CN108760275B - Device and method for analyzing static rigidity of combination part of cutter, cutter handle and main shaft system - Google Patents
Device and method for analyzing static rigidity of combination part of cutter, cutter handle and main shaft system Download PDFInfo
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Abstract
The invention mainly aims at a device and a method for analyzing the static rigidity of a cutter-cutter handle-main shaft system joint, which are used for carrying out simulation test and display analysis to obtain the static rigidity values of the cutter-cutter handle joint and the cutter handle-main shaft joint. The device comprises a test box body, a cutter handle, a broach structure, a simulated main shaft head, an axial and radial loading device, an axial and radial pressure sensor, an axial and radial displacement sensor and a bracket thereof, a control box digital display meter and a computer. The invention can realize the static stiffness test of various types of cutter-handle-main shaft systems, is convenient to assemble and disassemble during the test, can display and record the obtained data through a control box digital display table, can also output the data to a computer for display and analysis, and has important significance for researching the static performance of the cutter-handle-main shaft systems.
Description
Technical Field
The invention belongs to the technical field of machine design and manufacture, and particularly relates to a device and a method for simulating, testing and analyzing the static stiffness of a joint part of a cutter-handle-main shaft system.
Background
High speed machine tools are a basic index of the state of the art, and the performance of high speed machine tool systems directly affects the machining performance of the machine tools. The high-speed processing tool system can be simply summarized as a cutter-cutter handle-main shaft system, and the influence of the part for transmitting power and precision, namely a joint part, in the system on the system performance is particularly important because the static rigidity of materials such as cutter handles, cutters, main shafts and the like in the tool system is already determined. The factors influencing the rigidity of the cutter handle-main shaft combination part are mainly tension force of a broach structure, the factors influencing the rigidity of the cutter handle combination part are mainly fit length of the cutter handle, no scientific and reasonable effective reference basis exists for the factors in the actual machining process at present, unreasonable tension force, cutter interference magnitude and fit length can influence the machining precision and quality of a machine tool, and parts can be damaged under serious conditions to cause serious safety accidents.
The HSK knife handle is used as the knife handle tool most commonly used in a high-speed numerical control machine tool and a machining center in the current market, has the advantages of high rigidity, reliable connection performance, short transmission chain and the like, but the time that the shaped knife handle becomes an international standard is short, a market user has a lot of erroneous knowledge on the shaped knife handle, a lot of problems are not enough scientific demonstration, complete and comprehensive use specifications are lacked, such as the standard of the tension force and the broach structure does not meet the machining precision requirement, and the knife handle, the knife interference and the knife handle matching length are not in accordance with the standard. Therefore, the research on the static rigidity of the joint of the spindle and the cutter has important significance for improving the machining performance of the machine tool.
Disclosure of Invention
In order to solve the defects in the prior art, the invention provides a device for simulating and testing the static stiffness of a joint part of a cutter-handle-main shaft system, which is characterized by comprising the following components:
the test box body is provided with a test box body,
the first side surface of the test box body is embedded and fixed with the front end of the simulated main shaft head, and a cutter handle is arranged on the front end part of the simulated main shaft head extending into the test box body to form a cutter handle-main shaft combination part;
the front end part of the simulated main shaft head outside the test box body is connected with the rear end of the simulated main shaft head, and an axial loading device for applying axial force to the combined part of the cutter handle and the main shaft is arranged at the rear end of the simulated main shaft head;
the top of the test box body is embedded into and fixedly provided with a radial loading device which applies radial force to the combined part of the cutter handle and the main shaft;
the lower side of the tool handle is provided with a first radial displacement sensor and a second radial displacement sensor, and the displacement of the tool handle relative to the front end of the spindle head is detected.
Preferably, the axial loading device comprises: the device comprises a pull rod, an axial loading nut, a plane bearing, an axial pressure sensor, a belleville spring, a gasket A and a gasket B;
the first side surface of the axial pressure sensor is connected with the rear end of the simulated main shaft head;
the pull rod sequentially passes through the disc spring, the gasket A, the plane bearing, the gasket B, the axial pressure sensor, the rear end of the simulated main shaft head and the front end of the simulated main shaft head, and the first tail end of the pull rod contacts a broach structure arranged at the front end of the simulated main shaft head;
the axial loading nut is arranged at the second end of the pull rod;
the flat bearing prevents rotational movement from being transmitted to the axial pressure sensor and the belleville springs tighten the washers A and B during use.
Preferably, a first axial displacement sensor and a second axial displacement sensor are arranged on the upper side and the lower side of the tool handle, and the axial inclination condition of the tool handle is detected in the process that the tightening force of the tool handle is increased.
Preferably, an axial displacement sensor bracket is arranged at the front end of the simulated main shaft head and used for supporting the first axial displacement sensor and the second axial displacement sensor;
the front end of the simulated main shaft head is provided with a radial displacement sensor bracket which supports and moves the first radial displacement sensor and the second radial displacement sensor.
