Sealed cabin heating system for high-temperature rotary dynamic seal test and test device

Abstract

The invention relates to the technical field of sealing test, in particular to a sealed cabin heating system for high-temperature rotary dynamic sealing test and a test device. The device comprises a sealed cabin, a circulating pipeline is connected between a liquid inlet and a liquid outlet of the sealed cabin, and a circulating pump and a heater are mounted on the circulating pipeline; a high-level tank is further connected to the circulating pipeline so as to supplement liquid into the circulating pipeline when the liquid in the circulating pipeline is lost; the circulation pipeline or the sealed cabin is connected with a pressure relief pipeline, and a sealing valve is installed on the pressure relief pipeline. According to the invention, the burden and energy consumption of the heater are reduced, and the method also has the advantages of high medium temperature rise rate, short regulation time efficiency and high precision.

Description

Technical Field

[0001] The present invention relates to the technical field of seal testing, and specifically to a seal chamber heating system and a testing device for high-temperature rotary dynamic seal testing. Background Art

[0002] Rotary dynamic seals are key components used in rotating equipment such as pumps, fans, and compressors. Their function is to prevent the transported medium from leaking along the shaft end, thus avoiding accidents, and their importance is self-evident. Especially in high-temperature medium working conditions, if there is leakage of the sealing medium, it will trigger safety accidents that endanger property and life. Therefore, stricter requirements are imposed on the sealing performance and reliability of high-temperature seals.

[0003] Currently, the performance tests of rotary dynamic seals are basically carried out according to the requirements of international standards such as API682 and national standards such as GB14211. The standards have made quantitative and tolerance requirements for the stability of operating parameters such as test speed, pressure, and temperature. The design of rotary dynamic seal test devices not only needs to adapt to the structure and technical parameters of dynamic seals but also needs to optimize in terms of the stability of test parameters and operating reliability according to the standard requirements.

[0004] However, the existing high-temperature seal test devices basically still follow the design concept of conventional medium and low-parameter dynamic seal test devices. Most conventional medium and low-parameter dynamic seal test devices include a seal chamber for installing dynamic seal test pieces. The stationary part of the dynamic seal test piece is coaxially fixed on the end cover at the end of the seal chamber, and the rotating part of the dynamic seal test piece is fixed on the power shaft. By connecting the liquid inlet and outlet on the seal chamber to the water outlet and water return of the liquid storage tank respectively, the liquid circulates in the seal chamber. At the same time, the power shaft drives the rotating part to rotate, thereby detecting the sealing performance between the stationary part and the rotating part. Since the high-temperature seal test device requires a test environment of high-temperature liquid, a heater is set to heat the liquid entering the seal chamber. And due to the liquid loss that exists when the dynamic seal test piece leaks, in order to achieve the stable circulation of high-temperature liquid, the liquid in the liquid storage tank also needs to participate in the circulation to make up for the loss of the liquid. This results in an overly large base number of the liquid participating in the circulation, which not only increases the burden and energy consumption of the heater but also has problems such as slow liquid temperature increase rate, long adjustment time limit, and low accuracy, so it needs to be solved urgently. Summary of the Invention

[0005] In order to avoid and overcome the technical problems existing in the prior art, the present invention provides a seal chamber heating system and a testing device for high-temperature rotary dynamic seal testing, which reduces the burden and energy consumption of the heater and also has the advantages of fast medium temperature increase rate, short adjustment time limit, and high accuracy.

[0006] To achieve the above object, the present invention provides the following technical solutions:

[0007] A dynamic seal detection seal chamber heating system includes a seal chamber. A circulation pipeline is connected between the liquid inlet and the liquid outlet of the seal chamber. A circulation pump and a heater are installed on the circulation pipeline. A high-level tank is also connected to the circulation pipeline to supplement liquid into the circulation pipeline when the liquid in the circulation pipeline is lost. A pressure relief pipeline is connected to the circulation pipeline or the seal chamber, and a seal valve is installed on the pressure relief pipeline.

[0008] As a further solution of the present invention: The heater adjusts the operating power in real time through a PLC controller according to the following formula:

[0009] When P i = P max ;

[0010] When P

[0011]

[0012] In the formula: P i is the real-time operating power of the heater, in W;

[0013] P max is the maximum operating power of the heater, in W;

[0014] T set is the temperature set value in the seal chamber, in °C;

[0015] T i is the real-time measured value of the temperature in the seal chamber, in °C;

[0016] ΔT i is the temperature difference between the real-time measured value of the temperature in the seal chamber and the temperature set value. ΔT i = T set - T i ;

[0017] is the sum of the temperature differences ΔT i from the nth moment to the (n + k)th moment in the counting measurement period, where k is the number of measurements in the counting measurement period;

[0018] ΔT i (n + k)-ΔT i (n) is the difference between the temperature difference at the (n + k)th moment and the temperature difference at the nth moment in the counting measurement period from the nth moment to the (n + k)th moment; i ;

[0019] T i (n) is the temperature measured value at the nth moment, in °C;

[0020] t is the total measurement time of the k - th counting measurement cycle, with the unit of s;

[0021] h is the convective heat transfer coefficient of the natural convection between the test liquid medium and air, with the unit of W / m 2 ·℃

[0022] A is the heat transfer area of the sealed cabin in contact with air, with the unit of m 2 ;

[0023] T env is the ambient temperature monitored in real - time, with the unit of ℃.

