Miniature pipe jacking cutting machine head bearing sealing structure and cutting machine

Abstract

The invention provides a bearing sealing structure of a miniature pipeline jacking pipe cutting machine head and a cutting machine, and relates to the field of miniature pipeline jacking pipe cutting machine heads, the bearing sealing structure comprises a bearing inner ring, a bearing outer ring and a rolling body, and further comprises an elastic sealing ring and a metal ring; an extending part is arranged on the upper portion of the bearing inner ring, a groove is formed in the lower end of the extending part of the bearing inner ring, a supporting step is arranged on the upper portion of the side, close to the bearing inner ring, of the bearing outer ring, after the bearing outer ring is connected with the bearing inner ring, the groove and the supporting step form a containing space, and the metal ring is arranged in the containing space. An elastic sealing ring is arranged between the outer side of the metal ring and the groove, and an elastic sealing ring is also arranged between the outer side of the metal ring and the outer side of the supporting step. After the metal seal and the bearing are integrated, the sealing face directly acts on a rotating part of the bearing, and assembling gaps and connection errors possibly existing in a traditional split type seal are eliminated.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of micro-pipeline pipe jacking cutting machine head, in particular to a micro-pipeline pipe jacking cutting machine head bearing sealing structure and a cutting machine. BACKGROUND

[0002] In the micro-pipeline pipe jacking construction, the cutting machine head as a core component, the sealing and service life of the bearing inside directly determines the construction efficiency and equipment reliability. However, the working environment of the micro-pipe jacking cutting machine head is extremely poor, the silt, underground water and gravel particles in the underground soil layer will continuously invade the inside of the machine head, if the bearing sealing structure design is insufficient, impurities are easy to enter the bearing gap, causing the raceway wear, lubricating grease loss, and then causing the bearing jam, machine head deflection and even shutdown failure.

[0003] In the existing pipe jacking cutting device (such as CN 204060700U, a rotating joint device of a rectangular shield pipe jacking machine, CN214577043U, a hollow spindle structure of a pipe jacking machine power system), the bearing itself is not provided with a sealing structure, and some schemes will set an outer sealing layer at the outside of the bearing (such as the shaft coupling or the main shaft end cover). In the conventional working condition, it can meet the basic protection requirements, but in the harsh working conditions such as high water pressure and water-rich sand layer, the mud and fine sand still have the risk of invasion. Moreover, the above-mentioned outer sealing layer needs to occupy new installation space and connection structure, which is difficult to integrate in a miniaturized manner, and is not suitable for space-limited scenes. SUMMARY

[0004] The present application provides a micro-pipeline pipe jacking cutting machine head bearing sealing structure and a cutting machine to solve at least one of the technical problems in the background art.

[0005] To solve the above technical problems, the present application discloses a micro-pipeline pipe jacking cutting machine head bearing sealing structure, which comprises a bearing inner ring, a bearing outer ring and a rolling body, and further comprises an elastic sealing ring and a metal ring. The upper part of the bearing inner ring is provided with an extension, the lower end of the extension of the bearing inner ring is provided with a groove, the upper part of one side of the bearing outer ring close to the bearing inner ring is provided with a support step, the groove and the support step form an accommodation space after the bearing outer ring is connected with the bearing inner ring, the metal ring is arranged in the accommodation space, the elastic sealing ring is arranged between the outer side of the metal ring and the groove, and the elastic sealing ring is also arranged between the outer side of the metal ring and the outer side of the support step.

[0006] Preferably, the contact surface between the outer side of the metal ring and the elastic sealing ring is a tapered surface.

[0007] Preferably, the height of the tapered surface of the upper part of the metal ring close to one end of the axis is higher than the height of the other end away from the axis. The height of the cone surface at the bottom of the metal ring is lower at the end closest to the axis than at the end furthest from the axis. Preferably, the contact surfaces of the groove and the support step with the elastic sealing ring are auxiliary conical surface and auxiliary conical surface two, respectively, and the inclination direction of the auxiliary conical surface and auxiliary conical surface two is the same as the inclination direction of the conical surface corresponding to the elastic sealing ring.

[0008] Preferably, the two ends of the conical surface are arc-shaped concave surfaces.

[0009] Preferably, the elastic sealing ring is a rubber ring.

[0010] The present invention also discloses a miniature pipe jacking cutting machine, including a cutting head, wherein the cutting head adopts the aforementioned bearing sealing structure of the miniature pipe jacking cutting machine head.

[0011] Preferably, the cutting head further includes: The drive spindle is fixedly connected to the cutter head assembly and passes through the bearing sealing structure. The spindle power unit is used to drive the drive spindle. The headstock operation monitoring device is electrically connected to the main spindle power unit.

[0012] Preferably, the head unit operation monitoring device includes: Spindle detection module: used to detect the speed and working torque of the drive spindle; Bearing detection module: used to detect bearing vibration information and temperature; Spindle analysis module: used to determine the current torque-to-speed ratio coefficient based on the detection results of the spindle detection module during the operation of the cutting head; Module 2: Used to construct a torque-speed ratio trend line by obtaining the detection results of the spindle detection module within the analysis period two when the current torque-speed ratio is greater than the preset torque-speed ratio, and to construct an amplitude coefficient trend line by obtaining the bearing amplitude within the analysis period two. Calculation module: used to determine the equivalent load vibration coordination coefficient based on the construction results of module two; Control module: When the current torque-to-speed ratio coefficient is greater than the preset torque-to-speed ratio coefficient, or when the current equivalent load vibration coordination coefficient does not meet the preset equivalent load vibration coordination coefficient requirement, the control module controls the corresponding alarm unit of the alarm module to sound an alarm.