Preferably, the test box further comprises: a cutter is arranged on the overhanging end of the other side of the cutter handle to form a cutter handle-cutter combination part;
the first radial displacement sensor and the second radial displacement sensor are also positioned at the lower side of the cutter, and detect the displacement of the cutter relative to the front end of the main shaft head;
the radial loading device further comprises:
a radial loading seat is arranged on the upper surface of the base,
the radial loading seat is internally provided with a radial loading screw, the first end of the radial loading screw is exposed outside the test box body, and the second end of the radial loading screw is arranged on the first side surface of the radial pressure sensor;
the second side of the radial pressure sensor is provided with a pressure head, and the pressure head applies radial loading force to the cutter handle or the cutter.
Preferably, the front end of the simulated main shaft head, the rear end of the simulated main shaft head, the cutter handle and the cutter with different specifications and types are arranged on the test box body according to the specific test requirements;
the device also comprises a control box digital display meter and a computer, and the combination displacement condition is measured by adjusting the axial and radial loading devices and is displayed by the control box digital display meter; or (b)
And the static rigidity of the cutter handle-main shaft combination part under different tensioning force states is calculated and obtained by transmitting the static rigidity to a computer through a data transmission device, wherein the static rigidity of the cutter handle-main shaft combination part under different cutter-cutter handle combination lengths and different cutter interference magnitudes is calculated and obtained.
Preferably, the shank part of the tool shank is positioned in an inner taper hole at the front end of the main shaft head; the broach structure at the front end of the simulated main shaft head is fixed with the tool handle, and tension is applied to the tool handle to tighten the joint part of the tool handle and the main shaft.
A static stiffness simulation test analysis method for a combination part of a cutter-cutter handle-main shaft system, which utilizes a static stiffness simulation test analysis device for the combination part of the cutter-cutter handle-main shaft system to test the axial stiffness of the combination part of the cutter handle-main shaft, and does not clamp the cutter and apply radial pressure; tightening and loosening the axial loading nut, and applying tensioning forces with different magnitudes to the tool handle, wherein the magnitudes of the tensioning forces are measured by the axial pressure sensor; the first axial displacement sensor and the second axial displacement sensor are used for measuring the axial displacement of the tool shank relative to the front end of the spindle head; and obtaining the relation between the axial loading force and the axial rigidity of the joint part from the relation between the axial loading force and the axial displacement.
Preferably, the combined part static stiffness simulation test analysis device of the cutter-cutter handle-spindle system is utilized to test the radial stiffness and the angular stiffness of the combined part of the cutter handle-spindle, the cutter is not clamped, and the axial loading nut is rotated to determine the axial tension force; adjusting the pressure position of the radial loading device, and applying radial pressure to the overhanging end of the cutter handle; the radial loading screw is regulated, so that the pressure head acts on the tool handle with radial pressure of different magnitudes, and the joint part generates radial displacement and angular displacement;
establishing a coordinate system O-XYZ of a cutter handle-main shaft combination part, and radially loading force F z When acting on the overhanging end of the knife handle, the following formula is satisfied:
wherein the radial displacement measured by the first radial displacement sensor and the second radial displacement sensor is delta ZA 、δ ZB The method comprises the steps of carrying out a first treatment on the surface of the The knife handle is subjected to radial loading force F z The relative radial displacement d 0 The method comprises the steps of carrying out a first treatment on the surface of the The knife handle generates angular displacement d under radial loading force 1 The resulting displacement d 1 Elastic deformation d of the' and shank under radial loading force 2 ；
It is assumed here that the shank portion of the shank is not bent and deformed, so that only the relative radial displacement d of the shank-spindle junction 0 And angular displacement d 1 ；
According to the assumption, calculating the elastic deformation d of the overhanging end of the knife handle by finite element software 2 ；
The following formula is given:
wherein the distance between the measured O point and the first radial displacement sensor is l 1 The method comprises the steps of carrying out a first treatment on the surface of the The distance from the O point to the second radial displacement sensor is l 2 ；
Measuring radial loading force F by measuring device z And delta ZA 、δ ZB Is combined with the above formula to obtain the radial loading force F z With relative radial displacement d 0 Further deriving the radial stiffness K of the shank-spindle junction 0 ：
Measuring radial loading force F by measuring device z And delta ZA 、δ ZB Has M according to the bending moment formula 1 ＝F Z ·l 3 ；l 3 Is the distance from the O point to the radial loading force application point; is combined withThe bending moment M is obtained by the formula 1 And angular displacement d 1 Further deriving the angular stiffness K of the shank-spindle junction 1 ：