[0024] As a further solution of the present invention: the bottom end of the sealed cabin is connected to a low - level tank through a drain pipeline, and a drain valve is installed on the drain pipeline; the low - level tank is communicated with the circulation pipeline through a liquid inlet pipeline, and a liquid supplement pump and a liquid supplement valve are installed on the liquid inlet pipeline.

[0025] As a further solution of the present invention: the bottom of the high - level tank is connected to the outlet end of the liquid supplement valve through a liquid supplement branch pipe, a liquid level control pipe communicating with the low - level tank is installed on the side wall of the high - level tank, and a liquid level overflow valve is installed on the liquid level control pipe.

[0026] As a further solution of the present invention: a pressure regulating valve and a pressure relief valve are installed on the upper part of the high - level tank, and the inlet end of the pressure regulating valve is connected to a pressure source; a pressure sensor is installed on the sealed cabin, the output end of the pressure sensor is connected to a PLC controller, and the output end of the PLC controller is connected to the pressure regulating valve and the pressure relief valve.

[0027] As a further solution of the present invention: a cooler is installed on the circulation pipeline, and the cooler is arranged adjacent to the liquid discharge port of the sealed cabin.

[0028] A test device, which applies the sealed cabin heating system for high - temperature rotary dynamic seal testing described above, includes a bearing seat arranged coaxially with the sealed cabin. A power shaft is coaxially rotatably fitted with a support bearing on the bearing seat. The first end of the power shaft is connected to a motor, and the second end of the power shaft extends into the sealed cabin. Both the bearing seat and the sealed cabin are installed on a fixed seat. There is a heat dissipation interval between the adjacent ends of the bearing seat and the sealed cabin. A rotary self - heat dissipation wheel is coaxially fixed on the shaft body of the power shaft at the position of the heat dissipation interval, and a water - cooled sleeve sleeving the outer circumference of the support bearing is coaxially fixed on the bearing seat.

[0029] As a further solution of the present invention: the inside of the bearing seat has a lubrication cavity, the support bearing is arranged at the end of the lubrication cavity, a lubricating oil spray pipe inserted into the lubrication cavity is installed on the upper part of the bearing seat, the oil spray holes of the lubricating oil spray pipe point to the support bearing, and an oil return port communicating with the lubrication cavity is arranged at the bottom of the bearing seat.

[0030] As a further solution of the present invention: the inner end of the lubricating oil spray pipe is sealed, and the oil spray holes are arranged on the side wall of the lubricating oil spray pipe. The oil spray holes are provided with a plurality of "rice" - shaped structures arranged on the side wall of the lubricating oil spray pipe.

[0031] As a further solution of the present invention: at the end of the bearing seat through which the driven shaft passes, a seal is installed. The seal includes a labyrinth rotating part coaxially fixed on the outer periphery of the power shaft. The longitudinal section of the labyrinth rotating part is in a side - T - shaped structure, and the vertical part of the labyrinth rotating part faces outward and the horizontal part faces inward. The inner wall of the vertical part of the labyrinth rotating part is provided with labyrinth ring grooves. The labyrinth ring grooves are at least two annular grooves coaxially distributed with the power shaft. The outer periphery of the horizontal part of the labyrinth rotating part is provided with an oil - returning spiral groove for sending oil towards the lubricating cavity; coaxially and spacedly sleeved on the outer periphery of the horizontal part of the labyrinth rotating part is a seal stationary part fixedly sealed with the bearing seat. The seal stationary part is provided with a labyrinth snap ring inserted into the labyrinth ring groove, and there is a gap between the groove wall of the labyrinth ring groove and the outer surface wall of the labyrinth snap ring. A reflux hole communicating with the lubricating cavity is arranged at the lower gap between adjacent labyrinth snap rings.

