CN205036663U - Two dimension force feedback formula electro hydraulic servo valve based on case two freedoms - Google Patents
Two dimension force feedback formula electro hydraulic servo valve based on case two freedoms Download PDFInfo
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- CN205036663U CN205036663U CN201520748801.6U CN201520748801U CN205036663U CN 205036663 U CN205036663 U CN 205036663U CN 201520748801 U CN201520748801 U CN 201520748801U CN 205036663 U CN205036663 U CN 205036663U
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Abstract
Two dimension force feedback formula electro hydraulic servo valve based on case two freedoms is including oblique wing formula torque motor and hydraulic pressure mechanism of amplification, to one side wing formula torque motor's armature comprises center pin and the both sides airfoil of level setting, both sides airfoil, top yoke iron and down the yoke be and use the vertical axis as 180 array characteristics of center pin in the end terminal surface about, the both sides airfoil inserts between the end terminal surface of the indisputable and lower yoke of top yoke parallelly, forms four highly the same work air gaps, wing formula torque motor is connected to the one end of valve body to one side, the center pin of center pin and case of armature be located same straight line.
Description
Technical field
The utility model relates to electro-hydraulic servo control element field, especially a kind of two-dimentional force feedback type electrohydraulic control based on spool dual free dimension.
Background technique
Electro-hydraulic servo control technology is since the forties occurs, just the distinguishing feature such as the large and Static and dynamic performance excellence of, ouput force (moment) high with its power-weight ratio occupies high end position in Mechanical & Electrical Transmission and control technique, emphasis is applied to the various crucial occasions such as Aero-Space, military issue weapons, boats and ships, large-scale power station, iron and steel, material testing machine and vibrating table, thus is regarded as the crucial competitive ability of various countries' industry.And as the electrohydraulic control of core control unit, then playing conclusive influence to the performance of whole electrohydraulic servo system, is always one of study hotspot of Fluid-transmission and control field.
In order to effectively overcome hydraulic power thus obtain desirable Static and dynamic performance, servovalve is designed to the multilevel hierarchy of leading control formula by people usually.Among numerous structure innovations, method based on the two freedom of movement of spool is taken the course of its own, its basic thought is as follows: general valve core of the spool valve has radial rotary and moves axially two degrees of freedom, and mutually do not interfere, thus can realize by these two degrees of freedom the function leading control level and power stage respectively, consider that the area gradient of valve port of slide valve can be done very large, and spool is also easier to coordinate with end cap etc. form sensitive cavity in valve opening, the rotary motion of general available spool realizes the function leading control level, and realizes the opening of power stage with straight line motion.More than be the two-dimentional flow enlarger design philosophy based on spool dual free dimension, proposed when Harbin Institute of Technology does one's doctorate by Ruan Jian etc. the earliest.
Ruan Jian etc. propose a kind of position direct feedback two dimension electrohydraulic control based on this principle, intersect by a pair high low pressure hole of a pair spiral chute and spool periphery that are opened in valve pocket internal surface the flowed friction half-bridge that area forms and control the pressure of sensitive cavity, when electromechanical converter drives valve core rotation, the arcuate choke area different variation that on valve pocket, on spiral chute and spool, high low pressure hole is formed, cause spool two ends hydraulic coupling disequilibrium and move axially, spool travel feeds back to again the arcuate choke area of spiral chute and high low pressure hole formation in the process, it is finally made to trend towards gradually equal, now spool stops moving and being in new equilibrium position.The hydraulic pressure enlarged portion closed-loop feedback voluntarily of this valve can be seen, be therefore essentially the position direct feedback servovalve of two-stage.The major advantage of this valve leads control level and power stage unites two into one by originally discrete, and be integrated on single spool, not only structure is simple, dynamic response fast, and the contamination resistance of valve is greatly improved.But this valve also has problems: the spatially spiral groove structure mainly on its valve pocket generally needs the import spark-erosion machine tool of more than three axles to process, cost is higher, and work efficiency is very low, is in valve pocket internal surface due to it simultaneously, machining accuracy is difficult to ensure, also comparatively difficult during detection.
