WO2020034338A1 - 轴承动态特性试验机 - Google Patents

轴承动态特性试验机 Download PDF

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Publication number
WO2020034338A1
WO2020034338A1 PCT/CN2018/108518 CN2018108518W WO2020034338A1 WO 2020034338 A1 WO2020034338 A1 WO 2020034338A1 CN 2018108518 W CN2018108518 W CN 2018108518W WO 2020034338 A1 WO2020034338 A1 WO 2020034338A1
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WO
WIPO (PCT)
Prior art keywords
bearing
axial
main shaft
radial
testing machine
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Application number
PCT/CN2018/108518
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English (en)
French (fr)
Inventor
郑子勋
郑懿焜
郑蕾婷
Original Assignee
浙江优特轴承有限公司
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Application filed by 浙江优特轴承有限公司 filed Critical 浙江优特轴承有限公司
Publication of WO2020034338A1 publication Critical patent/WO2020034338A1/zh

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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/04—Bearings

Definitions

  • the invention belongs to the technical field of bearings and relates to a bearing dynamic characteristic testing machine.
  • the Chinese patent discloses an alternating load loading device for a bearing testing machine based on a screw drive mechanism [application number: 201711457298.9], including a rotating shaft. A bearing is mounted on the rotating shaft.
  • the loading device includes a clamp, and a plurality of rotary motors-screw transmission mechanisms-spring assemblies are arranged around the clamps. Each rotary motor-screw transmission mechanism-spring assembly includes sequentially connected rotary motors.
  • Screw drive mechanism and spring in which the screw drive mechanism includes couplings, screw bearings, screw nuts, screw and bearing seat, rotary motor drives the screw drive mechanism to move, control the spring to stretch or compress deformation, Apply an alternating load to the tested bearing in the fixture.
  • An object of the present invention is to provide a bearing dynamic characteristic testing machine in view of the above problems.
  • the present invention adopts the following technical solutions:
  • a bearing dynamic characteristic testing machine includes a driving mechanism, wherein the driving mechanism is connected to a main shaft so as to drive the main shaft to rotate in a circumferential direction.
  • the main shaft is located inside the fuselage and a bearing assembly is sleeved on the main shaft.
  • the end force applying mechanism that moves in the direction of the end of the main shaft so as to contact the end of the main shaft and apply pressure to the end of the main shaft further includes a displacement sensor connected to the main shaft.
  • the end force applying mechanism includes an axial force applying component capable of reciprocating in a horizontal direction, and the axial force applying component corresponds to an end surface of the main shaft.
  • the axial force applying component includes an axial screw rod disposed horizontally, and an axial driver connected to the axial screw rod so as to drive the axial screw rod to reciprocate in the horizontal direction.
  • a first load sensor is provided at an end of the axial screw rod.
  • an axial buffer is provided at an end of the axial screw rod, and the first load sensor is located on the axial buffer.
  • the axial buffer includes an axial joint fixedly connected to the axial screw rod, and an axial elastic seat is movably connected to the axial joint, and the first load sensor It is fixed on the axial elastic seat.
  • the axial elastic seat is set on an axial joint, the axial elastic seat is engaged with an axial positioning collar, and the axial positioning collar and the axial The end of the joint is close to the axial screw.
  • the axial joint is provided with a plurality of axial elastic member receiving grooves.
  • the axial elastic member receiving groove is provided with an axial elastic member. Both ends of the member abut against the inner walls of the axial elastic seat at the bottom of the axial elastic member receiving groove, respectively.
  • the end force applying mechanism includes a radial force applying component capable of reciprocating in a vertical direction, and the radial force applying component is located above the end of the main shaft.
  • the radial force applying component includes a radial screw that is vertically arranged, and a diameter connected to the radial screw to drive the radial screw to reciprocate in the vertical direction.
  • a second load sensor is provided at the end of the radial screw.
  • a radial buffer is provided at an end of the radial screw rod, and the second load sensor is located on the radial buffer.
  • the radial buffer includes a radial joint fixedly connected to a radial screw rod, and a radial elastic seat is movably connected to the radial joint, and the second load sensor It is fixed on the radial elastic seat.
  • the radial elastic seat is set on a radial joint, and the radial positioning seat is engaged with a radial positioning collar, and the radial positioning collar and the radial The end of the joint is close to the radial screw.
  • the radial joint is provided with a plurality of radial elastic member receiving grooves.
  • the radial elastic member receiving groove is provided with a radial elastic member. Both ends of the piece abut against the inner wall of the radial elastic seat at the bottom of the receiving groove of the radial elastic piece.
  • the main shaft end is provided with a static force component
  • the static force component is provided with a static holding bearing connected to the main shaft end and capable of rotating synchronously with the main shaft.
  • the static force component includes a rotary base connected to the end of the main shaft, and a static base sleeved on the rotary base.
  • the static holding bearing is located between the rotary base and the static base.
  • the inner ring of the holding bearing is fixedly connected to the rotating seat, and the outer ring of the static holding bearing is fixedly connected to the static seat.
  • the bearing assembly has two and is located at both ends of the main shaft, the fuselage includes a bearing sleeve sleeved outside the bearing component, and the bearing sleeve is provided with a control Temperature element.
  • the temperature control element includes an electric heating rod disposed in the bearing sleeve, and a cooling jacket corresponding to the position of the bearing component.
  • the cooling jacket is located inside the bearing sleeve, or the bearing sleeve and the outer wall of the bearing assembly surround to form a cooling jacket.
  • a cooling medium channel connected to a cooling jacket is provided in the bearing sleeve.
  • the bearing assembly includes a plurality of main shaft bearings provided on the main shaft, a bearing fixing sleeve placed outside the main shaft bearings, and a plurality of temperature sensors corresponding to the main shaft bearings.
  • the temperature sensor passes through the fuselage and the bearing fixing sleeve in order to directly contact the outer ring of the spindle bearing.
  • the cooperation of the axial force application component and the radial force application component can accurately simulate the force situation of the main shaft end, so as to obtain an accurate measurement of the accuracy retention time.
  • the flexible force contact between the axial force applying component and the radial force applying component and the main shaft is achieved, and the main shaft and the axial force applying component and the radial force are applied.
  • the components are protective.
  • the setting of temperature control elements can play a role in heating and cooling the bearing sleeve and bearing components, thereby simulating the working conditions in the fuselage, and measuring the accuracy retention time under different conditions.
  • the temperature sensor is in direct contact with the outer ring of the bearing, and the temperature detection is accurate.
  • FIG. 1 is a schematic structural diagram of the present invention.
  • FIG. 2 is a schematic diagram of another structure of the present invention.
  • FIG. 3 is a schematic diagram of another structure of the present invention.
  • FIG. 4 is a schematic structural diagram of a radial force applying component.
  • FIG. 5 is a schematic structural diagram of an axial force applying component.
  • FIG. 6 is a schematic structural diagram of a static force component.
  • drive mechanism 1 frame 1a, main shaft 2, fuselage 3, bearing assembly 4, end force mechanism 5, displacement sensor 6, axial force assembly 7, axial screw 8, axial drive 9 ,
  • the first load sensor 10 the axial buffer 11, the axial joint 12, the axial elastic seat 13, the axial positioning collar 14, the axial elastic member receiving groove 15, the axial elastic member 16, radial force Component 17, radial screw 18, radial driver 19, second load sensor 20, radial buffer 21, radial joint 22, radial elastic seat 23, radial positioning collar 24, and radial elastic piece accommodation Slot 25, radial elastic member 26, static force component 27, static holding bearing 28, rotating seat 29, static seat 30, bearing sleeve 31, temperature control element 32, electric heating rod 33, cooling jacket 34, bearing sleeve cooling The jacket 34a, the cooling medium passage 35, the main shaft bearing 36, the bearing fixing sleeve 37, and the temperature sensor 38.
  • a bearing dynamic characteristic testing machine includes a driving mechanism 1.
  • the driving mechanism 1 is a motor or a hydraulic motor, preferably a stepping motor.
  • the driving mechanism 1 is connected to the main shaft 2 so as to drive the main shaft 2 in a circumferential direction. Rotating, the main shaft 2 is located inside the fuselage 3 and a bearing assembly 4 is sleeved on the main shaft 2.
  • the main shaft 2 further includes a bearing assembly 4 capable of moving toward or away from the end of the main shaft 2 so as to contact the end of the main shaft 2 and end the main shaft 2.
  • the end force applying mechanism 5 applying pressure further includes a displacement sensor 6 connected to the main shaft 2, and the displacement sensor 6 is fixed on the fuselage 3.
  • the driving mechanism 1, the main body 3, and the end force applying mechanism 5 are all fixed on the frame 1a.
  • the displacement sensor 6 is a prior art, and a commercially available product may be adopted.
  • the end force applying mechanism 5 may be a hydraulic motor, a screw rod, a jack, or the like.
  • Suite that can exert pressure on the main shaft 2 can be used.
  • the end force applying mechanism 5 applies pressure to the end of the main shaft 2, the load on the end of the main shaft 2 can be simulated, and the displacement deviation of the main shaft 2 obtained by the displacement sensor 6 can reflect that the main shaft 2 can maintain accuracy under a certain load state The holding time within the qualified range, so as to obtain the holding time of the spindle 2 and the bearing assembly 4 under the load state.
  • the end force applying mechanism 5 includes an axial force applying component 7 capable of reciprocating in the horizontal direction.
  • the axial force applying component 7 corresponds to the end surface of the main shaft 2.
  • the end force applying mechanism 5 further includes a radial force applying component 17 capable of reciprocating in the vertical direction, and the radial force applying component 17 is located above the end of the main shaft 2.
  • the axial force applying component 7 can apply pressure to the end surface of the main shaft 2 to simulate the axial force of the main shaft
  • the radial force applying component 17 can apply pressure to the outer wall of the end of the main shaft 2 to simulate the main shaft 2 Radial force, the combination of the two forces, can fully reflect the load situation of the main shaft in actual work, so as to obtain a more accurate and reliable measurement of the accuracy retention time.
  • the axial force applying assembly 7 includes an axial screw rod 8 arranged horizontally, the axial screw rod 8 is sleeved with a screw sleeve, and further includes an axial screw rod 8 connected to drive the shaft.