[0032] Compared with the prior art, the beneficial effects of the present invention are:

[0033] 1. First, open the seal valve and inject liquid into the circulation pipeline. Release pressure and exhaust air through the pressure - relief pipeline, so that the circulation pipeline and the sealed cabin are stably filled with liquid until full load. Then, close the seal valve. At this time, the pressure in the high - level tank is balanced with the pressure in the circulation pipeline, and the liquid in the high - level tank will not flow into the circulation pipeline. Therefore, when the circulation pump makes the liquid circulate between the circulation pipeline and the sealed cabin, the liquid will not flow into the high - level tank, that is, the liquid in the high - level tank will not participate in the circulation of the liquid in the circulation pipeline and the sealed cabin. When the liquid in the circulation pipeline is lost, the pressure in the circulation pipeline decreases. At this time, the high - level tank will supply liquid to the circulation pipeline. Thus, it not only realizes the automatic compensation for the loss of the liquid in the circulation pipeline, but also reduces the amount of liquid participating in the circulation under the normal circulation state in the circulation pipeline. It not only reduces the burden and energy consumption of the heater, but also makes the temperature - rising rate of the liquid participating in the circulation fast, with short adjustment time limit and high precision.

[0034] 2. The heater adjusts the operating power in real time according to a preset formula through the PLC controller, ensuring that the test temperature parameters are maintained within the allowable error range of the set value, with a temperature control accuracy of ±1.2 °C, and having the advantages of good adjustment time limit, high adjustment accuracy and good stability.

[0035] 3. The bearing housing and the seal chamber are designed separately. Specifically, there is a heat dissipation interval between the adjacent ends of the bearing housing and the seal chamber. In addition, a rotating self-cooling wheel is coaxially fixed on the shaft body of the power shaft at the heat dissipation interval, and a water-cooling sleeve sleeved on the outer circumference of the support bearing is coaxially fixed on the bearing housing. The setting of the rotating self-cooling wheel increases the heat dissipation area of a section of the power shaft at the heat dissipation interval. In addition, the rotation of the rotating self-cooling wheel will cause gas turbulence at the heat dissipation interval, improve the heat transfer efficiency by increasing the air flow rate, and quickly discharge the hot air after heat exchange with the power shaft and the rotating self-cooling wheel from the heat dissipation interval, effectively improving the heat dissipation effect on the power shaft. Thus, the heat conducted by the power shaft in the seal chamber is diffused before reaching the bearing housing, maintaining the working temperature of the bearing housing and ensuring the operation reliability and service life of the test device. In addition, further, with the setting of the water-cooling sleeve, secondary heat dissipation of the support bearing is achieved, further ensuring the operation reliability of the bearing housing.

[0036] 4. The lubricating oil spray pipe adopts a form of uniformly spraying oil through a number of spray holes arranged in a "rice" shape on the side wall, ensuring the lubrication effect on the support bearing.

[0037] 5. To prevent the leakage of the lubricating fluid in the lubrication chamber, a seal is installed at the end of the bearing housing penetrated by the power shaft. The non-contact labyrinth path between the labyrinth snap ring and the labyrinth groove in the seal is used for sealing, and the reflux holes at the lower position of the labyrinth path return oil naturally, with good sealing effect and can adapt to the test working condition of the high-speed rotation of the power shaft. Description of the Drawings

[0038] Figure 1 It is a schematic diagram of the working process of the seal chamber heating system in the present invention.

[0039] Figure 2 It is a schematic diagram of the internal structure of the seal chamber and the bearing housing in the present invention.

[0040] Figure 3 It is a schematic diagram of the structure of the lubricating oil spray pipe in the present invention.

[0041] Figure 4 It is an exploded structure schematic diagram of the labyrinth rotating part and the seal stationary part in the present invention.

[0042] Figure 5 It is a schematic diagram of the side view structure of the seal chamber in the present invention.

[0043] In the figure: 10, bearing housing; 11, power shaft; 12, lubrication chamber; 13, support bearing; 14, lubricating oil spray pipe; 141, oil injection hole; 15, seal; 151, labyrinth rotating part; 1511, oil return spiral groove; 1512, labyrinth ring groove; 152, seal stationary part; 1521, labyrinth snap ring; 1522, backflow hole; 16, oil return port; 20, seal chamber; 21, end cover; 22, liquid inlet; 23, liquid outlet; 30, water cooling jacket; 40, rotating self-cooling wheel; 50, fixed seat; 60, circulation pipeline; 61, cooler; 62, circulation pump; 63, heater; 70, high-level tank; 71, liquid level control pipe; 72, liquid level overflow valve; 73, pressure regulating valve; 74, pressure relief valve; 80, low-level tank; 81, liquid inlet pipeline; 811, liquid supplement branch pipe; 82, drain pipeline; 83, drain valve; 84, liquid supplement pump; 85, liquid supplement valve; 90, pressure relief pipe; 91, seal valve; a, dynamic seal test piece; a1, stationary component; a2, rotating component. Detailed implementation mode

[0044] The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0045] For the convenience of understanding, the specific structure and working mode of the present invention are further described below with reference to the accompanying drawings:

[0046] The specific structure of the present invention is shown in Figures 1-5 and its main structure includes a seal chamber 20, a bearing housing 10, and a heating system for circulating and delivering high-temperature liquid into the seal chamber 20.

