A high-speed contact sealing structure for hydraulic dynamometer

Abstract

The present invention relates to the technical field of hydraulic dynamometers, and in particular to a high-speed contact sealing structure for a hydraulic dynamometer, comprising a housing and a rotating shaft of the hydraulic dynamometer, the rotating shaft being rotatably mounted on the housing, the rotating shaft being provided with a water slinger and a contact sealing assembly in sequence from the inner cavity of the housing to the outer side, the contact sealing assembly comprising a fixed sealing seat and a rotating sealing seat, the rotating sealing seat of the contact sealing assembly being connected to the water slinger by a pin, and a sealing ring being provided between the two, the contact sealing assembly being fixed to the housing via the outer ring of the fixed sealing seat, and a sealing ring being provided between the outer ring of the fixed sealing seat and the housing, a cooling water hole being provided between the fixed sealing seat and the housing, a sealed cooling water inlet channel being provided on the housing and communicating with the cooling water hole, and a radial through hole being provided on the fixed sealing seat. This sealing structure can reduce the heat generated by rotational friction through water cooling, thereby maintaining the effectiveness of the seal, meeting the sealing requirements during high-speed rotation, and preventing oil and water from mixing.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic dynamometers, and in particular to a high-speed contact sealing structure of a hydraulic dynamometer. Background Art

[0002] With the independent research and development of high-power heavy-duty gas turbines and aircraft engines, it is necessary to carry out various tests such as product performance development, calibration, matching, simulation, reliability and durability performance, and simulate the engine's power performance test on the test bench through a power loading device.

[0003] Due to the advantages of hydraulic dynamometers such as low unit cost, compact size, small inertia, fast transient response, large load absorption, and high-power operation, hydraulic dynamometers have always been important equipment for measuring and diagnosing the power performance of heavy-duty gas turbines and aircraft engines.

[0004] When the hydraulic dynamometer measures the power of the prime mover, the rotor rotates with the prime mover, stirring the water that enters the dynamometer. The water transmits the torque to the stator and housing, and drives the stator housing to rotate at a small angle relative to the dynamometer base. This movement trend of the stator and housing components is blocked by the tension and compression sensor components, and the magnitude of the tension (compression) force is measured by the tension and pressure sensors. Combined with the lever arm length and rotational speed, the power of the prime mover can be obtained.

[0005] At present, the high-speed sealing structure of traditional domestic hydraulic dynamometers will generate a lot of heat when running at high speed, which can easily lead to seal failure and serious leakage, resulting in reduced dynamometer accuracy and unable to meet the development and testing needs of high-power, high-speed, heavy-duty gas turbines and aircraft engines. Summary of the Invention

[0006] In order to solve the technical problems existing in the background technology, the present invention proposes a high-speed contact sealing structure of a hydraulic dynamometer.

[0007] The invention provides a high-speed contact sealing structure for a hydraulic dynamometer, comprising a housing and a rotating shaft of the hydraulic dynamometer. The rotating shaft is rotatably mounted on the housing, and a water slinger and a contact sealing assembly are sequentially mounted on the rotating shaft from the inner cavity of the housing to the outer side.

[0008] The contact seal assembly includes a fixed seal seat and a rotary seal seat. The rotary seal seat of the contact seal assembly is connected to the water-slinging ring by a pin shaft, and a sealing ring is provided between the two. The contact seal assembly is fixed to the housing through the outer ring of the fixed seal seat, and a sealing ring is provided between the outer ring of the fixed seal seat and the housing. A sealing sleeve and a spring seat are installed on the inner ring of the fixed seal seat. The sealing sleeve cooperates with the outer ring of the water-slinging ring. A sealing static ring is nested on the spring seat. The spring seat abuts against the end face of the rotating seal seat through the end face of the sealing static ring.

[0009] A cooling water hole is provided between the fixed sealing seat and the shell, and a sealed cooling water inlet channel is provided on the shell. The sealed cooling water inlet channel is communicated with the cooling water hole. A radial through hole is also provided on the fixed sealing seat to connect the gap between the outer ring of the rotating sealing seat and the inner ring of the fixed sealing seat with the cooling water hole.

[0010] Preferably, the sealing sleeve is fixed to the inner ring of the fixed sealing seat by bolts, and a sealing ring is provided between the sealing sleeve and the fixed sealing seat; the outer ring of the spring seat cooperates with the inner ring of the fixed sealing seat, and the inner ring of the fixed sealing seat is fixed with a retaining ring to axially position the spring seat between the retaining ring and the sealing sleeve, the outer ring of the sealing sleeve cooperates with the inner ring of the spring seat, and a sealing ring is provided between the two, the sealing sleeve is provided with a guide pin along its axial direction, and the spring seat is provided with a guide pin hole that cooperates with the guide pin, and the spring seat is provided with a mounting hole axially toward the side of the sealing sleeve, and a pressure spring is installed in the mounting hole, and the two ends of the pressure spring respectively abut against the spring seat and the sealing sleeve.

