assembly 20 and the support section assembly 24. Which is threaded onto the support section assembly 24 to secure the line assembly 20 via the plurality of sets of bolts. And the inner line of the pipeline is ensured to have no breakage in the whole attack angle range.
The support segment assembly 24 is shown in fig. 8. The hollow servo motor harmonic reducer comprises a fairing cone 24-1, a high-strength needle bearing 24-2, a straight support 24-3, a hollow shaft 24-4, an external shaft 24-5, a bearing cover 24-6, a motor base 24-7 and a hollow servo motor harmonic reducer assembly 24-8. The straight support 24-3 of the support segment assembly 24 is a straight joint with a pre-bias angle a of 30 °. The distance between the centers of the two lug seat holes is kept constant, the pre-deflection angle is realized by changing the distance between the centers of the two lug seat holes and the center of the cylinder of the supporting section assembly, and the original elbow joint is changed into a straight joint. The pre-deflection angle of a straight support 24-3 of the support section assembly 24 is from 0 degree to 60 degrees, and the whole mechanism realizes an attack angle of 60 degrees to 120 degrees; the material of the support section 24 is 30 CrMnSiA.
The straight support 24-3 hollow servo motor harmonic speed reducer assembly 24-8 is installed on a motor base 24-7, the motor base 24-7 is fixed on the rear end of the straight support 24-3, and the external shaft 24-5 is installed on the hollow servo motor harmonic speed reducer assembly 24-8. The hollow shaft 24-4 is connected with the external shaft 24-5 through a key, the hollow shaft 24-4 and the straight support 24-3 are connected through a pair of high-strength needle roller bearings 24-2 to rotate relatively, and two ends of the bearings are fixed through bearing covers 24-6. The rectifying cone 24-1 is arranged at the front end of the straight support 24-3. The hollow servo motor harmonic speed reducer assembly 24-8 drives the dummy support rod 25 connected with the hollow shaft 24-4 or the external balance model support rod assembly to realize 360-degree rolling. The control precision of the rolling angle can reach +/-3'.
The 90-degree attack angle mechanism and the 360-degree rolling mechanism operate independently.
The dummy post 25 is fixed to the support section assembly 24 by a post fitting, a key, a screw connection, or the like. The dummy bar 25 is used for early equipment commissioning to measure angle of attack. And in actual use, an external balance model support rod system is adopted for testing at a corresponding position.
The main motion flow is as follows: the power of the mechanism is transmitted by a servo motor speed reducer assembly 5 through a speed reduction gear set consisting of a main output gear 6, a large-diameter gear 7 and a small-diameter gear 10; the large-diameter gear 7 drives the support arm 21 through the main lead screw assembly 8, and the small-diameter gear 10 drives the pull rod 16 through the auxiliary lead screw assembly 9. The pull rod 16, the sharp wedge-shaped support arm 21, the support rod 22 and the support section assembly 24 form an eccentric crank sliding block mechanism; the relative motion is realized through the differential motion between the pull rod 16 and the support arm 21, and the difference of the relative motion distance enables the model support rod balance assembly 25 to raise and lower the head to form a positive attack angle and a negative attack angle, and the models at all attack angles are uniformly distributed between the upper wall plate and the lower wall plate of the test section. The variation range of the attack angle of the mechanism is-15-90 degrees, and the support section 24 of the 90-degree attack angle mechanism is an elbow joint with a pre-deflection angle of 30 degrees and is made of 30 CrMnSiA. The gear ratio can be changed by replacing the gear 6, the gear 7 and the gear 10, and the length of the diagonal draw bar 22 and the deflection angle of the support section 24-3 of the mechanism are changed, so that the attack angle can be enlarged to-15-120 degrees. The 24-3 deflection angle changing method comprises the following steps: the distance between the centers of the two lug seat holes is kept constant, the pre-deflection angle is realized by changing the distance between the centers of the two lug seat holes and the center of the cylinder of the supporting section assembly, and the original elbow joint is changed into a straight joint. A15-degree joint is used at the front end of the straight support 24-3, so that the attack angle operation range of 0-135 degrees can be realized. The structure diagrams of the 120-degree attack angle mechanism are shown in fig. 9 and fig. 10. The large attack angle test capability of the wind tunnel under supersonic speed and subsonic speed conditions can be enlarged.