  • An axial driver 9 reciprocating in a horizontal direction to the screw rod 8 the axial driver 9 is a motor or a hydraulic motor, preferably a stepper motor, and the axial screw rod 8 and the axial driver 9 may be connected by a pulley or a gear.
  • the load sensor is also called a load cell or a load cell sensor. It is a prior art and a commercially available product can be used.
  • An axial buffer 11 is provided at an end of the axial screw rod 8, and the first load sensor 10 is located on the axial buffer 11.
  • the first load sensor 10 can obtain a specific value of the load.
  • the axial buffer 11 is elastic and can be deformed, and can deform after the screw rod contacts the main shaft, preventing the axial screw rod 8 or the first load sensor 10 from rigidly colliding with the main shaft 2, so that the axial screw rod 8, the first A load sensor 10 and the main shaft 2 play a protective role.
  • the axial buffer 11 may be a spring or an elastic washer, and both ends thereof are respectively connected to the end of the axial screw rod 8 and the first load sensor 10 so as to play a buffering effect.
  • the axial buffer 11 includes an axial joint 12 fixedly connected to the axial screw rod 8, and an axial elastic seat 13 is movably connected to the axial joint 12.
  • the axial elastic seat 13 can move back and forth along the axial line of the axial joint 12 to play a buffering role.
  • the first load sensor 10 is fixed on the axial elastic seat 13, specifically, it is fixed on the axial elastic seat. 13 on the outer wall.
  • the axial elastic seat 13 is sleeved on the axial joint 12.
  • the axial elastic seat 13 is engaged with an axial positioning collar 14.
  • the axial positioning collar has a ring shape and plays a positioning role to prevent the axial elastic seat 13 from detaching.
  • An axial joint 12, the axial positioning collar 14 is engaged with an end of the axial joint near the axial screw 8, and the axial joint 12 is provided with a plurality of axial elastic member accommodation slots 15, and the shaft
  • An axial elastic member 16 is provided in the elastic member receiving groove 15, and both ends of the axial elastic member 16 abut against the inner wall of the axial elastic seat 13 at the bottom of the axial elastic member receiving groove 15, respectively. .
  • the plurality of axial elastic member receiving grooves 15 are arranged in a circular array, so that the elastic force is evenly distributed, and a stable buffer effect is achieved.
  • the axial elastic member 16 is a spring or an elastic washer.
  • the radial force applying component 17 includes a radial screw rod 18 arranged vertically, and a radial driver 19 connected to the radial screw rod 18 so as to be able to drive the radial screw rod 18 to reciprocate in the vertical direction.
  • the radial driver 19 is a motor or a hydraulic motor, preferably a stepper motor.
  • the radial screw rod 18 is connected to the radial screw rod 18 through a pulley or a gear, and a second load sensor 20 is provided at an end of the radial screw rod 18.
  • a radial buffer 21 is provided at an end of the radial screw 18, and the second load sensor 20 is located on the radial buffer 21.
  • the radial buffer 21 may be a spring or an elastic washer, and the two ends are respectively connected to the end of the radial screw rod 18 and the second load sensor 20, so as to play a buffer function.
  • the radial buffer 21 includes a radial joint 22 fixedly connected to the radial screw rod 18.
  • a radial elastic seat 23 is movably connected to the radial joint 22, and the second load sensor 20 is fixed to the radial elastic seat 23. on.
  • the radial elastic seat 23 is sleeved on the radial joint 22, and the radial elastic seat 23 is engaged with a radial positioning collar 24.
  • the radial positioning collar 24 and the radial joint are close to the radial direction.
  • One end of the screw rod 18 is engaged, and a plurality of radial elastic member receiving grooves 25 are provided in the radial joint 22.
  • the radial elastic member receiving grooves 25 are provided with radial elastic members 26. Both ends of the elastic member 26 abut against the inner wall of the radial elastic seat 23 at the bottom of the radial elastic member accommodating groove 25, respectively.
  • a plurality of radial elastic member receiving grooves 25 are arranged in a circular array, so that the elastic force is evenly distributed, and a stable buffer effect is achieved.
  • the radial elastic member 26 is a spring or an elastic washer.
  • the main shaft 2 When the main shaft 2 is working, it rotates in a circumferential direction. Therefore, when the axial screw 8 and the radial screw 18 approach the main shaft 2 and apply a force to the main shaft 2, friction occurs, that is, the first load sensor 10 and Friction is generated between the second load sensor 20 and the main shaft 2. In this case, the first load sensor 10, the second load sensor 20, and the main shaft 2 are all abraded, and the force test is also inaccurate.
  • a static force receiving component 27 is provided at the end of the main shaft 2 in this embodiment.
  • the static force receiving component 27 is provided with an end connected to the main shaft 2 and can be synchronized with the main shaft 2.
  • Rotating static holding bearing 28 That is, when the axial screw rod 8 and the radial screw rod 18 approach the main shaft 2 and apply a force to the main shaft 2, the first load sensor 10 and the second load sensor 20 are in static contact with the static force receiving component 27, No friction occurs, and the static force receiving component 27 forms a rolling connection with the main shaft 2 through the static holding bearing 28, and at the same time transmits the received force to the main shaft 2 through the static holding bearing 28.
  • the static force receiving component 27 includes a rotary base 29 connected to the end of the main shaft 2 and a static base 30 sleeved on the rotary base 29.
  • the static holding bearing 28 is located between the rotary base 29 and the static base 30, and holds statically.
  • the inner ring of the bearing 28 is fixedly connected to the rotating seat 29.
  • the outer ring of the static holding bearing 28 is fixedly connected to the static seat 30.
  • both the rotating seat 29 and the static seat 30 are provided with a clamping groove.
  • the static holding bearing 28 is inserted into the card groove to realize the connection between the rotating seat 29 and the static seat 30.
  • the static seat 30 can be detachable with bolts. Structure for easy installation.
  • the bearing assembly 4 has two and is located at both ends of the main shaft 2.
  • the fuselage 3 includes a bearing sleeve 31 sleeved outside the bearing assembly 4.
  • the bearing sleeve 31 is provided with a temperature control element 32, which controls the temperature.
  • the element 32 can regulate the temperature of the bearing sleeve 31, that is, heat or cool the bearing sleeve 31.
  • the temperature control element 32 includes an electric heating rod 33 provided in the bearing sleeve 31.
  • the electric heating rod 33 is the prior art, and a heating wire or other thermal resistance can be used to heat the bearing sleeve.
  • the specific setting can be A deep hole or groove suitable for the electric heating rod 33 is milled in the bearing sleeve 31.
  • the electric heating rod 33 is placed in the deep hole or groove, and the bearing sleeve can be heated after the switch and the power supply are connected.
  • the temperature control element 32 further includes a cooling jacket 34 corresponding to the position of the bearing assembly 4.
  • the cooling jacket 34 is located inside the bearing casing 31, or the bearing jacket 31 and the outer wall of the bearing assembly 4 form a cooling jacket 34.
  • the cooling jacket 34 may be provided with a jacket directly in the bearing sleeve 31, or may be formed by cooperation with the bearing assembly 4, and the jacket may cool the bearing assembly 4 and the bearing sleeve 31.
  • the bearing sleeve 31 is provided with a cooling medium channel 35 connected to the cooling jacket 34, and the cooling medium channel 35 is connected to a cooling medium supplier such as an oil pump or a water pump, and the cooling medium is driven into the cooling jacket 34, so that the bearing sleeve 31 and The bearing assembly is cooled down.
  • the cooling medium can be oil or water.
  • the cooling jacket 34 can also pass in a heat-conducting oil, which can heat the bearing sleeve and the bearing assembly, that is, The cooling jacket 34 has both cooling and heating functions.
  • a bearing sleeve cooling jacket 34a is provided between the fuselage 3 and the bearing sleeve 31.
  • the bearing sleeve cooling jacket 34a can pass a cooling medium, and the bearing sleeve cooling clip
  • the sleeve 34a is connected to a cooling medium supplier, such as an oil pump or a water pump, and drives the cooling medium into the bearing sleeve cooling jacket 34a, so as to cool the bearing sleeve 31.
  • the cooling medium may be oil or water.
  • the bearing assembly 4 includes a plurality of main shaft bearings 36 provided on the main shaft 2 and a bearing fixing sleeve 37 sleeved on the main shaft bearing 36.
  • the bearing fixing sleeve 37 is fixed to the outer ring of the main shaft bearing 36, and the main shaft bearing 36
  • the inner ring is fixed to the outer wall of the main shaft 2 and further includes a plurality of temperature sensors 38 corresponding to the main shaft bearings 36.
  • the temperature sensors 38 pass through the fuselage 3 and the bearing fixing sleeve 37 in order to directly contact the outer ring of the main shaft bearing 36.
  • This contact is a static contact, so that the temperature of the spindle bearing 36 is monitored in real time, and because the temperature sensor 38 directly contacts the outer ring of the spindle bearing 36, the detected temperature is the actual temperature of the spindle bearing 36, and the temperature detection is accurate and reliable.
  • a bearing dynamic characteristic testing machine includes a driving mechanism 1.
  • the driving mechanism 1 is a motor or a hydraulic motor, preferably a stepping motor.
  • the driving mechanism 1 is connected to the main shaft 2 so as to drive the main shaft 2 in a circumferential direction. Rotating, the main shaft 2 is located inside the fuselage 3 and a bearing assembly 4 is sleeved on the main shaft 2.
  • the main shaft 2 further includes a bearing assembly 4 capable of moving toward or away from the end of the main shaft 2 so as to contact the end of the main shaft 2 and end the main shaft 2.
  • the end force applying mechanism 5 applying pressure further includes a displacement sensor 6 connected to the main shaft 2, and the displacement sensor 6 is fixed on the fuselage 3.
  • the driving mechanism 1, the main body 3, and the end force applying mechanism 5 are all fixed on the frame 1a.
  • the displacement sensor 6 is a prior art, and a commercially available product may be adopted.
  • the end force applying mechanism 5 may be a hydraulic motor, a screw rod, a jack, or the like.
  • Suite that can exert pressure on the main shaft 2 can be used.