[0011] Preferably, the stator disk of the stator assembly is provided with a first air vent extending from its edge to the water inlet, and the intermediate shell is provided with a first air vent pipe, which passes from the outside of the intermediate shell into the inner cavity of the intermediate shell, and the first air vent pipe is communicated with the first air vent on the stator disk, and a first micro-vacuum balancing valve is installed at the outer end of the first air vent pipe.

[0012] Preferably, a sealing water leakage channel is provided on the shell, and the sealing water leakage channel passes through from the bottom of the shell to the outside of the fixed sealing seat.

[0013] Preferably, the material of the sealing static ring is silicon carbide.

[0014] Preferably, the surface of the rotary seal seat is provided with a sealing spray layer.

[0015] Preferably, the sealing spray layer is made of hard chrome, and the hardness of the sealing spray layer is greater than HRC55.

[0016] In the present invention, the high-speed contact sealing structure of the hydraulic dynamometer can reduce the heat generated by rotational friction through water cooling, thereby maintaining the effectiveness of the seal, meeting the sealing requirements during high-speed rotation, preventing oil and water from mixing, and promptly detecting leakage when the seal fails. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 A schematic structural diagram of a perforated disc hydraulic dynamometer proposed in an embodiment;

[0018] Figure 2 for Figure 1 A schematic diagram of a right side view of a hole-disc hydraulic dynamometer;

[0019] Figure 3 for Figure 1A left side schematic diagram of a hole-disc hydraulic dynamometer;

[0020] Figure 4 is a cross-sectional view of the housing assembly, stator assembly, and rotor assembly in the embodiment;

[0021] Figure 5 is a side view schematic diagram of the housing assembly in the embodiment;

[0022] Figure 6 Schematic diagram of the structure of the stator assembly and the rotor assembly in the embodiment;

[0023] Figure 7 is a perspective view of a stator disc in an embodiment from a front perspective;

[0024] Figure 8 is a cross-sectional view of a stator disc in an embodiment;

[0025] Figure 9 is a rear view of the stator disc in the embodiment;

[0026] Figure 10 Schematic diagram of the structure of the rotating shaft in the embodiment;

[0027] Figure 11 for Figure 10 Side view of the rotating shaft;

[0028] Figure 12 Schematic diagram of the structure of the spacer ring in the embodiment;

[0029] Figure 13 Schematic diagram of the structure of the rotor plate in the embodiment;

[0030] Figure 14 for Figure 13 Cross-sectional view of the middle rotor plate;

[0031] Figure 15 is a schematic diagram of a high-speed contact sealing structure in an embodiment;

[0032] Figure 16 is a schematic diagram of a high-speed bearing lubrication and sealing structure in an embodiment;

[0033] Figure 17 This is a structural schematic diagram of the force-measuring arm assembly and the preload arm assembly of the calibration device in the embodiment being installed on a dynamometer;

[0034] Figure 18 for Figure 17 Schematic diagram of the structure of the preload arm assembly of the calibration device;

[0035] Figure 19 Schematic diagram of the structure of the force measuring arm assembly and the calibration arm assembly of the calibration device in the embodiment installed on the dynamometer;

[0036] Figure 20 for Figure 17 A schematic diagram of the structure of the calibration arm assembly of the calibration device;

[0037] Figure 21 A schematic front view of a multi-stage series hydraulic dynamometer proposed in an embodiment;

[0038] Figure 22 for Figure 21 A side view schematic diagram of a multi-stage series hydraulic dynamometer;

[0039] Figure 23 for Figure 21 Schematic diagram of a top view of a multi-stage series hydraulic dynamometer. DETAILED DESCRIPTION

[0040] Please refer to Figure 1-23 As shown, a perforated disc hydraulic dynamometer according to an embodiment of the present invention includes a support assembly 100, a housing assembly 200, a stator assembly 300, a rotor assembly 400, a water inlet valve assembly 500, a water outlet valve assembly 600, a calibration device 700, and a speed measuring device 800. Among them:

[0041] The shell assembly 200 is installed on the support assembly 100, and the shell assembly 200 can swing around the horizontal axis on the support assembly 100; the stator assembly 300 and the rotor assembly 400 are installed inside the shell assembly 200, and both ends of the rotating shaft 410 of the rotor assembly 400 pass through the shell assembly 200 along the swing axis of the shell assembly 200, and a high-speed contact sealing structure and a high-speed bearing lubrication sealing structure are also provided between the rotating shaft 410 of the rotor assembly 400 and the shell assembly 200; a water inlet 211 and a water outlet 212 are provided on the shell assembly 200, the water inlet valve assembly 500 is connected to the water inlet 211, and the drain valve assembly 600 is connected to the water outlet 212; the calibration device 700 is installed on the support assembly 100 and connected to both sides of the shell assembly 200 for measuring the torque of the shell assembly 200; the speed measuring device 800 is used to detect the speed of the rotor assembly 400.

