29 results about "Bearing stiffness" patented technology

The application discloses a kind of centrifugal pump shafting critical speed calculation method, including the finite element calculation of radial roller bearing and thrust roller bearing stiffness coefficient curve, the prestressed modal analysis and critical speed calculation of centrifugal pump shafting considering different bearing stiffness coefficient.The setting of constraint condition of this method is in line with actual situation, which can realize the accurate calculation of centrifugal pump shafting critical speed, and help to improve the reliability of safety check of centrifugal pump shafting in design stage, at the same time, the calculation steps are simple, and the engineering application range is wide.

To provide a dynamic pressure bearing excellent in bearing rigidity at low cost.SOLUTION: A dynamic pressure generating part P is provided on each of two radial bearings A1, A2 provided at an interval in the axial direction, and a large diameter cylindrical surface 8b having a diameter larger than that of the radial bearings A1, A2 is provided between the radial bearings LA, LA. In the dynamic pressure bearing (bearing member 8) in which the dynamic pressure generating portion P is formed of a concavo-convex surface in which a plurality of dynamic pressure grooves 10 extending in the axial direction and convex hill portions 11 are alternately arranged in the circumferential direction, one radial bearing surface A1 and the large-diameter cylindrical surface 8b are connected via a tapered surface 8c inclined with respect to the axial direction, and the other radial bearing surface A2 and the large-diameter cylindrical surface 8b are connected via a tapered surface 8d having an inclination angle with respect to the axial direction smaller than that of the tapered surface 8b. The dynamic pressure grooves 10 formed in the A2 of the other radial surface are open to the 8d of the tapered surface.SELECTED DRAWING: Figure 4

This invention belongs to the field of air bearing technology and discloses a tilting pad air foil bearing with coordinated control of PZT and a bridge amplification mechanism. It includes a top foil, a corrugated foil sleeved outside the top foil, a bushing sleeve sleeved outside the corrugated foil, a through groove on the bushing, a PZT placed within the through groove, a bridge amplification mechanism connected to the PZT, and the bridge amplification mechanism connected to the tilting pad via a flexible hinge. The tilting pad contacts the corrugated foil, the PZT is connected to a power supply device, and the power supply device is connected to a controller. The advantages of this invention include oil-free lubrication, low friction loss, high rotational speed, adjustable bearing clearance, and adjustable bearing stiffness.

The invention discloses a non-coplanar multi-guide-rail error homogenization mechanism research test platform which comprises a base, a cross beam, a rolling linear guide rail pair, a sliding block, a ball screw, a servo motor, a sliding plate and the like. In the invention, the test bench is driven by the servo motor to drive the ball screw to rotate, and the ball screw drives the sliding plate, namely the workbench to move left and right on the guide rail along the guide rail, so that the processing process is realized. The device provided by the invention meets the experimental research of error homogenization, and has the innovation point that the non-coplanar multiple guide rails are symmetrically arranged up and down, so that the error homogenization mechanism test of the machine tool is met. Through the working stroke of left and right feeding of the workbench, the test bench can be used for testing geometric assembly errors on a numerical control machine tool, assembly errors of a lead screw, rigidity of a sliding block, rigidity of a bearing and the like, meets error homogenization mechanism tests, and is worthy of popularization and application.

The invention discloses a bearing rigidity indirect measurement method and system based on system error compensation, and the method comprises the following steps: installing a standard sample block in a test system, applying an axial load, measuring a first deformation amount of the standard sample block under each stage of load, and recording the first deformation amount as a system deformation amount; installing a measured bearing, applying axial loads of all levels which are the same as the axial loads of the step S1, measuring a second deformation amount of the measured bearing, and recording the second deformation amount as a total deformation amount; according to the obtained total deformation amount and the system deformation amount, calculating the real deformation amount of the measured bearing under each level of load; and determining a load-deformation function relationship based on a corresponding relationship between each stage of axial load and the real deformation amount, and obtaining the rigidity of the measured bearing. Compared with the prior art, the standard sample block is introduced for comparison testing, a system error compensation mechanism is innovatively provided, errors caused by self deformation of a testing system can be accurately eliminated, the real deformation amount of the bearing is obtained, the rigidity measurement precision is greatly improved, and the method is particularly suitable for accurate calibration of the high-rigidity bearing.

