A hydraulic dynamometer for aerospace power plant testing

Abstract

The utility model discloses a kind of for aerospace power machine test's hydraulic dynamometer, comprising: dynamometer, the first end and the second end of the main shaft of dynamometer are all extended from shell;The inside of main shaft is hollow structure, the inside of main shaft is coaxially arranged with exhaust pipe, and gap is left between exhaust pipe and main shaft to form interlayer lye flow channel;Two ends of exhaust pipe are respectively extended to the two ends of main shaft, and exhaust pipe seat is fixedly sleeved on the two ends of exhaust pipe, high-pressure rotary sealing mechanism is connected between each exhaust pipe seat and main shaft, and the closed chamber for being communicated with interlayer lye flow channel is formed between each exhaust pipe seat, exhaust pipe and high-pressure rotary sealing mechanism;Lye flow-through hole for communicating closed chamber and exhaust pipe inside is equipped on the first end of exhaust pipe, back pressure valve is connected to the second end of exhaust pipe, high-pressure lye inlet is arranged on the exhaust pipe seat of the second end of exhaust pipe.The invention can discharge after tail gas is neutralized with lye while dynamometer is measured.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic dynamometer technology, and in particular to a hydraulic dynamometer for testing aerospace power engines. Background Technology

[0002] In the development of aerospace engines, it is necessary to conduct simulated engine power performance tests on a test bench using a power loading device. Hydraulic dynamometers are commonly used in these tests, and some aerospace engines discharge exhaust gas directly from the power output connection, requiring pretreatment with high-pressure alkaline solution before discharge. Therefore, a hydraulic dynamometer capable of treating and discharging engine exhaust gas during dynamometer testing is needed. Utility Model Content

[0003] To address the technical problems existing in the background art, this utility model proposes a hydraulic dynamometer for testing aerospace power engines.

[0004] This utility model proposes a hydraulic dynamometer for testing aerospace power engines, comprising: a dynamometer and a support. The dynamometer includes a housing and a main shaft. The housing is oscillatingly mounted on the support. The main shaft is coaxially arranged inside the housing, with both the first and second ends of the main shaft extending out of the housing.

[0005] The spindle has a hollow interior and an exhaust pipe is coaxially arranged inside the spindle. A gap is left between the exhaust pipe and the spindle to form a sandwiched alkaline solution flow channel.

[0006] The first and second ends of the exhaust pipe extend out of the first and second ends of the main shaft respectively, and exhaust pipe seats are fixedly fitted on the first and second ends of the exhaust pipe. A high-pressure rotary sealing mechanism is connected between each exhaust pipe seat and the main shaft. Each exhaust pipe seat, exhaust pipe and high-pressure rotary sealing mechanism form a sealed chamber for communicating with the interlayer alkaline solution flow channel.

[0007] The first end of the exhaust pipe is provided with an alkaline solution flow hole for connecting the sealed chamber and the inside of the exhaust pipe. The second end of the exhaust pipe is connected to a back pressure valve. The exhaust pipe seat located at the second end of the exhaust pipe is provided with a high-pressure alkaline solution inlet for connecting the outside world and the sealed chamber.

[0008] Preferably, the high-pressure rotary sealing mechanism includes: a rotary sealing shell, a bushing, a sealing shell support bearing, a stationary ring seat, a stationary ring slide, a stationary sealing ring, and a rotating sealing ring;

[0009] The bushing is fixed at the first or second end of the main shaft. The sealing shell support bearing is sleeved and installed at the end of the bushing close to the housing, and the inner ring of the sealing shell support bearing is fixedly connected to the bushing. The rotating sealing shell is sleeved on the outside of the sealing shell support bearing, and one end of the rotating sealing shell is fixedly connected to the outer ring of the sealing shell support bearing, and the other end is fixedly connected to the exhaust pipe seat.

[0010] The sealing ring, the sealing ring, the ring slide, and the ring seat are sequentially fitted onto the bushing along the axial direction from the outer side to the inner side. The sealing ring is sealed and fixedly connected to the bushing, and a gap is left between the outer circumference of the sealing ring and the rotating sealing shell.