Preferably, when the radial rigidity and the angular rigidity of the cutter-cutter handle combination part are tested, after the cutter handle clamps the cutter, the position of the radial loading device is moved so that radial pressure is applied to the overhanging end of the cutter; after the clamping length of a cutter handle is determined, the radial loading screw is adjusted to enable the pressure head to act on the cutter with different pressures, so that the joint part is displaced;
radial loading force F z When acting on the cutter, the following formula is satisfied:
wherein, the second radial displacement sensor is arranged at the tail end of the overhanging end of the knife handle, and the radial displacement delta of the tail end of the overhanging end of the knife handle is measured ZB Then the first radial displacement sensor and the second radial displacement sensor are arranged on the cutter part to measure the radial displacement delta ZA ' and delta ZB 'A'; relative radial displacement d of tool relative to shank by radial loading force 3 The tool is subjected to radial loading force to generate angular displacement d relative to the tool shank 4 The resulting displacement d 4 Elastic deformation d of' and tool under radial loading force 5 ；
The distance between the tail end of the overhanging end of the knife handle and the first radial displacement sensor is l 4 The distance from the tail end of the overhanging end of the knife handle to the second radial displacement sensor is l 5 Solving the relative radial displacement d of the cutter-cutter handle combination part 3 And angular displacement d 4 ：
Measuring radial loading force F by measuring device z ' and delta ZA ”、δ ZB "in combination with the above formula to obtain the radial loading force F z ' and relative radial displacement d 3 Further deriving the radial stiffness K of the tool-shank junction 2 ：
Measuring radial loading force F by measuring device z ' and delta ZA ”、δ ZB "according to the bending moment formula
M 2 ＝F Z '·l 6
Wherein l 6 The distance from the tail end of the overhanging end of the knife handle to the radial loading force acting point; the bending moment M is obtained by combining the formulas 2 And angular displacement d 4 Further deriving the angular stiffness K of the tool-shank junction 2 ：
The invention can realize the static stiffness test of various types of cutter-handle-main shaft systems, is convenient to assemble and disassemble during the test, can display and record the obtained data through a control box digital display table, can also output the data to a computer for display and analysis, and has important significance for researching the static performance of the cutter-handle-main shaft systems.
Drawings
FIG. 1 is a schematic diagram of a simulation test analysis apparatus;
FIG. 2 is a schematic diagram of a simulation test analysis apparatus;
FIG. 3 is a schematic illustration of an axial stiffness test;
FIG. 4 is a schematic illustration of a handle-spindle static stiffness test;
FIG. 5 is a schematic view of a tool-shank static stiffness test;
FIG. 6 is a schematic diagram of a tool shank-spindle junction radial stiffness and angular stiffness solution;
FIG. 7 is a schematic diagram of a solution for the radial stiffness and angular stiffness of the tool-shank junction.
Detailed Description
The following detailed description of the embodiments is provided.
As shown in fig. 2, a device for simulating and testing the static stiffness of a joint part of a cutter-handle-main shaft system comprises: the testing box body (1), testing box body protective screen (2), simulation main shaft front end (3), simulation main shaft rear end (4), pull rod (5), axial loading nut (6), belleville spring (7), packing ring A (8), packing ring B (9), plane bearing (10), broach structure (11), axial displacement sensor support (12), radial displacement sensor support (13), axial pressure sensor (14), radial pressure sensor (15), handle of a knife (16), cutter (17), radial loading seat (18), radial loading screw (19), pressure head (20), axial displacement sensor A (21), axial displacement sensor B (22), radial displacement sensor A (23), radial displacement sensor B (24).
The front end (3) of the simulated main shaft head is embedded and fixed on the first side surface of the test box body (1), and a cutter handle (16) is arranged on the front end (3) part of the simulated main shaft head extending into the test box body to form a cutter handle-main shaft combination part; a cutter (17) can be arranged on the overhanging end of the other side of the cutter handle (16) to form a cutter handle-cutter combination part. The taper shank part of the shank (16) is positioned in an inner taper hole at the front end (3) of the main shaft head, and the front end (3) of the simulation main shaft head is provided with a broach structure (11) which is fixed with the shank (16).
The front end (3) of the simulated main shaft head outside the test box body is connected with the rear end (4) of the simulated main shaft head, and the rear end (4) of the simulated main shaft head is attached to the first side surface of the axial pressure sensor (14); the pull rod (5) sequentially passes through the axial pressure sensor (14), the rear end (4) of the simulated main shaft head and the front end (3) of the simulated main shaft head, and the first tail end of the pull rod contacts the junction of the tool handle and the main shaft; the second end of the pull rod (5) is provided with an axial loading nut (6); a planar bearing (10) for preventing rotational motion from being transmitted to the axial pressure sensor (14), the planar bearing being arranged on the second surface of the axial pressure sensor (14), and a gasket A (8) and a gasket B (9) being arranged on both sides of the planar bearing (10); a belleville spring (7) which is continuously required to be tightened in the use process of the gasket A (8) and the gasket B (9) is arranged between the gasket A (8) and the axial loading nut (6); the belleville springs (7), the washers A (8), the washers B (9) and the plane bearings (10) are all sleeved on the pull rod (5).