This invention provides an adjustable stiffness foil gas dynamic pressure bearing, comprising: a top foil, a first foil, an SMA foil group, a second foil, a bearing sleeve, a cooling plate, and a heat sink; wherein, the first foil and the second foil are each composed of two longitudinal beams connected at the ends of circumferentially distributed V-shaped beams, the circumferential length of the V-shaped beam of the first foil is less than the gap between two adjacent V-shaped beams of the second foil, and the V-shaped beam of the first foil is placed between the two V-shaped beams of the second foil; the SMA foil group is composed of a first SMA foil, an electrically controlled heating film, and a second SMA foil stacked sequentially, located in the middle of the first foil and the second foil, and its axial width is less than the axial width of the V-shaped beams of the first foil and the second foil; the cold end of the electrically controlled cooling plate is in close contact with the V-shaped beam of the second foil, and the hot end is connected to the heat sink; the top foil provides the bearing surface for the dynamic pressure gas film, and the bearing sleeve supports and fixes all components. This application achieves active adjustment of bearing stiffness by rapidly adjusting the elastic modulus of SMA foil through an electrically controlled heating film and cooling plate, thus solving the technical problem that existing foil gas dynamic bearings cannot cross critical speeds and ultra-high speed instability. The circumferentially spaced V-shaped beams enable the top foil and SMA foil group to participate in structural deformation as simply supported beams, improving impact resistance and durability. Under load, the top foil forms a V-shaped depression, producing a gas-gathering effect similar to that of grooved bearings, thereby improving the bearing's load-bearing capacity.

This invention discloses a semi-analytical method and system for calculating the stiffness and damping coefficients of foil gas dynamic bearings, relating to the field of air conditioning and clothing temperature control technology. It aims to address the shortcomings of traditional Reynolds equation methods in terms of accuracy and universality, as well as the low computational efficiency and mesh distortion issues of existing CFD methods. The method includes: constructing a fluid-structure interaction (FSI) computational model to calculate and obtain the static equilibrium position of the journal; applying an eccentricity perturbation at the static equilibrium position and performing an additional steady-state FSI calculation to obtain the four stiffness coefficients of the foil bearing using a first set of analytical formulas; applying small-amplitude simple harmonic vibrations along the x and y directions to the journal and performing two transient FSI calculations to obtain the four damping coefficients of the foil bearing using a second set of analytical formulas. This invention combines high accuracy and high computational efficiency, providing an efficient and reliable analytical tool for evaluating the dynamic characteristics of foil bearings and designing the stability of the rotor systems they support.

The invention provides a nonlinear vibration coupling analysis method for an aerostatic spindle under sliding mode control, and relates to the technical field of machine tool precision machining. A multi-degree-of-freedom system dynamics model is constructed by performing nonlinear coupling calculation on gas film force, unbalanced magnetic pulling force and mass eccentric excitation. Time-varying nonlinearity of bearing rigidity is accurately described through calculation of dynamic air film force, the two-way coupling effect between an electromagnetic field and mechanical motion is revealed through introduction of unbalanced magnetic pulling force, and complex combined frequency vibration can be generated through interaction of mass eccentricity serving as classical external synchronous excitation and the two kinds of internal excitation. According to the method, the controller design can consider and compensate the nonlinear time variation of the gas film force, the state dependence disturbance of the magnetic pulling force and the eccentric force excitation in advance, the reverse influence of the control action on the gas film stability and the electromagnetic field can be evaluated, and the real mechanical-electric-gas-control collaborative optimization is realized.

The invention discloses a vertical bearing seat capable of quickly adjusting bearing pre-tightening force, and relates to the technical field of bearing seats. When a main shaft bearing seat is used, pretightening force needs to be adjusted through a test so as to adjust the relation between the rigidity of a bearing and the temperature of the bearing, a method for replacing a pretightening elastic element is usually adopted for adjusting the pretightening force, and the process is time-consuming and labor-consuming. In order to solve the problem that the elastic pre-tightening force of a bearing cannot be quickly adjusted when the bearing seat is used, a power transmission rotating structure, a lubricating oil supply and return passage and a pre-tightening force adjusting structure are designed and invented, and the bearing seat applying the structure solves the problems that a shaft system needs to be disassembled and an elastic element needs to be replaced when the pre-tightening force of the bearing is adjusted. The invention is suitable for the technical field of bearing pedestals.