[0011] The stationary ring seat has an annular extension at one end located on the inner side of the axial direction. The annular extension is fixed to the rotary seal housing, and the end face and outer circumferential surface of the annular extension on the inner side of the axial direction are in sealing contact with the rotary seal housing. A gap is left between the stationary ring seat, the inner circumferential side of the annular extension, and the bushing. The stationary ring slide is slidably sealed on the outer circumferential side of the stationary ring seat along the axial direction, and a spring is connected between the stationary ring slide and the annular extension. A gap is left between the outer circumferential side of the stationary ring slide and the rotary seal housing. The sealing stationary ring is embedded and fixed on the end of the stationary ring slide near the sealing moving ring, and the sealing stationary ring abuts against the sealing moving ring in the axial direction under the action of the spring.

[0012] Preferably, the rotary sealing housing is provided with a limiting ring inside to restrict the distance the stationary ring slide moves toward the sealing moving ring.

[0013] Preferably, the bushing is provided with an anti-rotation pin to limit the rotation of the sealing ring.

[0014] Preferably, the stationary ring seat is provided with a guide post, the cross-section of which is a non-circular arbitrary geometric shape, and the stationary ring slide seat is provided with a guide groove that matches the guide post, and the guide post is slidably connected in the guide groove.

[0015] Preferably, the stationary ring slide has a plurality of first receiving grooves evenly distributed circumferentially at one end near the stationary ring seat, and each first receiving groove is provided with a spring, the two ends of the spring being fixedly connected to the bottom of the first receiving groove and the annular extension, respectively.

[0016] Preferably, it further includes: a torque measuring mechanism and a weight calibration mechanism, wherein the torque measuring mechanism is connected to the housing and is used to indirectly measure the torque of the power machine; the weight calibration mechanism is connected to the housing and is used to calibrate the accuracy of the measured torque.

[0017] Preferably, it also includes a speed measuring mechanism, which includes a speed measuring gear and a speed measuring sensor. The speed measuring gear is coaxially fixed on a bushing between a sealing shell support bearing and a stationary ring seat installed on the second end of the main shaft. The speed measuring sensor is installed on the rotating sealing shell at a position corresponding to the speed measuring gear.

[0018] The hydraulic dynamometer proposed in this invention for testing aerospace power engines can discharge exhaust gas through an exhaust pipe while measuring dynamometer power. During the discharge process, high-pressure alkali solution is introduced into the exhaust pipe through a high-pressure alkali solution inlet, a sealed chamber, a jacketed alkali solution channel, a sealed chamber, and an alkali solution flow hole. The exhaust gas and high-pressure alkali solution after neutralization reaction are then discharged through a back air valve. Attached Figure Description

[0019] Figure 1 This is a top view schematic diagram of a gate valve type hydraulic dynamometer for aerospace testing according to an embodiment of the present invention.

[0020] Figure 2 This is a side view schematic diagram of a gate valve type hydraulic dynamometer for aerospace testing according to an embodiment of the present invention.

[0021] Figure 3 This is a cross-sectional schematic diagram of a gate valve type hydraulic dynamometer for aerospace testing according to an embodiment of the present invention.

[0022] Figure 4 for Figure 3 A magnified view of a portion of the image.

[0023] Figure 5 for Figure 3 A magnified view of a portion of the image.

[0024] Figure 6 for Figure 5 A partial schematic diagram.

[0025] Figure 7 This is a schematic diagram of the structure of a gate drive assembly according to an embodiment of the present invention. Detailed Implementation

[0026] It should be noted that, where there is no conflict, the embodiments and features in the embodiments of this utility model can be combined with each other. The present utility model will now be described in detail with reference to the accompanying drawings and embodiments.

[0027] Reference Figure 1-7 The present invention proposes a hydraulic dynamometer for testing aerospace power engines, comprising: a dynamometer 1000 and a support 4000. The dynamometer 1000 includes a housing 1010 and a main shaft 1020. The housing 1010 is oscillatingly mounted on the support 4000. The main shaft 1020 is coaxially arranged inside the housing 1010, and both the first and second ends of the main shaft 1020 extend out of the housing 1010.

[0028] The main shaft 1020 has a hollow structure inside, and an exhaust pipe 1030 is coaxially arranged inside the main shaft 1020. A gap is left between the exhaust pipe 1030 and the main shaft 1020 to form a sandwich alkaline solution flow channel.