[0047] 1. Heating system

[0048] As Figure 1As shown, it includes a circulation pipeline 60 connecting the liquid inlet 22 and the liquid outlet 23 of the connection seal chamber 20. A circulation pump 62 and a heater 63 are installed on the circulation pipeline 60. The circulation pump 62 provides the circulation power, and the heater 63 heats the liquid. A high-level tank 70 is also connected to the circulation pipeline 60 to supplement the liquid to the circulation pipeline 60 when the liquid in the circulation pipeline 60 is lost. A pressure relief pipeline 90 is connected to the circulation pipeline 60 or the seal chamber 20, and a seal valve 91 is installed on the pressure relief pipeline 90. During use, first open the seal valve 91, inject liquid into the circulation pipeline 60, and relieve pressure and exhaust gas through the pressure relief pipeline 90, so that the circulation pipeline 60 and the seal chamber 20 are stably filled with liquid until full load. After that, close the seal valve 91. At this time, the pressure in the high-level tank 70 is balanced with the pressure in the circulation pipeline 60, and the liquid in the high-level tank 70 will not flow into the circulation pipeline 60. Therefore, when the circulation pump 62 makes the liquid circulate between the circulation pipeline 60 and the seal chamber 20, the liquid will not flow into the high-level tank 70, that is, the liquid in the high-level tank 70 will not participate in the circulation of the liquid in the circulation pipeline 60 and the seal chamber 20. When the liquid in the circulation pipeline 60 is lost, the pressure in the circulation pipeline 60 decreases. At this time, the high-level tank 70 will supplement the liquid to the circulation pipeline 60. Thus, it not only realizes the automatic compensation for the loss of the liquid in the circulation pipeline 60, but also reduces the amount of liquid participating in the circulation in the normal circulation state of the circulation pipeline 60. It not only reduces the burden and energy consumption of the heater 63, but also makes the temperature increase rate of the liquid participating in the circulation fast, the adjustment time limit short and the accuracy high.

[0049] To ensure a high-temperature test environment with a relatively constant temperature entering the seal chamber 20, the heater 63 adjusts the operating power in real time through a PIC controller according to the following formula:

[0050] When , P i =P max ;

[0051] When ,

[0052]

[0053] In the formula: P i is the real-time operating power of the heater 63, in W;

[0054] P max is the maximum operating power of the heater 63, in W;

[0055] T set is the temperature set value in the seal chamber 20, in °C;

[0056] T i is the real-time measured value of the temperature in the seal chamber 20, in °C;

[0057] ΔT i is the temperature difference between the real-time measured temperature value and the set temperature value inside the sealed cabin 20, ΔT i = T set - T i ;

[0058] is the sum of the temperature differences ΔT for the counting measurement period from the nth moment to the (n + k)th moment, where k is the number of measurements within the counting measurement period; i

[0059] ΔT i (n + k)-ΔT i (n) is the difference between the temperature difference at the (n + k)th moment and the temperature difference at the nth moment within the counting measurement period from the nth moment to the (n + k)th moment of the temperature difference ΔT i ;

[0060] T i (n) is the temperature measurement value at the nth moment, in °C;

[0061] t is the total measurement time for k counting measurement periods, in s;

[0062] h is the convective heat transfer coefficient of the natural convection of the test liquid medium and air, in W / m 2 ·°C

[0063] A is the heat transfer area of the sealed cabin 20 in contact with air, in m 2 ;

[0064] T env is the ambient temperature monitored in real time, in °C.

[0065] In the above formulas, the values that need to be measured in real time include the real-time measured temperature value T i inside the sealed cabin 20 and the ambient temperature T env monitored in real time. In actual implementation, the real-time measured temperature value T i inside the sealed cabin 20 can be obtained by setting a first temperature sensor connected to the PLC controller inside the sealed cabin 20; the ambient temperature T env monitored in real time can be obtained by setting a second temperature sensor connected to the PLC controller in the working environment. This temperature acquisition is prior art and will not be elaborated here.

[0066] During practical verification, Table 1 below is a statistical table of the set temperature value inside the sealed cabin 20 and the real-time measured temperature value inside the sealed cabin 20:

[0067]

[0068] ​Statistical Table of Temperature Set Values in the Sealed Compartment and Real-time Measured Temperature Values in the Sealed Compartment

[0069] As can be seen from Table 1, the heater 63 adjusts the operating power in real time according to the above formula through the PIC controller, ensuring that the test temperature parameters are maintained within the allowable tolerance range of the set value. The temperature control accuracy reaches ±1.2°C, with the advantages of good adjustment timeliness, high adjustment accuracy, and good stability.