The present application relates to the technical field of bearing detection, in particular to a kind of hub bearing rigidity test tool based on real vehicle steering knuckle, including tooling table, it is equipped with tooling assembly on it, it further includes loading flange plate, universal joint, it is arranged in the center of the loading flange plate, axial loading rod, it is along the axial direction of the loading flange plate and is arranged, radial loading rod, it is along the radial direction of the loading flange plate and is arranged, vertical slide rail and horizontal slide rail, the vertical slide rail is fixed to the tooling table, the vertical slide rail is slidably provided with sliding frame for installing the axial loading rod, the horizontal slide rail is fixed to the sliding frame, the radial loading rod is slidably arranged on the horizontal slide rail.The present application is rigidly fixed to tooling table by real vehicle steering knuckle, and is rigidly connected with hub bearing using loading flange plate, in combination with universal joint, so that axial load is stably transmitted and additional bending moment generated due to the inclination of flange plate can be released.

The invention belongs to the field of CARB bearing radial stiffness and elastohydrodynamic lubricating oil film stiffness, and discloses a stiffness calculation method applied to a full-complement CARB bearing of an icebreaker under a low-speed working condition, and the method comprises the steps: building a full-complement CARB bearing stiffness analysis model based on a structure of slice hierarchy-roller hierarchy-bearing hierarchy; and the rigidity of the full complement CARB bearing is solved by combining series coupling and parallel integration. According to the rigidity calculation method, the limitation that a traditional algorithm can only process ideal centering is broken through, the load unbalance loading effect and local oil film rigidity change of the bearing under the non-centering and heavy-load working conditions can be accurately quantified, therefore, the stress concentration risk of the roller edge is effectively recognized, refined modification of the roller convexity is guided, and the precision of the roller convexity is improved. And a nonlinear stiffness parameter conforming to a real physical state is provided for shafting dynamics simulation, and the reliability of bearing life prediction and structural design under a special working condition is remarkably improved.

The present application relates to air bearing test technical field, especially to a kind of air bearing stiffness testing device and method, including test table, air bearing installation mechanism, gas film gap adjusting mechanism, levelness adjusting mechanism and measurement system;Air bearing installation mechanism is invertedly installed on the top of test table, and gap detection assembly is provided on air bearing installation mechanism;Gas film gap adjusting mechanism is set in test table and is just for the below of air bearing installation mechanism;Levelness adjusting mechanism includes at least three flexible hinges, and flexible hinge is distributed between fixed seat and bearing platform in three-point support;Measurement system includes control unit, control unit is integrated with closed-loop control algorithm, and is connected with gap detection assembly, gas film gap adjusting mechanism communication respectively.The present application realizes micron gas film gap control by innovative gas film gap adjusting mode, levelness guarantee structure and air bearing installation mechanism inverted design, and significantly improves stiffness test precision.

This invention discloses an origami structure possessing both load-bearing and energy-absorbing properties, belonging to the field of buffer structure technology. The structure includes an outer sleeve and an inner sleeve. The inner sleeve is fixed to a top plate and a bottom plate at both ends, respectively. The outer sleeve is coaxially fitted with the inner sleeve, and its ends slide against the top and bottom plates, respectively. Both the outer and inner sleeves are origami tubes with pre-defined crease lines distributed circumferentially and axially on their surfaces. These crease lines form a periodic, inclined grid, allowing for regular torsional and folding deformation under axial compression. During the load-bearing stage, the crease directions of the outer and inner sleeves are staggered to provide axial load-bearing stiffness and bending stiffness. During the energy-absorbing stage, the outer and inner sleeves move relative to each other until their crease directions are aligned, allowing them to fold and deform along the creases to absorb impact energy. This structure integrates both load-bearing and buffering mechanical properties through the relative change in the crease directions of the inner and outer sleeves.

This invention proposes an automated testing line for multi-dimensional parameters of rolling bearings and a method for evaluating the grade of rolling bearings. The testing line includes a control system, a conveyor belt device connected to the control system, and a robotic arm device located outside the conveyor belt device. Along the length of the conveyor belt device are modules for testing rolling bearing stiffness, radial clearance, and vibration characteristics. By incorporating the conveyor belt device and robotic arm device, this invention can automatically detect parameters such as radial and axial support stiffness, radial clearance, and vibration characteristics of rolling bearings. In actual production, this invention can replace some single-function bearing performance testing devices, reducing or eliminating the need for manufacturers to construct additional rolling bearing testing and screening lines. This invention can promptly identify and screen out unqualified bearings, helping companies improve product quality and achieve the effects of reducing costs and increasing production efficiency.