[0029] The first end and the second end of the exhaust pipe 1030 extend out of the first end and the second end of the main shaft 1020 respectively, and an exhaust pipe seat 1140 is fixedly sleeved on the first end and the second end of the exhaust pipe 1030. A high-pressure rotary sealing mechanism is connected between each exhaust pipe seat 1140 and the main shaft 1020. Each exhaust pipe seat 1140, the exhaust pipe 1030 and the high-pressure rotary sealing mechanism form a sealed chamber for communicating with the interlayer alkaline solution flow channel.

[0030] The first end of the exhaust pipe 1030 is provided with an alkaline solution flow hole 1031 for connecting the sealed chamber and the interior of the exhaust pipe 1030. The second end of the exhaust pipe 1030 is connected to a back pressure valve 1170. The exhaust pipe seat 1140 located at the second end of the exhaust pipe 1030 is provided with a high-pressure alkaline solution inlet 1141 for connecting the outside and the sealed chamber.

[0031] In practice, the high-pressure alkali solution enters from the high-pressure alkali solution inlet 1141 and flows through the alkali solution jacket channel to the other end. Then, it flows into the interior of the exhaust pipe 1030 through several alkali solution flow holes 1031 provided on the exhaust pipe 1030, and after mixing and reacting with the exhaust gas, it is discharged through the back pressure valve 1170.

[0032] This embodiment can discharge exhaust gas through the exhaust pipe while measuring dynamism. During the discharge process, high-pressure alkali solution is sent into the exhaust pipe through the high-pressure alkali solution inlet, the sealed chamber, the jacketed alkali solution channel, the sealed chamber and the alkali solution flow hole. Then, the exhaust gas and high-pressure alkali solution after neutralization reaction are discharged through the back air valve.

[0033] In this embodiment, a rotor 1040 is coaxially fixed on a main shaft 1020 located inside the housing 1010. Stator 1050 is sleeved on the main shaft 1020 located at both ends of the rotor 1040. The inner and outer circumferences of the end of each stator 1050 facing away from the rotor 1040 are sealed and fixed to the housing 1010. A first lip rotary sealing assembly 1090, a water-slinging ring 1100, and a high-speed bearing 1120 are sequentially provided on the main shaft 1020 located on both sides of the stator 1050 for sealing the main shaft 1020 and the housing 1010.

[0034] An annular water inlet cavity 1053 is formed between the middle of the end of each stator 1050 facing away from the rotor 1040 and the housing 1010. A water inlet and outlet gap is left between the two stators 1050 and the rotor 1040. A stator water inlet hole 1052 is opened on the stator 1050 to connect the annular water inlet cavity 1053 and the water inlet and outlet gap.

[0035] An annular stator-rotor working cavity is formed between the stator 1050, the rotor 1040 and the housing 1010, arranged circumferentially along the rotor 1040.

[0036] The bottom of the housing 1010 is provided with a housing water inlet hole 1011 that communicates with the annular water inlet cavity 1053, and the top of the housing 1010 is provided with a housing water outlet 1012 that communicates with the annular stator rotor working cavity.

[0037] In this embodiment, the housing water inlet 1011 is sequentially connected to a water inlet flexible pipe 1014, a flexible pipe seat, and a lower water inlet interface, and the housing water outlet 1012 is sequentially connected to an external drainage pipe 1015.

[0038] Of course, the stator and rotor working chambers are connected to the inlet and outlet water gaps.

[0039] In practical use, water flows into the stator 1050 and rotor 1040 of the dynamometer 1000 through the lower water inlet interface, and flows through the flexible tube seat, the water inlet flexible tube 1014, the housing water inlet hole 1011, and the stator water inlet hole 1052 into the water inlet and outlet gap between the stator 1050 and the rotor 1040. Under the action of the centrifugal force of the rotor 1040 rotation and the water inlet pressure, the water flows out from the housing outlet 1012 to the external drainage pipe 1015.

[0040] In one specific embodiment, the hydraulic dynamometer 1000 is mounted on the support 4000 via a swing support bearing 4020 and a swing support bearing seat 4010.

[0041] In this embodiment, an overflow cavity is provided at the corresponding position of the housing 1010 and the water-slinging ring 1100. An overflow port 1013 is provided at the bottom of the overflow cavity. A small amount of leaked water from the lip seal flows into the overflow cavity and is discharged through the overflow port 1013.