The top of the test box body is inserted with a radial loading seat (18), a radial loading screw (19) is arranged in the radial loading seat (18), the radial loading screw (19) is rotated, radial pressure is transmitted to a pressure head (20) arranged at the bottom of the radial loading seat (18) through a radial pressure sensor (15), and the pressure head (20) applies radial loading force to the cutter handle (16) or the cutter (17); a radial pressure sensor (15) for measuring the radial loading force, which is arranged between the radial loading screw (19) and the pressure head (20).
The lower side of the tool shank (16) or the tool (17) is provided with radial displacement sensors (23) (24), and the measured displacement is that the tool shank (16) is displaced relative to the front end (3) of the spindle head or the tool (17) relative to the tool shank (16); axial sensors (21) and (22) are arranged on the upper side and the lower side of the tool handle (16), and the axial inclination condition of the tool handle (16) is detected in the process that the tightening force of the tool handle (16) is increased; an axial displacement sensor bracket (12) is arranged at the front end (3) of the simulation main shaft head and used for supporting the axial displacement sensors (21) (22); a radial displacement sensor holder (13) is provided at the front end (3) of the dummy spindle head, and the radial displacement sensors (24) (25) supported by the holder are movable.
As shown in figure 1, the device also comprises a control box digital display meter and a computer, and the combination displacement condition is measured by adjusting the axial and radial loading devices and is displayed by the control box digital display meter; or the static rigidity of the cutter handle-main shaft combination part under different tensioning force states is calculated and obtained by transmitting the static rigidity to a computer through a data transmission device, wherein the static rigidity of the cutter handle-main shaft combination part under different cutter-cutter handle combination lengths and different cutter interference magnitudes is calculated and obtained.
The test box body (1) is provided with simulated main shaft heads (3) (4), tool shanks (16) and cutters (17) with different specifications and types according to specific test requirements, and the tool shanks used in the preferred embodiment of the invention are HSK63 series tool shanks (16).
As shown in figure 3, when the axial rigidity test of the junction between the cutter handle (16) and the main shaft (3) is carried out, the cutter (17) is not clamped, radial pressure is not applied, the axial loading nut (6) is loosened by tightening, the tension forces with different magnitudes are applied to the cutter handle (16), and the magnitude of the tension force is measured by the axial pressure sensor (14). The disc spring (7) is adopted in the axial loading device, so that the continuous requirement on tightening in the using process of the gaskets (8) and (9) can be reduced. The use of a planar bearing (10) is mainly intended to prevent rotational movement from being transmitted to the axial pressure sensor (14) during rotation of the axial loading nut (6). The axial displacement sensor bracket (12) is fixed at the front end (3) of the main shaft head, so that the displacement measured by the axial displacement sensors (21) (22) is the axial displacement of the tool shank (16) relative to the front end (3) of the main shaft head, namely the axial displacement of the joint part of the tool shank (16) and the main shaft (3), thus ensuring that the displacement only comprises the axial deformation of the joint part of the tool shank (16) and the main shaft (3), and not affecting the data accuracy due to the deformation of other parts. By adopting two sets of axial displacement sensors (21) (22), whether the knife handle (16) inclines in the process of increasing the tensioning force can be detected, and the tensioning force is ensured to be along the axial direction. The data measured by the axial pressure and the axial displacement can be displayed on a control box digital display meter or a computer. From the axial loading force-axial displacement relationship, the relationship of the axial loading force-joint axial stiffness can be obtained.
As shown in fig. 4, when the radial rigidity and the angular rigidity of the junction between the cutter handle (16) and the main shaft (3) are tested, the cutter (17) is not clamped, and the pressure position of the radial loading device is adjusted so that the radial loading device applies radial pressure to the overhanging end of the cutter handle (16). After the axial tensioning force is determined by rotating the axial loading nut (6), the radial loading screw (19) is adjusted to enable the pressure head (20) to act on the tool handle (16) under different pressures, so that radial displacement and angular displacement are generated at the joint part, and the radial pressure is measured by the radial pressure sensor (15).
As shown in figure 5, when the device is used for testing the radial rigidity and the angular rigidity of the joint of the cutter (17) and the cutter handle (16), the cutter (17) is clamped, and the pressure position of the radial loading device is adjusted so that the radial loading device applies radial pressure to the overhanging end of the cutter (17). After the clamping length of a cutter (17) and a cutter handle (16) is determined, the radial loading screw (19) is adjusted to enable the pressure head (20) to act on the cutter (16) with different pressures, so that the joint is displaced, and the radial pressure is measured by the radial pressure sensor (15).