[0070] On this basis, as Figure 1 shown, the bottom end of the sealed compartment 20 is connected to a low-level tank 80 through a drain pipeline 82, and a drain valve 83 is installed on the drain pipeline 82; the low-level tank 80 is connected to the circulation pipeline 60 through a liquid inlet pipeline 81, and a liquid supplement pump 84 and a liquid supplement valve 85 are installed on the liquid inlet pipeline 81. After the test is completed, the drain valve 83 is opened, and by utilizing the low-level characteristic of the low-level tank 80, the liquid in the sealed compartment 20 automatically drains into the low-level tank 80 under the action of gravity. When conducting the next test, the liquid supplement pump 84 and the liquid supplement valve 85 are opened to inject liquid into the sealed compartment 20 and the circulation pipeline 60 again. Of course, in actual implementation, the liquid inlet pipeline 81 of the low-level tank 80 can also be only connected to the high-level tank 70, and the high-level tank 70 is used to inject liquid into the circulation pipeline 60 and the sealed compartment 20 again.

[0071] On this basis, as Figure 1 shown, the bottom of the high-level tank 70 is connected to the outlet end of the liquid supplement valve 85 through a liquid supplement branch pipe 811, and a liquid level control pipe 71 communicating with the low-level tank 80 is installed on the side wall of the high-level tank 70, and a liquid level overflow valve 72 is installed on the liquid level control pipe 71. Through the setting of the liquid supplement branch pipe 811, the low-level tank 80 can not only supplement liquid to the circulation pipeline 60 and the sealed compartment 20, but also supplement liquid to the high-level tank 70, without the need to additionally set up pipelines and pumps to supplement liquid to the high-level tank 70. In addition, through the setting of the liquid level control pipe 71 and the liquid level overflow valve 72, the automatic overflow of the excess liquid in the high-level tank 70 into the low-level tank 80 can be realized by opening the liquid level overflow valve 72, ensuring that the liquid in the high-level tank 70 is at an appropriate liquid level height.

[0072] In addition, as Figure 1 shown, a pressure regulating valve 73 and a pressure relief valve 74 are installed on the upper part of the high-level tank 70. The inlet end of the pressure regulating valve 73 is connected to a pressure source. By opening the pressure regulating valve 73, pressure is applied to the high-level tank 70, and the excess pressure can be relieved by using the pressure relief valve 74. A pressure sensor is installed on the sealed compartment 20, the output end of the pressure sensor is connected to the PLC controller, and the output end of the PLC controller is connected to the pressure regulating valve 73 and the pressure relief valve 74, thereby realizing the pressure control in the sealed compartment 20 and the high-level tank 70.

[0073] On the basis described above, a cooler 61 is installed on the circulating pipeline 60, and the cooler 61 is arranged adjacent to the liquid discharge port 23 of the sealed cabin 20. The cooler 61 is in a normally closed state during normal detection. When a temperature cycling experiment is required, the cooler 61 can be opened to rapidly cool the liquid. In addition, the cooler 61 can also be used in other situations where liquid cooling is required, such as when the pipeline is being repaired.

[0074] 2. Test device

[0075] As Figures 2-5 shown, the test device mainly includes a sealed cabin 20 connected to the above heating system and a bearing seat 10 arranged coaxially with the sealed cabin 20. A power shaft 11 is coaxially rotatably fitted on the bearing seat 10 through a support bearing 13. The first end of the power shaft 11 is connected to a motor, and the second end of the power shaft 11 extends into the sealed cabin 20. Both the bearing seat 10 and the sealed cabin 20 are installed on a fixed seat 50. During the test, the rotating part a2 of the dynamic seal test piece a is sealed and fixed on the power shaft 11, and the stationary part a1 of the dynamic seal test piece a is sleeved on the outer periphery of the rotating part a2 and is sealed and fixed to the end cover 21 of the sealed cabin 20. At this time, high-temperature liquid is input into the sealed cabin 20 through the liquid inlet 22, and at the same time, the high-temperature liquid is discharged through the liquid discharge port 23 to realize the circulation of the liquid at a constant temperature in the sealed cabin 20. Thereafter, the power shaft 11 is driven to rotate by the motor, driving the rotating part a2 to rotate synchronously, so as to realize the high-temperature rotary dynamic seal test between the rotating part a2 and the stationary part a1.