[Problem to be solved] To achieve an improvement in the layout flexibility for a drive unit while simultaneously ensuring the bearing stiffness of the drive unit. [Solution] An electric vehicle rear structure (100) comprises a rear floor panel (1) arranged above a drive unit (M), a pair of rear side elements (2, 2), several motor mounts (7), and an intermediate element (3) arranged between the pair of rear side elements (2, 2) and extending longitudinally along a lower surface of the rear floor panel (1). The rear floor panel (1) has an upper convex section (1a) that curves towards the top of the vehicle and a peripheral section (1b) that surrounds a perimeter of the upper convex section (1a). The intermediate element (3) is connected to a sidewall adjacent section (1b1) of the peripheral section (1b), the sidewall adjacent section (1b1) conforming to a sidewall (1a3) on one side of the upper convex section (1a) in the vehicle width direction. One target motor mount (7x) of the multiple motor mounts (7) is supported by the intermediate element (3).The drive unit (M) is located below the upper curved section (1a) and between a rear side element (2) of the paired rear side elements (2, 2) and the intermediate element (3) at the rear of the vehicle.

The invention relates to the technical field of safety control of high-speed direct drive units, in particular to an active anti-surge system and method for a magnetic suspension air blower, and the active anti-surge system and method for the magnetic suspension air blower are characterized in that vibration energy within 0.2-0.8 times of rotor fundamental frequency is extracted as surge energy by collecting rotor vibration signals in real time and performing spectral analysis; the surge signal is compared with an early warning threshold value, and a surge mark is generated; once early warning is carried out, the bias current of the magnetic bearing is dynamically adjusted to improve the rigidity, and the emergency shutdown threshold values of vibration and displacement are synchronously lowered; and meanwhile, the difference value between the actual operation flow and the surge boundary flow is continuously monitored, and opening and closing of an emptying valve are controlled in a grading mode in combination with surge marks. The method comprises the following steps: capturing the impending surge characteristics in advance through vibration spectrum analysis; the anti-surge curve and the dynamic safety margin are fused, and magnetic bearing rigidity-damping cooperative adjustment is achieved; and in an emergency, a forced emptying hard safety loop is established, and a graded active protection system is formed.

The invention belongs to the field of bearing structural mechanics, and relates to a single-row tapered roller bearing statics calculation method and system taking shaft deformation influence into account. Through roller axial slicing treatment, a mapping relation between slice deformation and bearing overall displacement is established, and a bearing stiffness matrix is deduced according to a binding force balance condition; a bearing-shaft coupling statics model is constructed based on the Euler beam unit theory, and system steady-state displacement is solved through iteration; and finally, calculating roller slice load and contact stress distribution according to the steady-state displacement. The method does not need to depend on a complex partial differential or numerical difference method, the calculation process is simplified, the result stability is improved, shaft deformation and multi-factor comprehensive influence are accurately considered, and reliable data support is provided for bearing structure optimization and service life evaluation.

The application belongs to the field of bridge structure vibration test and safety detection and evaluation, and particularly relates to a simply supported beam bridge bearing stiffness rapid test and evaluation method based on local vibration mode. A small number of acceleration sensors are arranged in the cross-bridge direction of the mid-span section of the simply supported beam bridge during the test. The first three orders of frequencies of the environment excitation bridge and the local vibration mode of the main beam are tested under the condition that the bridge traffic is not interrupted. The shape of the first three orders of local vibration modes is usually characterized by "one flat, two inclined and three curved" in the cross-bridge direction. Then, the displacement flexibility matrix of the main beam structure is calculated and identified in combination with the finite element model, the actual modal deflection of the mid-span measuring point of the bridge under the equivalent load of the static load test is predicted, the deflection checking coefficient of the main beam is calculated according to the actual modal deflection value of the mid-span measuring point of the bridge and the theoretical design deflection value, and whether the actual bearing state of the bridge structure meets the design requirements is judged. The method has the advantages that the detection and evaluation rate of the bearing state of the bridge is improved, the detection cost is reduced, and the bridge traffic does not need to be interrupted.

The application relates to the technical field of bearing detection, in particular to a rolling bearing stiffness identification method based on vibration response, which comprises the following steps: acquiring a measured vibration signal of a rolling bearing, and determining an estimated stiffness value based on a pre-constructed physical information neural network (PINN) model; calculating a time-varying effective contact stiffness which changes with the position of an inner rolling body of the rolling bearing and the fault position of an inner and outer ring; establishing a two-degree-of-freedom time-varying stiffness dynamics model according to the time-varying effective contact stiffness, in combination with an equivalent damping coefficient and an external force, so as to determine a simulation vibration signal of a fault bearing according to the estimated stiffness value; constructing a total loss function of the PINN model, which comprises a consistency loss determined by the root mean square value and the wave crest factor difference of the simulation vibration signal of the fault bearing and the measured vibration signal, and a boundary loss determined by the difference between the estimated stiffness value and a preset boundary condition; and iteratively optimizing the PINN model based on the total loss function to obtain a target identification stiffness value.