  • the end force applying mechanism 5 applies pressure to the end of the main shaft 2, the load on the end of the main shaft 2 can be simulated, and the displacement deviation of the main shaft 2 obtained by the displacement sensor 6 can reflect that the main shaft 2 can maintain accuracy under a certain load state The holding time within the qualified range, so as to obtain the holding time of the spindle 2 and the bearing assembly 4 under the load state.
  • a force applicator is provided on the fuselage, and the force applicator is provided on the fuselage and acts on the central region of the spindle, thereby forming pressure on the central part of the spindle to simulate the spindle load.
  • this method has the following disadvantages: the force application position is the middle part of the spindle instead of the end, and it cannot truly reflect the load force of the spindle end in the actual working state, that is, it cannot simulate the spindle end to eat a knife Load.
  • the end force applying mechanism 5 includes an axial force applying component 7 capable of reciprocating in the horizontal direction. As shown in FIG. 5, the axial force applying component 7 corresponds to the end surface of the main shaft 2.
  • the end force applying mechanism 5 further includes a radial force applying component 17 capable of reciprocating in the vertical direction, and the radial force applying component 17 is located above the end of the main shaft 2.
  • the axial force applying component 7 can apply pressure to the end surface of the main shaft 2 to simulate the axial force of the main shaft and reflect the axial load of the main shaft in actual work, thereby obtaining more accurate and reliable accuracy maintenance. Determination of time.
  • the axial force applying assembly 7 includes an axial screw rod 8 arranged horizontally, the axial screw rod 8 is sleeved with a screw sleeve, and further includes an axial screw rod 8 connected to drive the shaft.
  • An axial driver 9 reciprocating in a horizontal direction to the screw rod 8 the axial driver 9 is a motor or a hydraulic motor, preferably a stepper motor, and the axial screw rod 8 and the axial driver 9 may be connected by a pulley or a gear.
  • the end of the axial screw rod 8 is provided with a first Load sensor 10.
  • the load sensor is also called a load cell or a load cell sensor. It is a prior art and a commercially available product can be used.
  • An axial buffer 11 is provided at an end of the axial screw rod 8, and the first load sensor 10 is located on the axial buffer 11.
  • the first load sensor 10 can obtain a specific value of the load.
  • the axial buffer 11 is elastic and can be deformed, and can deform after the screw rod contacts the main shaft, preventing the axial screw rod 8 or the first load sensor 10 from rigidly colliding with the main shaft 2, so that the axial screw rod 8, the first A load sensor 10 and the main shaft 2 play a protective role.
  • the axial buffer 11 may be a spring or an elastic washer, and both ends thereof are respectively connected to the end of the axial screw rod 8 and the first load sensor 10 so as to play a buffering effect.
  • the axial buffer 11 includes an axial joint 12 fixedly connected to the axial screw rod 8, and an axial elastic seat 13 is movably connected to the axial joint 12.
  • the axial elastic seat 13 can move back and forth along the axial line of the axial joint 12 to play a buffering role.
  • the first load sensor 10 is fixed on the axial elastic seat 13, specifically, it is fixed on the axial elastic seat. 13 on the outer wall.
  • the axial elastic seat 13 is sleeved on the axial joint 12.
  • the axial elastic seat 13 is engaged with an axial positioning collar 14.
  • the axial positioning collar has a ring shape and plays a positioning role to prevent the axial elastic seat 13 from detaching.
  • An axial joint 12, the axial positioning collar 14 is engaged with an end of the axial joint near the axial screw 8, and the axial joint 12 is provided with a plurality of axial elastic member accommodation slots 15, and the shaft
  • An axial elastic member 16 is provided in the elastic member receiving groove 15, and both ends of the axial elastic member 16 abut against the inner wall of the axial elastic seat 13 at the bottom of the axial elastic member receiving groove 15, respectively. .
  • the plurality of axial elastic member receiving grooves 15 are arranged in a circular array, so that the elastic force is evenly distributed, and a stable buffer effect is achieved.
  • the axial elastic member 16 is a spring or an elastic washer.
  • a static force receiving component 27 is provided at the end of the main shaft 2 in this embodiment.
  • the static force receiving component 27 is provided with an end connected to the main shaft 2 and can be synchronized with the main shaft 2.
  • Rotating static holding bearing 28 That is, when the axial screw 8 approaches the main shaft 2 and exerts a force on the main shaft 2, the first load sensor 10 and the static force receiving component 27 are in static contact without friction, and the static force receiving component 27 passes through the static force.
  • a rolling connection is formed between the holding bearing 28 and the main shaft 2, and at the same time, the received force is transmitted to the main shaft 2 through the static holding bearing 28.
  • the static force receiving component 27 includes a rotary base 29 connected to the end of the main shaft 2 and a static base 30 sleeved on the rotary base 29.
  • the static holding bearing 28 is located between the rotary base 29 and the static base 30, and holds statically.
  • the inner ring of the bearing 28 is fixedly connected to the rotating seat 29.
  • the outer ring of the static holding bearing 28 is fixedly connected to the static seat 30.
  • the rotating seat 29 and the static seat 30 are each provided with a clamping slot, and the static holding bearing 28 is inserted into the card slot to realize the installation and connection between the rotating seat 29 and the static seat 30.
  • the static seat 30 can be detachable with bolts. Structure for easy installation.
  • the bearing assembly 4 has two and is located at both ends of the main shaft 2. Of course, the bearing assembly 4 may also have more than two.
  • the fuselage 3 includes a bearing sleeve 31 sleeved outside the bearing assembly 4, and the bearing sleeve 31 is provided with a temperature control element 32, which can adjust the temperature of the bearing sleeve 31, that is, heat or cool the bearing sleeve 31.
  • the temperature control element 32 includes an electric heating rod 33 provided in the bearing sleeve 31.
  • the electric heating rod 33 is a conventional technology, and a thermocouple, an electric heating wire, or other electric heating devices can be used to heat the bearing sleeve. .
  • a deep hole or slot suitable for the electric heating rod 33 can be drilled, milled, and / or cut in the bearing sleeve 31.
  • the electric heating rod 33 is placed in the deep hole or slot, and the switch and power supply can be connected. Achieve heating of the bearing sleeve.
  • the temperature control element 32 further includes a cooling jacket 34 corresponding to the position of the bearing assembly 4.
  • the cooling jacket 34 is located inside the bearing casing 31, or the bearing casing 31 and the outer wall of the bearing assembly 4 form a cooling jacket 34 and a cooling jacket. Coolant is passed in 34 for cooling.
  • the cooling jacket 34 may be provided with a jacket directly in the bearing housing 31, or may be formed through cooperation with the bearing assembly 4, and the jacket may cool the bearing assembly 4 and the bearing housing 31.
  • the bearing sleeve 31 is provided with a cooling medium channel 35 connected to the cooling jacket 34, and the cooling medium channel 35 is connected to a cooling medium supplier such as an oil pump or a water pump, and the cooling medium is driven into the cooling jacket 34, so that the bearing sleeve 31 and The bearing assembly is cooled down.
  • the cooling medium can be oil or water.
  • the cooling jacket 34 can also pass in a heat-conducting oil, which plays a heating role on the bearing sleeve and the bearing assembly, that is, The cooling jacket 34 has both cooling and heating functions.
  • the bearing assembly 4 includes a plurality of main shaft bearings 36 provided on the main shaft 2 and a bearing fixing sleeve 37 sleeved on the main shaft bearing 36.
  • the bearing fixing sleeve 37 is fixed to the outer ring of the main shaft bearing 36, and the main shaft bearing 36
  • the inner ring is fixed to the outer wall of the main shaft 2 and further includes a plurality of temperature sensors 38 corresponding to the main shaft bearings 36.
  • the temperature sensors 38 pass through the fuselage 3 and the bearing fixing sleeve 37 in order to directly contact the outer ring of the main shaft bearing 36.
  • This contact is a static contact, so that the temperature of the spindle bearing 36 is monitored in real time, and because the temperature sensor 38 directly contacts the outer ring of the spindle bearing 36, the detected temperature is the actual temperature of the spindle bearing 36, and the temperature detection is accurate and reliable.
  • a bearing dynamic characteristic testing machine includes a driving mechanism 1.
  • the driving mechanism 1 is a motor or a hydraulic motor, preferably a stepping motor.
  • the driving mechanism 1 is connected to the main shaft 2 so as to drive the main shaft 2 in a circumferential direction. Rotating, the main shaft 2 is located inside the fuselage 3 and a bearing assembly 4 is sleeved on the main shaft 2.
  • the main shaft 2 further includes a bearing assembly 4 capable of moving toward or away from the end of the main shaft 2 so as to contact the end of the main shaft 2 and end the main shaft 2.
  • the end force applying mechanism 5 applying pressure further includes a displacement sensor 6 connected to the main shaft 2, and the displacement sensor 6 is fixed on the fuselage 3.
  • the driving mechanism 1, the main body 3, and the end force applying mechanism 5 are all fixed on the frame 1a.
  • the displacement sensor 6 is a prior art, and a commercially available product may be adopted.
  • the end force applying mechanism 5 may be a hydraulic motor, a screw rod, a jack, or the like.
  • Suite that can exert pressure on the main shaft 2 can be used.
  • the end force applying mechanism 5 applies pressure to the end of the main shaft 2, the load on the end of the main shaft 2 can be simulated, and the displacement deviation of the main shaft 2 obtained by the displacement sensor 6 can reflect that the main shaft 2 can maintain accuracy under a certain load state The holding time within the qualified range, so as to obtain the holding time of the spindle 2 and the bearing assembly 4 under the load state.
  • the end force applying mechanism 5 includes a radial force applying component 17 capable of reciprocating in the vertical direction, and the radial force applying component 17 is located above the end of the main shaft 2.
  • the radial force component 17 can apply pressure to the outer wall of the end of the main shaft 2 to simulate the radial force of the main shaft 2 and can fully reflect the load situation of the main shaft in actual work, thereby obtaining more accurate and reliable accuracy maintenance Determination of time.
  • the radial force applying component 17 includes a radial screw rod 18 arranged vertically, and a radial driver 19 connected to the radial screw rod 18 so as to be able to drive the radial screw rod 18 to reciprocate in the vertical direction.
