CN113916424B - Hydraulic dynamometer load device suitable for high-power high-rotation-speed turbine platform and method thereof - Google Patents
Hydraulic dynamometer load device suitable for high-power high-rotation-speed turbine platform and method thereof Download PDFInfo
- Publication number
- CN113916424B CN113916424B CN202111199746.6A CN202111199746A CN113916424B CN 113916424 B CN113916424 B CN 113916424B CN 202111199746 A CN202111199746 A CN 202111199746A CN 113916424 B CN113916424 B CN 113916424B
- Authority
- CN
- China
- Prior art keywords
- speed
- increasing box
- speed increasing
- torque
- dynamometer
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000000034 method Methods 0.000 title claims abstract description 15
- 238000012360 testing method Methods 0.000 claims abstract description 58
- 230000005540 biological transmission Effects 0.000 claims abstract description 33
- 230000008878 coupling Effects 0.000 claims abstract description 18
- 238000010168 coupling process Methods 0.000 claims abstract description 18
- 238000005859 coupling reaction Methods 0.000 claims abstract description 18
- 238000013461 design Methods 0.000 claims description 17
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 16
- 230000008569 process Effects 0.000 claims description 5
- 238000011056 performance test Methods 0.000 claims description 3
- 230000009471 action Effects 0.000 claims description 2
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 238000005259 measurement Methods 0.000 abstract description 3
- 238000010521 absorption reaction Methods 0.000 abstract 2
- 238000002955 isolation Methods 0.000 abstract 1
- 238000009434 installation Methods 0.000 description 9
- 238000007789 sealing Methods 0.000 description 8
- 239000003921 oil Substances 0.000 description 5
- 238000011161 development Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 3
- 230000003020 moisturizing effect Effects 0.000 description 3
- 244000126211 Hericium coralloides Species 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000011229 interlayer Substances 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 229910001339 C alloy Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 238000005255 carburizing Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000007667 floating Methods 0.000 description 1
- 239000012208 gear oil Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 230000003137 locomotive effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000010791 quenching Methods 0.000 description 1
- 230000000171 quenching effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L3/00—Measuring torque, work, mechanical power, or mechanical efficiency, in general
- G01L3/24—Devices for determining the value of power, e.g. by measuring and simultaneously multiplying the values of torque and revolutions per unit of time, by multiplying the values of tractive or propulsive force and velocity
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M15/00—Testing of engines
- G01M15/02—Details or accessories of testing apparatus
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Chemical & Material Sciences (AREA)
- Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The invention discloses a hydraulic power measuring load device and a method thereof suitable for a high-power high-rotation-speed turbine platform, wherein the hydraulic power measuring load device comprises a turbine test section, a tooth-type coupler, a torque meter, a speed increasing box, a disc coupler, a hydraulic power measuring machine and the like; the torque measuring device is used for measuring the torque of the turbine test piece; the speed increasing box is used for increasing the output rotating speed of the turbine test piece, so that the hydraulic dynamometer reaches the most suitable power absorption rotating speed range; the hydraulic dynamometer is used for power absorption and preliminary measurement of the turbine test piece; the high-speed coupler and the low-speed coupler are used for power and rotation speed transmission among all rotating parts, coaxiality compensation and vibration isolation, and all vibration transmission and coupling are avoided. The invention adopts the domestic high-power low-rotation-speed dynamometer, and matches the high rotation speed through the speed increasing box, thereby achieving the purpose of high-speed high-power rotation speed control. Meanwhile, by arranging torque and rotation speed measuring equipment at the high-speed end, the work of the turbine test piece is accurately measured.
Description
Technical Field
The invention relates to the technical field of aeroengine testing, in particular to a hydraulic dynamometer load device and a hydraulic dynamometer load method suitable for a high-power high-rotation-speed turbine platform.
Background
Aeroengines are the "heart" of an aircraft, whose performance is the core basis for the development of the aeronautical equipment industry, currently aeroengines are mainly gas turbine engines. According to the different working principles, the gas turbine engines can be further divided into vortex shafts, vortex paddles, vortex fans and vortex jet engines. The high-speed hydraulic dynamometer load device is load simulation key equipment for the performance test, the endurance test and the offline test of a turboshaft engine and a turboprop engine, and is load simulation key equipment for the performance test and the endurance test of turbine part development links of a turbofan and a turbojet engine.
The domestic hydraulic dynamometer load device has a gap between the current performance and foreign products, only a low-power low-rotation-speed hydraulic dynamometer can be produced at present, and the high-power high-rotation-speed model is also limited by people, so that the requirement of high-power high-rotation-speed experiments is met by utilizing the existing technology and products.