[0042] In this embodiment, the housing 1010 is formed by joining left and right housings together.

[0043] In this embodiment, the rotor 1040 has a first annular accommodating cavity at each of its two axial ends. Each first annular accommodating cavity has a plurality of first blades evenly and spaced along the circumference to divide the first annular accommodating cavity into a plurality of first grooves 1041. Each stator 1050 has a second annular accommodating cavity at one end facing the rotor 1040. The second annular accommodating cavity has a plurality of second blades evenly and spaced along the circumference to divide the second annular accommodating cavity into a plurality of second grooves 1051.

[0044] The present invention improves the water flow coupling area between the stator 1050 and the rotor 1040 by providing grooves on the stator 1050 and the rotor 1040, which is beneficial for subsequently changing the water flow coupling area between the stator 1050 and the rotor 1040 by using a gate assembly.

[0045] In a further embodiment, the first groove 1041 and the second groove 1051 have the same shape.

[0046] In this embodiment, a gate assembly is provided in the stator-rotor working cavity for changing the water flow coupling area between the two stators 1050 and the rotor 1040. A gate drive assembly is provided on the housing 1010. The gate drive assembly is connected to the gate assembly. The gate assembly is used to drive the gate drive assembly to change the water flow coupling area between the two stators 1050 and the rotor 1040.

[0047] Of course, in this embodiment, the gate drive assembly and the housing 1010 are sealed and rotated together.

[0048] In this embodiment, a torque measuring mechanism 3000 and a weight calibration mechanism 2000 are also included. The torque measuring mechanism 3000 is connected to the housing 1010 and is used to indirectly measure the torque of the power machine. The weight calibration mechanism 2000 is connected to the housing 1010 and is used to calibrate the accuracy of the measured torque.

[0049] The housing 1010 in this embodiment is also provided with a rotation speed measuring mechanism.

[0050] In practice, the power unit is connected to the main shaft 1020 through the aerospace engine output interface and coupling 1130, and transmits power to the dynamometer 1000. The speed of the power unit is measured by the speed measuring mechanism and the torque is measured by the torque measuring mechanism 3000. The power of the power unit can be calculated by multiplying the two.

[0051] In this embodiment, the gate assembly includes two gates 1080, which are symmetrically arranged in the annular stator-rotor working cavities on both sides of the main shaft 1020. Each gate 1080 is provided with an annular valve plate 1081 at the corresponding position of the inlet / outlet gap on both sides of the rotor 1040, and the axis of the annular valve plate 1081 is parallel to the axis of the rotor 1040. The two gates 1080 can move closer to each other or further away from each other in a direction perpendicular to the axial direction of the main shaft 1020, so that the annular valve plate 1081 changes the water flow coupling area between the two stators 1050 and the rotor 1040.

[0052] Specifically, the gate drive assembly is used to drive two gates 1080 to move closer or further apart from each other in order to change the water flow coupling area between the two stators 1050 and the rotor 1040.

[0053] In a further embodiment, the gate drive assembly includes a servo geared motor 1320, a motor drive synchronous pulley 1330, a transmission structure, and two ball screws 1070.

[0054] Two ball screws 1070 are symmetrically arranged in the stator and rotor working cavities at both ends of the gate assembly, and their axes are perpendicular to the axis of the main shaft 1020. The first end of each ball screw 1070 is rotatably connected to the inside of the housing 1010, and the second end of each ball screw 1070 extends through the housing 1010 to the outside of the housing 1010 and is connected to the transmission structure. The second end of each ball screw 1070 is rotatably sealed to the housing 1010.

[0055] Each ball screw 1070 is symmetrically connected with a left-hand ball nut 1270 and a right-hand ball nut 1280 on the part located in the stator rotor working cavity. The left-hand ball nut 1270 and the right-hand ball nut 1280 of the same ball screw 1070 are fixedly connected to the same end of the two gates 1080 respectively.

[0056] Furthermore, at the corresponding ends of the housing 1010 and the gate 1080, gate guide grooves are respectively formed to restrict the rotation of the gate 1080 and allow the gate 1080 to move only along the axial direction of the ball screw 1070.

[0057] The servo geared motor 1320 is mounted on the outside of the housing 1010, and the output shaft of the servo geared motor 1320 is connected to the transmission structure to drive the two ball screws 1070 to rotate synchronously in the same direction and at the same speed.