Except the direct feedback of position, conventional electrohydraulic control also has displacement-force square reaction type (generally referred to as displacement-force reaction type or force feedback type).Traditional force feedback type electrohydraulic control (as popular Nozzle flapper valve and jet action valve etc.), its spool stroke and uninterrupted and force feedback coefficient are inversely proportional to, the stroke of increase spool and flow certainly will make the bad dynamic performance of servovalve, thus most occasion at below 100L/min uses, structure is not suitable as the servovalve of large discharge, control as large discharge will be realized, then must adopt more complicated, that cost is higher three grades of valve arrangements.
Summary of the invention
In order to the valve pocket internal surface spatially spiral groove structure processing cost overcoming the direct feedback two dimension electrohydraulic control existence of existing position is high, precision is difficult to ensure, and work efficiency is low, and traditional force feedback type electrohydraulic control is difficult to the deficiency being applied to high-pressure high-flow occasion. the utility model provides the two-dimentional force feedback type electrohydraulic control that a kind of structure is simple, processing cost is low, applicable high-pressure high-flow occasion uses.
In order to the technological scheme solving the problems of the technologies described above employing is:
Based on the two-dimentional force feedback type electrohydraulic control of spool dual free dimension, it is characterized in that: comprise oblique wing formula torque motor and hydraulic pressure enlarger;
Oblique wing formula torque motor is made up of upper yoke 16, lower yoke 22, armature 19, first permanent magnet 29, second permanent magnet 30, first spring rod 17, second spring rod 31, first coil 18, second coil 21; Upper yoke 16, lower yoke 22 and armature 19 are magnet case; First permanent magnet 29, second permanent magnet 30 respectively symmetry is positioned over outside yoke and lower yoke, is used to provide polarization magnetic potential; First coil 18, second coil 21 respectively symmetry is wound in inside yoke and lower yoke, is used to provide control magnetic potential; First spring rod 17, second spring rod 31 pierces into two apertures of armature about 19 crestal surface respectively as elastic element and is connected with it, its bulb end then inserts respectively in the ball-and-socket of upper yoke 16 and lower yoke 22 movably, armature 19 directly and spool 27 be connected and be maintained at the meta of motor thus;
Armature 19 is made up of horizontally disposed central shaft and two flank faces, tilt angle is had between the pole shoe surface of two flank faces, upper yoke 16 and lower yoke 22 and horizontal plane, with perpendicular to horizontal plane, axle straight up for Z axis, left and right aerofoil is in 180 ° of array features of axle centered by Z axis, after its left-wing face rotates 180 ° around Z axis, just overlap with right flank face; The pole shoe surface, left and right of upper yoke 16 and lower yoke 22 is also 180 ° of array features in axle centered by Z axis; Left wing face is inserted between yoke 16 and the left pole shoe surface of lower yoke 22, and three is parallel to each other and forms upper left working gas gap and lower-left working gas gap; Right flank face is inserted between yoke 16 and the right pole shoe surface of lower yoke 22, and three is parallel to each other and forms upper right working gas gap and bottom right working gas gap; The height of four working gas gaps is identical;
Hydraulic pressure enlarged portion comprises spool 27, valve pocket 11, valve body 6, back shroud 1, right plug ring 25, concentric ring 13, plug 3; Spool 27 coordinates with valve pocket 11, back shroud 1 and forms left sensitive cavity h, spool 27 left end shoulder near left sensitive cavity h offers two on the surface to axisymmetric height indent a and b, valve rod also has flowing hole c and d, high-pressure trough a, flowing hole c are connected by the flow channels being opened in valve core inside with flowing hole d, and trough of low pressure b is then directly connected with return opening; Spool 27 is loaded in valve pocket 11, is sealed between valve pocket 11 and valve body 6 by O RunddichtringO; Concentric ring 13 and right plug ring 25 spool 27 be equipped with to ensure spool 27, location between valve pocket 11 and valve body 6; The internal surface of valve pocket 11 offers a pair axisymmetric straight trough and experience passage f, the one end and the sensitive cavity h that experience passage communicate, and the other end forms resistance half-bridge with height indent a and b, and resistance half-bridge is by experiencing the pressure in passage f control sensitive cavity h;
Described oblique wing formula torque motor is connected to one end of valve body 6, and the central shaft of described armature 19 and the central shaft of spool 27 are located along the same line.