[0076] Since the sealed cabin 20 is in a high-temperature working environment, this high temperature will be conducted to the bearing seat 10 through the medium. In a long-term high-temperature environment, it will affect the service life of the support bearing 13 on the bearing seat 10. As Figure 2As shown, in the present invention, the bearing housing 10 and the sealing cabin 20 are designed separately. Specifically, there is a heat dissipation interval between the adjacent ends of the bearing housing 10 and the sealing cabin 20. In addition, a rotating self-cooling wheel 40 is coaxially fixed on the shaft body of the power shaft 11 at the heat dissipation interval, and a water-cooling sleeve 30 sleeved on the outer periphery of the support bearing 13 is coaxially fixed on the bearing housing 10. The setting of the rotating self-cooling wheel 40 increases the heat dissipation area of a section of the power shaft 11 at the heat dissipation interval. In addition, the rotation of the rotating self-cooling wheel 40 will cause gas turbulence at the heat dissipation interval, improve the heat transfer efficiency by increasing the air flow rate, and quickly discharge the hot air after heat exchange with the power shaft 11 and the rotating self-cooling wheel 40 from the heat dissipation interval, effectively improving the heat dissipation effect on the power shaft 11. Thus, the heat conducted by the sealing cabin 20 through the power shaft 11 is diffused before reaching the bearing housing 10, maintaining the working temperature of the bearing housing 10 and ensuring the operation reliability and service life of the test device. In addition, further, the setting of the water-cooling sleeve 30 realizes secondary heat dissipation of the support bearing 13, further ensuring the operation reliability of the bearing housing 10.

[0077] As Figure 5 shown, the bearing housing 10 and the sealing cabin 20 are designed separately. The side of the sealing cabin 20 can be fixedly connected to the connecting frame through radial bolts, and the connecting frame can be fixed on the fixed seat 50 through vertical bolts. It gets rid of the traditional positioning and matching mode of the sealing cabin 20 only through radial holes, avoiding the influence of processing errors. It not only has high coaxial matching adjustment accuracy, but also can be regularly calibrated for accuracy, and can maintain the operation accuracy for long-term use.

[0078] During practical verification, Table 2 below is a comparison table of the operating temperature of the support bearing 13 in the conventional technology and the operating temperature of the support bearing 13 in this solution:

[0079]

[0080] Table 2 Comparison table of the operating temperature of the support bearing in the conventional technology and the operating temperature of the support bearing in this solution

[0081] As can be seen from Table 2, the structural arrangement in the present invention effectively reduces the influence of the high-temperature environment of the sealing cabin 20 on the support bearing 13 compared with the conventional arrangement structure, ensuring the operation reliability of the test device and extending the service life of the test device.

[0082] On the above basis, as Figure 2As shown, the interior of the bearing housing 10 has a lubrication chamber 12. The support bearing 13 is arranged at the end of the lubrication chamber 12. The upper part of the bearing housing 10 is equipped with a lubricating oil spray pipe 14 inserted into the lubrication chamber 12. The oil spray holes 141 of the lubricating oil spray pipe 14 point to the support bearing 13. The bottom of the bearing housing 10 is provided with an oil return port 16 communicating with the lubrication chamber 12. During operation, lubricating oil is sprayed into the lubrication chamber 12 through the lubricating oil spray pipe 14. After lubricating the support bearing 13, the lubricating oil flows back to the fuel tank through the oil return port 16. This circulating spraying process of the lubricating oil not only lubricates the support bearing 13 stably but also has a certain heat dissipation effect on the support bearing 13, further improving the reliability and durability of the operation of the bearing housing 10.

[0083] Specifically, as Figure 2 and Figure 3 shown, the inner end of the lubricating oil spray pipe 14 is sealed, and the oil spray holes 141 are arranged on the side wall of the lubricating oil spray pipe 14. The oil spray holes 141 are set to be several that are arranged in a "rice" - shaped structure on the side wall of the lubricating oil spray pipe 14. This arrangement of the oil spray holes 141 ensures the uniformity of the lubricating oil sprayed onto the support bearing 13 and guarantees the lubrication effect on the support bearing 13.