[0058] It is important to understand that the left-hand ball nut 1270 and the right-hand ball nut 1280 have opposite helical directions, but the other parameters are the same.

[0059] In this embodiment, the housing 1010 is also provided with a gate valve displacement sensor 1310 for detecting the displacement of the gate 1080.

[0060] In a further embodiment, the gate valve displacement sensor 1310 includes a magnetic ring, a magnetic ring seat, a displacement sensor, and a sensor base. The sensor base is fixed to the housing 1010, with one end extending into the housing 1010. A second receiving groove is formed on the end of the sensor base extending into the housing 1010. The sensor is installed in the second receiving groove, with its free end extending out of the second receiving groove. The magnetic ring seat and magnetic ring sleeve are disposed on the sensor, with one end of the magnetic ring seat extending out of the second receiving groove and fixedly connected to the gate 1080, and the other end fixedly connected to the magnetic ring. In this embodiment, the sensor directly senses and measures the valve position through a non-contact magnetic ring, which has higher measurement and positioning accuracy than the traditional method of using a rotary potentiometer to measure and indicate the valve position through deceleration transmission, ensuring torque control accuracy.

[0061] In this embodiment, each ball screw 1070 is connected to the housing 1010 from the inside out by a retaining ring, a bearing, a second lip sealing ring group, a sealing seat, and a sealing cover.

[0062] In this embodiment, the first end of each ball screw 1070 is rotatably connected to the housing 1010 via a bearing and is sealed by a blind cover.

[0063] In one embodiment, the transmission structure is a gear and chain transmission structure.

[0064] In another embodiment, the transmission structure is a synchronous belt drive structure.

[0065] In one specific embodiment, the synchronous belt drive structure includes a driving synchronous pulley 1330, a first synchronous belt 1350, a double driven synchronous pulley 1340, a second synchronous belt, and a driven synchronous pulley. The driving synchronous pulley 1330 is coaxially fixed on the output shaft of the servo geared motor 1320. The double driven synchronous pulley 1340 is coaxially fixed on the second end of the ball screw 1070 near the servo geared motor 1320. The driven synchronous pulley is coaxially fixed on the second end of the ball screw 1070 away from the servo geared motor 1320. One pulley of the driving synchronous pulley 1330 and the double driven synchronous pulley 1340 is connected by the first synchronous belt 1350, and the other pulley of the double driven synchronous pulley 1340 is connected by the second synchronous belt and the driven synchronous pulley.

[0066] To ensure rotation, a tensioner is also included in the synchronous belt drive structure.

[0067] In this embodiment, a housing is fitted onto the transmission structure to ensure safe rotation.

[0068] In a further embodiment, an annular groove is provided on the outer periphery of the rotor 1040 to avoid the ball screw 1070.

[0069] In practical use, when the servo reduction motor 1320 rotates, it drives the active synchronous pulley 1330 to rotate, which in turn drives the driven pulley of the double driven synchronous pulley 1340 to rotate through the first synchronous belt 1350, thereby driving the ball screw 1070, which is coaxially fixed with the double driven synchronous pulley 1340, to rotate. The rotation of the ball screw 1070 drives the right-hand ball nut 1280 and the left-hand ball nut 1270 located on it to move closer or further away from each other along its axial direction.

[0070] Meanwhile, the other driven pulley of the double driven synchronous pulley 1340 drives the driven synchronous pulley to rotate through the second synchronous belt, thereby driving the ball screw 1070, which is fixed coaxially with the driven synchronous pulley, to rotate. The rotation of the ball screw 1070 drives the right-hand ball nut 1280 and the left-hand ball nut 1270 located thereon to move closer or further apart along their axial direction.

[0071] In other words, the two ball screws 1070 rotate synchronously, in the same direction and at the same speed to drive the two gates 1080 to move along the valve plate limiting groove of the housing 1010, thereby moving closer or further away from each other, so as to change the water flow coupling area between the two stators 1050 and the rotor 1040 by opening and closing the two sets of annular valve plates 1081.