[0042] The hydraulic dynamometer operates as follows: the rotating shaft 410 of the rotor assembly 400 is connected to the engine under test. When the engine starts, the rotor assembly 400 rotates, and water flows into the inner cavity of the housing assembly 200 through the water inlet 211. The rotor assembly 400 drives the water toward the inner wall of the housing assembly 200 under the action of centrifugal force, causing the housing assembly 200 to oscillate under the impact of the water. As the water impacts the inner wall of the housing assembly, the frictional resistance of the inner wall reduces its speed, expending kinetic energy and converting the absorbed mechanical energy into heat energy, ultimately increasing the water temperature. Due to the friction between the water and the inner wall, the swing speed of the shell assembly 200 is slower than the rotation speed of the rotor assembly 400. Therefore, the water will prevent the rotation of the rotor assembly 400 and generate a resistance torque. This resistance torque acts directly on the engine through the rotor assembly 400, forming an engine load, or in other words, the water absorbs the engine power. This load can be controlled by adjusting the water inlet and outlet. Therefore, the output torque or driving torque of the engine can be measured by the hydraulic dynamometer, and the output power or driving power of the engine can be calculated in combination with the measured rotational speed of the rotor assembly 400.

[0043] Reference Figure 1-18 The following content will provide a more detailed description of the hole-disc hydraulic dynamometer.

[0044] The support assembly 100 includes a support seat 110, a bearing seat 120 and a bracket 130. The two bearing seats 120 are fixed symmetrically on the support seat 110. The two bearing seats 120 are used to install and support the shell assembly 200. The bracket 130 is fixed on the support seat 110 for installing and supporting the water inlet valve assembly 500.

[0045] The housing assembly 200 includes a center housing 210 and two side housings 220. The side housings 220 are threadedly connected to the center housing 210 via screws. Specifically, through-holes are circumferentially provided in the center housing 210 and the side housings 220. Locking rods 240 extend through these holes, and locking nuts 250 are threadedly connected to the ends of the locking rods 240 to secure the side housings 220 to the center housing 210. A bearing housing 230 is also fixed to the outer end of each side housing 220 of the housing assembly 200. Specifically, the bearing housing 230 abuts against the outer port of the side housing 220 and the two are threadedly connected via screws. A sealing ring 231 is also provided between the bearing housing 230 and the outer port of the side housing 220. The housing assembly 200 is structurally designed to facilitate disassembly and assembly through threaded connections. During installation, the two bearing housings 230 are mounted on the two bearing seats 120 of the support assembly 100 via swing bearings 260, thereby rotatably mounting the housing assembly 200 on the support assembly 100. Swing bearing inner ring covers 270 are also fixedly mounted on the two bearing housings 230, while swing bearing outer ring covers 280 are fixedly mounted on the two bearing seats 120. These inner and outer ring covers 270 and 280 cooperate to protect the swing bearings 260.

[0046] The stator assembly 300 is installed within the inner cavity of the intermediate housing 210 of the housing assembly 200. The stator assembly 300 includes a stator disc 310 and a drain guide ring 320, which are arranged in series at intervals. Both the stator disc 310 and the drain guide ring 320 mate with the inner cavity of the intermediate housing 210. The stator disc 310, drain guide ring 320, and intermediate housing 210 are positioned by a keyway 311 and a key 330. The series connection of the stator disc 310 and drain guide ring 320 facilitates assembly and disassembly. The stator disc 310 has a water inlet 312 inside it, which communicates with the water inlet 211 at the top of the intermediate housing 210. A central through-hole 313, extending through the water inlet 312, is located at the center of the stator disc 310. Stator power absorption holes 314 are located on both end surfaces of the stator disc 310, distributed in a circular array along the circumference of the stator disc 310. The water inlet 312 of the stator disc 310 communicates with the inner cavity of the drainage guide ring 320 through the central through-hole 313. The inner cavity of the drainage guide ring 320, located between the two stator discs 310, forms a drainage channel 321. Drain holes 322, which communicate with the drainage channel 321, are located on both sides of the bottom of the drainage guide ring 320.

[0047] The rotor assembly 400 includes a rotating shaft 410, a rotor plate 420 and a spacer ring 430. The rotating shaft 410 has a non-circular triangular cam segment 411 for mounting the rotor plate 420 and the spacer ring 430. The rotor plate 420 is provided with a non-circular triangular center hole 421, and the spacer ring 430 is also provided with a non-circular triangular center hole 431. The rotor plate 420 and the spacer ring 430 are arranged in an interval and connected in series on the non-circular triangular cam segment 411 of the rotating shaft 410, and the two ends of the series connection are positioned on the rotating shaft 410 by a locking ring. The non-circular triangular cam segment 411 of the rotating shaft 410 has greater torsional strength and stiffness, so that the rotor assembly 400 can meet the testing requirements of high-torque engines. The rotor plates 420 are provided with rotor power absorption holes 422, which are distributed in a circular array along the circumference of the rotor plates 420. After the rotor assembly 400 is installed in the inner cavity of the intermediate housing 210, each rotor plate 420 is installed one-to-one within each drainage channel 321, and the spacer ring 430 is located within the central through-hole 313 of the stator disk 310. During operation, the rotor plates 420 stir the water in the drainage channel 321 through the rotor power absorption holes 422, causing the water to absorb the work of the engine. The rotor assembly 400 is designed with the rotor plates 420 and spacer rings 430 connected in series on the rotating shaft 410, which facilitates assembly and disassembly. Each rotor plate 420 is individually located in each drainage channel 321, which has the advantages of low power absorption density per rotor plate 420, strong cavitation resistance, and low high-speed centrifugal stress.