The change of four working gas gap height is not only subject to the impact of armature 19 rotation, is also subject to the impact of spool 27 axial displacement simultaneously, realizes the force feedback of spool travel to torque motor with this.During no electric circuit, motor non-moment exports, and armature is positioned at meta; When coil 18,21 is energized, the mutual differential superposition under four working gas gaps of the polarization magnetic potential of permanent magnet 29,30 and the control magnetic potential of coil, thus generation electromagnetic torque band moving armature 19 rotates, until the countertorque of electromagnetic torque and spring rod 17,31 balances mutually, armature 19 stops operating, now the output torque of armature 19 is directly proportional to control electric current, regulates size of current just can control the angle of swing of armature 19.When armature 19 has axial displacement, air gap height between the pole shoe of armature 19 and upper lower yoke 16,22 changes again, make the resultant moment of force disequilibrium acted on armature 19, thus band moving armature 19 and spool 27 rotate backward, until the air gap height between the pole shoe of armature 19 and upper lower yoke 16,22 returns to initial value in moving process simultaneously.In above process, the axial displacement of spool 27 changes by the air gap of armature 19 electromagnetic torque that armature 19 is exported to change, thus realize displacement-force feedback.
Resistance half-bridge by experiencing the pressure in passage f control sensitive cavity h, and controls the pressure difference at spool two ends thus.
The beneficial effects of the utility model are mainly manifested in: 1. structure is simple, and processing cost is low.The utility model adopts and armature aerofoil and upper lower yoke pole shoe is designed to the Novel inclined wing formula torque motor of 180 ° of array features of axle centered by Z axis as electromechanical converter, while driving Spool rotating, spool travel can also be fed back in armature moment, thus form displacement-force feedback mechanism.Compare the spatially spiral groove structure of existing position direct feedback two dimension servovalve valve pocket internal surface, the structure of two-dimentional force feedback type electrohydraulic control obviously than being easier to processing, and does not need high-end process equipment, and processing cost is also lower; 2. be applicable to high-pressure high-flow to control.For traditional electrohydraulic control by elastic feedback bar realizable force feedback (such as Nozzle flapper valve and jet action valve), the rigidity increasing feedback rod can improve the natural frequency of torque motor, thus improve the dynamic characteristic of servovalve, but make the stroke of spool reduce, flow reduces; And it is constant at the flow of maintaining valve, namely when feedback factor is constant, the global stiffness of torque motor can be increased by increasing the measures such as bourdon tube rigidity, thus improve the natural frequency of torque motor, but therefore open-loop gain reduces, the flow gain of leading control level nozzle-flapper valve can be increased in theory by increasing orifice size, thus compensate the reduction of open-loop gain, but increase orifice size to increase making the leakage flow of leading control level, and the liquid flowing resistance square making to act on baffle plate increases, thus in practice and infeasible.And the force feedback type two dimension servovalve that the utility model proposes can increase stroke and the flow of spool easily by the armature and yoke inclination angle reducing oblique wing formula torque motor, the open-loop gain reduced therefrom is then by increasing the axial width (area gradient) of high low pressure rectangle groove thus increasing the flow gain of leading control level and compensated, so the decline of servovalve dynamic performance can not be caused, thus be adapted at the application of high-pressure high-flow occasion.
Accompanying drawing explanation
Fig. 1 is the structure side view of two-dimentional force feedback type electrohydraulic control.
Fig. 2 is the structure rear view of two-dimentional force feedback type electrohydraulic control.
Fig. 3 is the structural representation of oblique wing formula torque motor armature.
The structural representation that Fig. 4 (a) and 4 (b) are yoke on oblique wing formula torque motor.
The structural representation that Fig. 5 (a) and 5 (b) are oblique wing formula torque motor lower yoke.
Fig. 6 is the structural representation of oblique wing formula torque motor first spring rod; The structure of the second spring rod is identical with it.
Fig. 7 is the structural representation of two-dimentional force feedback type electro-hydraulic servo valve bush.
Fig. 8 is the structural representation of two-dimentional force feedback type electro-hydraulic servo valve core.
Fig. 9 is the structural representation of two-dimentional force feedback type electrohydraulic control.
The working principle schematic diagram that Figure 10 (a), 10 (b) and 10 (c) are two-dimentional force feedback type electrohydraulic control.
Embodiment
Below in conjunction with accompanying drawing, the utility model is further described.