  • the radial driver 19 is a motor or a hydraulic motor, preferably a stepper motor.
  • the radial screw rod 18 is connected to the radial screw rod 18 through a pulley or a gear, and a second load sensor 20 is provided at an end of the radial screw rod 18.
  • a radial buffer 21 is provided at an end of the radial screw 18, and the second load sensor 20 is located on the radial buffer 21.
  • the radial buffer 21 may be a spring or an elastic washer, and the two ends are respectively connected to the end of the radial screw rod 18 and the second load sensor 20, so as to play a buffer function.
  • the radial buffer 21 includes a radial joint 22 fixedly connected to the radial screw rod 18.
  • a radial elastic seat 23 is movably connected to the radial joint 22, and the second load sensor 20 is fixed to the radial elastic seat 23. on.
  • the radial elastic seat 23 is sleeved on the radial joint 22, and the radial elastic seat 23 is engaged with a radial positioning collar 24.
  • the radial positioning collar 24 and the radial joint are close to the radial direction.
  • One end of the screw rod 18 is engaged, and a plurality of radial elastic member receiving grooves 25 are provided in the radial joint 22.
  • the radial elastic member receiving grooves 25 are provided with radial elastic members 26. Both ends of the elastic member 26 abut against the inner wall of the radial elastic seat 23 at the bottom of the radial elastic member accommodating groove 25, respectively.
  • a plurality of radial elastic member receiving grooves 25 are arranged in a circular array, so that the elastic force is evenly distributed, and a stable buffer effect is achieved.
  • the radial elastic member 26 is a spring or an elastic washer.
  • the main shaft 2 When the main shaft 2 is working, it rotates in a circumferential direction. Therefore, when the axial screw 8 and the radial screw 18 approach the main shaft 2 and apply a force to the main shaft 2, friction occurs, that is, the first load sensor 10 and Friction is generated between the second load sensor 20 and the main shaft 2. In this case, the first load sensor 10, the second load sensor 20, and the main shaft 2 are all abraded, and the force test is also inaccurate.
  • a static force receiving component 27 is provided at the end of the main shaft 2 in this embodiment.
  • the static force receiving component 27 is provided with an end connected to the main shaft 2 and can be synchronized with the main shaft 2.
  • Rotating static holding bearing 28 That is, when the axial screw rod 8 and the radial screw rod 18 approach the main shaft 2 and apply a force to the main shaft 2, the first load sensor 10 and the second load sensor 20 are in static contact with the static force receiving component 27, No friction occurs, and the static force receiving component 27 forms a rolling connection with the main shaft 2 through the static holding bearing 28, and at the same time transmits the received force to the main shaft 2 through the static holding bearing 28.
  • the static force receiving component 27 includes a rotary base 29 connected to the end of the main shaft 2 and a static base 30 sleeved on the rotary base 29.
  • the static holding bearing 28 is located between the rotary base 29 and the static base 30, and holds statically.
  • the inner ring of the bearing 28 is fixedly connected to the rotating seat 29.
  • the outer ring of the static holding bearing 28 is fixedly connected to the static seat 30.
  • the rotating seat 29 and the static seat 30 are each provided with a clamping slot, and the static holding bearing 28 is inserted into the card slot to realize the installation and connection between the rotating seat 29 and the static seat 30.
  • the static seat 30 can be detachable with bolts. Structure for easy installation.
  • the bearing assembly 4 has two and is located at both ends of the main shaft 2.
  • the fuselage 3 includes a bearing sleeve 31 sleeved outside the bearing assembly 4.
  • the bearing sleeve 31 is provided with a temperature control element 32, which controls the temperature.
  • the element 32 can regulate the temperature of the bearing sleeve 31, that is, heat or cool the bearing sleeve 31.
  • the temperature control element 32 includes an electric heating rod 33 provided in the bearing sleeve 31.
  • the electric heating rod 33 is a conventional technology, and a thermocouple, a heating wire, or other thermal resistance can be used to heat the bearing sleeve.
  • a deep hole or groove suitable for the electric heating rod 33 can be milled in the bearing sleeve 31.
  • the electric heating rod 33 is placed in the deep hole or groove, and the bearing sleeve can be realized after connecting the switch and the power supply. heating.
  • the temperature control element 32 further includes a cooling jacket 34 corresponding to the position of the bearing assembly 4.