[0048] The non-circular triangular cam segment 411 of the rotating shaft 410 has cylindrical segments 412 at both ends. A high-speed contact seal structure and a high-speed bearing lubrication seal structure can be installed between the cylindrical segment 412 and the housing assembly 200, thereby meeting the lubrication and high-speed sealing requirements of the high-speed bearing 1200. The rotating shaft 410 also has splines 413 at both ends. The splines 413 are used to fit the rotating shaft 410 with a coupling 440. The outer end of the spline 413 has a threaded hole. The coupling 440 is threadedly connected to the threaded hole of the spline 413 and locked to the end of the rotating shaft 410 via a threaded member. The coupling 440 can be used to connect the rotating shafts 410 of two or more perforated disc hydraulic dynamometers in series, thereby forming a multi-stage series hydraulic dynamometer.

[0049] In this embodiment, the stator disk 310 of the stator assembly 300 is further provided with a first vent hole 315 extending from its edge to the water inlet 312. A first vent pipe 213 is provided on the intermediate housing 210 of the housing assembly 200. The first vent pipe 213 extends from the exterior of the intermediate housing 210 into the interior of the intermediate housing 210 and communicates with the first vent hole 315 on the stator disk 310. A first micro-vacuum balancing valve 214 is mounted on the outer end of the first vent pipe 213. The first vent hole 315, first vent pipe 213, and first micro-vacuum balancing valve 214 allow the water inlet 312 to communicate with the external airflow, achieving internal and external air pressure balance, thereby eliminating bubbles generated in the water inlet 312 during operation. The stator disc 310 is also provided with a second vent hole 316 extending from its edge to both axial ends. A second vent pipe 215 is provided on the side housing 220 of the housing assembly 200. This second vent pipe 215 extends from the exterior of the side housing 220 into the interior of the intermediate housing 210. The inner end of the second vent pipe 215 communicates with the second vent hole 316, and a second micro-vacuum balancing valve 216 is mounted on the outer end of the second vent pipe 215. Through the second vent hole 316, the second vent pipe 215, and the second micro-vacuum balancing valve 216, the drain channel 321 is connected to the external airflow, achieving internal and external pressure balance, thereby eliminating bubbles generated in the drain channel 321 during operation. This elimination of bubbles in the water inlet channel 312 and drain channel 321 effectively reduces or prevents cavitation on the surfaces of the stator disc 310 and rotor plate 420, improving the cavitation resistance and service life of the orifice-disc hydraulic dynamometer. In this example, a cavitation detection rod 221 is installed on each of the two side shells 220 of the shell assembly 200. The inner ends of the two cavitation detection rods 221 are respectively located at the two ends of the stator assembly 300, and can monitor the cavitation phenomenon on the stator disk 310.

[0050] Reference Figure 4 and Figure 15The high-speed contact sealing structure provided on the rotating shaft 410 includes a contact sealing assembly 900 and a water slinger 1000, wherein the contact sealing assembly 900 includes a fixed sealing seat 910, a sealing sleeve 920, a spring seat 930, a retaining ring 914 and a rotating sealing seat 940. The fixed sealing seat 910 is fixed to the side housing 220 by screws 911. A cooling water hole 912 is provided between the outer ring of the fixed sealing seat 910 and the side housing 220. A sealing ring 913 is provided between the outer ring of the fixed sealing seat 910 and the side housing 220. The sealing sleeve 920 is fixed to the fixed sealing seat 910 by bolts 921. The inner ring of the sealing seat 910, a sealing ring 915 is provided between the sealing sleeve 920 and the fixed sealing seat 910; the outer ring of the spring seat 930 cooperates with the inner ring of the fixed sealing seat 910, and the inner ring of the fixed sealing seat 910 is fixed with a retaining ring 914 to axially position the spring seat 930 between the retaining ring 914 and the sealing sleeve 920. The outer ring of the sealing sleeve 920 cooperates with the inner ring of the spring seat 930 and a sealing ring 922 is provided between the two. The sealing sleeve 920 is provided with a guide pin 923 along its axial direction, and the spring seat 930 is provided with a guide pin hole 931 that cooperates with the guide pin 923. A mounting hole is axially provided on one side of 930 facing the sealing sleeve 920, and a pressure spring 932 is installed in the mounting hole. The two ends of the pressure spring 932 are respectively against the spring seat 930 and the sealing sleeve 920. A sealing static ring 933 is nested on the other side of the spring seat 930. The material of the sealing static ring 900 is silicon carbide, which has wear-resistant and high-temperature resistant properties to ensure a good sealing effect; the rotating sealing seat 940 and the water-slinging ring 1000 are sequentially mounted on the rotating shaft 410 from the inside to the outside, and the rotating sealing seat 940 and the water-slinging ring 1000 are axially positioned by cooperating with the pin shaft 941 and the hole, and the two A sealing ring 942 is provided in between, the sealing sleeve 920 is located on the outer ring of the water-throwing ring 1000, the end face of the rotating sealing seat 940 abuts against the end face of the sealing static ring 933 on the spring seat 930, and the fixed sealing seat 910 is also provided with radial through holes 915 distributed along its circumference. The radial through holes 915 connect the gap between the outer ring of the rotating sealing seat 940 and the inner ring of the fixed sealing seat 910 with the cooling water hole 912. The surface of the rotating sealing seat 940 is provided with a sealing spray layer, and the material of the sealing spray layer is hard chromium. The hardness of the sealing spray layer is greater than HRC55, and it has the advantages of wear resistance and high temperature resistance.