By adopting the radial loading seat (18), the radial loading screw (19) and the pressure head (20) can be positioned on the same axis, and the radial pressure can be ensured to act on the central axes of the cutter (17) and the cutter handle (16) vertically. The radial displacement sensor bracket (13) is fixed at the front end (3) of the main shaft head, so that the displacement measured by the radial displacement sensors (23) (24) is the displacement of the cutter (17) and the cutter handle (16) relative to the front end (3) of the main shaft head, and the accuracy of data can be ensured not to be influenced by the deformation of other parts. The radial displacement and the angular displacement of the joint can be resolved by adopting two sets of radial displacement sensors (23) (24), so that the radial rigidity and the angular rigidity of the joint can be calculated. The data measured by the radial pressure and the radial displacement value can be displayed on a control box digital display table or a computer. From the radial loading force-radial displacement relationship, the relationship of the radial loading force-radial rigidity of the joint can be obtained; from the bending moment-angular displacement relationship, a relationship of bending moment-joint angular stiffness can be obtained.
By adjusting the axial loading nut (6), selecting different interference amounts of the cutter (17) and the matching length of the cutter handle (16) of the cutter (17), and combining the radial rigidity and angular rigidity testing method of the combination part, the radial loading force-radial rigidity relation of the combination part and the angular rigidity relation of the bending moment-combination part can be obtained.
The radial stiffness and angular stiffness solving process of the tool shank (16) -spindle (3) joint is described in detail below.
The tool shank (16) does not hold the tool (17) when measuring the radial stiffness and the angular stiffness of the shank (16) -spindle (3) joint.
As shown in fig. 6, a coordinate system O-XYZ of the combination part of the cutter handle (16) and the main shaft (3) is established, and the radial loading force F is applied z Acting on the overhanging end of the knife handle (16), and measuring radial displacement delta by a radial displacement sensor A (23) and a radial displacement sensor B (24) ZA And delta ZB The displacement consists of three parts: the shank (16) is subjected to a radial loading force F z The relative radial displacement d 0 The knife handle (16) generates angular displacement d under radial loading force 1 The resulting displacement d 1 ' He knifeElastic deformation d of the shank (16) under radial loading force 2 The method comprises the following steps:
since the shank (16) is shorter and located in the head of the spindle (3), it is assumed here that the shank (16) is not bent, so that only the relative radial displacement d of the shank (16) -spindle (3) joint is 0 And angular displacement d 1 。
According to the assumption, the elastic deformation d of the overhanging end of the knife handle (16) is calculated by finite element software 2 。
The distance from the measured O point to the radial displacement sensor A (23) is l 1 The distance from the O point to the sensor B is l 2 。
From the geometrical relationships, it is known that:
solving the relative radial displacement d of the combination part of the cutter handle (16) and the main shaft (3) 0 And angular displacement d 1 ：
Measuring radial loading force F by measuring device z And delta ZA 、δ ZB Is combined with the above formula to obtain the radial loading force F z With relative radial displacement d 0 Further deriving the radial stiffness K of the junction between the shank (16) and the spindle (3) 0 ：
Measuring radial loading force F by measuring device z And delta ZA 、δ ZB Has M according to the bending moment formula 1 ＝F Z ·l 3 (l 3 Distance from O point to radial loading force application point), and combining the above formula to obtain bending moment M 1 And angular displacement d 1 Further deriving the angular stiffness K of the junction between the shank (16) and the spindle (3) 1 ：
The radial stiffness and angular stiffness solving process of the tool (17) -shank (16) joint is described in detail below.
After the cutter (17) is clamped by the cutter handle (16), the position of the radial loading seat (18) is adjusted so that radial pressure acts on the cutter (17), and the cutter (17) and the cutter handle (16) are displaced due to stress. As shown in FIG. 7, when radial load is applied to the tool (17), the shank (16) is subjected to a radial loading force F corresponding to the above z Acting on the end of the overhanging end of the shank (16), in this case l 3 Equal to the distance from O to the tail end of the overhanging end of the knife handle (16), and the displacement condition of the knife handle (16) is analyzed according to the condition.
Firstly, a radial displacement sensor B (24) is arranged at the tail end of the overhanging end of the knife handle (16), and the radial displacement delta of the tail end of the overhanging end of the knife handle (16) is measured ZB Then, the radial displacement sensor A (23) and the radial displacement sensor B (24) are arranged on the cutter (17) to measure the radial displacement delta ZA ' and delta ZB ' the radial displacement of the tool (17) relative to the shank (16) is
Displacement delta ZA "and delta ZB "consists of three parts: relative radial displacement d of the tool (17) relative to the shank (16) under radial loading force 3 The tool (17) is angularly displaced d relative to the shank (16) by a radial loading force 4 The resulting displacement d 4 Elastic deformation d of the' and the cutter (17) under radial loading force 5 The method comprises the following steps:
since the clamped portion of the tool (17) is within the shank (16) and the clamped portion is relatively short, the elastic deformation of the clamped portion is negligible, i.e., the elastic deformation of the tool (17) occurs only at the overhanging end of the tool (17).