With reference to Fig. 1 ~ Figure 10, a kind of two-dimentional force feedback type electrohydraulic control, comprises oblique wing formula torque motor and hydraulic pressure enlarged portion.Oblique wing formula torque motor is made up of upper yoke 16, lower yoke 22, armature 19, first permanent magnet 29, second permanent magnet 30, first spring rod 17, second spring rod 31, first coil 18, second coil 21 and set screw etc.Upper yoke 16, lower yoke 22 and armature 19 are magnet case; First permanent magnet 29, second permanent magnet 30 respectively symmetry is positioned over outside yoke and lower yoke, is used to provide polarization magnetic potential; First coil 18, second coil 21 respectively symmetry is wound in inside yoke and lower yoke, is used to provide control magnetic potential; First spring rod 17, second spring rod 31 pierces into two apertures of armature about 19 crestal surface as elastic element and is connected with it, its bulb end then inserts respectively in the ball-and-socket of upper yoke 16 and lower yoke 22 movably, armature 19 directly and spool 27 be connected and be maintained at the meta of motor thus.After whole torque motor assembling, then be affixed to one end of valve body by screw.
As shown in Fig. 3, Fig. 4 and Fig. 5.With the common torque motor being used as Nozzle flapper valve and jet action valve electromechanical converter unlike, for oblique wing formula torque motor, armature 19 is made up of horizontally disposed central shaft and two flank faces, tilt angle is had between the pole shoe surface of two flank faces, upper yoke 16 and lower yoke 22 and horizontal plane, with perpendicular to horizontal plane, axle straight up for Z axis, left and right aerofoil is in 180 ° of array features of axle centered by Z axis, after its left-wing face rotates 180 ° around Z axis, just overlap with right flank face; The pole shoe surface, left and right of upper yoke 16 and lower yoke 22 is also 180 ° of array features in axle centered by Z axis; Left wing face is inserted between yoke 16 and the left pole shoe surface of lower yoke 22, and three is parallel to each other and forms upper left working gas gap and lower-left working gas gap; Right flank face is inserted between yoke 16 and the right pole shoe surface of lower yoke 22, and three is parallel to each other and forms upper right working gas gap and bottom right working gas gap; The height of four working gas gaps is identical; The change of four working gas gap height is not only subject to the impact of armature 19 rotation, is also subject to the impact of spool 27 axial displacement simultaneously, realizes the force feedback of spool travel to torque motor with this.During no electric circuit, motor non-moment exports, and armature is positioned at meta; When coil 18,21 is energized, the mutual differential superposition under four working gas gaps of the polarization magnetic potential of permanent magnet 29,30 and the control magnetic potential of coil, thus generation electromagnetic torque band moving armature 19 rotates, until electromagnetic torque and spring rod 17,31 countertorque balance mutually, armature 19 stops operating, now the output torque of armature 19 is directly proportional to control electric current, regulates size of current just can control the angle of swing of armature 19.When armature 19 has axial displacement, air gap height between the pole shoe of armature 19 and upper lower yoke 16,22 changes again, make the resultant moment of force disequilibrium acted on armature 19, thus band moving armature 19 and spool 27 rotate backward, until the air gap height between the pole shoe of armature 19 and upper lower yoke 16,22 returns to initial value in moving process simultaneously.In above process, the axial displacement of spool 27 changes by the air gap of armature 19 electromagnetic torque that armature 19 is exported to change, thus realize displacement-force feedback.
As shown in Figure 1, Figure 2, shown in Fig. 7, Fig. 8 and Fig. 9, hydraulic pressure enlarged portion comprises spool 27, valve pocket 11, valve body 6, back shroud 1, right plug ring 25, concentric ring 13, plug 3, O RunddichtringO 4,5,7,8,9,10,12,15,26 and some screws etc.Spool 27 coordinates with valve pocket 11, back shroud 1 and forms left sensitive cavity h, spool 27 left end shoulder near left sensitive cavity h offers two on the surface to axisymmetric height indent a and b, valve rod also has flowing hole c and d, high-pressure trough a, flowing hole c are connected by the flow channels being opened in valve core inside with flowing hole d, and trough of low pressure b is then directly connected with return opening; Spool 27 is loaded in valve pocket 11, is sealed between valve pocket 11 and valve body 6 by O RunddichtringO 5,7,8,9,10; Concentric ring 13 and right plug ring 25 spool 27 be equipped with to ensure spool 27, location between valve pocket 11 and valve body 6; The internal surface of valve pocket 11 offers a pair axisymmetric straight trough and experience passage f, the one end and the sensitive cavity h that experience passage communicate, and the other end forms resistance half-bridge with height indent a and b, and resistance half-bridge is by experiencing the pressure in passage f control sensitive cavity h.