  • the cooling jacket 34 is located inside the bearing casing 31, or the bearing jacket 31 and the outer wall of the bearing assembly 4 form a cooling jacket 34.
  • the cooling jacket 34 may be provided with a jacket directly in the bearing sleeve 31, or may be formed by cooperation with the bearing assembly 4, and the jacket may cool the bearing assembly 4 and the bearing sleeve 31.
  • the bearing sleeve 31 is provided with a cooling medium channel 35 connected to the cooling jacket 34, and the cooling medium channel 35 is connected to a cooling medium supplier such as an oil pump or a water pump, and the cooling medium is driven into the cooling jacket 34, so that the bearing sleeve 31 and The bearing assembly is cooled down.
  • the cooling medium can be oil or water.
  • the cooling jacket 34 can also pass in a heat-conducting oil, which plays a heating role on the bearing sleeve and the bearing assembly, that is, The cooling jacket 34 has both cooling and heating functions.
  • the bearing assembly 4 includes a plurality of main shaft bearings 36 provided on the main shaft 2 and a bearing fixing sleeve 37 sleeved on the main shaft bearing 36.
  • the bearing fixing sleeve 37 is fixed to the outer ring of the main shaft bearing 36, and the main shaft bearing 36
  • the inner ring is fixed to the outer wall of the main shaft 2 and further includes a plurality of temperature sensors 38 corresponding to the main shaft bearings 36.
  • the temperature sensors 38 pass through the fuselage 3 and the bearing fixing sleeve 37 in order to directly contact the outer ring of the main shaft bearing 36.
  • This contact is a static contact, so that the temperature of the spindle bearing 36 is monitored in real time, and because the temperature sensor 38 directly contacts the outer ring of the spindle bearing 36, the detected temperature is the actual temperature of the spindle bearing 36, and the temperature detection is accurate and reliable.

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Abstract

一种轴承动态特性试验机，属于轴承技术领域。包括驱动机构（1），驱动机构（1）连接主轴（2）从而能驱动主轴（2）周向转动，主轴（2）位于机身（3）内部且主轴（2）上套设有轴承组件（4），还包括能向靠近或远离主轴（2）端部方向移动从而与主轴（2）端部接触并对主轴（2）的端部施加压力的端部施力机构（5），还包括与主轴（2）连接的位移传感器（6）。通过对主轴（2）端部直接施加作用力，从而模拟主轴（2）端部在吃刀情况下的受力，通过位移传感器（6）检测主轴（2）配合轴承组件（4）的精度保持时间。

Description

轴承动态特性试验机 技术领域
本发明属于轴承技术领域，涉及一种轴承动态特性试验机。
背景技术
众所周知，主轴外需要套设轴承，当主轴在高速运动时，轴承会产生温升，轴承的精度也会随之发生变化，反应到主轴是主轴的位移产生变化如旋转跳动等，轴承的性能及可靠性是轴承的最重要的性能指标，由于影响轴承性能因素较多，在测试主轴是带负荷情况下精度的保持时间是轴承试验的一种有效手段。
在现有技术中，在模拟主轴负荷状态时，采用在机身上设有施力器，施力器设在机身上并作用于主轴中部区域(前后轴承组的跨距之间)，从而对主轴中部形成压力，来模拟主轴负荷下的工作状态，这种方法存在以下的缺点：是施力位置为主轴中部而非端部，并不能真正反应出主轴端部在实际工作状态下的负载力，也即无法模拟主轴端部吃刀时的负荷。
人们经过不断探索，提出了各种各样的解决方案，如中国专利公开了一种基于丝杆传动机构的轴承试验机用交变载荷加载装置[申请号：201711457298.9]，包括旋转轴，被试轴承安装在所述旋转轴上，该加载装置包括夹具，以及设置在夹具周围的多个旋转电机-丝杆传动机构-弹簧组件，各旋转电机-丝杆传动机构-弹簧组件包括依次连接旋转电机、丝杆传动机构和弹簧，其中丝杆传动机构包括联轴器、丝杆轴承、丝杆螺母、丝杆和轴承座，旋转电机驱动丝杆传动机构运动，控制弹簧发生拉伸或压缩形变，对夹具内的被试轴承施加交变载荷。
但是，仔细研究后可以发现，在实际工作时，通常是主轴吃力后将力传递给轴承内圈，从而使轴承吃力，但上述方案是直接将力施加给轴承外圈，因此，模拟轴承吃力情况与实际工况是相反的，并不能直接反应主轴吃力时的工况。
发明内容
本发明的目的是针对上述问题，提供一种轴承动态特性试验机。
为达到上述目的，本发明采用了下列技术方案：
一种轴承动态特性试验机，包括驱动机构，所述的驱动机构连接主轴从而能驱动主轴周向转动，主轴位于机身内部且主轴上套设有轴承组件，还包括能向靠近或远离所述的主轴端部方向移动从而与主轴端部接触并对主轴的端部施加压力的端部施力机构，还包括与主轴连接的位移传感器。
在上述的轴承动态特性试验机中，所述的端部施力机构包括能沿水平方向往复运动的轴向施力组件，所述的轴向施力组件与主轴的端面相对应。
在上述的轴承动态特性试验机中，所述的轴向施力组件包括呈水平设置的轴向丝杆，以及连接轴向丝杆从而能驱动轴向丝杆沿水平方向往复运动的轴向驱动器，所述的轴向丝杆的端部设有第一荷重传感器。
在上述的轴承动态特性试验机中，所述的轴向丝杆的端部设有轴向缓冲器，第一荷重传感器位于轴向缓冲器上。
在上述的轴承动态特性试验机中，所述的轴向缓冲器包括与轴向丝杆固定连接的轴向接头，所述的轴向接头上活动连接有一个轴向弹性座，第一荷重传感器固定在轴向弹性座上。
在上述的轴承动态特性试验机中，所述的轴向弹性座套设在轴向接头上，轴向弹性座上卡接有轴向定位卡圈，所述的轴向定位卡圈与轴向接头靠近轴向丝杆的一端卡接，轴向接头内设有若干轴向弹性件容置槽，所述的轴向弹性件容置槽内设有轴向弹性件，所述的轴向弹性件的两端分别抵靠在轴向弹性件容置槽的底部的轴向弹性座的内壁上。
在上述的轴承动态特性试验机中，所述的端部施力机构包括能沿竖直方向往复运动的径向施力组件，所述的径向施力组件位于主轴端部上方。
在上述的轴承动态特性试验机中，所述的径向施力组件包括呈竖直设置的径向丝杆，以及连接径向丝杆从而能驱动径向丝杆沿竖直方向往复运动的径向驱动器，所述的径向丝杆的端部设有第二荷重传感器。
在上述的轴承动态特性试验机中，所述的径向丝杆的端部设有径向缓冲器，第二荷重传感器位于径向缓冲器上。
在上述的轴承动态特性试验机中，所述的径向缓冲器包括与径向丝杆固定连接的径向接头，所述的径向接头上活动连接有一个径向弹性座，第二荷重传感器固定在径向弹性座上。
在上述的轴承动态特性试验机中，所述的径向弹性座套设在径向接头上，径向弹性座上卡接有径向定位卡圈，所述的径向定位卡圈与径向接头靠近径向丝杆的一端卡接，径向接头内设有若干径向弹性件容置槽，所述的径向弹性件容置槽内设有径向弹性件，所述的径向弹性件的两端分别抵靠在径向弹性件容置槽的底部的径向弹性座的内壁上。
在上述的轴承动态特性试验机中，所述的主轴端部设有一个静态受力组件，所述的静态受力组件内设有连接主轴端部并能与主轴同步转动的静态保持轴承。
在上述的轴承动态特性试验机中，所述的静态受力组件包括连接主轴端部的转动座，以及套设在转动座上的静态座，静态保持轴承位于转动座和静态座之间，静态保持轴承的内圈与转动座固定连接，静态保持轴承的外圈与静态座固定连接。
在上述的轴承动态特性试验机中，所述的轴承组件有两个且位于主轴的两端，所述的机身包括套设在轴承组件外的轴承套，所述的轴承套内设有控温元件。
在上述的轴承动态特性试验机中，所述的控温元件包括设置在轴承套内的电加热棒，以及与轴承组件的位置相对应的冷却夹套。
在上述的轴承动态特性试验机中，所述的冷却夹套位于轴承套内部，或者轴承套与轴承组件的外壁合围形成冷却夹套。
在上述的轴承动态特性试验机中，所述的轴承套内设有连接冷却夹套的冷却介质通道。
在上述的轴承动态特性试验机中，所述的轴承组件包括若干套设在主轴上的主轴轴承，以及套在主轴轴承外的轴承固定套，还包括若干与主轴轴承一一对应的温度传感器，所述的温度传感器依次穿过机身、轴承固定套后直接与主轴轴承的外圈接触。
与现有的技术相比，本发明的优点在于：
1、通过对主轴端部直接施加作用力，从而模拟主轴端部在吃刀情况下的受力，通过位移传感器检测主轴配合轴承组件的精度保持时间。
2、轴向施力组件和径向施力组件的配合，准确的模拟主轴端部的受力情况，从而能得到准确的精度保持时间的测定。
3、通过设置轴向缓冲器和径向缓冲器，使轴向施力组件和径向施力组 件与主轴之间实现柔性的作用力接触，对主轴及轴向施力组件和径向施力组件均起到保护作用。
4、通过设置静态受力组件，使作用力施加于静态受力组件，再通过静态受力组件作用于主轴端部，对传感器、主轴均起到保护作用，也可以准确的控制施加的作用力的大小。