[0072] With this configuration, the two sets of annular valve plates 1081 in this embodiment are driven by two sets of high-precision, backlash-free ball screws 1070, supported by bearings, and positioned by the valve plate limiting groove in the housing 1010. This ensures high transmission rigidity and guarantees the motion accuracy of the gate assembly. The annular valve plates 1081 can move at high speed via the high-speed operation of the servo reduction motor 1320, ensuring a high-speed response for the annular valve plates 1081.

[0073] As the annular valve plates 1081 of the two gates 1080 move within the gap between the stator 1050 and rotor 1040 of the dynamometer 1000, the alignment area of ​​the grooves on the stator 1050 and rotor 1040 changes, directly affecting the effective energy absorption cross-sectional area A. The energy absorption power P of the dynamometer 1000 is related to the effective cross-sectional area A, the flow velocity v, and the pressure difference Δp. The energy absorption formula of the dynamometer 1000 is: P∝A×v×Δp.

[0074] As water flows through the grooves, it forms eddies that generate tangential forces on the rotor 1040 blades, producing torque. Under constant external water pressure and flow rate, adjusting the coupling area of ​​the grooves in the stator 1050 and rotor 1040 proportionally changes the absorbed power. External water enters the stator-rotor working chamber through the housing inlet 1011. Under the action of the inlet water pressure and the centrifugal force of the rotating rotor 1040, the water is discharged from the housing outlet 1012, carrying away the absorbed energy through the cooling water.

[0075] In this embodiment, a coupling 1130 for connecting a power source is fixedly sleeved on the first end of the spindle 1020.

[0076] Specifically, the coupling 1130 is sleeved on the outside of the exhaust pipe seat 1140 and the high-pressure rotary sealing mechanism on the first end of the exhaust pipe 1030. The exhaust pipe 1030 is connected to the exhaust port of the pneumatic motor through a bellows.

[0077] To ensure the flow of high-pressure alkaline solution, high-pressure rotary sealing mechanisms with serial numbers are installed at both ends of the shaft.

[0078] In this embodiment, the high-pressure rotary sealing mechanism includes: a rotary sealing shell, a bushing 1180, a sealing shell support bearing 1190, a stationary ring seat 1230, a stationary ring slide 1220, a sealing stationary ring 1210, and a sealing dynamic ring 1200.

[0079] The bushing 1180 is fixed to the first or second end of the main shaft 1020, and the bushing 1180 and the main shaft 1020 are sealed together; the sealing shell support bearing 1190 is sleeved and installed on the end of the bushing 1180 near the housing 1010, and the inner ring of the sealing shell support bearing 1190 is fixedly connected to the bushing 1180.

[0080] The rotary sealing housing is located on the outside of the sealing housing support bearing 1190, and one end of the rotary sealing housing is fixedly connected to the outer ring of the sealing housing support bearing 1190, and the other end is sealed and fixedly connected to the exhaust pipe seat 1140.

[0081] The sealing ring 1200, sealing ring 1210, sealing ring slide 1220 and sealing ring seat 1230 are sequentially sleeved on the bushing 1180 from the outer side to the inner side of the shaft sleeve 1180. The sealing ring 1200 is sealed and fixedly connected to the bushing 1180, and a gap is left between the outer circumference of the sealing ring 1200 and the rotating sealing shell.

[0082] The stationary ring seat 1230 has an annular extension at one end located on the inner side of the axial direction. The annular extension is fixed on the rotary seal shell, and the end face and outer circumferential surface of the annular extension on the inner side of the axial direction are in sealing contact with the rotary seal shell.

[0083] A gap is left between the stationary ring seat 1230, the inner circumferential side of the annular extension, and the bushing 1180; the stationary ring slide 1220 is slidably sealed on the outer circumferential side of the stationary ring seat 1230 along the axial direction, and a spring 1240 is connected between the stationary ring slide 1220 and the annular extension; a gap is left between the outer circumferential side of the stationary ring slide 1220 and the rotary sealing shell; the sealing stationary ring 1210 is embedded and fixed on one end of the stationary ring slide 1220 near the sealing rotating ring 1200, and the sealing stationary ring 1210 abuts against the sealing rotating ring 1200 in the axial direction under the action of the spring 1240.

[0084] In this embodiment, the inner circumferential side of the bushing 1180 is provided with at least one sealing groove, and the sealing groove is filled with a sealing ring.