The basic principle of the attack angle movement of the mechanism utilizes the inverse movement of the eccentric crank slider mechanism to accurately realize the attack angle of-15 degrees to 90 degrees. As shown in fig. 11. The angle of attack mechanism system is the core component to achieve a given angle of attack. The basic principle for realizing the attack angle movement is that the eccentric crank slider moves in the reverse direction, the slider C, namely the pull rod 16, moves in the guide groove of the pointed wedge-shaped support arm 21 to drive the connecting rod BC, namely the support rod 22, so that the connecting rod AB, namely the support section assembly 24, moves on the pointed wedge-shaped support arm 21 around the point A to realize the attack angle movement. When the difference is different, the differential displacement of the C and the A drives the connecting rod AB to realize the change of the attack angle, the actual design parameters of the differential quantity are brought into the corresponding motion law, and the specific motion law can be obtained through corresponding calculation.
The preliminary determination method of the reduction ratio i of the large-diameter gear 7 and the small-diameter gear 10 comprises the following steps: ((L)Z+LM)sinαmax+Lx)/((LZ+LM)sinαmax) (ii) a In the formula: l isZIs the length of the strut, LMFor testing model length, αmaxIs the maximum angle of attack. Lx is the link 22 length. The formula is generally suitable for the selection method of 60-120 degree attack angle mechanism of the mechanism, and the methodThe model center and the wind tunnel axis can be ensured to be basically coincided. For example: 60 degree angle of attack mechanism, LZIs 450mm, LM1050mm, Lx 236mm, i ═ 1.28; 90 degree angle of attack mechanism, LZIs 500mm, LM800mm, Lx 333.75mm, i 1.37;
any angle of attack α, sideslip angle β of the model may be changed by an angle of attack mechanism αmAnd a rolling mechanism gamma. The solving formula is as follows:
tanα＝cosγ·tanαm
sinβ＝sinγ·sinαm
the front end of the supporting section assembly 24 is additionally provided with a slip angle beta joint of-2 degrees to 22 degrees as shown in figure 12 through column matching. The multi-attitude coupling simulation of an attack angle alpha of 90 degrees and 120 degrees, a roll angle gamma of 360 degrees and a sideslip angle beta of 22 degrees can be realized.
The dummy strut 25 is equivalent to the balance model strut system by measuring the actual angle of rotation of the model with a dummy strut 25 mounted on the support section assembly 24 by the mechanism through different angles of attack. And the potentiometer of the stay wire sensor 18 arranged on the support arm 21 is used for obtaining the degree of the attack angle and the feedback voltage of the potentiometer, the actual value of the attack angle and the feedback voltage is uploaded to an industrial personal computer, and the fitting relation between the attack angle and the potential is obtained, so that in the test process, the real attack angle is obtained through different feedback voltages, the attack angle range is-15 degrees to 90 degrees and 120 degrees, and the angle is transmitted to a wind tunnel measurement and control system. The computer executes corresponding control action according to the program, so that the accuracy of measuring the attack angle is improved, and the control precision of the attack angle can reach +/-3'.
The whole system 0-0 is modularized, and is fixedly arranged on a positioning platform on a special test section 0-1 through a lower bottom plate 1 by using a plurality of groups of bolts, so that the disassembly and the assembly are very convenient, and the wind tunnel body blowing time is not occupied for test preparation and evacuation. Not influence each other, improved efficiency of blowing and experimental efficiency of preparing. As shown in fig. 13. Finally, a multi-attitude angle coupling simulation wind tunnel test of the 90-degree 120-degree large-attack-angle coupling 360-degree rolling device is completed.
Those skilled in the art will appreciate that those matters not described in detail in the present specification are well known in the art.