5、控温元件的设置，对轴承套和轴承组件能起到加热和降温的作用，从而模拟机身内的工况，实现在不同条件的精度保持时间的测定。
6、温度传感器直接与轴承外圈接触，温度检测准确。
本发明的其它优点、目标和特征将部分通过下面的说明体现，部分还将通过对本发明的研究和实践而为本领域的技术人员所理解。
附图说明
图1是本发明的结构示意图。
图2是本发明的另一种结构示意图。
图3是本发明的另一种结构示意图。
图4是径向施力组件的结构示意图。
图5是轴向施力组件的结构示意图。
图6是静态受力组件的结构示意图。
图中：驱动机构1、机架1a、主轴2、机身3、轴承组件4、端部施力机构5、位移传感器6、轴向施力组件7、轴向丝杆8、轴向驱动器9、第一荷重传感器10、轴向缓冲器11、轴向接头12、轴向弹性座13、轴向定位卡圈14、轴向弹性件容置槽15、轴向弹性件16、径向施力组件17、径向丝杆18、径向驱动器19、第二荷重传感器20、径向缓冲器21、径向接头22、径向弹性座23、径向定位卡圈24、径向弹性件容置槽25、径向弹性件26、静态受力组件27、静态保持轴承28、转动座29、静态座30、轴承套31、控温元件32、电加热棒33、冷却夹套34、轴承套冷却夹套34a、冷却介质通道35、主轴轴承36、轴承固定套37、温度传感器38。
具体实施方式
下面结合附图对本发明作进一步说明。
实施例1
如图1所示，一种轴承动态特性试验机，包括驱动机构1，驱动机构1为电机或液压马达，优选为步进电机，所述的驱动机构1连接主轴2从而能驱动主轴2周向转动，主轴2位于机身3内部且主轴2上套设有轴承组件4，还包括能向靠近或远离所述的主轴2端部方向移动从而与主轴2端部接触并对主轴2的端部施加压力的端部施力机构5，还包括与主轴2连接的位移传感器6，位移传感器6固定在机身3上。驱动机构1、机身3和端部施力机构5均固定在机架1a上。
本领域技术人员应当理解，位移传感器6为现有技术，可采用市售产品。
在本实施例中，端部施力机构5可以是液压马达、丝杆或千斤顶等的，凡是能对主轴2形成压力的均可以使用。在端部施力机构5对主轴2端部施加压力时，能模拟主轴2端部的负荷，通过位移传感器6得到的主轴2位移偏差，可反应出主轴2在某一负载状态下能够保持精度在合格范围内的保持时间，从而获得该主轴2与轴承组件4在该负荷状态下保持精度的时间。
在现有技术中，在模拟主轴负荷状态时，采用在机身上设有施力器，施力器设在机身上并作用于主轴中部区域，从而对主轴中部形成压力，来模拟主轴负荷下的工作状态，这种方法存在以下的缺点：其一是施力位置为主轴中部而非端部，并不能真正反应出主轴端部在实际工作状态下的负载力，也即无法模拟主轴端部吃刀时的负荷；其二是施加的压力始终为径向力，模拟的负载比较单一。
在本实施例中，结合图5所示，端部施力机构5包括能沿水平方向往复运动的轴向施力组件7，所述的轴向施力组件7与主轴2的端面相对应，端部施力机构5还包括能沿竖直方向往复运动的径向施力组件17，所述的径向施力组件17位于主轴2端部上方。
在本实施例中，轴向施力组件7能够对主轴2的端面施加压力，模拟主轴的轴向受力，径向施力组件17能够对主轴2的端部外壁施加压力，模拟主轴2的径向受力，两个力的结合，能够完整的反应主轴在实际工作中的负荷状况，从而获得更为精确、可靠的精度保持时间的测定。
具体的说，在本实施例中，轴向施力组件7包括呈水平设置的轴向丝杆8，轴向丝杆8套设有螺套，还包括连接轴向丝杆8从而能驱动轴向丝 杆8沿水平方向往复运动的轴向驱动器9，轴向驱动器9为电机或液压马达，优选为步进电机，轴向丝杆8与轴向驱动器9之间可以通过皮带轮或齿轮连接，通过轴向驱动器9的转动，带动套设在轴向丝杆8上的螺套转动，从而带动轴向丝杆8前进或后退，所述的轴向丝杆8的端部设有第一荷重传感器10。荷重传感器也叫荷重元或荷重元传感器，为现有技术，可采用市售产品。
轴向丝杆8的端部设有轴向缓冲器11，第一荷重传感器10位于轴向缓冲器11上。当轴向丝杆8靠近主轴2并对主轴2端面施加轴向负荷时，第一荷重传感器10可获得该负荷的具体数值。轴向缓冲器11有弹性可发生形变，能在丝杆与主轴接触后产生形变，防止轴向丝杆8或者第一荷重传感器10与主轴2发生刚性撞击，从而对轴向丝杆8、第一荷重传感器10和主轴2起到保护作用。
轴向缓冲器11可以是弹簧或者弹性垫片，两端分别与轴向丝杆8的端部及第一荷重传感器10连接，从而起到缓冲作用。
作为一种优选的方案，在本实施例中，轴向缓冲器11包括与轴向丝杆8固定连接的轴向接头12，所述的轴向接头12上活动连接有一个轴向弹性座13，轴向弹性座13能沿轴向接头12的轴心线方向前后移动，从而起到缓冲作用，第一荷重传感器10固定在轴向弹性座13上，具体的说，固定在轴向弹性座13的外壁上。
轴向弹性座13套设在轴向接头12上，轴向弹性座13上卡接有轴向定位卡圈14，轴向定位卡圈呈环形，起到定位作用，防止轴向弹性座13脱离轴向接头12，所述的轴向定位卡圈14与轴向接头靠近轴向丝杆8的一端卡接，轴向接头12内设有若干轴向弹性件容置槽15，所述的轴向弹性件容置槽15内设有轴向弹性件16，所述的轴向弹性件16的两端分别抵靠在轴向弹性件容置槽15的底部的轴向弹性座13的内壁上。
优选方案，若干轴向弹性件容置槽15呈环形阵列设置，使弹性力均匀分布，起到稳定的缓冲效果。轴向弹性件16为弹簧或弹性垫片。
结合图4所示，径向施力组件17包括呈竖直设置的径向丝杆18，以及连接径向丝杆18从而能驱动径向丝杆18沿竖直方向往复运动的径向驱动器19，径向驱动器19为电机或液压马达，优选为步进电机，通过皮带轮或齿轮连接径向丝杆18，径向丝杆18的端部设有第二荷重传感器20。
径向丝杆18的端部设有径向缓冲器21，第二荷重传感器20位于径向缓冲器21上。径向缓冲器21可以是弹簧或者弹性垫片，两端分别与径向丝杆18的端部及第二荷重传感器20连接，从而起到缓冲作用。
径向缓冲器21包括与径向丝杆18固定连接的径向接头22，所述的径向接头22上活动连接有一个径向弹性座23，第二荷重传感器20固定在径向弹性座23上。
具体的说，径向弹性座23套设在径向接头22上，径向弹性座23上卡接有径向定位卡圈24，所述的径向定位卡圈24与径向接头靠近径向丝杆18的一端卡接，径向接头22内设有若干径向弹性件容置槽25，所述的径向弹性件容置槽25内设有径向弹性件26，所述的径向弹性件26的两端分别抵靠在径向弹性件容置槽25的底部的径向弹性座23的内壁上。
优选方案，若干径向弹性件容置槽25呈环形阵列设置，使弹性力均匀分布，起到稳定的缓冲效果。径向弹性件26为弹簧或弹性垫片。
当主轴2在工作时，呈周向旋转运动，因此轴向丝杆8和径向丝杆18在靠近主轴2并对主轴2施加作用力时，会产生摩擦，也即第一荷重传感器10和第二荷重传感器20与主轴2之间产生摩擦，在这种情况下，会对第一荷重传感器10、第二荷重传感器20和主轴2均产生磨损，同时也造成作用力测试不准。
为了克服上述缺陷，本实施例在主轴2端部设置了一个静态受力组件27，结合图6所示，所述的静态受力组件27内设有连接主轴2端部并能与主轴2同步转动的静态保持轴承28。也即，当轴向丝杆8和径向丝杆18在靠近主轴2并对主轴2施加作用力时，第一荷重传感器10和第二荷重传感器20与静态受力组件27静态接触，之间不产生摩擦，而静态受力组件27则通过静态保持轴承28与主轴2之间形成滚动连接，同时将受到的作用力通过静态保持轴承28传递给主轴2。
如上所述，静态受力组件27包括连接主轴2端部的转动座29，以及套设在转动座29上的静态座30，静态保持轴承28位于转动座29和静态座30之间，静态保持轴承28的内圈与转动座29固定连接，静态保持轴承28的外圈与静态座30固定连接，静态座30在受到作用力时，保持静止，转动座29随主轴2同步转动。
在本实施例中，转动座29和静态座30均设有卡槽，静态保持轴承28 插入到卡槽中实现安装与转动座29和静态座30的连接，静态座30可以用螺栓实现可拆卸的结构，便于安装。
轴承组件4有两个且位于主轴2的两端，所述的机身3包括套设在轴承组件4外的轴承套31，所述的轴承套31内设有控温元件32，该控温元件32可以调节轴承套31的温度，即加热或冷却轴承套31。
控温元件32包括设置在轴承套31内的电加热棒33，电加热棒33为现有技术，可采用加热丝，或者其他热电阻等，起到加热轴承套的作用，具体的设置，可以在轴承套31内铣削出与电加热棒33相配适的深孔或槽，电加热棒33放置在深孔或槽里，连接开关和电源后即可实现对轴承套的加热。控温元件32还包括与轴承组件4的位置相对应的冷却夹套34，冷却夹套34位于轴承套31内部，或者轴承套31与轴承组件4的外壁合围形成冷却夹套34。
也即，冷却夹套34可以是直接在轴承套31内设置夹套，也可以是通过与轴承组件4的配合形成夹套，该夹套可以对轴承组件4以及轴承套31实现降温。
轴承套31内设有连接冷却夹套34的冷却介质通道35，冷却介质通道35连接冷却介质供应器，如油泵或水泵，将冷却介质打入到冷却夹套34中，从而对轴承套31和轴承组件实现降温冷却，冷却介质可以是油或者水。
虽然本实施例提供了冷却夹套34对轴承套和轴承组件的冷却作用，但在实际应用中，冷却夹套34也可以通入导热油，对轴承套和轴承组件起到加热作用，也即，冷却夹套34同时具备冷却和加热两种作用。
另外，为进一步加强冷却效果，本实施例中，机身3和轴承套31之间设置了一个轴承套冷却夹套34a，该轴承套冷却夹套34a中可通入冷却介质，轴承套冷却夹套34a连接冷却介质供应器，如油泵或水泵，将冷却介质打入到轴承套冷却夹套34a中，从而对轴承套31实现降温冷却，冷却介质可以是油或者水。
在本实施例中，轴承组件4包括若干套设在主轴2上的主轴轴承36，以及套在主轴轴承36外的轴承固定套37，轴承固定套37与主轴轴承36外圈固定，主轴轴承36内圈与主轴2外壁固定，还包括若干与主轴轴承36一一对应的温度传感器38，所述的温度传感器38依次穿过机身3、轴承固定套37后直接与主轴轴承36的外圈接触，这种接触是静态接触，从 而对主轴轴承36的温度得到实时监测，且由于温度传感器38直接与主轴轴承36外圈接触，检测到的温度为主轴轴承36的实际温度，温度检测准确可靠。
实施例2
如图2所示，一种轴承动态特性试验机，包括驱动机构1，驱动机构1为电机或液压马达，优选为步进电机，所述的驱动机构1连接主轴2从而能驱动主轴2周向转动，主轴2位于机身3内部且主轴2上套设有轴承组件4，还包括能向靠近或远离所述的主轴2端部方向移动从而与主轴2端部接触并对主轴2的端部施加压力的端部施力机构5，还包括与主轴2连接的位移传感器6，位移传感器6固定在机身3上。驱动机构1、机身3和端部施力机构5均固定在机架1a上。
本领域技术人员应当理解，位移传感器6为现有技术，可采用市售产品。
在本实施例中，端部施力机构5可以是液压马达、丝杆或千斤顶等的，凡是能对主轴2形成压力的均可以使用。在端部施力机构5对主轴2端部施加压力时，能模拟主轴2端部的负荷，通过位移传感器6得到的主轴2位移偏差，可反应出主轴2在某一负载状态下能够保持精度在合格范围内的保持时间，从而获得该主轴2与轴承组件4在该负荷状态下保持精度的时间。
在现有技术中，在模拟主轴负荷状态时，采用在机身上设有施力器，施力器设在机身上并作用于主轴中部区域，从而对主轴中部形成压力，来模拟主轴负荷下的工作状态，这种方法存在以下的缺点：施力位置为主轴中部而非端部，并不能真正反应出主轴端部在实际工作状态下的负载力，也即无法模拟主轴端部吃刀时的负荷。