The elastic deformation d of the tool (17) part can be calculated by finite element software 5 。
The distance from the tail end of the overhanging end of the knife handle (16) to the sensor A is l 4 The distance from the tail end of the overhanging end of the knife handle (16) to the sensor B is l 5 。
From the geometrical relationships, it is known that:
solving the relative radial displacement d of the combination part of the cutter (17) and the cutter handle (16) 3 And angular displacement d 4 ：
Measuring radial loading force F by measuring device z ' and delta ZA ”、δ ZB "in combination with the above formula to obtain the radial loading force F z ' and relative radial displacement d 3 Further deriving the radial stiffness K of the tool (17) -shank (16) joint 2 ：
Measuring radial loading force F by measuring device z ' and delta ZA ”、δ ZB "has M according to the bending moment formula 2 ＝F Z '·l 6 (l 6 The distance from the end of the overhanging end of the shank (16) to the point of application of the radial loading force, combined withThe bending moment M is obtained by the formula 2 And angular displacement d 4 Further deriving the angular stiffness K of the tool (17) -shank (16) joint 2 ：
While the present invention has been described in detail through the foregoing description of the preferred embodiment, it should be understood that the foregoing description is not to be considered as limiting the invention. Many modifications and substitutions of the present invention will become apparent to those of ordinary skill in the art upon reading the foregoing. Accordingly, the scope of the invention should be limited only by the attached claims.
Claims (10)
1. The utility model provides a quiet rigidity simulation test analytical equipment of joint part of cutter-handle of a knife-main shaft system which characterized in that contains:
a test box body (1),
the front end (3) of the simulated main shaft head is embedded and fixed on the first side surface of the test box body, and a cutter handle (16) is arranged on the front end (3) part of the simulated main shaft head extending into the test box body to form a cutter handle-main shaft combination part;
the front end (3) of the simulated main shaft head outside the test box body is connected with the rear end (4) of the simulated main shaft head, and an axial loading device for applying axial force to the combined part of the cutter handle and the main shaft is arranged at the rear end (4) of the simulated main shaft head;
the overhanging end of the knife handle (16) is used for arranging a knife (17) to form a knife-knife handle combination part;
the top of the test box body is embedded and fixed with a radial loading device, and the position of the radial loading device at the top of the test box body is adjustable and is used for applying radial loading force to the cutter handle (16) or the cutter (17);
when the radial rigidity and the angular rigidity of the combination part of the cutter handle and the main shaft are tested, the cutter handle (16) does not clamp the cutter (17); the position of the radial loading device is regulated, and radial pressure is applied to the overhanging end of the cutter handle (16) through the radial loading device, so that radial displacement and angular displacement are generated at the joint part of the cutter handle and the main shaft; the first radial displacement sensor (23) and the second radial displacement sensor (24) are positioned at the lower side of the tool shank (16) and are used for detecting the displacement of the tool shank (16) relative to the front end (3) of the simulated main shaft head;
when the radial rigidity and angular rigidity of the cutter-cutter handle combination part are tested, the cutter handle (16) clamps the cutter (17), the position of the radial loading device is moved, and radial pressure is applied to the overhanging end of the cutter (17) through the radial loading device, so that the radial displacement and the angular displacement of the cutter-cutter handle combination part are generated; the first radial displacement sensor (23) and the second radial displacement sensor (24) are positioned at the lower side of the cutter (17) and are used for detecting the displacement of the cutter (17) relative to the front end (13) of the spindle head.
2. The tool-shank-spindle system joint static stiffness simulation test analysis device according to claim 1, wherein the axial loading device comprises: the device comprises a pull rod (5), an axial loading nut (6), a plane bearing (10), an axial pressure sensor (14), a belleville spring (7), a gasket A (8) and a gasket B (9);
the first side surface of the axial pressure sensor (14) is connected with the rear end (4) of the simulated main shaft head;
the pull rod (5) sequentially passes through the disc spring (7), the gasket A (8), the plane bearing (10), the gasket B (9), the axial pressure sensor (14), the rear end (4) of the simulated main shaft head and the front end (3) of the simulated main shaft head, and then the first tail end of the pull rod contacts the broach structure (11) arranged at the front end (3) of the simulated main shaft head;
the axial loading nut (6) is arranged at the second end of the pull rod (5);
the flat bearing (10) prevents rotational movements from being transmitted to the axial pressure sensor (14), and the belleville spring (7) tightens the washer A (8) and the washer B (9) during use.