[0013] Preferably, the bearing detection module is also used to detect the temperature of the bearing's temperature detection area, and the headstock operation monitoring device also includes: Module 1: Used to acquire the bearing detection results from the bearing detection module within the analysis period to construct the bearing amplitude sequence and bearing temperature sequence; The trigger condition for obtaining the sequence includes: any of the following conditions occurs: bearing temperature is greater than a preset temperature value, bearing temperature rise rate is greater than a preset temperature rise rate value, torque-to-speed ratio coefficient is greater than a preset torque-to-speed ratio coefficient, and a periodic collection time length of reaching a continuous tunneling steady state stage; The bearing analysis module is configured to determine a coupling temperature rise influence coefficient based on the bearing amplitude sequence, the bearing temperature sequence, and the torque-to-speed ratio coefficient; and determine an amplitude temperature rise hysteresis coefficient based on the bearing amplitude sequence and the bearing temperature sequence when the coupling temperature rise influence coefficient is greater than a preset value. When the coupling temperature rise influence coefficient is greater than the preset value, the calculation module determines an updated preset coupling temperature rise influence coefficient based on the amplitude temperature rise hysteresis coefficient and the preset coupling temperature rise influence coefficient. When the coupling temperature rise influence coefficient is greater than the updated preset coupling temperature rise influence coefficient, the control module controls the alarm unit of the alarm module to alarm.

[0014] The technical solutions of the present application will be further described in detail below with the help of the accompanying drawings and examples.

[0015] Compared with the prior art, the present application has the following beneficial effects: 1. Compact structure, high space utilization: The integrated design directly integrates the metal seal inside the bearing, eliminating the installation space and connection structure of the traditional split seal, making the overall structure more compact. This integrated design is particularly suitable for space-limited engineering machinery application scenarios, effectively reducing the size of the equipment and improving the flexibility of the overall layout.

[0016] 2. Significant improvement in sealing performance: After the integration of the metal seal and the bearing, the sealing surface directly acts on the rotating part of the bearing, eliminating the assembly gap and connection error that may exist in the traditional split seal. The rubber or metal spring can automatically adjust the sealing gap according to the working state, always maintaining the best sealing state under high-speed rotation, vibration impact, and other working conditions, effectively preventing lubricating oil leakage and external contamination.

[0017] 3. Service life is greatly extended: The integrated design reduces the relative motion parts and connection links of the seal, reducing wear and failure points. The automatic compensation function of the metal seal can adapt to the thermal deformation and vibration of the shaft system, and itself generates a lubricating oil film to prevent excessive wear of the sealing surface. At the same time, the sealing medium directly acts on the lubrication system of the bearing, forming good lubrication conditions, further extending the service life of the seal and the bearing.

[0018] 4. Easy installation and maintenance: The traditional split seal requires the installation of a sealing device and a bearing separately, which has high centering accuracy and complex assembly. The integrated design regards the seal and the bearing as a whole unit, which only needs to be centered once during installation, greatly simplifying the assembly process, reducing the installation difficulty and time. When maintaining, only the entire sealing unit needs to be replaced, without disassembling the bearing, making the maintenance more convenient.

[0019] 5. High reliability in operation: The integrated structure reduces the connecting parts and mating surfaces, reducing the risk of failure caused by loose connection and changes in mating gap. The automatic compensation function of the metal seal can adapt to the thermal expansion, vibration and deformation of the bearing, maintaining stable sealing performance under various working conditions, improving the reliability and safety of the equipment.

[0020] 6. The integrated design simplifies the structure, facilitates installation and maintenance, prolongs the service life, and significantly improves the overall cost-effectiveness. It reduces spare parts inventory, maintenance time and downtime losses, and reduces the use cost throughout the production cycle.

[0021] 7. Wide range of applications: This integrated design is suitable for various harsh working conditions, such as high dust, high humidity, strong vibration, etc., and has a wide range of applications.

[0022] 8. The scheme forms an accommodation space through the groove and the support step, which accurately positions the sealing assembly in the core area of the bearing. The contact surface between the metal ring and the elastic sealing ring adopts a tapered structure, and the two ends of the tapered surface are arc-shaped concave. The taper allows the elastic sealing ring to tightly fit the tapered surface of the metal ring when it is squeezed, forming a wedge-shaped sealing surface. When vibration, temperature changes or slight movement of the shaft system occur during construction, the inclined angle of the tapered surface can guide the elastic sealing ring to automatically adjust the contact position, compensate for the sealing gap through elastic deformation, and always maintain the pressure of the sealing surface. The arc-shaped transition design at both ends of the tapered surface avoids the cutting and stress concentration of the sealing ring by traditional right-angle or sharp-angle edges, greatly reducing the wear rate and tearing risk of the sealing ring under dynamic working conditions; at the same time, the arc-shaped concave surface can guide the sealing medium to form a uniform contact pressure distribution, further improving the tightness of the sealing surface and reducing the leakage channel. BRIEF DESCRIPTION OF DRAWINGS

[0023] The accompanying drawings are included to provide a further understanding of the application, and constitute a part of the specification, together with the embodiments of the application, to explain the application, and do not constitute a limitation on the application. In the drawings: Figure 1 It is the overall structure schematic diagram of the bearing sealing structure of the application.