Claims (6)
1. A subspan super wind tunnel 90-degree large attack angle coupling 360-degree rolling device is characterized in that: the device comprises a lower base plate (1), a limiter (2), a stand column (3), an upper base plate (4), a servo motor speed reducer assembly (5), a main output gear (6), a large-diameter gear (7), a main screw rod assembly (8), an auxiliary screw rod assembly (9), a small-diameter gear (10), a vertical bevel gear assembly (11), a horizontal bevel gear assembly (12), a counterweight assembly (13), an auxiliary screw rod adapter assembly (14), a main screw rod adapter assembly (15), a pull rod (16), an oil cup (17), a pull wire sensor (18), a sealing plate (19), a pipeline assembly (20), a support arm (21), a connecting rod (22), a pipe joint assembly (23), a support section assembly (24), a dummy support rod (25), a linear guide rail (26) and a sliding block support assembly (27);
the lower bottom plate (1) is connected with the upper bottom plate (4) through the upright post (3); limiting stoppers (2) are arranged at the upper and lower stroke limits of the upright post (3) to limit the up-and-down movement of the counterweight component (13);
a servo motor speed reducer component (5), a main output gear (6), a large-diameter gear (7), a main lead screw component (8), an auxiliary lead screw component (9), a small-diameter gear (10), a vertical bevel gear component (11), a horizontal bevel gear component (12) and a counterweight component (13) are all arranged on the upper base plate (4); the vertical bevel gear component (11) and the horizontal bevel gear component (12) are mutually vertical to form a hand-operated mechanism;
an output shaft of the servo motor speed reducer assembly (5) is fixedly connected with the main output gear (6); the large-diameter gear (7) is fixedly connected with a nut seat of the main screw rod assembly (8); the main screw rod assembly (8) is fixedly connected with the support arm (21) through a main screw rod adapter assembly (15); the small-diameter gear (10) is fixedly connected with a nut seat of the auxiliary lead screw assembly (9); the auxiliary lead screw assembly (9) is fixedly connected with the pull rod (16) through an auxiliary lead screw adapter assembly (14); the pull rod (16) is connected with the connecting rod (22), the connecting rod (22) is connected with the supporting section assembly (24), and the support arm (21) is connected with the supporting section assembly (24) through a needle bearing to form relative rotation, so that the pull rod (16), the support arm (21), the connecting rod (22) and the supporting section assembly (24) form an eccentric crank slider mechanism;
the oil cup (17) is fixedly arranged on the baffle of the support arm (21);
one end of a stay wire of the stay wire sensor (18) is fixedly connected with the support arm (21), and the other end is fixed on the lower bottom plate (1);
the sealing plate (19) is fixed on the lower bottom plate (1);
one end of the pipeline component (20) is connected with the tail end of the supporting section component (24), and the other end is fixed on the lower bottom plate (1);
the linear guide rail (26) fixed on the support arm (21) and the sliding block support assembly (27) fixed on the lower bottom plate (1) realize vertical relative movement;
the motion process is as follows: the eccentric crank sliding block mechanism adopts a servo motor speed reducer component (5) as a drive and is driven by a speed reducing gear set consisting of a main output gear (6), a large-diameter gear (7) and a small-diameter gear (10); the large-diameter gear (7) drives the support arm (21) through the main lead screw component (8), and the small-diameter gear (10) drives the pull rod (16) through the auxiliary lead screw component (9); the differential motion between the pull rod (16) and the support arm (21) is used for realizing the relative motion, and the relative motion distances are different, so that the model support rod balance assembly arranged on the support section assembly (24) is raised and lowered to form positive and negative attack angles, and the models at all the attack angles are uniformly distributed between the upper wall plate and the lower wall plate of the test section; the attack angle of the mechanism is changed within the range of-15 degrees to 90 degrees; the change of the gear ratio is realized by replacing the main output gear (6), the large-diameter gear (7) and the small-diameter gear (10), and the angle of attack can be enlarged to 120 degrees by changing the length of the connecting rod (22) and the deflection angle of the straight support (24-3); the pipe joint assembly (23) is used for connecting the pipeline assembly (20) and the support section assembly (24); the pipe joint assembly (23) is connected with the supporting section assembly (24) through threads, and the pipeline assembly (20) is fixed through a plurality of groups of bolts;
the support arm (21) realizes vertical movement through a linear guide rail (26) and a sliding block support assembly (27) arranged on the lower base plate (1); the support arm (21) is made of 30CrMnSiA and is divided into an upper part, a middle part and a lower part, the cross section of the upper part is of a structure with a rectangular groove, and a fixed linear guide rail (26) is arranged in the groove; the cross section of the middle part is of a sharp wedge-shaped structure with an included angle of 45 degrees, and the longitudinal section of the lower part is of a sharp angle-shaped structure with a front end of 15 degrees and a rear end of 60 degrees;
the support section assembly (24) comprises a rectifying cone (24-1), a high-strength needle bearing (24-2), a straight support (24-3), a hollow shaft (24-4), an external shaft (24-5), a bearing cover (24-6), a motor base (24-7) and a hollow servo motor harmonic speed reducer assembly (24-8); the hollow servo motor harmonic speed reducer component (24-8) is arranged on the motor base (24-7), the motor base (24-7) is fixed on the rear end of the straight support (24-3), and the external shaft (24-5) is arranged on the hollow servo motor harmonic speed reducer component (24-8); the hollow shaft (24-4) is connected with the external shaft (24-5) through a key, the hollow shaft (24-4) and the straight support (24-3) are connected through a pair of high-strength needle roller bearings (24-2) to rotate relatively, and two ends of the bearings are fixed through bearing covers (24-6); the rectifying cone (24-1) is arranged at the front end of the straight support (24-3); the hollow servo motor harmonic speed reducer assembly (24-8) drives a dummy support rod (25) connected with the hollow shaft (24-4) or an external model support rod balance assembly to realize 360-degree rolling.