3. The device for simulating and testing and analyzing the static stiffness of the joint part of the cutter, the cutter handle and the main shaft according to claim 2, wherein a first axial displacement sensor (21) and a second axial displacement sensor (22) are arranged on the upper side and the lower side of the cutter handle (16), and the axial inclination condition of the cutter handle (16) in the process of increasing the tension force is detected.
4. A tool-shank-spindle system joint static stiffness simulation test analysis device according to claim 3, characterized in that an axial displacement sensor bracket (12) is arranged at the front end (3) of the simulation spindle head to support the first axial displacement sensor (21) and the second axial displacement sensor (22); the front end (3) of the simulation main shaft head is provided with a radial displacement sensor bracket (13) for supporting and moving the first radial displacement sensor (23) and the second radial displacement sensor (24).
5. The tool-shank-spindle system joint static stiffness simulation test analysis device according to claim 4, wherein the radial loading device further comprises:
the radial loading seat (18), a radial loading screw (19) is arranged in the radial loading seat (18), a first end of the radial loading screw (19) is exposed outside the test box body (1), and a second end of the radial loading screw is arranged on the first side surface of the radial pressure sensor (15);
a second side of the radial pressure sensor (15) is provided with a pressure head (20), and the pressure head (20) applies radial loading force to the tool shank (16) or the tool (17).
6. The device for simulating and testing the static stiffness of the joint part of the cutter-handle-spindle system according to claim 5, wherein the front end (3), the rear end (4), the handle (16) and the cutter (17) of the simulated spindle heads with different specification types are arranged on the testing box body (1) according to specific testing requirements;
the device also comprises a control box digital display meter and a computer, and the combination displacement condition is measured by adjusting the axial and radial loading devices and is displayed by the control box digital display meter; or (b)
And the static rigidity of the cutter handle-main shaft combination part under different tensioning force states is calculated and obtained by transmitting the static rigidity to a computer through a data transmission device, wherein the static rigidity of the cutter handle-main shaft combination part under different cutter-cutter handle combination lengths and different cutter interference magnitudes is calculated and obtained.
7. The device for simulating and testing and analyzing the static stiffness of the joint part of the cutter-cutter handle-main shaft system according to claim 2, wherein the taper shank part of the cutter handle (16) is positioned in an inner taper hole at the front end (3) of the main shaft head; the broach structure (11) of the front end (3) of the simulated main shaft head is fixed with the tool shank (16), and a pulling force is applied to the tool shank (16) to tighten the tool shank-main shaft joint.
8. The method for simulating, testing and analyzing the static stiffness of the joint of the cutter, the cutter handle and the main shaft is characterized in that the device for simulating, testing and analyzing the static stiffness of the joint of the cutter, the cutter handle and the main shaft is used for testing the axial stiffness of the joint of the cutter handle and the main shaft, and the cutter (17) is not clamped and the radial pressure is not applied; tightening and loosening the axial loading nut (6), applying tensioning forces with different magnitudes to the tool shank (16), wherein the magnitudes of the tensioning forces are measured by the axial pressure sensor (14); a first axial displacement sensor (21) and a second axial displacement sensor (22) for measuring the axial displacement of the tool shank (16) relative to the front end (3) of the spindle head; obtaining the relation between the axial loading force and the axial rigidity of the joint part according to the relation between the axial loading force and the axial displacement;
when the radial rigidity and the angular rigidity of the combination part of the cutter handle and the main shaft are tested, the cutter handle (16) does not clamp the cutter (17); the position of the radial loading device is regulated, and radial pressure is applied to the overhanging end of the cutter handle (16) through the radial loading device, so that radial displacement and angular displacement are generated at the joint part of the cutter handle and the main shaft; the first radial displacement sensor (23) and the second radial displacement sensor (24) are positioned at the lower side of the tool shank (16), and detect the displacement of the tool shank (16) relative to the front end (3) of the spindle head; when the radial rigidity and angular rigidity of the cutter-cutter handle combination part are tested, the cutter handle (16) clamps the cutter (17), the position of the radial loading device is moved, and radial pressure is applied to the overhanging end of the cutter (17) through the radial loading device, so that the radial displacement and the angular displacement of the cutter-cutter handle combination part are generated; the first radial displacement sensor (23) and the second radial displacement sensor (24) are positioned at the lower side of the cutter (17), and detect the displacement of the cutter (17) relative to the front end (13) of the spindle head.