[0024] In the figure: 1. Inner ring of bearing; 11. Groove; 111. Auxiliary conical surface one; 12. Extension; 2. Outer ring of bearing; 21. Support step; 211. Auxiliary conical surface two; 3. Elastic seal ring; 4. Metal ring; 41. Conical surface; 5. Rolling element; 6. Accommodation space. Detailed Implementation

[0025] The preferred embodiments of the present invention will be described below with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are for illustration and explanation only and are not intended to limit the present invention.

[0026] Furthermore, in this invention, the use of terms such as "first" and "second" is for descriptive purposes only and does not specifically refer to any order or sequence, nor is it intended to limit the invention. They are merely used to distinguish components or operations described using the same technical terms and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the technical solutions and features of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. If a combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0027] The present invention provides the following embodiments: Example 1: This embodiment of the invention provides a sealing structure for the bearing of a miniature pipe jacking cutting head, such as... Figure 1 As shown, the bearing includes an inner ring 1, an outer ring 2, and rolling elements 5 (the positions and connections of the components and the bearing structure other than the sealing structure are existing technologies), as well as an elastic sealing ring 3 and a metal ring 4. An extension 12 is provided on the upper part of the inner ring 1 of the bearing, and a groove 11 is provided at the lower end of the extension 12 of the inner ring 1 of the bearing. A support step 21 is provided on the upper part of the outer ring 2 of the bearing near the inner ring 1 of the bearing. After the outer ring 2 of the bearing is connected to the inner ring 1 of the bearing, the groove 11 and the support step 21 form a receiving space 6. The metal ring 4 is disposed in the receiving space 6. An elastic sealing ring 3 is provided between the outer side of the metal ring 4 and the groove 11, and an elastic sealing ring 3 is also provided between the outer side of the metal ring 4 and the outer side of the support step 21.

[0028] The outer surface of the metal ring 4 that contacts the elastic sealing ring 3 is set as a conical surface 41.

[0029] Among them, the height of the end of the cone surface 41 on the upper part of the metal ring 4 near the axis is higher than the height of the end away from the axis. The height of the cone surface 41 at the lower part of the metal ring 4 near the axis is lower than the height of the end away from the axis. The contact surface of the groove 11 and the support step 21 with the elastic sealing ring 3 is auxiliary conical surface 41 and auxiliary conical surface 42 respectively, and the inclination direction of the auxiliary conical surface 41 and the auxiliary conical surface 42 is the same as the inclination direction of the corresponding conical surface 41 of the corresponding elastic sealing ring 3.

[0030] The two ends of the conical surface 41 are arc concave surfaces.

[0031] The elastic sealing ring 3 is a rubber ring, and can also be a metal spring sealing ring.

[0032] The application further discloses a micro-pipeline pipe jacking cutting machine comprising a cutting machine head, and the cutting machine head adopts the micro-pipeline pipe jacking cutting machine head bearing sealing structure.

[0033] The above technical scheme has the following beneficial effects: 1. Compact structure and high space utilization: The integrated design directly integrates the metal seal in the bearing, eliminating the installation space and connection structure of the traditional split seal, making the overall structure more compact. This integrated design is particularly suitable for space-limited engineering machinery application scenarios, effectively reducing the equipment size and improving the flexibility of the overall layout.

[0034] 2. Significant improvement in sealing performance: After the integration of the metal seal and the bearing, the sealing surface directly acts on the rotating part of the bearing, eliminating the assembly gap and connection error that may exist in the traditional split seal. The rubber or metal spring can automatically adjust the sealing gap according to the working state, always maintaining the best sealing state under high-speed rotation, vibration, and impact conditions, effectively preventing lubricating oil leakage and external contamination.

[0035] 3. Substantially extended service life: The integrated design reduces the relative motion parts and connection links of the seal, reducing wear and failure points. The automatic compensation function of the metal seal can adapt to the thermal deformation and vibration of the shaft system, and itself generates a lubricating oil film to prevent excessive wear of the sealing surface. At the same time, the sealing medium directly acts on the lubrication system of the bearing, forming good lubrication conditions, further extending the service life of the seal and the bearing.

[0036] 4. Easy installation and maintenance: The traditional split seal requires separate installation of the sealing device and the bearing, with high centering accuracy and complex assembly. The integrated design integrates the seal and the bearing as a whole unit, requiring only one centering during installation, greatly simplifying the assembly process and reducing installation difficulty and time. When maintaining, only the entire sealing unit needs to be replaced, without the need to disassemble the bearing, making maintenance more convenient.

[0037] 5. High operational reliability: The integrated structure reduces the number of connecting parts and mating surfaces, thereby reducing the risk of failure due to loose connections and changes in mating clearances. The automatic compensation function of the metal seal can adapt to the thermal expansion, vibration and deformation of the bearing, maintaining stable sealing performance under various operating conditions and improving the reliability and safety of the equipment.

[0038] 6. The integrated design simplifies the structure, facilitates installation and maintenance, prolongs the service life, and significantly improves the overall cost-effectiveness. It reduces spare parts inventory, maintenance time and downtime losses, and reduces the overall production cycle cost.

[0039] 7. Wide range of applications: This integrated design is suitable for various harsh operating conditions, such as high dust, high humidity, strong vibration, etc., and has a wide range of applications.