在本实施例中，端部施力机构5包括能沿水平方向往复运动的轴向施力组件7，结合图5所示，所述的轴向施力组件7与主轴2的端面相对应，端部施力机构5还包括能沿竖直方向往复运动的径向施力组件17，所述的径向施力组件17位于主轴2端部上方。
在本实施例中，轴向施力组件7能够对主轴2的端面施加压力，模拟主轴的轴向受力，反应主轴在实际工作中轴向负荷状况，从而获得更为精 确、可靠的精度保持时间的测定。
具体的说，在本实施例中，轴向施力组件7包括呈水平设置的轴向丝杆8，轴向丝杆8套设有螺套，还包括连接轴向丝杆8从而能驱动轴向丝杆8沿水平方向往复运动的轴向驱动器9，轴向驱动器9为电机或液压马达，优选为步进电机，轴向丝杆8与轴向驱动器9之间可以通过皮带轮或齿轮连接，通过轴向驱动器9的转动，带动套设在轴向丝杆8上的螺套转动，从而带动轴向丝杆8前进或后腿，所述的轴向丝杆8的端部设有第一荷重传感器10。荷重传感器也叫荷重元或荷重元传感器，为现有技术，可采用市售产品。
轴向丝杆8的端部设有轴向缓冲器11，第一荷重传感器10位于轴向缓冲器11上。当轴向丝杆8靠近主轴2并对主轴2端面施加轴向负荷时，第一荷重传感器10可获得该负荷的具体数值。轴向缓冲器11有弹性可发生形变，能在丝杆与主轴接触后产生形变，防止轴向丝杆8或者第一荷重传感器10与主轴2发生刚性撞击，从而对轴向丝杆8、第一荷重传感器10和主轴2起到保护作用。
轴向缓冲器11可以是弹簧或者弹性垫片，两端分别与轴向丝杆8的端部及第一荷重传感器10连接，从而起到缓冲作用。
作为一种优选的方案，在本实施例中，轴向缓冲器11包括与轴向丝杆8固定连接的轴向接头12，所述的轴向接头12上活动连接有一个轴向弹性座13，轴向弹性座13能沿轴向接头12的轴心线方向前后移动，从而起到缓冲作用，第一荷重传感器10固定在轴向弹性座13上，具体的说，固定在轴向弹性座13的外壁上。
轴向弹性座13套设在轴向接头12上，轴向弹性座13上卡接有轴向定位卡圈14，轴向定位卡圈呈环形，起到定位作用，防止轴向弹性座13脱离轴向接头12，所述的轴向定位卡圈14与轴向接头靠近轴向丝杆8的一端卡接，轴向接头12内设有若干轴向弹性件容置槽15，所述的轴向弹性件容置槽15内设有轴向弹性件16，所述的轴向弹性件16的两端分别抵靠在轴向弹性件容置槽15的底部的轴向弹性座13的内壁上。
优选方案，若干轴向弹性件容置槽15呈环形阵列设置，使弹性力均匀分布，起到稳定的缓冲效果。轴向弹性件16为弹簧或弹性垫片。
当主轴2在工作时，呈周向旋转运动，因此轴向丝杆8和径向丝杆18 在靠近主轴2并对主轴2施加作用力时，会产生摩擦，也即第一荷重传感器10与主轴2之间产生摩擦，在这种情况下，会对第一荷重传感器10和主轴2均产生磨损，同时也造成作用力测试不准。
为了克服上述缺陷，本实施例在主轴2端部设置了一个静态受力组件27，结合图6所示，所述的静态受力组件27内设有连接主轴2端部并能与主轴2同步转动的静态保持轴承28。也即，当轴向丝杆8靠近主轴2并对主轴2施加作用力时，第一荷重传感器10与静态受力组件27静态接触，之间不产生摩擦，而静态受力组件27则通过静态保持轴承28与主轴2之间形成滚动连接，同时将受到的作用力通过静态保持轴承28传递给主轴2。
如上所述，静态受力组件27包括连接主轴2端部的转动座29，以及套设在转动座29上的静态座30，静态保持轴承28位于转动座29和静态座30之间，静态保持轴承28的内圈与转动座29固定连接，静态保持轴承28的外圈与静态座30固定连接，静态座30在受到作用力时，保持静止，转动座29随主轴2同步转动。
在本实施例中，转动座29和静态座30均设有卡槽，静态保持轴承28插入到卡槽中实现安装与转动座29和静态座30的连接，静态座30可以用螺栓实现可拆卸的结构，便于安装。
轴承组件4有两个且位于主轴2的两端，当然，轴承组件4也可以有两个以上，所述的机身3包括套设在轴承组件4外的轴承套31，所述的轴承套31内设有控温元件32，该控温元件32可以调节轴承套31的温度，即加热或冷却轴承套31。
控温元件32包括设置在轴承套31内的电加热棒33，电加热棒33为现有技术，可采用热电偶，也可采用电热丝或者其他电加热器件等，起到加热轴承套的作用。具体的设置，可以在轴承套31内钻、铣和/或削出与电加热棒33相配适的深孔或槽，电加热棒33放置在深孔或槽里，连接开关和电源后即可实现对轴承套的加热。控温元件32还包括与轴承组件4的位置相对应的冷却夹套34，冷却夹套34位于轴承套31内部，或者轴承套31与轴承组件4的外壁合围形成冷却夹套34，冷却夹套34中通入冷却液，用于降温。
也即，冷却夹套34可以是直接在轴承套31内设置夹套，也可以是通过与轴承组件4的配合形成夹套，该夹套可以对轴承组件4以及轴承套31 实现降温。
轴承套31内设有连接冷却夹套34的冷却介质通道35，冷却介质通道35连接冷却介质供应器，如油泵或水泵，将冷却介质打入到冷却夹套34中，从而对轴承套31和轴承组件实现降温冷却，冷却介质可以是油或者水。
虽然本实施例提供了冷却夹套34对轴承套和轴承组件的冷却作用，但在实际应用中，冷却夹套34也可以通入导热油，对轴承套和轴承组件起到加热作用，也即，冷却夹套34同时具备冷却和加热两种作用。
在本实施例中，轴承组件4包括若干套设在主轴2上的主轴轴承36，以及套在主轴轴承36外的轴承固定套37，轴承固定套37与主轴轴承36外圈固定，主轴轴承36内圈与主轴2外壁固定，还包括若干与主轴轴承36一一对应的温度传感器38，所述的温度传感器38依次穿过机身3、轴承固定套37后直接与主轴轴承36的外圈接触，这种接触是静态接触，从而对主轴轴承36的温度得到实时监测，且由于温度传感器38直接与主轴轴承36外圈接触，检测到的温度为主轴轴承36的实际温度，温度检测准确可靠。
实施例3
结合图3所示，一种轴承动态特性试验机，包括驱动机构1，驱动机构1为电机或液压马达，优选为步进电机，所述的驱动机构1连接主轴2从而能驱动主轴2周向转动，主轴2位于机身3内部且主轴2上套设有轴承组件4，还包括能向靠近或远离所述的主轴2端部方向移动从而与主轴2端部接触并对主轴2的端部施加压力的端部施力机构5，还包括与主轴2连接的位移传感器6，位移传感器6固定在机身3上。驱动机构1、机身3和端部施力机构5均固定在机架1a上。
本领域技术人员应当理解，位移传感器6为现有技术，可采用市售产品。
在本实施例中，端部施力机构5可以是液压马达、丝杆或千斤顶等的，凡是能对主轴2形成压力的均可以使用。在端部施力机构5对主轴2端部施加压力时，能模拟主轴2端部的负荷，通过位移传感器6得到的主轴2位移偏差，可反应出主轴2在某一负载状态下能够保持精度在合格范围内的保持时间，从而获得该主轴2与轴承组件4在该负荷状态下保持精度的 时间。
在现有技术中，在模拟主轴负荷状态时，采用在机身上设有施力器，施力器设在机身上并作用于主轴中部区域，从而对主轴中部形成压力，来模拟主轴负荷下的工作状态，这种方法存在以下的缺点：其一是施力位置为主轴中部而非端部，并不能真正反应出主轴端部在实际工作状态下的负载力，也即无法模拟主轴端部吃刀时的负荷。
在本实施例中，端部施力机构5包括能沿竖直方向往复运动的径向施力组件17，所述的径向施力组件17位于主轴2端部上方。，径向施力组件17能够对主轴2的端部外壁施加压力，模拟主轴2的径向受力，能够完整的反应主轴在实际工作中的负荷状况，从而获得更为精确、可靠的精度保持时间的测定。
结合图4所示，径向施力组件17包括呈竖直设置的径向丝杆18，以及连接径向丝杆18从而能驱动径向丝杆18沿竖直方向往复运动的径向驱动器19，径向驱动器19为电机或液压马达，优选为步进电机，通过皮带轮或齿轮连接径向丝杆18，径向丝杆18的端部设有第二荷重传感器20。
径向丝杆18的端部设有径向缓冲器21，第二荷重传感器20位于径向缓冲器21上。径向缓冲器21可以是弹簧或者弹性垫片，两端分别与径向丝杆18的端部及第二荷重传感器20连接，从而起到缓冲作用。
径向缓冲器21包括与径向丝杆18固定连接的径向接头22，所述的径向接头22上活动连接有一个径向弹性座23，第二荷重传感器20固定在径向弹性座23上。
具体的说，径向弹性座23套设在径向接头22上，径向弹性座23上卡接有径向定位卡圈24，所述的径向定位卡圈24与径向接头靠近径向丝杆18的一端卡接，径向接头22内设有若干径向弹性件容置槽25，所述的径向弹性件容置槽25内设有径向弹性件26，所述的径向弹性件26的两端分别抵靠在径向弹性件容置槽25的底部的径向弹性座23的内壁上。
优选方案，若干径向弹性件容置槽25呈环形阵列设置，使弹性力均匀分布，起到稳定的缓冲效果。径向弹性件26为弹簧或弹性垫片。
当主轴2在工作时，呈周向旋转运动，因此轴向丝杆8和径向丝杆18在靠近主轴2并对主轴2施加作用力时，会产生摩擦，也即第一荷重传感器10和第二荷重传感器20与主轴2之间产生摩擦，在这种情况下，会对 第一荷重传感器10、第二荷重传感器20和主轴2均产生磨损，同时也造成作用力测试不准。
为了克服上述缺陷，本实施例在主轴2端部设置了一个静态受力组件27，结合图6所示，所述的静态受力组件27内设有连接主轴2端部并能与主轴2同步转动的静态保持轴承28。也即，当轴向丝杆8和径向丝杆18在靠近主轴2并对主轴2施加作用力时，第一荷重传感器10和第二荷重传感器20与静态受力组件27静态接触，之间不产生摩擦，而静态受力组件27则通过静态保持轴承28与主轴2之间形成滚动连接，同时将受到的作用力通过静态保持轴承28传递给主轴2。
如上所述，静态受力组件27包括连接主轴2端部的转动座29，以及套设在转动座29上的静态座30，静态保持轴承28位于转动座29和静态座30之间，静态保持轴承28的内圈与转动座29固定连接，静态保持轴承28的外圈与静态座30固定连接，静态座30在受到作用力时，保持静止，转动座29随主轴2同步转动。
在本实施例中，转动座29和静态座30均设有卡槽，静态保持轴承28插入到卡槽中实现安装与转动座29和静态座30的连接，静态座30可以用螺栓实现可拆卸的结构，便于安装。
轴承组件4有两个且位于主轴2的两端，所述的机身3包括套设在轴承组件4外的轴承套31，所述的轴承套31内设有控温元件32，该控温元件32可以调节轴承套31的温度，即加热或冷却轴承套31。
控温元件32包括设置在轴承套31内的电加热棒33，电加热棒33为现有技术，可采用热电偶，也可采用加热丝，或者其他热电阻等，起到加热轴承套的作用，具体的设置，可以在轴承套31内铣削出与电加热棒33相配适的深孔或槽，电加热棒33放置在深孔或槽里，连接开关和电源后即可实现对轴承套的加热。控温元件32还包括与轴承组件4的位置相对应的冷却夹套34，冷却夹套34位于轴承套31内部，或者轴承套31与轴承组件4的外壁合围形成冷却夹套34。
也即，冷却夹套34可以是直接在轴承套31内设置夹套，也可以是通过与轴承组件4的配合形成夹套，该夹套可以对轴承组件4以及轴承套31实现降温。
轴承套31内设有连接冷却夹套34的冷却介质通道35，冷却介质通道 35连接冷却介质供应器，如油泵或水泵，将冷却介质打入到冷却夹套34中，从而对轴承套31和轴承组件实现降温冷却，冷却介质可以是油或者水。
虽然本实施例提供了冷却夹套34对轴承套和轴承组件的冷却作用，但在实际应用中，冷却夹套34也可以通入导热油，对轴承套和轴承组件起到加热作用，也即，冷却夹套34同时具备冷却和加热两种作用。