9. The method for simulating and analyzing the static stiffness of the joint of the cutter-handle-spindle system according to claim 8, wherein the device for simulating and analyzing the static stiffness of the joint of the cutter-handle-spindle system according to claim 5 is used for testing the radial stiffness and the angular stiffness of the joint of the handle-spindle without clamping the cutter (17), and the axial tension force is determined by rotating the axial loading nut (6); adjusting the pressure position of the radial loading device, and applying radial pressure to the overhanging end of the knife handle (16); the radial loading screw (19) is adjusted to enable the pressure head (20) to act on the tool handle (16) with radial pressure of different magnitudes, so that radial displacement and angular displacement are generated at the joint of the tool handle and the main shaft;
establishing a coordinate system O-XYZ of a cutter handle-main shaft combination part, and radially loading force F z When acting on the overhanging end of the shank (16), the following formula is satisfied:
wherein the radial displacement measured by the first radial displacement sensor (23) and the second radial displacement sensor (24) is delta ZA 、δ ZB The method comprises the steps of carrying out a first treatment on the surface of the The shank (16) is subjected to a radial loading force F z The relative radial displacement d 0 The method comprises the steps of carrying out a first treatment on the surface of the The knife handle (16) generates angular displacement d under radial loading force 1 The resulting displacement d 1 Elastic deformation d of the' and shank (16) by radial loading force 2 ；
It is assumed here that the shank (16) is not bent and deformed, so that only the relative radial displacement d of the shank-spindle junction 0 And angular displacement d 1 ；
According to the assumption, the elastic deformation d of the overhanging end of the knife handle (16) is calculated by finite element software 2 ；
The following formula is given:
wherein the distance between the measured O point and the first radial displacement sensor (23) is l 1 The method comprises the steps of carrying out a first treatment on the surface of the The distance from the O point to the second radial displacement sensor (24) is l 2 ；
Measuring radial loading force F by measuring device z And delta ZA 、δ ZB Is combined with the above formula to obtain the radial loading force F z With relative radial displacement d 0 Further deriving the radial stiffness K of the shank-spindle junction 0 ：
Measuring radial loading force F by measuring device z And delta ZA 、δ ZB Has M according to the bending moment formula 1 ＝F Z ·l 3 ；l 3 Is the distance from the O point to the radial loading force application point; the bending moment M is obtained by combining the formulas 1 And angular displacement d 1 Further deriving the angular stiffness K of the shank-spindle junction 1 ：
10. The method for simulating test analysis of the static stiffness of the joint of a cutter-handle-spindle system according to claim 8, wherein when the device for simulating test analysis of the static stiffness of the joint of a cutter-handle-spindle system according to claim 5 is used for testing the radial stiffness and the angular stiffness of the joint of the cutter-handle, the position of the radial loading device is moved after the cutter handle (16) clamps the cutter (17) so as to apply radial pressure to the overhanging end of the cutter (17); after the clamping length of a cutter handle is determined, the radial loading screw (19) is adjusted to enable the pressure head (20) to act on the cutter (16) with different pressures, so that the combination part of the cutter and the handle generates radial displacement and angular displacement;
radial loading force F z When acting on the tool (17), the following formula is satisfied:
wherein a second radial displacement sensor (24) is firstly arranged at the tail end of the overhanging end of the knife handle (16), and the radial displacement delta of the tail end of the overhanging end of the knife handle (16) is measured ZB Then, the first radial displacement sensor (23) and the second radial displacement sensor (24) are arranged on the cutter (17) to measure the radial displacement delta ZA ' and delta ZB 'A'; relative radial displacement d of the tool (17) relative to the shank (16) under radial loading force 3 The tool (17) is angularly displaced d relative to the shank (16) by a radial loading force 4 The resulting displacement d 4 Elastic deformation d of the' and the cutter (17) under radial loading force 5 ；
The distance from the tip of the overhanging end of the knife handle (16) to the first radial displacement sensor (23) is l 4 The distance from the tip of the overhanging end of the shank (16) to the second radial displacement sensor (24) is l 5 Solving the relative radial displacement d of the cutter-cutter handle combination part 3 And angular displacement d 4 ：
Measuring radial loading force F by measuring device z ' and delta ZA ”、δ ZB "in combination with the above formula to obtain the radial loading force F z ' and relative radial displacement d 3 Further deriving the radial stiffness K of the tool-shank junction 2 ：
Measuring radial loading force F by measuring device z ' and delta ZA ”、δ ZB Relationship of "rootAccording to the formula of bending moment
M 2 ＝F Z '·l 6 (8)
Wherein l 6 Is the distance from the tail end of the overhanging end of the knife handle (16) to the radial loading force acting point; the bending moment M is obtained by combining the formulas 2 And angular displacement d 4 Further deriving the angular stiffness K of the tool-shank junction 2 ：
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| CN112417736B (en) * | 2020-12-03 | 2022-08-16 | 天津大学 | Method for designing static stiffness of complete machine tool |
| CN114526879B (en) * | 2022-03-01 | 2023-06-23 | 烟台大学 | Bidirectional measuring device and method for rigidity of aviation pipeline joint |
| CN116067692B (en) * | 2023-04-06 | 2023-06-16 | 山东普鲁特机床有限公司 | High-speed turning and milling composite machining center performance test bed |
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