[0040] 8. The scheme precisely positions the sealing assembly in the core area of the bearing through the accommodating space 6 formed by the groove 11 and the support step 21. The contact surface between the metal ring 4 and the elastic sealing ring 3 adopts a tapered surface 41 structure, and the two ends of the tapered surface 41 are arc-shaped concave surfaces. The tapered surface 41 allows the elastic sealing ring 3 to tightly fit the tapered surface 41 of the metal ring 4 when it is squeezed, forming a wedge-shaped sealing surface. When vibration, temperature changes or slight shaft movement occur during construction, the inclined angle of the tapered surface 41 can guide the elastic sealing ring 3 to automatically adjust the contact position, compensate for the sealing gap through elastic deformation, and always maintain the tightness of the sealing surface. The arc-shaped transition design at both ends of the tapered surface 41 avoids the cutting and stress concentration of the sealing ring by traditional right-angle or sharp-angle edges, significantly reducing the wear rate and tearing risk of the sealing ring under dynamic operating conditions; at the same time, the arc-shaped concave surface can guide the sealing medium to form a uniform contact pressure distribution, further improving the tightness of the sealing surface and reducing the leakage path.

[0041] In embodiment 2, based on embodiment 1, the machine head operation monitoring device comprises: a main shaft detection module for detecting the rotation speed and working torque of the driving main shaft; a bearing detection module for detecting the vibration information of the bearing; a main shaft analysis module for determining the current torque-speed ratio coefficient based on the detection results of the main shaft detection module during the operation of the cutting machine head; a second construction module for constructing a torque-speed ratio coefficient trend line based on the detection results of the main shaft detection module in the second analysis period when the current torque-speed ratio coefficient is greater than the preset torque-speed ratio coefficient, and constructing a vibration amplitude coefficient trend line based on the vibration amplitude in the second analysis period; a calculation module for determining the equivalent load vibration synergy coefficient based on the construction results of the second construction module; The control module: when the current torque-speed ratio coefficient is greater than the preset torque-speed ratio coefficient, and the current equivalent load vibration synergy coefficient does not meet the preset equivalent load vibration synergy coefficient requirement, the control module controls the alarm unit of the alarm module to alarm.

[0042] 1. Rotational speed detection: real-time acquisition of the rotational speed of the driving spindle through a non-contact magneto-electric encoder or an optical encoder; Working torque detection: real-time monitoring of the torque value borne by the spindle during the cutting process through a strain torque sensor or a magneto-elastic torque sensor installed on the driving spindle transmission path.

[0043] The vibration information can adopt a high-frequency piezoelectric acceleration sensor. 2. Torque-speed ratio coefficient = (actual torque ÷ actual speed) ÷ (rated torque ÷ rated speed); Actual torque ÷ actual speed reflects the actual load corresponding to the unit speed of the cutter head under the current cutting working condition; the torque-speed ratio coefficient is 1: the current load density is completely matched with the design benchmark. The rated speed refers to the reference speed of the driving spindle when the micro-pipeline pipe jacking cutting machine can operate stably, safely and for a long time under the design working condition (the unit is usually r / min). The rated torque refers to the maximum safe torque that the driving spindle of the micro-pipeline pipe jacking cutting machine can continuously output under the design working condition.

[0044] Amplitude coefficient = actual amplitude ÷ maximum allowable amplitude of the bearing; The maximum allowable amplitude of the bearing refers to the maximum amplitude allowed by the bearing under the premise of the design life and safe operation of the equipment, which is a core index for judging whether the bearing is in a healthy operating state.

[0045] The preset torque-speed coefficient is a risk warning threshold of the torque-speed ratio coefficient determined based on the equipment design margin, material fatigue characteristics and engineering experience, and its core role is to trigger the system to enter the risk assessment process when the current torque-speed coefficient exceeds the threshold, rather than directly determining the fault. When this condition is met, the system will automatically activate analysis period two (this is a dynamic data acquisition and analysis window for high-load risk verification, which can be valued at 30S to 5min).

[0046] 3. The equivalent load vibration synergy coefficient is determined in combination with the torque-speed ratio coefficient trend line (the horizontal coordinate is the current running time of the machine head in the current operation, and the vertical coordinate is the torque-speed ratio corresponding to the horizontal coordinate) and the amplitude coefficient trend line (the horizontal coordinate is the current running time of the machine head in the current operation, and the vertical coordinate is the amplitude coefficient corresponding to the horizontal coordinate). The torque speed ratio coefficient trend line and the amplitude coefficient trend line are divided into corresponding torque speed ratio sections and amplitude coefficient sections, the time period of the corresponding torque speed ratio section and the amplitude coefficient section is the same, the average slope of each corresponding torque speed ratio section and the average slope of the amplitude coefficient section are determined; The average slope of the current torque speed ratio section: the torque speed ratio coefficient at the end of the current torque speed ratio section is subtracted from the torque speed ratio coefficient at the beginning of the current torque speed ratio section, and then divided by the time length of the current torque speed ratio section, to obtain the average change rate of the internal load density of the current torque speed ratio section.

[0047] The average slope of the current amplitude coefficient section: the amplitude coefficient at the end of the current amplitude coefficient section is subtracted from the amplitude coefficient at the beginning of the current amplitude coefficient section, and then divided by the time length of the current amplitude coefficient section, to obtain the average change rate of the bearing vibration level of the current amplitude coefficient section.

[0048] The average change rate of the average slope of the torque speed ratio section is: First, the average slopes of all torque speed ratio sections arranged in time sequence in the current analysis period two are obtained; the change rate of the average slope of adjacent two sections is calculated: the average slope of the latter torque speed ratio section is subtracted from the average slope of the former torque speed ratio section, and then divided by the interval of the starting time of the two torque speed ratio sections.