Application number: CN2011200178453, publication No.: CN201993192U discloses a hydraulic power measurement test device of diesel locomotive, including diesel engine, control cabinet, cardan shaft first, hydraulic torque converter, hydraulic power meter, dynamometer, cardan shaft second, moisturizing device, be connected with cardan shaft first between diesel engine and the hydraulic torque converter, be connected with cardan shaft second between hydraulic torque converter and the hydraulic power meter, the belonged hydraulic power meter passes through the arm of force and is connected with the dynamometer, moisturizing device and hydraulic power meter sealing connection, the control cabinet is connected with diesel engine, hydraulic torque converter, hydraulic power meter, dynamometer and moisturizing device electricity respectively.
Application number: CN2019107514812, publication No.: CN110529507a discloses a connection and an adjusting method of a hydraulic dynamometer and a marine diesel engine, solves the problem of difficult centering adjustment and installation of shafting of the marine diesel engine, a middle shaft and the hydraulic dynamometer, and achieves good effects of improving accuracy, being simple to operate, safe and reliable.
Application number CN2019220001240, bulletin number: CN211121713U discloses a novel high power density hydraulic dynamometer, which comprises a base, a spindle and a coupling, wherein the end part of the spindle is provided with the coupling, the spindle is arranged in a shell, the shell is provided with an oil dripping lubrication nozzle, the top is provided with a vent pipe, a stator and a rotor are arranged in the shell, the stator is fixed in the shell, a plurality of blades are arranged in the stator, the blades and the end face form 90 degrees, a plurality of water inlet holes and a plurality of vent holes are arranged on the blades, the vent holes are communicated with the vent pipe arranged on the shell, the water inlet holes are communicated with the water inlet flexible pipe arranged on the side face of the shell, the rotor is provided with a plurality of blades, and the blades and the end face form 90 degrees.
Application number CN201922000841.3, bulletin number: CN 211121714U discloses a novel high-speed hydraulic dynamometer, which comprises a machine base and a housing, wherein a weight static calibration device, a force measuring device and a speed measuring device are connected to the housing through screws, a left housing and a right housing are fixed to the housing through fixing bolts, a cavity is formed in the left housing, the right housing and the housing, the cavity is connected with a flexible water inlet and drainage pipe through a water inlet and drainage pipe bend, a main shaft is fixed to the inside of the right housing and the inside of the left housing through left and right high-speed bearings respectively, a high-speed floating carbocycle seal and a bushing composition seal pair are arranged in the left housing and the right housing respectively, and a water seal pair is arranged on the inner side of an oil-water seal ring in the left housing and the right housing.
Application number CN202021411992.4, bulletin number: CN 213543862U discloses a high-power high-speed hydraulic dynamometer, which mainly comprises a stator (stator), a rotor, a guide ring, a shell, an end cover, a water seal, an oil seal, a bearing seat support, a main shaft, a coupling, an oil pan, a water inlet valve, a drain valve, a centralized control box, a vibration monitoring system and the like. The power absorbed by the water pump is increased and decreased in proportion to the water flowing through the rotor, and the adjustment of the absorbed power is controlled by the water inlet/outlet control valve.
Application number CN202022985826.1, bulletin number: CN213600263U discloses a transmission structure of the input end of a hydraulic dynamometer, which comprises a universal transmission shaft, a bearing bracket, a diaphragm coupler, a torque rotation speed sensor, a speed increasing box and the hydraulic dynamometer; the power source is connected with the bearing frame through the universal transmission shaft, the bearing frame is connected with the torque rotating speed sensor through the diaphragm coupling, the torque rotating speed sensor is connected with the input flange of the speed increasing box through the diaphragm coupling, and the output flange of the speed increasing box is connected with the input end of the hydraulic dynamometer through the diaphragm coupling.
Although the patents relate to the hydraulic dynamometer, the application scenes and innovation points are different, and the difficult problem of dynamometer of the high-power high-rotation-speed turbine platform cannot be solved; the speed increasing requirement in a wide rotating speed range cannot be met; the centering and vibration problems cannot be solved.
Disclosure of Invention
The invention aims to provide a hydraulic dynamometer load device suitable for a high-power high-rotation-speed turbine platform, so as to solve the problems of the existing products and technologies.
In order to achieve the above object, the present invention provides the following solutions: the invention provides a hydraulic power measurement load device suitable for a high-power high-rotation-speed turbine platform, which comprises a turbine test section, a tooth-type coupler, a torque meter, a speed increasing box, a disc coupler, a hydraulic power meter and a supporting seat; the turbine test section is connected with the torque measuring device through a tooth coupling; the input shaft and the output shaft of the speed increasing box are both provided with flange structures, and the input flange is directly connected with the torque meter; the disc coupler is used for transmitting power and rotating speed between the speed increasing box and the hydraulic dynamometer; the hydraulic dynamometer, the speed increasing box and the turbine test section are arranged on the supporting seat.
Preferably, the speed increasing box and the torque measuring device are integrated, and a hanging structure is formed into a whole, so that the installation steps can be reduced, and the centering difficulty is reduced; the torque measuring device is directly hung at the input shaft end of the speed increasing box.