[0051] To address this high-speed contact seal structure, the side housing 220 is further provided with a sealed cooling water inlet channel 222 and a sealed water leakage channel 223. Specifically, the sealed cooling water inlet channel 222 extends from the upper portion of the side housing 220 to the cooling water hole 912 on the outer ring of the fixed seal seat 910, while the sealed water leakage channel 223 extends from the bottom of the side housing 220 to the outer side of the fixed seal seat 910. The sealed cooling water inlet channel 222 can be connected to a cooling water circulation system to circulate cold water into the cooling water hole 912 to cool the high-speed contact seal structure. The operating principle is that cold water first enters the cooling water hole 912 through the sealed cooling water inlet channel 222, then enters the outer ring of the sealing stationary ring 933 and the rotating seal seat 940 through radial through-holes 915 for radial cooling. The cooled water then flows axially along the rotating shaft 410 into the inner cavity of the rotor assembly 400, and is ultimately discharged through the water outlet 212 of the housing assembly 200. Furthermore, if the high-speed contact seal fails, water in the inner cavity of the intermediate housing 210 will flow outside the fixed seal seat 910. The water slinger 1000 will sling the cooling water in all directions and into the sealing water leakage channel 223. Therefore, this high-speed contact seal design can meet the sealing requirements during high-speed rotation, prevent oil and water crosstalk, reduce frictional heat through water cooling, and promptly detect leaks in the event of a seal failure.

[0052] Reference Figure 4 and Figure 16 The high-speed bearing lubrication seal structure on the rotating shaft 410 includes an inner lubricating oil seal 1100, a high-speed bearing 1200, and an outer lubricating oil seal 1300, which are sequentially installed between the two cylindrical sections 412 and the two bearing housings 230 from the inside to the outside. The inner lubricating oil seal 1100 includes an inner oil seal comb seal seat 1110 and an inner oil slinger 1120. The inner oil slinger 1120 is sleeved on the cylindrical section 412 of the rotating shaft 410. The inner oil seal comb seal seat 1110 is fixed to the side housing 220 by bolts. The inner ring of the inner oil seal comb seal seat and the outer ring of the inner oil slinger 1120 are tightly matched. The inner ring of the high-speed bearing 1200 is fixed to the cylindrical section 412 of the rotating shaft 410. The outer ring of the high-speed bearing 1200 is fixed on the bearing housing 230; the lubricating oil outer seal 1300 includes an outer seal oil comb seal seat 1310 and an outer oil ring 1320, the outer oil ring 1320 is sleeved on the cylindrical section 412 of the rotating shaft 410, the outer seal oil comb seal seat 1310 is fixed to the bearing housing 230 through a positioning retaining ring, and the inner ring 1310 of the outer seal oil comb seal seat is tightly matched with the outer ring of the outer oil ring 1320.

[0053] For this high-speed bearing lubrication and seal structure, an oil injection pipe 232 is installed on the bearing housing 230. This pipe extends from the outside of the bearing housing 230 to between the outer lubricating oil seal 1300 and the high-speed bearing 1200. An oil sump 224 is installed on the side housing 220, located outside the inner lubricating oil seal 1100. The bearing housing 230 is provided with an oil return hole 233, which connects the oil sump 224 to the inside of the outer lubricating oil seal 1300. The bearing housing 230 is also provided with a lubrication vacuum return oil passage 225, which communicates with the oil sump 224. A bearing temperature sensor 234 is also installed on the bearing housing 230. This sensor extends from the outside of the bearing housing 230 to the outer ring of the high-speed bearing 1200 to measure the temperature of the high-speed bearing 1200. During operation, the oil injection pipe 232 and the lubricating vacuum suction return oil channel 225 are connected to the lubricating oil circulation system. Lubricating oil can be injected into the high-speed bearing 1200 through the oil injection pipe 232, and the lubricating oil can be discharged through the lubricating vacuum suction return oil channel 225. When the bearing temperature sensor 234 detects that the temperature of the high-speed bearing 1200 is too high, an alarm can be issued to the operator to remind inspection.