The application discloses a model for identifying dynamic stiffness of a turbine pump rotor bearing, which is used for improving the accuracy of dynamic parameter design of the turbine pump rotor bearing, supporting high-speed, high-power and long-time stable operation of the turbine pump rotor, and providing important support for design of a liquid rocket engine turbine pump rotor.

The present application relates to a kind of parameterized evaluation prediction methods of wheel hub bearing stiffness, comprising: step 1, the structural parameterization of the influence wheel hub bearing stiffness is parameterized, the design space of wheel hub bearing stiffness parameter is established, and a series of design schemes are determined;Step 2, the method for establishing finite element simulation model is simulated stiffness test test, and the stiffness simulation of series design scheme is carried out using finite element simulation model;Step 3, according to the simulation result of step 2, construct the neural network model for predicting and evaluating wheel hub bearing stiffness and carry out training;Step 4, the accuracy of the neural network model established in step 3 is verified and prediction is carried out.The present application can quickly predict the product stiffness in the design link, without needing to carry out stiffness test to all design products, greatly improve the design efficiency, reduce cost, short cycle, conducive to the development of multi-species small batch products.

The application discloses a high-speed porous gas bearing main shaft for a hard turning and grinding machine tool, which comprises a main shaft base, a main shaft rotating body and a main shaft fixing part arranged in the main shaft base, the main shaft rotating body comprises a main shaft, a torque motor and an encoder, and the main shaft fixing part comprises a front end shaft sleeve, a rear end shaft sleeve, a thrust graphite sheet, a radial graphite sleeve one and a radial graphite sleeve two. The porous graphite throttle structure is adopted, and the porous graphite material is specifically applied to the key throttle components, i.e. the thrust graphite sheet, the radial graphite sleeve one and the radial graphite sleeve two, so that the traditional discrete small-hole throttle structure is replaced, the bearing stiffness and dynamic stability under the high-speed working condition are effectively improved, the gas hammer instability phenomenon is obviously inhibited, the risk of the main shaft seizure during high-speed operation is reduced, the main shaft can still maintain high rotation accuracy and good operation reliability above 30000 rpm, and the high-speed, high-precision and high-stability use requirements of the hard turning and grinding composite machining are better met.

The invention relates to the technical field of bearing measurement, in particular to a multi-parameter collaborative measurement method and system for a hydrostatic bearing, and the method comprises the steps: dividing a contour boundary region and a sealing oil bearing region based on the geometric contour of a bearing oil cavity; selecting discrete calculation position points, and executing local rigidity component acquisition; integrating the rigidity components, constructing a pressure control equation set, and solving to obtain global pressure distribution of the sealing oil bearing area; performing flow dynamic calculation on each oil cavity to obtain three-way fluid output parameters; calculating a theoretical flow value of each oil cavity based on the global pressure distribution, performing deviation comparison with the total flow output by the three-way fluid, and controlling an iterative updating process of an oil supply pressure value; and according to the oil supply pressure value after iteration convergence, generating a bearing rigidity performance parameter and a flow parameter of each oil cavity system. According to the invention, the technical problem of inaccurate detection of thermal parameter dynamic coupling drift and structure inflection point flow field of the hydrostatic bearing in the existing hydrostatic bearing test is effectively solved.

The application provides a large-deformation high-load-bearing flexible skin structure and a preparation method thereof. The flexible skin structure comprises a skeleton structure with a three-dimensional zero-Poisson's ratio deformation characteristic and an elastic matrix filling or covering the skeleton structure. The skeleton structure is composed of two layers of panel structures with a zero-Poisson's ratio deformation characteristic and a plurality of vertical plate structures with a zero-Poisson's ratio deformation characteristic connected between the two layers of panel structures. The skeleton structure extends the two-dimensional zero-Poisson's ratio effect to three-dimensional space, so that when the structure is stretched / compressed in the plane, large displacement can be achieved through the coordinated deformation of the internal mechanism, while the transverse shrinkage in the plane is inhibited, the efficiency and stability of the deformation are ensured. The application has excellent in-plane large-deformation capacity, high normal load-bearing stiffness and smooth continuous outer surface. The application can meet the actual use requirements of future advanced aircrafts.