Preferably, the input shaft and the output shaft of the speed increasing box are horizontally arranged; the output shaft is parallel to the input shaft, horizontally eccentric and with a center distance of 355mm. The horizontal installation is for the convenience of axial installation, and does not need to change the direction of torque transmission, and according to the size of the hydraulic dynamometer, under the condition that interference of components is avoided and the occupied area is not increased as much as possible, the center distance is determined to be 355mm.
Preferably, the speed increasing box needs to bear the ultra-large torque of 3500 N.m, and three transmission shafts of the speed increasing box all adopt herringbone gears and are positioned in the middle of the transmission shafts.
Preferably, the output shaft I transmission ratio of the speed increasing box is as follows: 6.8; output shaft II transmission ratio of speed increasing box: 2.4; in order to ensure the sealing effect under high rotation speed, the speed increasing box shell adopts a sandwich structure, the joint of the sandwich structure adopts a comb tooth for sealing, and three transmission shafts of the speed increasing box all adopt a step design to ensure the positioning precision of the herringbone gear during high-speed rotation.
Preferably, the input shaft and the output shaft of the speed increasing box are both provided with flange structures, and the input flange of the input shaft of the speed increasing box is directly connected with the torque meter; the flange plate and the shaft are manufactured in an integrated design.
Preferably, the input end of the speed increasing box is connected with the turbine test section through the tooth-shaped coupling, and the output end of the speed increasing box is connected with the hydraulic dynamometer through the disc coupling;
preferably, the input shaft of the speed increasing box adopts transition fit because of good coaxiality and frequent disassembly; the hydraulic dynamometer is not required to be frequently disassembled, and torque loss is caused by relative movement, so that the two output shafts of the speed increasing box are in interference fit;
preferably, the supporting seat adopts a thermal centering bracket, is provided with a sliding rail, is convenient to move and install, and can ensure that the deviation of the rotation center of a test piece, the rotation center of a hydraulic dynamometer and the rotation center of an input shaft of a speed increasing box is not large through centering of a turbine test section and an exhaust volute centering spigot.
The invention also discloses a hydraulic dynamometer load testing method which comprises the hydraulic dynamometer load device suitable for the high-power high-rotation-speed turbine platform.
1. The problem of how to accurately calculate the power after the speed increasing box is added is solved;
2. the speed increasing requirement in a wide rotating speed range is met;
3. the speed increasing box is optimized for high torque and sealing problems of high rotating speed, a supporting seat is added, and the problems of centering and vibration are solved under the condition of high rotating speed;
4. the connection mode adopts flange connection, but adopts integrated design, does not need to carry out additional dynamic balance, and solves the centering and vibration problems at high rotating speed;
5. the invention has lower design cost and convenient installation, conveniently realizes the difficult problem of dynamometer load of the high-power high-rotation-speed turbine platform, and provides an effective means for guaranteeing the development of turbine platform tests under high working conditions.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions of the prior art, the drawings that are needed in the embodiments will be briefly described below, it being obvious that the drawings in the following description are only some embodiments of the present invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of a hydraulic dynamometer load device suitable for a high-power high-speed turbine platform according to the present invention;
FIG. 2 is a schematic diagram of a shafting layout of the present invention;
FIG. 3 is a schematic diagram of a single-input double-output structure of the speed increasing box, wherein the speed increasing box is connected with a turbine test section through a tooth coupling, a torque meter is directly hung at the input shaft end of the speed increasing box, and the output end of the speed increasing box is connected with a hydraulic dynamometer through a disc coupling;
wherein: the device comprises a 1-turbine test section, a 2-tooth coupler, a 3-torque meter, a 4-speed increasing box, a 5-disc coupler, a 6-hydraulic dynamometer and a 7-supporting seat.
Description of the embodiments
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In order that the above-recited objects, features and advantages of the present invention will become more readily apparent, a more particular description of the invention will be rendered by reference to the appended drawings and appended detailed description.