The present embodiment take valve core diameter as the two-dimentional force feedback type electrohydraulic control of the 120L/min flow of 12.5mm is example, and the utility model is described in further detail by reference to the accompanying drawings.
The working principle of two dimension force feedback type electrohydraulic control is as follows: as shown in Figure 9, when oil hydraulic pump is opened, when oblique wing formula torque motor is not energized, armature 19 is in meta under the first spring rod 17 and the second spring rod 31 support, the lower work air gap height of its two flank face is equal (to be g), the right chamber k of two dimension force feedback type electrohydraulic control is by flowing hole d, communicate with oil-feed P mouth (system pressure) through aperture c and spool 27 bar internal channel, the bearing area of right chamber k is the half of left sensitive cavity h area; The pressure of left sensitive cavity h is experienced by a pair height indent a and b be opened on spool 27 left end shoulder and a pair straight trough being opened in valve pocket 11 internal surface the flowed friction half-bridge that two crossing micro rectangle windows of passage f connect and is controlled.If do not consider the impact of frictional force and hydraulic power when static state, the pressure of left sensitive cavity h is the half of P mouth pressure (system pressure), and spool 27 axially keeps static balance, and the masked area experiencing the crossing height indent both sides of passage f with straight trough is equal.
As shown in Figure 10 (a), 10 (b) He 10 (c), when oblique wing formula torque motor energising, armature 19 drives spool 27 to do clockwise rotation (seeing from left to right), until the equilibrium position that the resisting moment of output torque and the first spring rod 17 and the second spring rod 31 is equal, as shown in Figure 10 (a); Now armature 19 lower work air gap height changes (g
1and g
2, g
1>g, g
2<g), spool trough of low pressure b and straight trough are experienced the choke area that passage f forms and are increased, high-pressure trough a with experience the choke area that passage f forms and reduce, the pressure reduction in sensitive cavity h, the axial disequilibrium of spool 27 is moved to the left; Due to the oblique wing structure of motor, spool 27 moves axially and causes the lower work air gap height of armature 19 to change once again (g
3and g
4, g
3<g
1, g
4>g
2), as shown in Figure 10 (b), now act on the resultant moment of force disequilibrium on armature 19, reverse rotation is done while armature 19 and spool 27 move axially, until two choke areas experienced between passage f with height indent are returned to equal, now armature 19 stops operating, and spool 27 stops moving axially and is in a new equilibrium position, its sensitive cavity h pressure reverts to again the half of system pressure, as shown in Figure 10 (c).In above process, the axial displacement of spool 27 changes by the air gap of armature 19 electromagnetic torque that armature 19 is exported and changes and realize displacement-force feedback, and therefore this valve is essentially the force feedback type electrohydraulic control of two-stage.
Above-mentioned embodiment is used for explaining the utility model; instead of the utility model is limited; in the protection domain of spirit of the present utility model and claim, any amendment make the utility model and change, all fall into protection domain of the present utility model.