[0049] The arithmetic mean of the change rates of the average slopes of all adjacent two sections in the current analysis period two is the average change rate of the average slope of the torque speed ratio section.

[0050] The average change rate of the average slope of the amplitude coefficient of the amplitude coefficient section is: First, the average slopes of all amplitude coefficient sections arranged in time sequence in the current analysis period two are obtained; the change rate of the average slope of adjacent two sections is calculated: the average slope of the latter amplitude coefficient section is subtracted from the average slope of the former amplitude coefficient section, and then divided by the interval of the starting time of the two amplitude coefficient sections.

[0051] The arithmetic mean of the change rates of the average slopes of all adjacent two sections in the current analysis period two is the average change rate of the average slope of the amplitude coefficient section.

[0052] 4. When the average amplitude of the amplitude coefficient trend line is less than the preset amplitude, the equivalent load vibration synergy coefficient is 0; When the average amplitude of the amplitude coefficient trend line is greater than or equal to the preset amplitude, the equivalent load vibration synergy coefficient of the current analysis period two = (average change rate of average slope of torque speed ratio segment determined by the current analysis period two ÷ maximum allowable value of average change rate of average slope of torque speed ratio segment determined by analysis period two) ÷ [(average change rate of average slope of amplitude coefficient determined by the current analysis period two + maximum allowable value of average change rate of average slope of amplitude coefficient determined by analysis period two) ÷ maximum allowable value of average change rate of average slope of amplitude coefficient determined by analysis period two]; The preset amplitude here is a vibration safety benchmark value set based on the bearing vibration tolerance capacity, which is the core threshold for the system to determine whether the bearing vibration enters the risk interval.

[0053] Among them, the "maximum allowable value of average change rate of average slope of torque speed ratio segment determined by analysis period two" limits the upper limit of the acceleration of load deterioration, and the "maximum allowable value of average change rate of average slope of amplitude coefficient determined by analysis period two" limits the upper limit of the acceleration of bearing vibration deterioration; they jointly act as a normalization benchmark in the calculation formula of the equivalent load vibration synergy coefficient, and their determination needs to be combined with equipment bench test data, historical fault cases on site and industry standards, and the critical value of the deterioration rate before failure is extracted through full life cycle data.

[0054] The preset equivalent load vibration synergy coefficient requirement: the allowable range of the equivalent load vibration synergy coefficient corresponding to the current cutting head.

[0055] The equivalent load vibration synergy coefficient is focused on the synergistic change trend of the load state and the vibration state. The larger the coefficient, the higher the acceleration of load deterioration relative to the acceleration of vibration deterioration, indicating that load change is the main inducement for driving bearing vibration to exceed the standard.

[0056] The abnormal judgment of the equivalent load vibration synergy coefficient must be based on the preset allowable range, and exceeding the range is judged as an abnormal running state. Combined with the numerical deviation direction and auxiliary conditions, the specific analysis is as follows: The coefficient is higher than the upper limit of the allowable range: it means that the normalized value of the load change acceleration relative to the normalized term of the vibration change acceleration occupies too high a proportion, and it is highly probable that the dynamic load fluctuation is severe, which has become the dominant factor driving vibration deterioration, and the rate of load deterioration exceeds the safe matching threshold with vibration. Trigger load fluctuation warning immediately, and remind to optimize cutting parameters (which can be optimized based on the preset optimization strategy based on the control module) to suppress load impact.

[0057] Coefficient below the lower limit of the allowed range: indicates that the proportion of load change acceleration normalized value to vibration change acceleration normalized term is too low, and this abnormality needs to be judged in two cases: one is if the load average is in the normal interval, it means that the vibration deterioration is probably dominated by bearing faults, lubrication failure, installation deviation and other non-load factors; two is if the load average is long-term high (needs to be reduced), or the bearing is in a critical deterioration state (needs to be replaced), it may be a stable high load cumulative damage, or a small load disturbance triggering a strong coupling risk of severe vibration response, immediately triggering a bearing risk warning, increasing the frequency of vibration and lubrication state monitoring, and at the same time verifying the time correlation of load small fluctuations and vibration mutations (correlation analysis can be based on the corresponding trend line); if it is a stable high load cumulative damage, optimize the load curve and perform preventive maintenance on the bearing; if it is a bearing critical deterioration, immediately stop and replace the bearing; if it is a small load disturbance leading to vibration failure, optimize the load fluctuation suppression strategy while replacing the bearing; finally, update the experience of this time to the system model to improve the warning rules.

[0058] The coefficient is within the allowed range: whether the value is biased towards the high segment or the low segment, it is determined that the cooperative relationship between load and vibration is in the safe interval, and the device is in a stable running state. Only the existing monitoring frequency needs to be maintained, and daily operation and maintenance can be done.

[0059] The beneficial effects of the above technical solutions are: Traditional monitoring only alarms when the absolute value of load or vibration exceeds the limit, and cannot distinguish between "load fluctuation causing vibration" and "bearing fault causing vibration", often leading to blind troubleshooting and excessive maintenance by maintenance personnel. This scheme quantifies the dynamic correlation ratio of "load change acceleration" and "vibration deterioration acceleration" through equivalent load vibration cooperation coefficient, accurately positioning the dominant cause of vibration anomalies. For example: When the coefficient is higher than the upper limit, it directly points to dynamic load fluctuation as the main cause, and cutting parameters can be adjusted without the need for shutdown and inspection, reducing invalid maintenance; When the coefficient is lower than the lower limit, combined with the load average and bearing health, it can distinguish between "non-load factor dominant" and "strong coupling risk triggered by small load disturbance", avoiding misjudgment of bearing critical deterioration as normal vibration.