In the prior art closest to the design thought of the invention, chinese patent has the application number: CN2020229858261, publication No.: CN213600263U discloses a transmission structure of the input end of a hydraulic dynamometer, comprising a universal transmission shaft, a bearing bracket, a diaphragm coupler, a torque rotation speed sensor, a speed increasing box, the hydraulic dynamometer, a power source, a tube type cooler and a low-pressure gear oil pump; the power source is connected with the bearing frame through the universal transmission shaft, the rear end of the shaft of the bearing frame is connected with the diaphragm coupler through the double flat keys, and the diaphragm coupler is connected with the torque rotating speed sensor through the double flat keys. The torque rotation speed sensor is connected with an input flange of the speed increasing box through a diaphragm coupler, and an output flange of the speed increasing box is connected with an input end of the hydraulic dynamometer through the diaphragm coupler. The problem of how to accurately calculate the power after increasing the speed increasing box is not solved in this patent, and the speed increasing box is single-shaft, and as known from the transmission ratio calculation formula i=w1/w2=n1/n2=z2/z1=d2/d 1, when the transmission ratio is too large, the diameter of the gear with low rotation speed is multiplied, resulting in too large structural size, so that the speed increasing requirement in a wide rotation speed range cannot be met, the speed increasing box is not optimized for high torque and sealing problems with high rotation speed, and the problem of centering and vibration is difficult to solve without a supporting seat under the condition of high rotation speed. The connection is a flange connection, but is not an integrated design, and additional dynamic balancing is required, which also causes centering and vibration problems at high rotational speeds. On the basis of the prior art, the invention provides a hydraulic power measuring load device and a hydraulic power measuring load method suitable for a high-power high-rotation-speed turbine platform, and the technical scheme is shown by referring to FIG. 1, and the hydraulic power measuring load device suitable for the high-power high-rotation-speed turbine platform comprises a turbine test section 1, a tooth coupler 2, a torque meter 3, a speed increasing box 4, a disc coupler 5, a hydraulic power measuring machine 6 and a supporting seat 7; the turbine test section 1 is connected with the torque meter 3 through a tooth coupler 2; the hydraulic dynamometer 6, the speed increasing box 4 and the turbine test section 1 are arranged on the supporting seat 7; the speed increasing box 4 and the torque meter 3 are integrated and are in a hanging structure; the torque meter 3 is directly hung at the input shaft end of the speed increasing box 4; the input shaft and the output shaft of the speed increasing box 4 are both provided with flange structures, the input flange is directly connected with the torque meter 3, the disassembly is convenient, and the flange and the shaft are both manufactured in an integrated design; the disc coupling 5 is used for transmitting power and rotating speed between the speed increasing box 4 and the hydraulic dynamometer 6; the hydraulic dynamometer 6, the speed increasing box 4 and the turbine test section 1 are arranged and adjusted on the supporting seat 7; the speed increasing box 4 is in a single-input double-output structure, and the rotation speed of the highest output shaft I is: 2500r/min; highest output shaft II rotation speed: 7083r/min; the input shaft and the output shaft of the speed increasing box 4 are horizontally arranged; the output shaft is parallel to the input shaft, horizontally eccentric and with a center distance of 355mm; because the speed increasing box 4 bears the ultra-large torque of 3500 N.m, the conventional helical gear has the defect that axial force is generated, the axial force is large under the condition of heavy load, the additional axial force is unfavorable to transmission, and in order to eliminate the axial force, the speed increasing box adopts a herringbone gear; the supporting seat 7 adopts a thermal centering bracket, and through the centering of the test piece and the exhaust volute centering spigot, the rotation center of the test piece, the rotation center of the hydraulic dynamometer and the rotation center deviation of the input shaft of the speed increasing box are ensured to be not large, and when the test piece is installed, the laser centering instrument is adopted for leveling and centering operation, so that complex centering work can be completed, and the hydraulic dynamometer is an important guarantee for installation precision.
Referring to fig. 2-3, to more clearly illustrate the mounting arrangement of the present invention, the shafting arrangement on the support base 7 is: turbine test section 1- & gt tooth coupling 2- & gt torque measuring device 3- & gt speed increasing box 4- & gt disc coupling 5- & gt hydraulic power measuring machine 6. The hydraulic dynamometer 6 is of a low-speed hydraulic dynamometer type. The disc coupling 5 is used for transmitting power and rotating speed between the speed increasing box 4 and the hydraulic dynamometer 6 and compensating the different axiality between the transmission parts. The connection part has small thermal expansion and small axial compensation, so that the disc coupling 5 is adopted. The speed increasing box 4 and the torque measuring device 3 adopt an integrated design and a hanging structure. The speed increasing box 4 adopts a single-input double-output structure form. When the test piece 6000 rotates, the rotation speed of the input end (namely one end of the tested piece) of the speed increasing box 4 is 6000 revolutions at maximum, the hydraulic dynamometer is connected with the 2500-rotation output shaft, and under the condition of the rotation working condition of the hydraulic dynamometer 2500, the power measuring requirement of the existing 6000-rotation turbine test piece is met. And under the working condition of high rotation speed of the turbine test section 1, the translational hydraulic dynamometer 6 is connected to the 7083 rotary output shaft, so that the dynamometer requirement of the turbine test section 1 with 17000 revolutions can be met. Speed increasing box 4 output shaft I transmission ratio: 6.8; speed increasing box 4 output shaft II transmission ratio: 2.4. the shell of the speed increasing box 4 adopts a sandwich structure, and the transmission shaft adopts a step design so as to solve the problem of high-rotation-speed shaft oil sealing. The input shaft and the output shaft of the speed increasing box 4 are both provided with flange structures, the input flange is directly connected with the torque meter, the disassembly is convenient, and the flange and the shaft are both manufactured in an integrated design. The torque measuring device is arranged at the input shaft end of the speed increasing box so as to shorten the shaft system, provide the rigidity of the rotor by increasing the diameter of the input shaft, improve the critical rotation speed of the shaft system and avoid the dynamic risk of the rotor; meanwhile, the torque meter and the input shaft of the speed increasing box are integrally adjusted to be in dynamic balance and then mounted on the supporting seat, so that the vibration problem caused by unbalanced rotor is avoided.