[0084] On the above basis, to prevent the leakage of the lubricating fluid in the lubrication chamber 12, a seal 15 is installed at the end of the bearing housing 10 through which the driven shaft 11 passes. Specifically, as Figure 2 and Figure 4As shown, the seal 15 includes a labyrinth rotating member 151 coaxially fixed to the outer periphery of the power shaft 11. The longitudinal section of the labyrinth rotating member 151 has a side T-shaped structure, and the vertical part of the labyrinth rotating member 151 faces outward while the horizontal part faces inward. A labyrinth ring groove 1512 is formed in the inner wall of the vertical part of the labyrinth rotating member 151. The labyrinth ring groove 1512 is at least two annular grooves coaxially distributed with the power shaft 11. In addition, a seal stationary member 152 sealingly fixed to the bearing housing 10 is coaxially and spacedly sleeved on the outer periphery of the horizontal part of the labyrinth rotating member 151. The seal stationary member 152 is provided with a labyrinth snap ring 1521 inserted into the labyrinth ring groove 1512, and there is a gap between the groove wall of the labyrinth ring groove 1512 and the outer surface wall of the labyrinth snap ring 1521. A reflux hole 1522 communicating with the lubricating cavity 12 is provided at the lower gap between adjacent labyrinth snap rings 1521. When lubricating oil enters between the labyrinth ring grooves 1512, due to the design of at least two annular grooves of the labyrinth ring grooves 1512 and combined with the labyrinth snap rings 1521 inserted into the labyrinth ring grooves 1512, a winding labyrinth path is formed between the groove wall of the labyrinth ring groove 1512 and the outer surface wall of the labyrinth snap ring 1521, so that the lubricating oil cannot directly flow into the outermost annular groove body. When the lubricating oil flows to the lower part of the labyrinth ring groove 1512, part of the lubricating oil flows back to the lubricating cavity 12 through the reflux hole 1522; and, as the labyrinth rotating member 151 continues to rotate, it will drive part of the lubricating oil flowing to the lower part of the labyrinth ring groove 1512 to flow to the upper part of the labyrinth ring groove 1512 again, and under the action of gravity, it will flow back into the innermost annular groove body or even the lubricating cavity 12, thereby forming a non-contact seal between the labyrinth snap ring 1521 and the labyrinth ring groove 1512. In addition, an oil return spiral groove 1511 for sending oil towards the lubricating cavity 12 is provided on the outer periphery of the horizontal part of the labyrinth rotating member 151. When the labyrinth rotating member 151 drives the oil return spiral groove 1511 to rotate, by the action of centrifugal force, the lubricating oil is obliquely thrown into the lubricating cavity 12 along the cavity of the oil return spiral groove 1511. Thus, most of the lubricating oil is blocked from flowing to the labyrinth ring groove 1512 on the vertical part of the labyrinth rotating member 151, further improving the anti-leakage effect of the lubricating cavity 12.

[0085] Of course, for those skilled in the art, the present invention is not limited to the details of the above exemplary embodiments, but also includes the same or similar structures that can be implemented in other specific forms without departing from the spirit or basic characteristics of the present invention. Therefore, from any point of view, the embodiments should be regarded as exemplary and non-limiting. The scope of the present invention is defined by the appended claims rather than the above description. Therefore, all changes falling within the meaning and scope of the equivalent elements of the claims are intended to be included in the present invention. Any reference signs in the claims should not be regarded as limiting the claims involved.

[0086] In addition, it should be understood that although this specification is described according to embodiments, not every embodiment only contains an independent technical solution. This narrative way of the specification is only for clarity. Those skilled in the art should regard the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0087] The technologies, shapes, and structures not detailedly described in the present invention are all well-known technologies.

Claims

1. A dynamic seal detection seal chamber heating system, characterized in that, It includes a sealed chamber (20), a circulation pipeline (60) is connected between the liquid inlet (22) and the liquid outlet (23) of the sealed chamber (20), and a circulation pump (62) and a heater (63) are installed on the circulation pipeline (60); a high-level tank (70) is also connected to the circulation pipeline (60) to supplement liquid into the circulation pipeline (60) when the liquid in the circulation pipeline (60) is lost; a pressure relief pipeline (90) is connected to the circulation pipeline (60) or the sealed chamber (20), and a sealing valve (91) is installed on the pressure relief pipeline (90).

2. The heating system of the sealing cabin for high-temperature rotary dynamic seal test according to claim 1, wherein, The heater (63) adjusts the operating power in real time through a PLC controller according to the following formula: When , P i = P max ; When then In the formula: Px is the real-time operating power of the heater (63), unit W; P max is the maximum operating power of the heater (63), in W; T set is the set value of the temperature inside the sealed cabin (20), in °C; T i is the real-time measured temperature value inside the sealed cabin (20), unit: °C; ΔT i is the temperature difference between the real-time measured temperature value and the set temperature value inside the sealed cabin (20), ΔT i =T set -T i ; Is the sum of the temperature differences ΔT for the counting measurement period from the nth moment to the (n + k)th moment, where k is the number of measurements within the counting measurement period; i ​ ΔT i (n + k)-ΔT i (n) is the difference between the temperature difference at the (n + k)-th moment and the temperature difference ΔT at the n-th moment within the counting measurement period from the n-th moment to the (n + k)-th moment i minus; T i (n) is the temperature measurement value at time n, in °C; t is the total measurement time of the kth counting measurement period, unit s; h is the convective heat transfer coefficient of natural convection between the test liquid medium and air, with the unit of W / m 2 ·℃ A is the heat exchange area where the sealed cabin (20) contacts the air, unit: m 2 ; T env is the ambient temperature for real-time monitoring, in °C.