[0060] In pipe jacking construction, bearings often have a "small input - large output" sensitive response to small load disturbances due to long-term stable high load cumulative damage or critical deterioration. Traditional monitoring relies on absolute value thresholds and cannot capture this implicit risk. This scheme verifies the time correlation of load small fluctuations and vibration mutations, which can identify coupling risks before bearing failure, trigger preventive maintenance in advance, and avoid construction stagnation and safety accidents caused by sudden shutdown.

[0061] The scheme introduces a dynamic triggering mechanism of "analysis period two". Only when the torque-to-speed ratio coefficient exceeds the preset threshold, the high-load risk verification process is activated, avoiding excessive calculation in non-risk scenarios. At the same time, the normalized reference value (maximum allowed value of load / vibration deterioration acceleration) is dynamically calibrated based on bench tests, historical failure data and industry standards, which can adapt to different geological conditions and cutting parameters, ensuring the accuracy of risk assessment.

[0062] In embodiment 3, on the basis of embodiment 2, the bearing detection module is further used to detect the temperature of the temperature detection area of the bearing, and the machine head operation monitoring device further comprises: The construction module one is used to obtain the bearing amplitude sequence and the bearing temperature sequence constructed by the detection results of the bearing detection module in the analysis period one; The triggering condition for obtaining the sequence includes any one of the following conditions: the bearing temperature is greater than a preset temperature value (a temperature that needs to pay attention to temperature change, which can be set based on 0.8-0.85 times of the temperature safety threshold of the heat resistance limit of the bearing material, the failure temperature of the lubricating grease, and bench test data), the bearing temperature rise rate is greater than a preset temperature rise rate value, the torque-to-speed ratio coefficient is greater than a preset torque-to-speed ratio coefficient, and the periodic collection time length of the continuous tunneling steady state stage (after the equipment enters the continuous and stable tunneling state, the system automatically triggers the analysis of "analysis period one" once every fixed period (such as every 30 minutes)); The bearing analysis module is used to determine the coupling temperature rise influence coefficient based on the bearing amplitude sequence (a group of time sequences composed of bearing vibration amplitude data continuously collected in time sequence in "analysis period one"), the bearing temperature sequence (a group of time sequences composed of bearing temperature data continuously collected in time sequence in "analysis period one (which can be 30s-5min)"), and the torque-to-speed ratio coefficient. When the coupling temperature rise influence coefficient is greater than a preset value (less than the initial preset coupling temperature rise influence coefficient, which is 0.8-0.9 times the initial preset coupling temperature rise influence coefficient), the amplitude temperature rise lag coefficient is determined based on the bearing amplitude sequence and the bearing temperature sequence (when the coefficient is positive (the amplitude mutation is later than the temperature mutation), it is determined that the temperature rise drives the vibration, and the control module will automatically trigger the high-frequency lubrication of the lubrication system, check the cooling pipeline, and other targeted actions to solve the problem of thermal degradation. When the coefficient is negative (the amplitude mutation is earlier than the temperature mutation), it is determined that the vibration drives the temperature rise, and the control will directly generate a bearing disassembly inspection work order and simultaneously lock the spare parts and prompt the special tools to quickly locate the wear or installation deviation problem); When the coupling temperature rise influence coefficient is greater than a preset value (less than the initial preset coupling temperature rise influence coefficient, which is 0.8-0.85 times the initial preset coupling temperature rise influence coefficient), the calculation module determines the updated preset coupling temperature rise influence coefficient based on the amplitude temperature rise lag coefficient and the preset coupling temperature rise influence coefficient; Updated preset coupling temperature rise influence coefficient = initial preset coupling temperature rise influence coefficient × (1 - (amplitude temperature rise lag coefficient ÷ time length of analysis period one) × compensation coefficient); When the coupling temperature rise influence coefficient is greater than the preset coupling temperature rise influence coefficient (updated preset coupling temperature rise influence coefficient), the control module controls the alarm unit corresponding to the alarm module to alarm (when the coupling temperature rise influence coefficient exceeds the standard, the control module will automatically adjust the load and then link the lubrication system to actively relieve the risk).

[0063] Analysis period one: a dynamic data acquisition and analysis window specially set by the system for bearing temperature-vibration coupling risk, which will only be activated when the trigger condition is met.

[0064] The temperature difference between adjacent time points is calculated through a sliding window to obtain the instantaneous temperature rise rate. The preset temperature rise rate is the abnormal risk of temperature rise rate (the value can be 0.8-0.85 times the bearing normal thermal equilibrium state set temperature rise rate safety threshold / the maximum allowed bearing temperature rise rate).

[0065] Coupling temperature rise influence coefficient = average torque-speed ratio coefficient of analysis period two × ; The average bearing temperature rise rate is determined based on the bearing temperature sequence; the average bearing amplitude is determined based on the bearing amplitude sequence; The maximum allowed bearing amplitude refers to the safe upper limit of the vibration amplitude determined through bench test verification under the premise of guaranteeing the bearing design life and safe operation of the equipment, combined with the bearing design parameters, the actual working conditions of the pipe jacking machine, industry standards and historical failure data.