In addition, since the speed increasing box bears the ultra-large torque of 3500 n.m, the conventional helical gear has a disadvantage that axial force is generated, the axial force is large under the condition of heavy load, the additional axial force is unfavorable to transmission, and the speed increasing box adopts a herringbone gear in order to eliminate the axial force. The speed increasing box has input-output 1 gear ratio of 3 (when 6000rpm is input, 2000rpm is output), the speed increasing box adopts high-quality low-carbon alloy steel 18CrNiMo7-6, adopts carburizing and quenching heat treatment, has tooth surface hardness of HRC 58-HRC 62, has tooth surface contact strength of 1500Mpa, tooth root bending strength of 550 Mpa, ensures ME level for material manufacturing level, and adopts MQ level during design. The invention fully considers the thermal deformation and the elastic deformation to shape the gear tooth profile and the spiral line. Gear machining precision GB/T10095-4 level. The gear is designed according to infinite service life (10 ten thousand hours), the safety coefficient meets SH >1.3, SF >1.6, and the speed increasing box design and inspection accords with the API 613.
Aiming at the problems of high torque and sealing at high rotating speed, and considering the centering and vibration problems at high rotating speed, the invention designs the speed increasing box for optimization, and simultaneously increases the supporting seat. The speed increasing box is of a single-input double-output structure, has the overall dimension length and width of about 1.1 x 0.4 x 0.5 m, and is provided with an input shaft and two output shafts, wherein the three shafts are horizontally arranged; parallel to each other, the horizontal installation is in order to facilitate the axial installation, and does not need to change the direction of torque transmission, so that the transmission direction can be prevented from being changed by adopting a bevel gear, and the complexity of the structure is reduced; in addition, according to the requirements of the size and the transmission ratio of the hydraulic dynamometer, under the condition that interference of components is avoided and occupied area is not increased as much as possible, two output shafts are designed to be horizontally and eccentrically placed, and the center distance is 355mm. The speed increasing box shell is integrally cast and formed, an interlayer design is adopted, a comb tooth sealing structure is adopted in the middle of the interlayer, thus the oil leakage problem during high-speed rotation can be effectively prevented, the strength of the shell is also effectively increased, and three transmission shafts of the speed increasing box are all provided with herringbone gears and are positioned at the position with the largest radius in the middle of the transmission shafts because the speed increasing box is required to bear the oversized torque of 3500 N.m. In addition, three transmission shafts of the speed increasing box are designed in a stepped mode and are stably placed in grooves of the speed increasing box, and positioning accuracy of the herringbone gears during high-speed rotation is guaranteed. The input shaft has high rotation speed, so that the diameter of the input shaft is increased, and the torque meter is directly welded and suspended at the end of the input shaft so as to shorten the shaft system, increase the rigidity of the rotor and facilitate dynamic balance and centering. Output shaft I transmission ratio of speed increasing box: 6.8; output shaft II transmission ratio of speed increasing box: 2.4; when the initial rotation speed is lower, the input shaft is meshed with the output shaft II through the herringbone gear, when the rotation speed is higher, the speed increasing box is arranged on the sliding rail of the supporting seat, the input shaft is kept motionless, and the input shaft is meshed with the output shaft I through the translation speed increasing box, so that the rotation speed of the output shaft is not too large. Because of good coaxiality and frequent disassembly, the input shaft of the speed increasing box is in transition fit with the turbine test section; the hydraulic dynamometer does not need to be frequently disassembled, and torque loss is caused by relative motion, so that the two output shafts of the speed increasing box are in interference fit with the hydraulic dynamometer.
The working principle of the device and the specific process of the working method thereof are described in detail as follows:
when the hydraulic dynamometer 6 is in operation, firstly, the hydraulic dynamometer 6 is opened, the dynamometer is ensured to be set in a rotating speed control mode, and a lower control rotating speed is preset;
the turbine test section 1 starts to rotate under the action of air flow, and the rotating speed is continuously increased until the preset control rotating speed of the hydraulic dynamometer 6 is reached, and at low rotating speed, the hydraulic dynamometer 6 starts to take over the rotating speed of the turbine test section by using the output shaft I;
under the condition that the temperature and the pressure of the air flow continuously increase, the hydraulic dynamometer 6 automatically adjusts the water loading under the rotating speed control mode, so that the rotating speed of the turbine test section 1 is kept unchanged, and the torque continuously increases;
when the torque is accumulated enough to jump to a higher rotating speed, the hydraulic dynamometer 6 is switched to a manual mode, the water quantity is rapidly released, the load is reduced, and the rotating speed of the equipment is regulated to a new set rotating speed target value; when the rotating speed exceeds 10000rpm, the speed increasing box 4 is translated, so that the hydraulic dynamometer 6 starts to take over the rotating speed of the turbine test section 1 by the output shaft II;
when setting the rotation speed target value, stable working rotation speed should be selected, and rotation speed points with large vibration are avoided. Meanwhile, the working envelope of the hydraulic dynamometer 6 is referred to, so that the test process is within the controllable capacity envelope;
and repeating the process until the turbine test section 1 reaches the rotating speed required by the test working point. Then, the torque and the rotation speed are measured by the torque meter 3;
finally, the output power of the turbine test section 1 is calculated. The formula is:
p=f·v= (T/R) · (N pi R/30) =n pi T/30, p=power unit W, t=torque unit n·m, n=rpm unit revolution/min, if the unit of P is replaced by KW, the following formula is given: p=npi T/30=tn, p=tn 3.1415926/30000
I.e. power = torque speed/9550.