Claims (1)
1. based on the two-dimentional force feedback type electrohydraulic control of spool dual free dimension, it is characterized in that: comprise oblique wing formula torque motor and hydraulic pressure enlarger;
Oblique wing formula torque motor is made up of upper yoke (16), lower yoke (22), armature (19), the first permanent magnet (29), the second permanent magnet (30), the first spring rod (17), the second spring rod (31), the first coil (18), the second coil (21); Upper yoke (16), lower yoke (22) and armature (19) are magnet case; First permanent magnet (29), the second permanent magnet (30) respectively symmetry are positioned over outside yoke and lower yoke, are used to provide polarization magnetic potential; First coil (18), the second coil (21) respectively symmetry are wound in inside yoke and lower yoke, are used to provide control magnetic potential; First spring rod (17), the second spring rod (31) pierce into two apertures of the upper and lower crestal surface of armature (19) respectively as elastic element and are connected with it, its bulb end then inserts respectively in the ball-and-socket of upper yoke (16) and lower yoke (22) movably, and the direct and spool (27) of armature (19) is connected and is maintained at the meta of motor thus;
Armature (19) is made up of horizontally disposed central shaft and two flank faces, tilt angle is had between the pole shoe surface of two flank faces, upper yoke (16) and lower yoke (22) and horizontal plane, with perpendicular to horizontal plane, axle straight up for Z axis, left and right aerofoil is in 180 ° of array features of axle centered by Z axis, after its left-wing face rotates 180 ° around Z axis, just overlap with right flank face; The pole shoe surface, left and right of upper yoke (16) and lower yoke (22) is also 180 ° of array features in axle centered by Z axis; Left wing face is inserted between yoke (16) and the left pole shoe surface of lower yoke (22), and three is parallel to each other and forms upper left working gas gap and lower-left working gas gap; Right flank face is inserted between yoke (16) and the right pole shoe surface of lower yoke (22), and three is parallel to each other and forms upper right working gas gap and bottom right working gas gap; The height of four working gas gaps is identical;
Hydraulic pressure enlarged portion comprises spool (27), valve pocket (11), valve body (6), back shroud (1), right plug ring (25), concentric ring (13), plug (3); Spool (27) coordinates with valve pocket (11), back shroud (1) and forms left sensitive cavity h, spool (27) left end shoulder near left sensitive cavity h offers two on the surface to axisymmetric height indent a and b, valve rod also has flowing hole c and d, high-pressure trough a, flowing hole c are connected by the flow channels being opened in valve core inside with flowing hole d, and trough of low pressure b is then directly connected with return opening; Spool (27) is loaded in valve pocket (11), is sealed between valve pocket (11) and valve body (6) by O RunddichtringO; Concentric ring (13) and right plug ring (25) spool (27) be equipped with to ensure spool (27), location between valve pocket (11) and valve body (6); The internal surface of valve pocket (11) offers a pair axisymmetric straight trough and experience passage f, the one end and the sensitive cavity h that experience passage communicate, the other end forms resistance half-bridge with height indent a and b, and resistance half-bridge is by experiencing the pressure in passage f control sensitive cavity h;
Described oblique wing formula torque motor is connected to one end of valve body (6), and the central shaft of described armature (19) and the central shaft of spool (27) are located along the same line.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201520748801.6U CN205036663U (en) | 2015-09-25 | 2015-09-25 | Two dimension force feedback formula electro hydraulic servo valve based on case two freedoms |
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| CN201520748801.6U CN205036663U (en) | 2015-09-25 | 2015-09-25 | Two dimension force feedback formula electro hydraulic servo valve based on case two freedoms |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105201945A (en) * | 2015-09-25 | 2015-12-30 | 浙江工业大学 | Two-dimensional force feedback type electro-hydraulic servo valve based on two freedom degrees of valve element |
| CN105866686A (en) * | 2016-06-01 | 2016-08-17 | 浙江工业大学 | Yoke iron actuation based oblique wing torque motor characteristic testing device |
| CN114046536A (en) * | 2021-11-01 | 2022-02-15 | 中国科学院力学研究所 | Gas atomizing nozzle with adjustable annular spray hole and gas atomizing adjusting method |
-
2015
- 2015-09-25 CN CN201520748801.6U patent/CN205036663U/en not_active Withdrawn - After Issue
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105201945A (en) * | 2015-09-25 | 2015-12-30 | 浙江工业大学 | Two-dimensional force feedback type electro-hydraulic servo valve based on two freedom degrees of valve element |
| CN105201945B (en) * | 2015-09-25 | 2017-03-22 | 浙江工业大学 | Two-dimensional force feedback type electro-hydraulic servo valve based on two freedom degrees of valve element |
| CN105866686A (en) * | 2016-06-01 | 2016-08-17 | 浙江工业大学 | Yoke iron actuation based oblique wing torque motor characteristic testing device |
| CN105866686B (en) * | 2016-06-01 | 2018-08-21 | 浙江工业大学 | Oblique wing power square motor characteristics test device based on yoke start |
| CN114046536A (en) * | 2021-11-01 | 2022-02-15 | 中国科学院力学研究所 | Gas atomizing nozzle with adjustable annular spray hole and gas atomizing adjusting method |
| CN114046536B (en) * | 2021-11-01 | 2022-11-08 | 中国科学院力学研究所 | Gas atomizing nozzle with adjustable annular spray hole and gas atomizing adjusting method |
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