[0085] In this embodiment, the high-pressure alkaline solution flows in through the interlayer flow channel of the hollow main shaft 1020 of the exhaust pipe 1030 and the dynamometer 1000. At the same time, the high-pressure alkaline solution enters both sides of the sealing moving ring 1200 and the sealing stationary ring 1210 in the high-pressure rotary sealing mechanism. The appropriate contact area is designed to ensure the contact pressure spring force of the sealing moving ring 1200 and the sealing stationary ring 1210, thereby eliminating the influence of the high-pressure alkaline solution on the sealing pair and ensuring the life of the sealing pair and the reliability of the seal.

[0086] In this embodiment, a sealing ring is provided between the outer peripheral side of the stationary ring seat 1230 and the inner peripheral side of the stationary ring slide 1220, so that the outer peripheral side of the stationary ring seat 1230 and the inner peripheral side of the stationary ring slide 1220 are in sealed contact while the stationary ring slide 1220 slides along the axial direction of the stationary ring seat 1230.

[0087] In this embodiment, the rotary sealing shell is provided with a limiting ring 1250 for limiting the distance that the stationary ring slide 1220 moves toward the sealing moving ring 1200.

[0088] In this embodiment, the sealing ring 1200 and the bushing 1180 are sealed and fixed together by a sealing ring.

[0089] In this embodiment, the bushing 1180 is provided with an anti-rotation pin 1260 for limiting the rotation of the sealing ring 1200.

[0090] In this embodiment, a guide post 1270 is provided on the stationary ring seat 1230. The cross-section of the guide post is any non-circular geometric shape. The stationary ring slide seat 1220 is provided with a guide groove that matches the guide post. The guide post 1270 is slidably connected in the guide groove.

[0091] With this configuration, this embodiment ensures that the stationary ring slide 1220 can only slide along the axial direction and cannot rotate.

[0092] In one embodiment, the stationary ring slide 1220 is provided with a plurality of first receiving grooves evenly distributed circumferentially at one end near the stationary ring seat 1230. Each first receiving groove is provided with a spring 1240. The two ends of the spring 1240 are fixedly connected to the bottom of the first receiving groove and the annular extension, respectively. The spring 1240 is used to apply a force to the stationary ring slide 1220 to move the sealing moving ring 1200 axially, so that the sealing stationary ring 1210 located on the stationary ring slide 1220 abuts against the sealing moving ring 1200.

[0093] When the high-pressure rotary sealing mechanism is installed on the second end of the main shaft 1020, a speed measuring gear 1150 is fixed on the bushing 1180 located between the sealing shell support bearing 1190 and the stationary ring seat 1230, and a speed measuring sensor 1160 is provided on the rotary sealing shell at the position corresponding to the speed measuring gear 1150.

[0094] Therefore, the speed measuring mechanism in this embodiment includes a speed measuring gear 1150 and a speed measuring sensor 1160. The speed measuring gear 1150 is coaxially fixed on a bushing 1180 between a sealing shell support bearing 1190 and a stationary ring seat 1230 installed on the second end of the main shaft 1020. The speed measuring sensor 1160 is installed on the rotating sealing shell at the position corresponding to the speed measuring gear 1150.

[0095] When the high-pressure rotary sealing mechanism is installed on the first end of the main shaft 1020, the coupling 1130 is sleeved on the exhaust pipe seat 1140 on the first end of the exhaust pipe 1030 and the outside of the high-pressure rotary sealing mechanism, and the coupling 1130 is fixedly connected to the main shaft 1020.

[0096] The above description is only a preferred embodiment of the present utility model, but the protection scope of the present utility model is not limited thereto. Any equivalent substitutions or changes made by those skilled in the art within the technical scope disclosed in the present utility model, based on the technical solution and the inventive concept of the present utility model, should be included within the protection scope of the present utility model.