The invention is improved on the basis of a low-power low-rotation-speed hydraulic dynamometer, and a speed increasing box is additionally arranged at the front part of the hydraulic dynamometer and is connected with the hydraulic dynamometer through a disc coupler; however, after the speed increasing box is additionally arranged, the power loss is difficult to accurately calculate, the hydraulic dynamometer cannot accurately measure the power of the turbine, so that the torque measuring device is additionally arranged and directly hung at the input shaft end of the speed increasing box, the torque measuring device is connected with the rotating shaft of the turbine test section through the tooth-shaped coupler, all the components are arranged on the supporting seat to ensure stable work, the rotating shaft is not eccentric, and meanwhile, the guide rail is arranged on the supporting seat to facilitate installation and movement.
The above embodiments are only illustrative of the preferred embodiments of the present invention and are not intended to limit the scope of the present invention, and various modifications and improvements made by those skilled in the art to the technical solutions of the present invention should fall within the protection scope defined by the claims of the present invention without departing from the design spirit of the present invention.
Claims (2)
1. The hydraulic dynamometer load testing method comprises a hydraulic dynamometer load device suitable for a high-power high-rotation-speed turbine platform, and the hydraulic dynamometer load device suitable for the high-power high-rotation-speed turbine platform comprises the following components: the device comprises a turbine test section (1), a tooth coupler (2), a torque meter (3), a speed increasing box (4), a disc coupler (5), a hydraulic dynamometer (6) and a supporting seat (7); the turbine test section (1) is connected with the torque meter (3) through a tooth coupler (2); the input shaft and the output shaft of the speed increasing box (4) are provided with flange structures, and the input flange is directly connected with the torque measuring device (3); the disc coupling (5) is used for transmitting power and rotating speed between the speed increasing box (4) and the hydraulic dynamometer (6); the hydraulic dynamometer (6), the speed increasing box (4) and the turbine test section are arranged on the supporting seat (7); the speed increasing box (4) and the torque measuring device (3) are integrated, and are in a hanging structure to form a whole; the torque meter (3) is directly hung at the input shaft end of the speed increasing box (4); the speed increasing box (4) is in a single-input double-output structure; the input shaft and the output shaft of the speed increasing box (4) are horizontally arranged; the output shaft is parallel to the input shaft, horizontally eccentric and with a center distance of 355mm; because the speed increasing box (4) needs to bear the ultra-large torque of 3500 N.m, the speed increasing box (4) adopts a herringbone gear; output shaft I transmission ratio of speed increasing box (4): 6.8; output shaft II transmission ratio of speed increasing box: 2.4; the speed increasing box shell adopts a sandwich structure, and a transmission shaft of the speed increasing box adopts a step design; the input shaft and the output shaft of the speed increasing box (4) are respectively provided with a flange structure, and the input flange of the input shaft of the speed increasing box is directly connected with the torque meter (3); the flange plate and the shaft are manufactured in an integrated design; the support seat (7) adopts a thermal centering bracket, is provided with a sliding rail, is convenient to move and install, and ensures that the rotation center of a test piece, the rotation center of a hydraulic dynamometer and the rotation center of an input shaft of a speed increasing box are not greatly deviated through centering of a turbine test section and an exhaust volute centering spigot;
the method is characterized in that: the method comprises the following steps:
step 1: opening a hydraulic dynamometer, ensuring that the dynamometer is set in a rotating speed control mode, and presetting a lower control rotating speed;
step 2: the turbine test section starts to rotate under the action of air flow, the rotating speed is continuously increased, and when the rotating speed reaches the preset control rotating speed of the dynamometer, the dynamometer starts to take over the rotating speed of the turbine test section by the output shaft I at the low rotating speed;
step 3: under the condition that the temperature and the pressure of the air flow continuously increase, the dynamometer automatically adjusts the water loading under the rotating speed control mode, so that the rotating speed of a test piece is kept unchanged, and the torque continuously increases;
step 4: when the torque is accumulated to a higher rotating speed enough to jump, the dynamometer is switched to a manual mode, the water quantity is rapidly released, the load is reduced, and the rotating speed of the equipment is regulated to a new set rotating speed target value; when the rotating speed exceeds 10000rpm, the speed increasing box is translated, so that the dynamometer starts to take over the rotating speed of the turbine test section by the output shaft II;
step 5: when setting a rotating speed target value, selecting a stable working rotating speed, and avoiding a rotating speed point with larger vibration; meanwhile, referring to a working envelope of the dynamometer, the test process is in a controllable capacity envelope of the dynamometer;
step 6: repeating the above process until the turbine test piece reaches the rotating speed required by the test working point; then, measuring torque and rotation speed by a torque meter;
step 7: calculating the output power of the turbine test section; the formula is:
p=f·v= (T/R) · (N pi R/30) =n pi T/30, p=power unit W, t=torque unit n·m, n=rpm unit revolution/min, if the unit of P is replaced by KW, the following formula is given: p=nρt/30=t×n, p=t×n× 3.1415926/30000, i.e. power=torque×rotational speed/9550.