在本实施例中，轴承组件4包括若干套设在主轴2上的主轴轴承36，以及套在主轴轴承36外的轴承固定套37，轴承固定套37与主轴轴承36外圈固定，主轴轴承36内圈与主轴2外壁固定，还包括若干与主轴轴承36一一对应的温度传感器38，所述的温度传感器38依次穿过机身3、轴承固定套37后直接与主轴轴承36的外圈接触，这种接触是静态接触，从而对主轴轴承36的温度得到实时监测，且由于温度传感器38直接与主轴轴承36外圈接触，检测到的温度为主轴轴承36的实际温度，温度检测准确可靠。
本文中所描述的具体实施例仅仅是对本发明精神作举例说明。本发明所属技术领域的技术人员可以对所描述的具体实施例做各种各样的修改或补充或采用类似的方式替代，但并不会偏离本发明的精神或者超越所附权利要求书所定义的范围。
尽管本文较多地使用了驱动机构1、机架1a、主轴2、机身3、轴承组件4、端部施力机构5、位移传感器6、轴向施力组件7、轴向丝杆8、轴向驱动器9、第一荷重传感器10、轴向缓冲器11、轴向接头12、轴向弹性座13、轴向定位卡圈14、轴向弹性件容置槽15、轴向弹性件16、径向施力组件17、径向丝杆18、径向驱动器19、第二荷重传感器20、径向缓冲器21、径向接头22、径向弹性座23、径向定位卡圈24、径向弹性件容置槽25、径向弹性件26、静态受力组件27、静态保持轴承28、转动座29、静态座30、轴承套31、控温元件32、电加热棒33、冷却夹套34、冷却介质通道35、主轴轴承36、轴承固定套37、温度传感器38等术语，但并不排除使用其它术语的可能性。使用这些术语仅仅是为了更方便地描述和解释本发明的本质，把它们解释成任何一种附加的限制都是与本发明精神相违背的。

Claims (18)

  1. 一种轴承动态特性试验机，包括驱动机构(1)，所述的驱动机构(1)连接主轴(2)从而能驱动主轴(2)周向转动，主轴(2)位于机身(3)内部且主轴(2)上套设有轴承组件(4)，其特征在于，还包括能向靠近或远离所述的主轴(2)端部方向移动从而与主轴(2)端部接触并对主轴(2)的端部施加压力的端部施力机构(5)，还包括与主轴(2)连接的位移传感器(6)。
  2. 根据权利要求1所述的轴承动态特性试验机，其特征在于，所述的端部施力机构(5)包括能沿水平方向往复运动的轴向施力组件(7)，所述的轴向施力组件(7)与主轴(2)的端面相对应。
  3. 根据权利要求2所述的轴承动态特性试验机，其特征在于，所述的轴向施力组件(7)包括呈水平设置的轴向丝杆(8)，以及连接轴向丝杆(8)从而能驱动轴向丝杆(8)沿水平方向往复运动的轴向驱动器(9)，所述的轴向丝杆(8)的端部设有第一荷重传感器(10)。
  4. 根据权利要求3所述的轴承动态特性试验机，其特征在于，所述的轴向丝杆(8)的端部设有轴向缓冲器(11)，第一荷重传感器(10)位于轴向缓冲器(11)上。
  5. 根据权利要求4所述的轴承动态特性试验机，其特征在于，所述的轴向缓冲器(11)包括与轴向丝杆(8)固定连接的轴向接头(12)，所述的轴向接头(12)上活动连接有一个轴向弹性座(13)，第一荷重传感器(10)固定在轴向弹性座(13)上。
  6. 根据权利要求5所述的轴承动态特性试验机，其特征在于，所述的轴向弹性座(13)套设在轴向接头(12)上，轴向弹性座(13)上卡接有轴向定位卡圈(14)，所述的轴向定位卡圈(14)与轴向接头靠近轴向丝杆(8)的一端卡接，轴向接头(12)内设有若干轴向弹性件容置槽(15)，所述的轴向弹性件容置槽(15)内设有轴向弹性件(16)，所述的轴向弹性件(16)的两端分别抵靠在轴向弹性件容置槽(15)的底部的轴向弹性座(13)的内壁 上。
  7. 根据权利要求1所述的轴承动态特性试验机，其特征在于，所述的端部施力机构(5)包括能沿竖直方向往复运动的径向施力组件(17)，所述的径向施力组件(17)位于主轴(2)端部上方。
  8. 根据权利要求7所述的轴承动态特性试验机，其特征在于，所述的径向施力组件(17)包括呈竖直设置的径向丝杆(18)，以及连接径向丝杆(18)从而能驱动径向丝杆(18)沿竖直方向往复运动的径向驱动器(19)，所述的径向丝杆(18)的端部设有第二荷重传感器(20)。
  9. 根据权利要求8所述的轴承动态特性试验机，其特征在于，所述的径向丝杆(18)的端部设有径向缓冲器(21)，第二荷重传感器(20)位于径向缓冲器(21)上。
  10. 根据权利要求1所述的轴承动态特性试验机，其特征在于，所述的径向缓冲器(21)包括与径向丝杆(18)固定连接的径向接头(22)，所述的径向接头(22)上活动连接有一个径向弹性座(23)，第二荷重传感器(20)固定在径向弹性座(23)上。
  11. 根据权利要求10所述的轴承动态特性试验机，其特征在于，所述的径向弹性座(23)套设在径向接头(22)上，径向弹性座(23)上卡接有径向定位卡圈(24)，所述的径向定位卡圈(24)与径向接头靠近径向丝杆(18)的一端卡接，径向接头(22)内设有若干径向弹性件容置槽(25)，所述的径向弹性件容置槽(25)内设有径向弹性件(26)，所述的径向弹性件(26)的两端分别抵靠在径向弹性件容置槽(25)的底部的径向弹性座(23)的内壁上。
  12. 根据权利要求1所述的轴承动态特性试验机，其特征在于，所述的主轴(2)端部设有一个静态受力组件(27)，所述的静态受力组件(27)内设有连接主轴(2)端部并能与主轴(2)同步转动的静态保持轴承(28)。
  13. 根据权利要求12所述的轴承动态特性试验机，其特征在于，所述的静态受力组件(27)包括连接主轴(2)端部的转动座(29)，以及套设在转动座(29)上的静态座(30)，静态保持轴承(28)位于转动座(29)和静态座(30)之间，静态保持轴承(28)的内圈与转动座(29)固定连接，静态保持轴承(28)的外圈与静态座(30)固定连接。
  14. 根据权利要求1所述的轴承动态特性试验机，其特征在于，所述的轴承组件(4)有两个且位于主轴(2)的两端，所述的机身(3)包括套设在轴承组件(4)外的轴承套(31)，所述的轴承套(31)内设有控温元件(32)。
  15. 根据权利要求14所述的轴承动态特性试验机，其特征在于，所述的控温元件(32)包括设置在轴承套(31)内的电加热棒(33)，以及与轴承组件(4)的位置相对应的冷却夹套(34)。
  16. 根据权利要求15所述的轴承动态特性试验机，其特征在于，所述的冷却夹套(34)位于轴承套(31)内部，或者轴承套(31)与轴承组件(4)的外壁合围形成冷却夹套(34)。
  17. 根据权利要求16所述的轴承动态特性试验机，其特征在于，所述的轴承套(31)内设有连接冷却夹套(34)的冷却介质通道(35)。
  18. 根据权利要求1所述的轴承动态特性试验机，其特征在于，所述的轴承组件(4)包括若干套设在主轴(2)上的主轴轴承(36)，以及套在主轴轴承(36)外的轴承固定套(37)，还包括若干与主轴轴承(36)一一对应的温度传感器(38)，所述的温度传感器(38)依次穿过机身(3)、轴承固定套(37)后直接与主轴轴承(36)的外圈接触。
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111721532A (zh) * 2020-05-22 2020-09-29 扬州市舜意机械有限公司 一种长杆类杆端关节轴承内外圈同步转动试验机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110044617B (zh) * 2019-04-23 2021-02-09 宁波梦创信息科技有限公司 一种用于样品轴承性能测试设备

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009150687A (ja) * 2007-12-19 2009-07-09 Ntn Corp 軸受の回転精度の測定装置
JP2009250797A (ja) * 2008-04-07 2009-10-29 Ntn Corp 転がり軸受用潤滑剤の潤滑性評価装置および潤滑性評価方法
CN102072816A (zh) * 2010-05-21 2011-05-25 浙江八环轴承有限公司 轴承试验机
CN102636348A (zh) * 2012-04-10 2012-08-15 洛阳轴研科技股份有限公司 高速轴承试验机
CN106404395A (zh) * 2016-08-31 2017-02-15 洛阳轴研科技股份有限公司 轴承试验装置
CN207516030U (zh) * 2017-10-13 2018-06-19 人本集团有限公司 卡车轮毂轴承的检测装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005172717A (ja) * 2003-12-15 2005-06-30 Nsk Ltd 転がり軸受の振動測定装置
CN102778345A (zh) * 2012-02-10 2012-11-14 青海华鼎实业股份有限公司 一种模拟工况的主轴加载测试装置
CN102854014A (zh) * 2012-09-13 2013-01-02 河南科技大学 角接触球轴承保持架动态性能试验装置
KR101579282B1 (ko) * 2014-07-23 2015-12-21 한국과학기술연구원 베어링의 내구성을 시험하기 위한 베어링의 시험 장치
CN105136457B (zh) * 2015-06-03 2017-10-17 重庆大学 高低温可控多规格滚动轴承试验台
CN107367388B (zh) * 2017-08-25 2023-02-24 西安工业大学 航空滚动轴承热稳定性测试装置
CN208653800U (zh) * 2018-08-13 2019-03-26 浙江优特轴承有限公司 轴承动态特性试验机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009150687A (ja) * 2007-12-19 2009-07-09 Ntn Corp 軸受の回転精度の測定装置
JP2009250797A (ja) * 2008-04-07 2009-10-29 Ntn Corp 転がり軸受用潤滑剤の潤滑性評価装置および潤滑性評価方法
CN102072816A (zh) * 2010-05-21 2011-05-25 浙江八环轴承有限公司 轴承试验机
CN102636348A (zh) * 2012-04-10 2012-08-15 洛阳轴研科技股份有限公司 高速轴承试验机
CN106404395A (zh) * 2016-08-31 2017-02-15 洛阳轴研科技股份有限公司 轴承试验装置
CN207516030U (zh) * 2017-10-13 2018-06-19 人本集团有限公司 卡车轮毂轴承的检测装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111721532A (zh) * 2020-05-22 2020-09-29 扬州市舜意机械有限公司 一种长杆类杆端关节轴承内外圈同步转动试验机
CN111721532B (zh) * 2020-05-22 2022-08-09 扬州市舜意机械有限公司 一种长杆类杆端关节轴承内外圈同步转动试验机

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