[0054] The perforated disc hydraulic dynamometer is also equipped with a safety monitoring device 1400 for monitoring the high-speed contact seal structure and high-speed bearing lubrication seal structure on the rotor assembly 400. Specifically, the safety monitoring device 1400 includes a pipeline interface module 1410, a pressure sensor 1420, a temperature sensor 1430, and a data acquisition control box 1440. The pipeline interface module 1410 is equipped with a lubrication oil supply interface 1411, a lubrication oil return interface 1412, a seal cooling water supply interface 1413, and a seal cooling water return interface 1414. The lubrication oil supply interface 1411 is connected to the oil injection pipe 232 via a pipeline. The lubrication oil return interface 1412 is connected to the lubrication vacuum suction return oil channel 225 via a pipeline. The seal cooling water supply interface 1413 is connected to the seal cooling water inlet channel 222 via a pipeline. The seal cooling water return interface 1414 is connected to the seal water leakage channel 223 via a pipeline. The lubricating oil return interface 1412 is installed with a temperature sensor 1430. The lubricating oil supply interface 1411, the lubricating oil return interface 1412, and the sealing cooling water supply interface 1413 are respectively connected to a pressure sensor 1420 through a pressure measuring hose 1450, and the pressure sensor 1420 is integrated and installed on the integrated mounting block 1460. The temperature sensor 1430 and each pressure sensor 1420 are respectively connected to the acquisition control box 1440, and the collected temperature and pressure signals are sent to the acquisition control box 1440, which can detect the temperature and pressure of the lubricating oil, as well as the pressure of the sealing cooling water. According to the temperature of the lubricating oil, it can be determined whether the temperature of the high-speed bearing 1200 is too high. According to the pressure of the lubricating oil and the sealing cooling water, it can be monitored whether the supply pressure of the lubricating oil and the sealing cooling water exceeds the set range and an alarm is issued to prevent the high-speed contact sealing structure and the high-speed bearing lubrication sealing structure from malfunctioning due to lack of water and oil.

[0055] like Figure 1 As shown, the water inlet valve assembly 500 includes an electro-hydraulic servo-controlled butterfly valve 510 and a water inlet flexible pipe 520. The electro-hydraulic servo-controlled butterfly valve 510 is fixedly mounted on the bracket 130 of the support assembly 100 via a first mounting flange 530. The water inlet flexible pipe is connected between the electro-hydraulic servo-controlled butterfly valve 510 and the water inlet 211 of the intermediate housing 210. O-rings are provided at both ends of the water inlet flexible pipe 520 to ensure the sealing of the water inlet flexible pipe 520. The electro-hydraulic servo-controlled butterfly valve 510 has the advantages of low inertia, high driving torque, fast response speed, and remote control capability.

[0056] The drain valve assembly 600 includes an electro-hydraulic servo-controlled sleeve-type regulating valve 610, a flexible drain pipe 620, and a drain elbow 630. The electro-hydraulic servo-controlled sleeve-type regulating valve 610 is fixedly mounted to the support base 110 of the support assembly 100 via a second mounting flange 640. The flexible drain pipe 620 is connected to the water outlet 212 of the intermediate housing 210, and the drain elbow 630 is connected between the flexible pipe and the electro-hydraulic servo-controlled sleeve-type regulating valve 610. To ensure a tight connection, O-rings are installed at both ends of the flexible drain pipe 620 and the drain elbow 630. Using an electro-hydraulic servo system to control the sleeve-type regulating valve offers the advantages of high output torque, fast response speed, linear valve plate opening, and a wide adjustment range.

[0057] Reference Figure 17-20 The calibration device 700 includes a force-measuring arm assembly 710, a calibration arm assembly 730, and a pre-tensioning arm assembly 720. The force-measuring arm assembly 710 is mounted on one side of the housing assembly 200, while the calibration arm assembly 730 and the pre-tensioning arm assembly 720 are mounted on the other side of the housing assembly 200. The force-measuring arm assembly 710 is provided with a tension and pressure sensor 712 for measuring the torque applied to the housing assembly 200. The calibration arm assembly 730 includes a force sensor 731 and an energy storage and force adjustment member, which can adjust the static calibration tension or pressure applied by the calibration arm assembly 730 to the housing assembly 200. The pre-tensioning arm assembly 720 includes an elastic energy storage member and a length adjustment member. By adjusting the length of the length adjustment member, the elastic energy storage member can apply a pre-tensioning force to the housing assembly 200.

[0058] Specifically, the force arm assembly 710 includes a brake arm 711, a tension and pressure sensor 712, an upper connecting screw 713, and a lower connecting screw 714. The brake arm 711 is fixed on the outer wall of the intermediate shell 210. The upper end of the tension and pressure sensor 712 is connected to the upper joint bearing 715 through the upper connecting screw 713. The upper joint bearing 715 is hinged to one end of the brake arm 711. The lower end of the tension and pressure sensor 712 is connected to the lower joint bearing 716 through the lower connecting screw 714. The lower joint bearing 716 is hinged to the support seat 110.