3. The heating system for the sealed chamber used in the high-temperature rotary dynamic seal test according to claim 1 or 2, characterized in that, The bottom end of the sealed chamber (20) is connected to a low-level tank (80) through a drainage pipeline (82), and a drainage valve (83) is installed on the drainage pipeline (82); the low-level tank (80) is communicated with the circulation pipeline (60) through a liquid inlet pipeline (81), and a liquid supplement pump (84) and a liquid supplement valve (85) are installed on the liquid inlet pipeline (81).

4. A sealing chamber heating system for high-temperature rotary dynamic seal testing according to claim 1 or 2, characterized in that, The bottom of the high-level tank (70) is connected to the outlet end of the liquid supplement valve (85) through a liquid supplement branch pipe (811), a liquid level control pipe (71) communicating with the low-level tank (80) is installed on the side wall of the high-level tank (70), and a liquid level overflow valve (72) is installed on the liquid level control pipe (71).

5. A sealing chamber heating system for high-temperature rotary dynamic seal testing according to claim 1 or 2, characterized in that, A pressure regulating valve (73) and a pressure relief valve (74) are installed on the upper part of the high-level tank (70), and the inlet end of the pressure regulating valve (73) is connected to a pressure source; a pressure sensor is installed on the sealed chamber (20), the output end of the pressure sensor is connected to the PLC controller, and the output end of the PLC controller is connected to the pressure regulating valve (73) and the pressure relief valve (74).

6. A sealing chamber heating system for high-temperature rotary dynamic seal testing according to claim 1 or 2, characterized in that, A cooler (61) is installed on the circulation pipeline (60), and the cooler (61) is arranged adjacent to the liquid outlet (23) of the sealed chamber (20).

7. A test device, which applies a sealing chamber heating system for high-temperature rotary dynamic seal testing as described in any one of claims 1-6, includes a bearing housing (10) arranged coaxially with the sealing chamber (20). A power shaft (11) is coaxially rotatably fitted on the bearing housing (10) through a support bearing (13). The first end of the power shaft (11) is connected to a motor, and the second end of the power shaft (11) extends into the sealing chamber (20), characterized in that, The bearing seat (10) and the sealed chamber (20) are both installed on the fixed seat (50), there is a heat dissipation interval between the adjacent ends of the bearing seat (10) and the sealed chamber (20), a rotating self-cooling wheel (40) is coaxially fixed on the shaft body of the power shaft (11) located at the heat dissipation interval, and a water-cooled sleeve (30) sleeved on the outer periphery of the support bearing (13) is coaxially fixed on the bearing seat (10).

8. The testing device according to claim 7, characterized in that The inside of the bearing seat (10) has a lubrication cavity (12), the support bearing (13) is arranged at the end of the lubrication cavity (12), a lubrication spray oil pipe (14) inserted into the lubrication cavity (12) is installed on the upper part of the bearing seat (10), the oil injection holes (141) of the lubrication spray oil pipe (14) point to the support bearing (13), and an oil return port (16) communicated with the lubrication cavity (12) is arranged at the bottom of the bearing seat (10).

9. The test device according to claim 8, wherein, The inner end of the lubrication spray oil pipe (14) is sealed, the oil injection holes (141) are arranged on the side wall of the lubrication spray oil pipe (14), and the oil injection holes (141) are arranged as several ones forming a "rice" - shaped structure in the side wall of the lubrication spray oil pipe (14).

10. The test device according to claim 8, wherein, A seal (15) is installed at the end of the driven shaft (11) passing through the bearing housing (10). The seal (15) includes a labyrinth rotating member (151) coaxially fixed to the outer periphery of the power shaft (11). The longitudinal section of the labyrinth rotating member (151) has a side-T-shaped structure, and the vertical part of the labyrinth rotating member (151) faces outward and the horizontal part faces inward. A labyrinth ring groove (1512) is formed in the inner wall of the vertical part of the labyrinth rotating member (151). The labyrinth ring groove (1512) is at least two annular grooves coaxially distributed with the power shaft (11). An oil return spiral groove (1511) for sending oil towards the lubrication chamber (12) is provided on the outer periphery of the horizontal part of the labyrinth rotating member (151). A sealing stationary member (152) sealed and fixed to the bearing housing (10) is coaxially and spacedly sleeved on the outer periphery of the horizontal part of the labyrinth rotating member (151). The sealing stationary member (152) is provided with a labyrinth snap ring (1521) inserted into the labyrinth ring groove (1512), and there is a gap between the groove wall of the labyrinth ring groove (1512) and the outer surface wall of the labyrinth snap ring (1521). A backflow hole (1522) communicating with the lubrication chamber (12) is provided at the lower gap between adjacent labyrinth snap rings (1521).

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