2. The aeroengine performance test method is characterized by comprising the following steps of: the hydraulic dynamometer load testing method of claim 1 is applied to the aeroengine performance testing method.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111199746.6A CN113916424B (en) | 2021-10-14 | 2021-10-14 | Hydraulic dynamometer load device suitable for high-power high-rotation-speed turbine platform and method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111199746.6A CN113916424B (en) | 2021-10-14 | 2021-10-14 | Hydraulic dynamometer load device suitable for high-power high-rotation-speed turbine platform and method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113916424A CN113916424A (en) | 2022-01-11 |
| CN113916424B true CN113916424B (en) | 2024-02-09 |
Family
ID=79240443
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111199746.6A Active CN113916424B (en) | 2021-10-14 | 2021-10-14 | Hydraulic dynamometer load device suitable for high-power high-rotation-speed turbine platform and method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113916424B (en) |
Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09268926A (en) * | 1996-03-31 | 1997-10-14 | Mazda Motor Corp | Auxiliary machine mounting structure for engine |
| CN102192098A (en) * | 2010-03-19 | 2011-09-21 | 丁树才 | Efficient and low-speed wing-type vertical-shaft wind driven generator |
| CN102507166A (en) * | 2011-10-17 | 2012-06-20 | 西南石油大学 | Bilaterally-charging high-pressure dynamic-seal test bed and test method |
| KR20120126002A (en) * | 2011-05-10 | 2012-11-20 | 주수 김 | High Performance Two Way Gearless Tidal Power Plant using Synchronized Dual Drive Axles |
| CN102809485A (en) * | 2012-07-16 | 2012-12-05 | 西安交通大学 | Test bed for radial elastic foil gas bearings of integrated high-speed coupling |
| CN103487182A (en) * | 2013-09-12 | 2014-01-01 | 北京航空航天大学 | High-accuracy measuring method and device for high-speed rotor flow resistance torque |
| CN203412847U (en) * | 2013-08-19 | 2014-01-29 | 山海关船舶重工有限责任公司 | Loading device suitable for low-speed high-torque hydraulic motor testing system |
| CN204705495U (en) * | 2015-04-10 | 2015-10-14 | 徐州徐工基础工程机械有限公司 | Cantilevered rock tunnel(ling) machine overall test device |
| CN106198034A (en) * | 2016-06-27 | 2016-12-07 | 大连海事大学 | A kind of rotary punching Compressor test system |
| CN108398262A (en) * | 2018-02-08 | 2018-08-14 | 北京航空航天大学 | A kind of wet friction subband row's torque test platform and test method |
| CN208366604U (en) * | 2018-03-21 | 2019-01-11 | 苏州华业检测技术服务有限公司 | A kind of test-bed for two-output impulse generator hybrid gearbox |
| CN111521403A (en) * | 2020-05-06 | 2020-08-11 | 河南柴油机重工有限责任公司 | Automatic load regulation control method and system for cold and hot shock test of diesel engine |
| CN111609092A (en) * | 2020-06-04 | 2020-09-01 | 清研众智测试技术（天津）有限公司 | Gearbox testboard drive assembly integrated device |
| CN213600263U (en) * | 2020-12-11 | 2021-07-02 | 徐州凯尔农业装备股份有限公司 | Transmission structure of input end of hydraulic dynamometer |
-
2021
- 2021-10-14 CN CN202111199746.6A patent/CN113916424B/en active Active
Patent Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09268926A (en) * | 1996-03-31 | 1997-10-14 | Mazda Motor Corp | Auxiliary machine mounting structure for engine |
| CN102192098A (en) * | 2010-03-19 | 2011-09-21 | 丁树才 | Efficient and low-speed wing-type vertical-shaft wind driven generator |
| KR20120126002A (en) * | 2011-05-10 | 2012-11-20 | 주수 김 | High Performance Two Way Gearless Tidal Power Plant using Synchronized Dual Drive Axles |
| CN102507166A (en) * | 2011-10-17 | 2012-06-20 | 西南石油大学 | Bilaterally-charging high-pressure dynamic-seal test bed and test method |
| CN102809485A (en) * | 2012-07-16 | 2012-12-05 | 西安交通大学 | Test bed for radial elastic foil gas bearings of integrated high-speed coupling |
| CN203412847U (en) * | 2013-08-19 | 2014-01-29 | 山海关船舶重工有限责任公司 | Loading device suitable for low-speed high-torque hydraulic motor testing system |