[0066] High load will directly increase the friction heat, causing the temperature rise rate to rise; temperature rise will cause bearing thermal deformation and lubrication failure, further aggravating vibration; vibration will further aggravate friction, causing the temperature rise rate to further rise. This coupling effect will cause the risk to grow nonlinearly, and the coupling temperature rise influence coefficient can more accurately reflect this risk amplification effect.

[0067] Amplitude temperature rise lag coefficient = time point corresponding to bearing amplitude peak value in amplitude sequence - time point corresponding to bearing temperature peak value in temperature sequence; The compensation coefficient is an empirical correction coefficient calibrated based on historical fault data of the equipment and field working conditions, and the value range is usually 0.1-0.5. The acquisition method is: through statistical analysis of the corresponding relationship between the amplitude temperature rise lag coefficient and the actual fault development speed of the same type of equipment under similar tunneling conditions, and combined with the real-time working conditions such as current geological hardness and main shaft speed, dynamic fine tuning is carried out. When the field working conditions are complex (such as hard rock tunneling), the compensation coefficient is taken as 0.3-0.5 to enhance the early warning sensitivity; when the working conditions are stable (such as soft soil tunneling), the compensation coefficient is taken as 0.1-0.3 to avoid over-warning, so that the updated preset coupling temperature rise influence coefficient is more in line with the actual risk, and the false alarm and missed alarm are reduced.

[0068] The beneficial effects of the above technical solutions are: The triggering condition of obtaining the sequence can actively collect data when the equipment enters a stable tunneling state, so that the system can capture the abnormal linkage of temperature, temperature rise rate and torque-speed ratio in the fault germination stage, rather than alarming when the fault develops to the obvious stage, thereby gaining valuable pre-processing time for subsequent precise intervention.

[0069] The coupling temperature rise influence coefficient integrates the related risks of load, temperature rise and vibration, avoiding the one-sidedness of single parameter monitoring; the amplitude temperature rise lag coefficient accurately distinguishes the cause and effect relationship of the fault by comparing the mutation time sequence of amplitude and temperature. When it is determined that the temperature rise drives the vibration, the system automatically triggers the high-frequency lubrication system, checks the cooling pipeline, and directly solves the root cause of thermal degradation; when it is determined that the vibration drives the temperature rise, the system directly generates a bearing disassembly inspection work order and locks the spare parts, avoiding blind inspection and making every intervention directly hit the problem core.

[0070] The system adopts a hierarchical intervention strategy: when the risk is in the 0.8-0.85 times of the early warning interval, the system actively relieves through warm means such as high-frequency lubrication and small amplitude load reduction; when the risk exceeds the updated threshold, the system triggers an alarm and automatically adjusts the load and the lubrication system.

[0071] This logic of first intervention and then alarm avoids the impact of excessive downtime on construction progress, ensuring the stability of tunneling efficiency; at the same time, the automatic adjustment of the load and the lubrication system can also inhibit the nonlinear growth of the risk in the early stage of the fault, reducing the irreversible damage to the bearing.

[0072] In any one of embodiments 1-3, the intelligent testing device further comprises: The data acquisition module is configured to acquire the torque of the main shaft, the current of the main shaft driving device, and the surface temperature of the bearing seat. Test control module: used to periodically send no-load idle speed test commands to the spindle drive device, control the spindle to run at the rated idle speed of 50-100r / min for 30 seconds, lock the cutting machine's propulsion system during the test, and synchronously collect the spindle torque detection value, the current detection value of the spindle drive device, and the surface temperature of the bearing housing under idle conditions; Calculation Module 2: Used to determine the actual torque-current balance coefficient based on the spindle torque detection value and the current detection value of the spindle drive device under idling conditions; Alarm Module 2: An alarm will be triggered when the actual torque-current balance coefficient does not meet the corresponding torque-current balance coefficient range.

[0073] Torque-current balance coefficient = ; Preset Temperature Range Reference Library: Before the equipment leaves the factory, idle speed tests are performed in multiple continuous and non-overlapping bearing housing surface temperature ranges (e.g., 20-25℃, 25-30℃, 30-35℃, etc.). The average initial torque and average initial current for each temperature range are collected and stored, forming a "temperature range - reference value" correspondence library. The average current detection value and the average spindle torque detection value of the bearing housing surface temperature range in the reference library corresponding to the current idle bearing housing temperature are the average values ​​of the target current detection value and the target spindle torque detection value.

[0074] The beneficial effects of the above technical solution are as follows: The surface temperature of the bearing housing directly reflects the thermal state of the bearing housing and may affect lubrication. The preset temperature range reference library provides a key basis for eliminating the interference of temperature on the balance coefficient.

[0075] By calculating the torque-current balance coefficient under no-load idling conditions, a direct quantitative characterization of bearing housing friction resistance is achieved. Based on the above, an early warning can be issued when the bearing housing friction resistance is abnormal, and the trend of bearing housing friction resistance change can also be judged based on the torque-current balance coefficient under no-load idling conditions.

[0076] The above method can be used as an auxiliary judgment of the bearing sealing condition. When the seal is worn, aged or damaged, external contaminants will enter the bearing and cause the frictional resistance to rise abnormally. This change will be directly reflected in the drift or sudden change of the torque-current balance coefficient. This method does not require additional sensors or offline disassembly. It can complete the sealing condition monitoring in real time and non-invasively during equipment operation, give early warning of the risk of sealing deterioration, and provide accurate basis for equipment maintenance.