2. The sub-span super wind tunnel 90-degree large-attack-angle coupling 360-degree rolling device according to claim 1, wherein: the straight support (24-3) is a straight joint with a pre-deflection angle of 0-60 degrees, the distance between the centers of the two ear seat holes is kept constant, and the original elbow joint can be changed into the straight joint by changing the distance between the centers of the two ear seat holes and the center of the support section assembly cylinder.
3. The sub-span super wind tunnel 90-degree large-attack-angle coupling 360-degree rolling device according to claim 1, wherein: the front end of the supporting section component (24) is additionally provided with a joint with a sideslip angle beta of 0-22 degrees.
4. The sub-span super wind tunnel 90-degree large-attack-angle coupling 360-degree rolling device according to claim 3, wherein: the outer support rod connected with the supporting section assembly (24) is arranged on a sideslip angle beta joint additionally arranged at the front end of the supporting section assembly (24) in the circumferential direction, and the supporting section assembly (24) is additionally provided with a key groove of 0-360 degrees and a wedge hole.
5. The sub-span super wind tunnel 90-degree large-attack-angle coupling 360-degree rolling device according to claim 1, wherein: the counterweight component (13) comprises a guide wheel (13-1), a guide wheel supporting component (13-2), a steel wire rope (13-3), a steel wire rope clamp (13-4), a counterweight block (13-5) and a connecting pin (13-6); the guide wheel (13-1) is arranged on the guide wheel supporting component (13-2), the steel wire rope (13-3) is wound in a groove of the guide wheel (13-1), one end of the steel wire rope is connected with the main screw rod adapter assembly (15) through a connecting pin (13-6), and the other end of the steel wire rope is connected with the balancing weight (13-5); the steel wire rope clamp (13-4) is used for fixing the steel wire rope.
6. The sub-span super wind tunnel 90-degree large-attack-angle coupling 360-degree rolling device according to claim 1, wherein: the vertical bevel gear assembly (11) comprises a straight gear (11-1), a support (11-2), a shaft (11-3), paired conical roller bearings (11-4) and bevel gears (11-5); a straight gear (11-1) is arranged at one end of a shaft (11-3), a bevel gear (11-5) is arranged at the other end of the shaft (11-3), and the shaft (11-3) is connected with a support (11-2) through a pair of tapered roller bearings (11-4); the horizontal bevel gear component (12) comprises a bevel gear (12-1), a shaft (12-2), a support (12-3), a pair of tapered roller bearings (12-4) and a crank (12-5); the bevel gear (12-1) is arranged at one end of the shaft (12-2), the crank (12-5) is arranged at the other end of the shaft (12-2), and the shaft (12-2) is connected with the support (12-3) through the paired tapered roller bearings (12-4).
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| CN111289209A (en) * | 2020-03-06 | 2020-06-16 | 中国空气动力研究与发展中心低速空气动力研究所 | Model pitch angle motion supporting device suitable for wind tunnel test of wing-body fusion aircraft |
| CN111307400B (en) * | 2020-03-31 | 2022-02-22 | 中国空气动力研究与发展中心低速空气动力研究所 | Back support device for wind tunnel ground effect test |
| CN112345195B (en) * | 2020-11-17 | 2022-10-18 | 中国航天空气动力技术研究院 | Test device for high-speed wind tunnel ultra-large attack angle multi-frequency compound motion |
| CN114310734B (en) * | 2022-03-14 | 2022-10-28 | 中国空气动力研究与发展中心低速空气动力研究所 | Airplane model sinking and floating supporting device and four-degree-of-freedom supporting device |
| CN116007890A (en) * | 2023-03-23 | 2023-04-25 | 中国空气动力研究与发展中心超高速空气动力研究所 | Device for measuring micro pressure on surface of inner model of wind tunnel height Wen Liuchang |
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| CN202547900U (en) * | 2012-04-23 | 2012-11-21 | 中国航天空气动力技术研究院 | Automatic rolling tail support mechanism applied to high-speed wind tunnel |
| CN203365102U (en) * | 2013-07-18 | 2013-12-25 | 中国航天空气动力技术研究院 | An ejection-type large-attack-angle mechanism used for a wind-tunnel |
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| CN106840583B (en) * | 2016-12-29 | 2019-12-20 | 中国航天空气动力技术研究院 | Sub-span supersonic wind tunnel large attack angle mechanism with translation function |
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