[0059] The energy storage and force adjustment parts of the calibration arm assembly 730 include a calibration arm rod 732, a force transmission rod 733, an upper adjustment nut 734, an upper butterfly spring group 735, a lower adjustment nut 736, and a lower butterfly spring group 737. The calibration arm rod 732 is fixedly connected to the outer wall of the intermediate housing 210, the force transmission rod 733 moves along the vertical direction and penetrates the calibration arm rod 732, the upper adjustment nut 734 is threadedly connected to the upper end of the force transmission rod 733, and the upper butterfly spring group 735 is fixedly connected to the outer wall of the intermediate housing 210. It is mounted on the force transmission rod 733 and located between the upper adjusting nut 734 and the calibration arm 732. The lower adjusting nut 736 is threadedly connected to the lower end of the force transmission rod 733. The lower butterfly spring group 737 is mounted on the force transmission rod 733 and located between the lower adjusting nut 736 and the calibration arm 732. The lower end of the force transmission rod 733 is fixedly connected to the force sensor 731, and the force sensor 731 is hinged to the support seat 110 through the joint bearing 738.

[0060] The length adjustment part of the pre-tensioning arm assembly 720 includes a mounting plate 721, a load-bearing plate 722, a guide seat 723, and a guide rod 724. The elastic energy storage part is a tension spring 725. The mounting plate 721 is fixed on the outer wall of the intermediate shell 210. The load-bearing plate 722 and the guide seat 723 are fixed on the mounting plate 721 from top to bottom. The guide rod 724 is slidably installed on the guide seat 723. The upper end of the guide rod 724 is fixedly connected to a force adjusting bolt. The upper end of the force adjusting bolt passes through the load-bearing plate 722 and is threadedly connected to an adjusting nut 726. The two ends of the tension spring 725 are connected between the lower end of the guide rod 724 and the support seat 110 through hooks.

[0061] The operating principle of calibration device 700 is as follows: preload arm assembly 720 serves as an auxiliary device to improve the calibration accuracy of calibration device 700. During installation, force measuring arm assembly 710 and preload arm assembly 720 are first installed, followed by calibration arm assembly 730. After force measuring arm assembly 710 and preload arm assembly 720 are installed, the movement of guide rod 724 on guide seat 723 can be adjusted by turning adjustment nut 726, thereby adjusting the tightness of tension spring 725 to achieve the purpose of adjusting the preload tension of tension spring 725. The damping produced by the installation of force measuring arm assembly 710 on housing assembly 200 can also be adjusted, thereby ensuring the accuracy of subsequent calibration. During the calibration process, by turning the upper adjusting nut 734 or the lower adjusting nut 736 on the calibration arm assembly 730, the butterfly spring can apply static calibration pressure or tension to the force transmission rod 733. The magnitude of the static calibration force can be displayed by the force sensor 731. The static calibration force is compared with the value displayed by the tension and pressure sensor 712 on the force arm assembly 710. After measuring several sets of data, the tension and pressure sensor 712 can be calibrated through the calibration program.

[0062] The calibration device 700 can calibrate a wide torque range and can meet the testing requirements of high-power, high-speed rotating machinery. It can achieve stepless adjustment of the static calibration force through the upper and lower adjustment nuts and butterfly springs of the calibration arm assembly 730. It has a large adjustment range, easy operation, high fine-tuning sensitivity and accuracy, and is more conducive to large torque calibration.

[0063] The speed measuring device 800 includes a speed sensor 810, a speed sensor seat 820, and a speed measuring gear 830. Figure 4 As shown, a speed sensor 810 is fixedly mounted on the swing bearing inner ring cover 270 via a speed sensor mount 820. A speed gear 830 is coaxially mounted on the coupling 440 of the rotating shaft 410. The speed sensor 810 is located on one side of the speed gear 830 in the circumferential direction. During operation, the speed gear 830 rotates with the rotating shaft 410. The speed sensor 810 measures the speed of the speed gear 830, which is the speed of the rotating shaft 410.

[0064] Reference Figure 19-21 Based on the aforementioned orifice-disc hydraulic dynamometer, embodiments of the present invention further provide a multi-stage tandem hydraulic dynamometer, comprising at least two orifice-disc hydraulic dynamometers connected in series. This multi-stage tandem hydraulic dynamometer offers a wider power testing range, meeting the testing requirements of high-power, high-speed rotating machinery such as heavy-duty gas turbines and aircraft engines.

[0065] This multi-stage tandem hydraulic dynamometer includes a base 1500 and at least two of the aforementioned orifice-disc hydraulic dynamometers. These orifice-disc hydraulic dynamometers are spaced axially at the upper end of the base 1500. Adjacent orifice-disc hydraulic dynamometers are connected to a high-speed drive shaft 1600 via a coupling 440 mounted at the end of a rotating shaft 410. An axial adjustment assembly 1510 and a radial adjustment assembly 1520 are mounted on the upper end of the base 1500. The axial adjustment assembly 1510 allows the orifice-disc hydraulic dynamometers to be adjusted in length axially to position the support base 110. The radial adjustment assembly 1520 allows the orifice-disc hydraulic dynamometers to be adjusted in length radially to position the support base 110. The bottom edge of the support base 110 of the orifice-disc hydraulic dynamometer is also secured to the base 1500 via a locking bolt 1530.