Claims

1. A hydraulic dynamometer for testing aerospace power engines, characterized in that, include: The dynamometer and its support: the dynamometer includes a housing and a main shaft. The housing is oscillatingly mounted on the support. The main shaft is coaxially arranged inside the housing, with both the first and second ends of the main shaft extending out of the housing. The spindle has a hollow interior and an exhaust pipe is coaxially arranged inside the spindle. A gap is left between the exhaust pipe and the spindle to form a sandwiched alkaline solution flow channel. The first and second ends of the exhaust pipe extend out of the first and second ends of the main shaft respectively, and exhaust pipe seats are fixedly fitted on the first and second ends of the exhaust pipe. A high-pressure rotary sealing mechanism is connected between each exhaust pipe seat and the main shaft. Each exhaust pipe seat, exhaust pipe and high-pressure rotary sealing mechanism form a sealed chamber for communicating with the interlayer alkaline solution flow channel. The first end of the exhaust pipe is provided with an alkaline solution flow hole for connecting the sealed chamber and the inside of the exhaust pipe. The second end of the exhaust pipe is connected to a back pressure valve. The exhaust pipe seat located at the second end of the exhaust pipe is provided with a high-pressure alkaline solution inlet for connecting the sealed chamber.

2. The hydraulic dynamometer for testing aerospace power engines according to claim 1, characterized in that, The high-pressure rotary seal mechanism includes: a rotary seal housing, a bushing, a seal housing support bearing, a stationary ring seat, a stationary ring slide, a stationary sealing ring, and a rotating sealing ring; The bushing is fixed at the first or second end of the main shaft. The sealing shell support bearing is sleeved and installed at the end of the bushing close to the housing, and the inner ring of the sealing shell support bearing is fixedly connected to the bushing. The rotating sealing shell is sleeved on the outside of the sealing shell support bearing, and one end of the rotating sealing shell is fixedly connected to the outer ring of the sealing shell support bearing, and the other end is fixedly connected to the exhaust pipe seat. The sealing ring, the sealing ring, the ring slide, and the ring seat are sequentially fitted onto the bushing along the axial direction from the outer side to the inner side. The sealing ring is sealed and fixedly connected to the bushing, and a gap is left between the outer circumference of the sealing ring and the rotating sealing shell. The stationary ring seat has an annular extension at one end located on the inner side of the axial direction. The annular extension is fixed to the rotary seal housing, and the end face and outer circumferential surface of the annular extension on the inner side of the axial direction are in sealing contact with the rotary seal housing. A gap is left between the stationary ring seat, the inner circumferential side of the annular extension, and the bushing. The stationary ring slide is slidably sealed on the outer circumferential side of the stationary ring seat along the axial direction, and a spring is connected between the stationary ring slide and the annular extension. A gap is left between the outer circumferential side of the stationary ring slide and the rotary seal housing. The sealing stationary ring is embedded and fixed on the end of the stationary ring slide near the sealing moving ring, and the sealing stationary ring abuts against the sealing moving ring in the axial direction under the action of the spring.

3. The hydraulic dynamometer for testing aerospace power engines according to claim 2, characterized in that, The rotating sealing housing is equipped with a limiting ring inside to restrict the distance that the stationary ring slide moves toward the rotating sealing ring.

4. The hydraulic dynamometer for testing aerospace power engines according to claim 2, characterized in that, The bushing is equipped with an anti-rotation pin to limit the rotation of the sealing ring.

5. The hydraulic dynamometer for testing aerospace power engines according to claim 2, characterized in that, The stationary ring seat is equipped with a guide post, the cross-section of which is a non-circular arbitrary geometric shape. The stationary ring slide seat is provided with a guide groove that matches the guide post, and the guide post is slidably connected in the guide groove.

6. The hydraulic dynamometer for testing aerospace power engines according to claim 2, characterized in that, The stationary ring slide has multiple first receiving grooves evenly distributed circumferentially at one end near the stationary ring seat. Each first receiving groove is equipped with a spring, and the two ends of the spring are fixedly connected to the bottom of the first receiving groove and the annular extension, respectively.

7. The hydraulic dynamometer for testing aerospace power engines according to claim 1, characterized in that, Also includes: The torque measuring mechanism and the weight calibration mechanism are connected to the housing and are used to indirectly measure the torque of the power machine; the weight calibration mechanism is connected to the housing and is used to calibrate the accuracy of the measured torque.

8. The hydraulic dynamometer for testing aerospace power engines according to claim 1, characterized in that, It also includes a speed measuring mechanism, which includes a speed measuring gear and a speed measuring sensor. The speed measuring gear is coaxially fixed on the bushing between the sealing shell support bearing and the stationary ring seat installed on the second end of the main shaft. The speed measuring sensor is installed on the rotating sealing shell at the position corresponding to the speed measuring gear.

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