[0077] The torque-current balance system directly quantifies the matching relationship between the spindle torque and the drive current, eliminating the risk of misjudgment caused by fluctuations in a single parameter, and achieving accurate characterization of the frictional resistance of the bearing housing.

[0078] Obviously, numerous modifications and variations of the present application are possible in light of the above teachings. It is therefore to be understood that within the scope of the appended claims, the application can be practiced otherwise than as specifically described herein.

Claims

1. A bearing sealing structure for a micro-pipe jacking cutting head, comprising an inner bearing ring (1), an outer bearing ring (2), and rolling elements (5), characterized in that: It also includes an elastic sealing ring (3) and a metal ring (4); An extension (12) is provided on the upper part of the inner ring (1) of the bearing. A groove (11) is provided at the lower end of the extension (12) of the inner ring (1). A support step (21) is provided on the upper part of the outer ring (2) of the bearing near the inner ring (1). After the outer ring (2) of the bearing is connected to the inner ring (1), the groove (11) and the support step (21) form a receiving space (6). The metal ring (4) is placed in the receiving space (6). An elastic sealing ring (3) is provided between the outer side of the metal ring (4) and the groove (11). An elastic sealing ring (3) is also provided between the outer side of the metal ring (4) and the outer side of the support step (21).

2. The bearing sealing structure of a micro-pipe jacking cutting head according to claim 1, characterized in that: The contact surface between the outer side of the metal ring (4) and the elastic sealing ring (3) is set as a conical surface (41).

3. The bearing sealing structure of a micro-pipe jacking cutting head according to claim 1, characterized in that: The height of the cone surface (41) on the upper part of the metal ring (4) near the axis is higher than the height of the end away from the axis; The height of the cone surface (41) at the lower part of the metal ring (4) near the axis is lower than the height of the end away from the axis.

4. The bearing sealing structure of a micro-pipe jacking cutting head according to claim 1, characterized in that: The contact surfaces of the groove (11) and the support step (21) with the elastic sealing ring (3) are the auxiliary cone surface (41) and the second auxiliary cone surface (42), respectively. The inclination directions of the auxiliary cone surface (41) and the second auxiliary cone surface (42) are the same as the inclination direction of the cone surface (41) corresponding to the elastic sealing ring (3).

5. The bearing sealing structure of a micro-pipe jacking cutting head according to claim 4, characterized in that: The two ends of the conical surface (41) are arc-shaped concave surfaces.

6. The bearing sealing structure of a micro-pipe jacking cutting head according to claim 1, characterized in that: The elastic sealing ring (3) is a rubber ring.

7. A miniature pipe jacking cutting machine, comprising a cutting head, characterized in that: The cutting head adopts a bearing sealing structure for a micro-pipe jacking cutting head as described in any one of claims 1-6.

8. A miniature pipe jacking and cutting machine according to claim 7, characterized in that: The cutting head also includes: The drive spindle is fixedly connected to the cutter head assembly and passes through the bearing sealing structure. The spindle power unit is used to drive the drive spindle. The headstock operation monitoring device is electrically connected to the main spindle power unit.

9. A miniature pipe jacking and cutting machine according to claim 8, characterized in that: The nose section operation monitoring device includes: Spindle detection module: used to detect the speed and working torque of the drive spindle; Bearing detection module: used to detect bearing vibration information and temperature; Spindle analysis module: used to determine the current torque-to-speed ratio coefficient based on the detection results of the spindle detection module during the operation of the cutting head; Module 2: Used to construct a torque-speed ratio trend line by obtaining the detection results of the spindle detection module within the analysis period two when the current torque-speed ratio is greater than the preset torque-speed ratio, and to construct an amplitude coefficient trend line by obtaining the bearing amplitude within the analysis period two. Calculation module: used to determine the equivalent load vibration coordination coefficient based on the construction results of module two; Control module: When the current torque-to-speed ratio coefficient is greater than the preset torque-to-speed ratio coefficient, or when the current equivalent load vibration coordination coefficient does not meet the preset equivalent load vibration coordination coefficient requirement, the control module controls the corresponding alarm unit of the alarm module to sound an alarm.

10. A miniature pipe jacking and cutting machine according to claim 9, characterized in that: The bearing detection module is also used to detect the temperature of the bearing's temperature detection area. The headstock operation monitoring device also includes: Module 1: Used to acquire the bearing detection results from the bearing detection module within the analysis period to construct the bearing amplitude sequence and bearing temperature sequence; The triggering conditions for obtaining the sequence include: the bearing temperature is greater than the preset temperature value, the bearing temperature rise rate is greater than the preset temperature rise rate value, the torque-speed ratio coefficient is greater than the preset torque-speed ratio coefficient, and any one of the following occurs during the periodic acquisition time of the continuous tunneling steady state stage. The bearing analysis module is used to determine the coupling temperature rise influence coefficient based on the bearing amplitude sequence, bearing temperature sequence, and torque-speed ratio coefficient. When the coupling temperature rise influence coefficient is greater than the preset value, the amplitude temperature rise lag coefficient is determined based on the bearing amplitude sequence and bearing temperature sequence. When the coupling temperature rise influence coefficient is greater than the preset value, the calculation module determines the updated preset coupling temperature rise influence coefficient based on the amplitude temperature rise lag coefficient and the preset coupling temperature rise influence coefficient. When the coupling temperature rise influence coefficient is greater than the updated preset coupling temperature rise influence coefficient, the control module controls the alarm unit corresponding to the alarm module to sound an alarm.

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