[0066] Specifically, the axial adjustment assembly 1510 includes a first fixing block 1511 and a first positioning bolt 1512. The first fixing block 1511 is fixedly connected to the base 1500 and has a first threaded through hole parallel to the axis of the single-stage dynamometer. The first positioning bolt 1512 is threadedly engaged with the first threaded through hole. The radial adjustment assembly 1520 includes a second fixing block 1521 and a second positioning bolt 1522. The second fixing block 1521 is fixedly connected to the base 1500 and has a second threaded through hole perpendicular to the axis of the single-stage dynamometer. The second positioning bolt 1522 is threadedly engaged with the second threaded through hole.

[0067] The position of the orifice-disc hydraulic dynamometer can be easily adjusted through the axial adjustment assembly 1510 and the radial adjustment assembly 1520 . At the same time, the orifice-disc hydraulic dynamometer can ensure good coaxiality when connected in series.

[0068] A transmission shaft shield seat 1540 is also fixed to the upper end of base 1500. A transmission shaft shield 1550 is fixedly connected to the upper end of transmission shaft shield seat 1540. Transmission shaft shield 1550 covers and protects high-speed transmission shaft 1600. The bottom edge of base 1500 is fixed by a spherical combination washer 1560, an anchor bolt 1570, and a nut threaded connection to ensure the installation level of base 1500.

[0069] The above description is only a preferred specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any technician familiar with the technical field, within the technical scope disclosed by the present invention, who makes equivalent replacements or changes based on the technical solution and inventive concept of the present invention, should be covered by the scope of protection of the present invention.

Claims

1. A high-speed contact sealing structure for a hydraulic dynamometer, characterized in that: The invention comprises a housing and a rotating shaft (410) of a hydraulic dynamometer, wherein the rotating shaft (410) is rotatably mounted on the housing, and a water slinger (1000) and a contact sealing assembly (900) are sequentially mounted on the rotating shaft (410) from the inner cavity of the housing to the outer side. The contact seal assembly (900) comprises a fixed seal seat (910) and a rotary seal seat (940). The rotary seal seat (940) of the contact seal assembly (900) is connected to the water-slinging ring (1000) via a pin shaft, and a sealing ring is provided between the two. The contact seal assembly (900) is fixed to the housing via the outer ring of the fixed seal seat (910), and a sealing ring is provided between the outer ring of the fixed seal seat (910) and the housing. A sealing shaft sleeve (920) and a spring seat (930) are installed on the inner ring of the fixed seal seat (910). The sealing shaft sleeve (920) cooperates with the outer ring of the water-slinging ring (1000). A sealing static ring (933) is nested on the spring seat (930). The spring seat (930) abuts against the end surface of the rotary seal seat (940) via the end surface of the sealing static ring (933). A cooling water hole (912) is provided between the fixed sealing seat (910) and the shell, a sealed cooling water inlet channel (222) is provided on the shell, and the sealed cooling water inlet channel (222) is communicated with the cooling water hole (912). A radial through hole (915) is also provided on the fixed sealing seat (910), so that the gap between the outer ring of the rotating sealing seat (940) and the inner ring of the fixed sealing seat (910) is communicated with the cooling water hole (912).

2. The high-speed contact sealing structure of the hydraulic dynamometer according to claim 1, characterized in that: The sealing sleeve (920) is fixed to the inner ring of the fixed sealing seat (910) by means of bolts (921), and a sealing ring is provided between the sealing sleeve (920) and the fixed sealing seat (910); the outer ring of the spring seat (930) cooperates with the inner ring of the fixed sealing seat (910), and a retaining ring (914) is fixed to the inner ring of the fixed sealing seat (910) to axially position the spring seat (930) between the retaining ring (914) and the sealing sleeve (920), and the outer ring of the sealing sleeve (920) is in contact with the spring seat. The inner ring of the sealing sleeve (930) is matched with the inner ring of the sealing sleeve (930), and a sealing ring is provided between the two. The sealing sleeve (920) is provided with a guide pin (923) along its axial direction. The spring seat (930) is provided with a guide pin hole (931) that matches the guide pin (923). The spring seat (930) is provided with an axial mounting hole on the side facing the sealing sleeve (920). A pressure spring (932) is installed in the mounting hole. The two ends of the pressure spring (932) respectively abut against the spring seat (930) and the sealing sleeve (920).

3. The high-speed contact sealing structure of the hydraulic dynamometer according to claim 1, characterized in that: A sealing water leakage channel (223) is provided on the shell, and the sealing water leakage channel (223) passes through from the bottom of the shell to the outside of the fixed sealing seat (910).

4. The high-speed contact sealing structure of the hydraulic dynamometer according to claim 2, characterized in that: The material of the sealing static ring (933) is silicon carbide.

5. The high-speed contact sealing structure of the hydraulic dynamometer according to claim 2, characterized in that: The surface of the rotary seal seat (940) is provided with a sealing spray layer.

6. The high-speed contact sealing structure of the hydraulic dynamometer according to claim 5, characterized in that: The material of the sealing spray layer is hard chrome, and the hardness of the sealing spray layer is greater than HRC55.

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