The invention discloses a square pipe jacking well structure convenient to assemble on site, relates to the field of municipal pipelines, and aims to solve the problems that in the background technology, when huge horizontal thrust generated by pipe jacking is borne, brittle failure is prone to occurring, potential safety hazards exist, the positioning precision between modules is difficult to guarantee, splicing seams are not tight, the integrity is poor, and the construction cost is low. According to the scheme, the structure comprises a bottom plate composed of a plurality of bottom plate modules, the bottom plate modules are steel reinforced concrete with the two sides provided with 45-degree positioning slopes, clamping grooves are formed in the outer walls of the two sides of the top of each bottom plate module, and two positioning holes are formed in the inner walls of the bottoms of the two clamping grooves; two limiting rods are embedded in the two sides of each bottom plate module correspondingly, and a fixing mechanism is arranged between every two adjacent bottom plate modules. According to the invention, the overall rapid assembly can be realized, and meanwhile, the integrity of a bottom plate system, the force transmission performance in the horizontal direction and the bearing rigidity and stability of an end structure can be improved.

The invention discloses a method for controlling the critical rotating speed of a rotor by adjusting the rigidity of a bearing supporting system, and relates to the field of heavy rotating equipment with a bearing support. The method for controlling the critical rotating speed of the rotor by adjusting the rigidity of the bearing supporting system comprises the following steps that a rigidity model of the bearing supporting system is built, a rigidity calculation point is marked as O1, and supporting points at the two ends are marked as O2 and O3; collecting the distance a between the O1 and the O2, and collecting the distance b between the O1 and the O3; the bearing rigidity K2 at the O2 position is collected, and the bearing rigidity K3 at the O3 position is collected; according to a, b, K2 and K3, the bearing supporting rigidity K0 at the position of O1 is obtained; the rigidity KM1 borne by the mass M1 at the position O1 is obtained according to the bearing supporting rigidity K0 at the position O1 and the transverse rigidity K1 of the shaft at the position O1; and obtaining the critical rotating speed of the rotor according to the M1 and the KM1. According to the method, the rigidity borne by the mass of the point is calculated, the critical rotating speed of the rotor is obtained, the critical rotating speed of the rotor can be controlled by adjusting the rigidity of a bearing supporting system, and resonance is avoided.

The invention discloses an electromagnetic bearing rigidity parameter identification method and system. The method comprises the steps of obtaining operation data of an electromagnetic bearing rotor; determining an electromagnetic estimation force of the electromagnetic bearing based on the operation data and a preset electromagnetic force observation model; carrying out feature component extraction on the electromagnetic estimated force, and determining an electromagnetic feature force and a feature moment corresponding to the electromagnetic feature force; based on the characteristic moment, an identification data set aligned with the time sequence of the electromagnetic characteristic force is determined, and the identification data set comprises current data and displacement data; based on the identification data set and a preset rigidity model, determining output force of the rigidity model; determining an identification error based on the stiffness model output force and the electromagnetic characteristic force; and based on the identification error and a self-adaptive iterative algorithm, carrying out iterative updating on the current stiffness parameter and the displacement stiffness parameter in the stiffness model, and determining the stiffness parameter of the electromagnetic bearing after convergence. The method has the technical effect of accurately identifying the rigidity parameter of the electromagnetic bearing on line.

The invention relates to the technical field of bearing rigidity measurement, in particular to a bearing rigidity measuring device which comprises a test bed arranged at the bottom. Through grooves which are evenly distributed are formed in the long edge direction of the top face of the test bed, a tested bearing is arranged on the top face of the test bed, an axial rigidity measuring mechanism is arranged behind the tested bearing, and a radial rigidity measuring mechanism is arranged on the side of the tested bearing. The axial rigidity measuring mechanism comprises a vertical plate A which is vertically arranged at the top of the test bed; the middle part of the vertical plate A is connected with a horizontal vertical plate which is horizontally arranged through a bolt; and a lead screw motor A is further arranged at the top of the vertical plate A. The axial and radial rigidity of the bearing to be measured can be measured, the acting force generated by opposite movement and mutual extrusion of the inclined sliding blocks and the force generated by expansion of the piezoelectric ceramic displacement device are transmitted to the shaft system, accurate loading of axial and radial loads is achieved, and real-time and accurate control can be achieved.