| CN103487182A (en) * | 2013-09-12 | 2014-01-01 | 北京航空航天大学 | High-accuracy measuring method and device for high-speed rotor flow resistance torque |
| CN204705495U (en) * | 2015-04-10 | 2015-10-14 | 徐州徐工基础工程机械有限公司 | Cantilevered rock tunnel(ling) machine overall test device |
| CN106198034A (en) * | 2016-06-27 | 2016-12-07 | 大连海事大学 | A kind of rotary punching Compressor test system |
| CN108398262A (en) * | 2018-02-08 | 2018-08-14 | 北京航空航天大学 | A kind of wet friction subband row's torque test platform and test method |
| CN208366604U (en) * | 2018-03-21 | 2019-01-11 | 苏州华业检测技术服务有限公司 | A kind of test-bed for two-output impulse generator hybrid gearbox |
| CN111521403A (en) * | 2020-05-06 | 2020-08-11 | 河南柴油机重工有限责任公司 | Automatic load regulation control method and system for cold and hot shock test of diesel engine |
| CN111609092A (en) * | 2020-06-04 | 2020-09-01 | 清研众智测试技术（天津）有限公司 | Gearbox testboard drive assembly integrated device |
| CN213600263U (en) * | 2020-12-11 | 2021-07-02 | 徐州凯尔农业装备股份有限公司 | Transmission structure of input end of hydraulic dynamometer |
Non-Patent Citations (3)
| Title |
|---|
| Different Arrangements for Dual-Rotor Dual-Output Radial-Flux Motors;Yu-Han Yeh等;IEEE TRANSACTIONS ON INDUSTRY APPLICATIONS;第48卷(第2期);第612-622页 * |
| Experimental investigation of turbulent flow in a rotating straight channel with continuous ribs;Haiwang Li;Physics of Fluids;第15114-1至015114-13页 * |
| 气动活塞调节阀工作不稳定原因分析及处理;李兴平等;大氮肥;第36卷(第3期);第181-183页 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113916424A (en) | 2022-01-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Anderson et al. | An analytical method to predict efficiency of aircraft gearboxes | |
| CN108519235A (en) | Air impeller drive-type birotor testing stand | |
| CN102607846B (en) | Comprehensive test stand for water-lubricated bearings for pumps | |
| CN113310701B (en) | Complete machine tester for mechanical system of military turbofan engine | |
| JP2017120087A (en) | Method for improving performance of gas turbine engine | |
| CN109322848B (en) | Rotor assembly of gas compressor test piece and gas compressor test piece | |
| CN109612655B (en) | Inter-shaft seal dynamic test device | |
| CN110006659B (en) | Gear drive fan engine low pressure rotor system model test ware | |
| JP2019163763A (en) | Passive lubrication system for gas turbine engine gearbox during wind milling | |
| JP2014040795A (en) | Rotary machine and clearance adjustment method thereof | |
| US10677087B2 (en) | Support structure for geared turbomachine | |
| CN113916424B (en) | Hydraulic dynamometer load device suitable for high-power high-rotation-speed turbine platform and method thereof | |
| CN110132594A (en) | A kind of engine bearing friction measurement device | |
| CN113109054A (en) | Complete machine dynamics dual-rotor test bed for turboshaft engine | |
| CN110954334B (en) | Pneumatic performance test device for test piece | |
| CN110513197A (en) | A kind of aviation transmission system high speed elongated shaft auxiliary support apparatus | |
| CN110907186B (en) | Rotor vibration phase measuring and calculating method for aeroengine test bed | |
| CN110284930B (en) | Siemens 9F gas turbine combined cycle unit constant exhaust cylinder temperature clutch engagement control method | |
| JP2004162777A (en) | Fixed structure of rotary shaft part and gear | |
| RU2410662C2 (en) | Bench for running-in and test of hydraulic bottomhole motors | |
| CN211477612U (en) | Testing system for floating thrust bearing of axial flow turbine supercharger | |
| CN114878163A (en) | High-precision dynamic pressure thrust foil bearing dynamic and static synchronous loading testing device | |
| Mizutani et al. | Effects of lubrication on the performance of high speed spur gears | |
| Massini et al. | Windage losses of a meshing gear pair measured at different working conditions | |
| CN101666731B (en) | Jiggle corrosion abrasion-micro amplitude collision abrasion test machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |