CN111504685A - Vibration cutting device and design method thereof - Google Patents
Vibration cutting device and design method thereof Download PDFInfo
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- CN111504685A CN111504685A CN202010345513.1A CN202010345513A CN111504685A CN 111504685 A CN111504685 A CN 111504685A CN 202010345513 A CN202010345513 A CN 202010345513A CN 111504685 A CN111504685 A CN 111504685A
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Abstract
The invention discloses a vibration cutting device and a design method thereof, and belongs to the field of biological tissue cutting. The vibration cutting device includes a cutting portion, a driving portion, and a guide portion. The cutting part comprises a vibration mass and a blade, and the vibration mass and the blade are integrally subjected to reciprocating linear motion under the action of the driving part. The guide part comprises a pair of guide blocks symmetrically connected to the first side surface and the second side surface, each guide block is provided with a double-parallelogram flexible mechanism, the guide part and the cutting part form a spring mass system, the natural frequency of the system is the same as the driving frequency of the driving part, and the system can resonate with the cutting part to improve the amplitude of the blade. The double-parallelogram flexible mechanism can eliminate the deviation of the non-vibration direction and provide a guide effect for the vibration of the cutting part so as to reduce parasitic motion errors caused by reciprocating linear motion, thereby realizing high-precision reciprocating linear motion of the blade.
Description
Technical Field
The invention relates to the field of biological tissue cutting, in particular to a vibration cutting device and a design method thereof.
Background
In modern biological research and medical examination, it is often necessary to make a thin section of biological tissue to a certain thickness using a cutting device for further processing and observation such as immunohistochemistry, staining, imaging, and the like. The vibration cutting device can drive the blade to vibrate back and forth along the blade by using a certain driving force so as to tear the soft biological tissue, and simultaneously the blade is fed along the direction vertical to the vibration direction or the sample is fed along the direction vertical to the vibration direction, so that the slicing process is realized, and the biological tissue is cut into thin slices of tens of micrometers to hundreds of micrometers.
The vibration cutting device in the related art generally uses a set of single parallel flexible mechanisms formed by two parallel flexible leaf springs as a guide mechanism to guide the movement of the cutting blade. One end of each flexible plate spring is fixed on the base, the other end of each flexible plate spring is connected with the other end of each flexible plate spring through a vibration end, and the blades are fixed on the vibration ends through fixing devices. The driving device of the vibration cutting device provides driving force for the deformation of the flexible plate spring of the guide mechanism, so that the flexible plate spring generates vibration and drives the blade to perform vibration cutting. However, because one end of the flexible plate spring of the guide mechanism is fixed, the other end of the flexible plate spring does not strictly move linearly in the vibration process, and the blade forms an arc shape on the horizontal plane along with the motion track of the vibration end, so that the quality of a cutting section is influenced.
Disclosure of Invention
The embodiment of the invention provides a vibration cutting device and a design method thereof, which can enable a blade to do high-precision reciprocating linear motion, and further improve the quality of a cut section.
According to a first aspect of embodiments of the present disclosure, there is provided a vibratory cutting apparatus including:
a cutting portion including a vibrating mass including first and second relatively parallel sides and third and fourth sides connecting the first and second sides, and a blade connected with the third side;
the driving part comprises a fixing part and a driving part, the driving part is connected with the fourth side face, the driving part is used for providing power for the cutting part to do reciprocating linear motion, and the motion direction of the reciprocating linear motion is parallel to the extension direction of the blade; and the number of the first and second groups,
the guide part comprises a pair of guide blocks symmetrically connected to the first side surface and the second side surface, each guide block is provided with a double-parallelogram flexible mechanism, the pair of double-parallelogram flexible mechanisms and the cutting part form a spring mass system, the driving frequency of the driving part is the same as the natural frequency of the spring mass system, and the driving frequency is the movement frequency of the driving part for driving the cutting part to perform reciprocating linear movement;
every two parallelogram flexible mechanism include four flexible leaf springs, first connecting block and second connecting block, four the parallel symmetrical arrangement of flexible leaf spring, every the one end of flexible leaf spring with first connecting block links to each other, two symmetrical the other end of flexible leaf spring with vibrating mass block links to each other, two symmetrical other the other end of flexible leaf spring with the second connecting block links to each other, first connecting block with the clearance has between the second connecting block, the first end of second connecting block with the mounting of drive division is connected, first end is the second connecting block is kept away from the one end of flexible leaf spring.
Further, the driving part is a voice coil motor, the fixing part comprises a stator of the voice coil motor, the driving part comprises a rotor of the voice coil motor, and the center line of the rotor passes through the center of mass of the cutting part.
Further, the cutting portion further comprises a balance mass, the vibrating mass further comprises a fifth side surface connected with the first side surface and the second side surface, the fifth side surface is a side surface relatively parallel to the third side surface, and the balance mass is connected with the fifth side surface of the vibrating mass, so that the center of mass of the cutting portion of the vibrating cutting device coincides with the center of stiffness of the guide portion.
Furthermore, the fixing part further comprises a mounting seat, one end, far away from the driving part, of the stator is fixed on the end face of the mounting seat, and the opposite side faces of the mounting seat are interacted with the first ends of the two second connecting blocks through set screws respectively and used for adjusting the gap between the mounting seat and the second connecting blocks.
Further, the cutting part further comprises a blade mounting frame and a blade clamp, the blade mounting frame is connected with the vibration mass block, and the blade is fixed on the blade mounting frame through the blade clamp.
According to a second aspect of the embodiments of the present disclosure, there is provided a design method adapted to the above-described vibration cutting apparatus, the method including:
determining the vibration frequency required by cutting, and determining the natural frequency of the spring mass system according to the required frequency;
determining a first mass, the first mass being a mass of a first portion, the first portion including the cutting portion and the driver;
determining the rigidity of a vibration direction according to the natural frequency and the first mass, wherein the vibration direction is the reciprocating linear motion direction of the cutting part;
determining a width of the flexible leaf spring and a length of the flexible leaf spring;
determining the thickness of the flexible plate spring according to the rigidity of the vibration direction, the width of the flexible plate spring and the length of the flexible plate spring.
Further, the stiffness in the vibration direction is determined by the following formula:
K＝4π2mf2
in the formula: k is the stiffness in the vibration direction; m is the first mass; f is the natural frequency.
Further, of said flexible leaf spring
The thickness is determined using the following formula:
in the formula: k is the stiffness in the vibration direction; b is the width of the flexible leaf spring; l is the length of the flexible leaf spring; e is the elastic modulus of the flexible plate spring.
Further, when the cutting portion includes a balance mass, the determining a first mass includes:
determining a mass of the balancing mass;
determining a first mass based on the mass of the balancing mass.
Further, the mass of the balancing mass is determined using the following formula:
in the formula: m is1Is the mass of the balancing mass block; l1A distance between a center of mass of the balance mass and a center of stiffness of the guide portion; m is2A mass of a second portion, the second portion being the cutting portion excluding the other portion of the balance mass; l2Is the distance between the center of mass of the second portion and the center of stiffness of the guide portion.
The technical scheme provided by the embodiment of the invention has the beneficial effects that at least:
the vibration cutting device includes a cutting portion, a driving portion, and a guide portion. The cutting part comprises a vibrating mass block and a blade, and the blade is connected with the vibrating mass block; the driving part of the driving part acts on the vibration mass block and provides power for the cutting part to do reciprocating linear motion. The vibrating mass and the blade as a whole perform reciprocating linear motion under the action of the driving part. The guide part comprises a pair of guide blocks symmetrically connected to the first side surface and the second side surface, each guide block is provided with a double-parallelogram flexible mechanism, the guide part and the cutting part form a spring mass system, and the driving frequency of the driving part is the same as the natural frequency of the spring mass system, so that the device can work in a resonance state, the amplitude of the blade is improved, and the surface quality of a cutting section is further improved.
Simultaneously, every two parallelogram flexible mechanism includes four flexible leaf springs, first connecting block and second connecting block, four flexible leaf spring parallel symmetrical arrangement, the one end of every flexible leaf spring links to each other with first connecting block, the other end of two symmetrical flexible leaf springs links to each other with the vibrating mass piece, the other end of two symmetrical other flexible leaf springs links to each other with the second connecting block, the clearance has between first connecting block and the second connecting block, the first end of second connecting block is connected with the mounting of drive division, the one end that flexible leaf spring was kept away from for the second connecting block to first end. The symmetrical double-parallelogram flexible mechanism can eliminate the deviation of the blade in the non-vibration direction, and provides a guide effect for the vibration of the cutting part, so that the parasitic motion error caused by the reciprocating linear motion is reduced, and the high-precision reciprocating linear motion of the blade is realized.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a vibration cutting apparatus according to an embodiment of the present invention;
FIG. 2 is a schematic view of a single compliant leaf spring construction;
FIG. 3 is a schematic diagram of a symmetrical double parallelogram flexure mechanism;
fig. 4 is a schematic structural diagram of a vibration cutting apparatus according to an embodiment of the present invention;
FIG. 5 is a flow chart of a design method provided by an embodiment of the present invention;
fig. 6 is a schematic structural diagram of a vibration cutting apparatus according to an embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
Fig. 1 is a schematic structural diagram of a vibration cutting apparatus according to an embodiment of the present invention. As shown in fig. 1, the vibration cutting apparatus includes a cutting part 100, a driving part 200, and a guide part 300.
The cutting part 100 includes a vibrating mass 110 and a blade 120, the vibrating mass 110 includes first and second sides that are relatively parallel and third and fourth sides connecting the first and second sides, and the blade 120 is connected to the third side. The driving part 200 includes a fixing member 210 and a driving member 220, the driving member 220 is connected to the fourth side, and the driving member 220 is used for providing a power of reciprocating linear motion to the cutting part 100, and the motion direction of the reciprocating linear motion is parallel to the extending direction of the blade 120. The guide part 300 includes a pair of guide blocks 310 symmetrically connected to the first side surface and the second side surface, each guide block 310 has a double parallelogram flexible mechanism, the guide part and the cutting part together form a spring-mass system, the driving frequency of the driving part 200 is the same as the natural frequency of the spring-mass system, and the driving frequency is also the movement frequency of the driving part 220 driving the cutting part 100 to perform reciprocating linear movement.
In implementation, as shown in fig. 1, the vibrating mass 110 may be a rectangular parallelepiped structure, and the vibrating mass 110 has two opposite upper and lower end surfaces and four side surfaces connecting the upper and lower end surfaces. The third side may be a lower end face of the cuboid, and accordingly the first and second sides may be left and right sides of the cuboid, and the fourth side may be a front side or a rear side of the cuboid.
The driving member 220 of the driving part 200 acts on the vibration mass 110 to provide power for the cutting part 100 to perform reciprocating linear motion in the X direction. Since the vibrating mass 110 and the blade 120 as a whole perform the reciprocating linear motion by the driving part 200, it is possible to ensure that the motion of the blade 120 is the reciprocating linear motion. The guide part 300 includes a pair of guide blocks 310 symmetrically connected to the first and second sides, each guide block 310 has a double-parallelogram flexible mechanism, the pair of double-parallelogram flexible mechanisms and the cutting part together form a spring mass system, and the driving frequency of the driving part 200 is the same as the natural frequency of the spring mass system, so that the device can work in a resonance state, the amplitude of the blade is increased, and the surface quality of the cutting section is improved.
Each double-parallelogram flexible mechanism comprises four flexible plate springs 311, a first connecting block 312 and a second connecting block 313, wherein the four flexible plate springs 311 are symmetrically arranged in parallel, one end of each flexible plate spring 311 is connected with the first connecting block 312, the other ends of two symmetrical flexible plate springs 311 are connected with the vibrating mass 110, the other ends of the other two symmetrical flexible plate springs 311 are connected with the second connecting block 313, a gap is reserved between the first connecting block 312 and the second connecting block 313, a first end 313a of the second connecting block 313 is connected with the fixing part 210 of the driving part 200, and a first end 313a is one end of the second connecting block 313 far away from the flexible plate springs 311.
Fig. 2 is a schematic structural diagram of a single flexible plate spring 311, and as shown in fig. 2, one end of the single flexible plate spring 311 is fixed, and the other end of the single flexible plate spring 311 generates a deformation displacement and a deformation angle θ under an external force. Fig. 3 is a schematic diagram of a symmetrical double-parallelogram flexure mechanism, and as shown in fig. 3, the symmetrical double-parallelogram flexure mechanism includes a pair of symmetrically arranged double-parallelogram flexure mechanisms, wherein each double-parallelogram flexure mechanism includes four flexible plate springs 311, a first connecting block 312 and a second connecting block 313, one end of each flexible plate spring 311 is connected to the first connecting block 312, the other ends of two symmetrical flexible plate springs 311 are connected to the vibrating mass 110, and the other ends of the other two symmetrical flexible plate springs 311 are fixed to the second connecting block 313. The outer pair of compliant leaf springs 311, the first connecting block 312 and the second connecting block 313 form one parallelogram, the inner pair of compliant leaf springs 311, the first connecting block 312 and the seismic mass 110 form another parallelogram, and the two parallelograms are connected in series to form a double-parallelogram compliant mechanism.
As can be seen from fig. 3, all the flexible plate springs are symmetrically arranged with the center of mass of the vibrating mass 110 as the center of symmetry, so as to completely eliminate the deformation displacement and the deformation angle θ of the vibrating mass 110, thereby realizing that the displacement of the vibrating mass 110 linearly moves along the force direction. Therefore, the symmetrical double-parallelogram flexure mechanism can completely eliminate the displacement in the non-vibration direction, and provide a guide effect for the vibration of the cutting part 100 to reduce parasitic motion errors due to the reciprocating linear motion, thereby achieving high-precision reciprocating linear motion of the blade 120. Referring to fig. 1, preferably, the fixing member 210, the driving member 220, and the vibrating mass 110 are linearly arranged in sequence. The two guide blocks 310 are both columnar and symmetrically arranged on two sides of the driving member 220, one end of the guide block 310 having a double-parallelogram flexible mechanism is connected with the vibrating mass 110 through a flexible plate spring 311, and the other end of the guide block 310 (i.e. the first end 313a of the second connecting block 313) is fixedly connected with the fixing member 210, so that the vibrating cutting device has a compact structure and saves space.
Preferably, the second connecting block 313 is provided with a plurality of through holes, and the vibration cutting device is fixed on the base by bolts.
Further, the cutting part 100 further comprises a mounting frame 131 and a clamp 132, the mounting frame 131 is connected with the vibrating mass 110, the blade 120 is fixed on the mounting frame 131 through the clamp 132, preferably, the mounting frame 131, the clamp 132 and the vibrating mass 110 are fixed through bolts, and the clamp 132 is rigidly fixed with the blade 120. further, the driving part 200 is a voice coil motor, the driving force generated by the voice coil motor can be changed by adjusting the magnitude of the coil current, when the input current is changed in a sine manner, the magnitude of the generated driving force F is in accordance with the sine distribution, and the cutting part and the symmetrical double parallelogram flexible mechanism together form a spring-mass system, so that the single-degree-of-freedom simple harmonic vibration of the blade is realized.
Preferably, the driving part 200 further includes a power amplifier, a signal generator, a power supply, and the like. The sinusoidal signal generated by the signal generator is input into the coil of the voice coil motor through the power amplifier, so that the voice coil motor generates the driving force F which conforms to the sinusoidal distribution.
Fig. 4 is a schematic structural diagram of a vibration cutting apparatus according to an embodiment of the present invention. As shown in fig. 4, the guide part 300 includes a pair of guides symmetrically connected to the first and second sides of the vibrating mass 110Blocks 310, each guide block 310 having a double parallelogram flexure mechanism, and thus, the center of stiffness M of the guide 3001Is located at the centroid of the guide 300, i.e., coincides with the centroid point of the vibrating mass 110.
Further, the fixing member 210 includes a stator 211 of a voice coil motor, the driving member 220 includes a mover of the voice coil motor, and the center of mass of the cutting part 100 of the vibration cutting apparatus is located at a point M2The position of (a). At this time, the center line of the mover passes through the mass center point M of the cutting part 1002So that the driving force acts on the center of mass of the cutting part 100, avoiding a rotational moment due to the driving force not acting on the center of mass, further reducing the rotational movement of the blade along the vertical plane, and further reducing the influence on the vibrating mass 110 and the blade 120. Optionally, the center line of the mover may also pass through the stiffness center of the guide portion 300, which may avoid the deflection of the vibration component due to the asymmetric stiffness of the guide portion along the action line of the driving force, reduce the generation of the rotational motion of the blade along the vertical plane, avoid the generation of the additional Z-direction parasitic motion, and further ensure the high-precision reciprocating linear motion of the blade 120.
Further, referring to fig. 1, the cutting part 100 further includes a balance mass 140, the vibrating mass 110 further includes a fifth side surface connecting the first side surface and the second side surface, the fifth side surface being a side surface relatively parallel to the third side surface, the balance mass 140 being connected to the fifth side surface of the vibrating mass 110 such that a center of mass of the cutting part 100 of the vibrating cutting apparatus coincides with a center of stiffness of the guide part 300.
In implementation, the fifth side surface may be an upper end surface of the aforementioned rectangular parallelepiped structure, and the balance mass 140 is fixedly connected to the upper end surface of the vibration mass 110.
Referring to fig. 4, when the balance mass 140 is not mounted, the blade 120, the mounting frame 131, and the clamp 132 are attached due to the lower end surface of the vibration mass 110. At this time, the center of mass of the cutting portion 100 of the vibration cutting apparatus is located at the point M2Is lower than the centroid position of the vibrating mass 110 (i.e., the center of stiffness M of the guide 300)1). In the embodiment of the present invention, a balance mass is disposed on the upper end surface of the vibration mass 110140 to balance the mass of the second part so that the center of mass of the cutting part 100 of the vibration cutting apparatus moves upward to coincide with the center of stiffness of the guide part 300, ensuring that the line of action of the driving force provided by the voice coil motor can pass through the center of mass M2And center of stiffness M1Further, the rotary motion of the blade along the vertical surface is eliminated, and the Z-direction parasitic motion is reduced. The second portion refers to the other portion of the cutting portion 100 excluding the balance mass 140, and specifically includes: the weight of the vibrating mass 110, the mounting bracket 131, the clamp 132, the blade 120.
Preferably, the balance mass 140 is provided with mounting holes 141, and bolts fix the balance mass 140 to the upper end surface of the vibration mass 110 through the mounting holes 141. The arrangement of the mounting holes 141 may be symmetrical with respect to the X-direction symmetrical plane and the Y-direction symmetrical plane of the vibrating mass 110 to ensure that no other directional components are generated while balancing the second partial mass, and to prevent the mass center of the cutting part 100 from being shifted to the X-direction or the Y-direction.
Further, the fixing member 210 further includes a mounting seat 212, one end of the stator 211, which is far away from the driving member 220, is fixed on an end surface of the mounting seat 212, opposite side surfaces of the mounting seat 212 interact with first ends 313a of the two second connection blocks 313 through set screws 213, respectively, and the set screws 213 are used for adjusting a gap between the mounting seat 212 and the second connection blocks 313. The gap between the mounting base 212 and the second connection block 313 is adjusted by the set screw 213, so that the spatial position of the voice coil motor can be finely adjusted, and the direction of the driving force can be finely adjusted.
The base is fixed with the first ends 313a of the second connecting blocks 313 on two sides, the mounting plate is L-shaped, the horizontal arm of the mounting plate is fixed on the upper end surface of the base, and the end of the stator 211, which is far away from the driving piece 220, is fixed on the vertical arm of the mounting plate.
Optionally, the base is integrated with the second connection blocks 313 on both sides to reduce assembly errors of the base.
Fig. 5 is a flowchart of a design method according to an embodiment of the present invention. As shown in fig. 5, the design method is applied to the vibration cutting apparatus described above, and includes:
step 101: determining a demand frequency, and determining the natural frequency of the spring mass system according to the demand frequency.
The guide part and the cutting part jointly form a spring mass system, and in order to enable the vibration cutting device to work in a resonance mode, the required vibration frequency is the natural frequency of the spring mass system. The frequency is typically determined based on prior experience and tissue cutting requirements.
It should be noted that, in some embodiments, the vibration frequency at which the cutting portion is driven by the driving member to perform the reciprocating linear motion, i.e., the driving frequency, may also be determined according to the natural frequency of the spring-mass system. When the driving frequency of the driving part is the same as the natural frequency of the spring mass system, the vibration cutting device can work in a resonance mode, the vibration amplitude of the blade can be improved in the resonance mode, and the surface quality of a cutting section can be improved.
Reciprocating linear motion
Step 102: a first quality is determined.
The first mass is the mass of the first part, and the first part is the mass of the vibrating part of the vibrating cutting device, and comprises a cutting part and a driving part.
Specifically, the first mass may be a sum of masses of the vibrating mass, the blade mounting bracket, the blade clamp, and the mover of the voice coil motor.
Further, when the cutting portion includes a balance mass, determining the first mass includes:
step 102 a: the mass of the balancing mass is determined.
Specifically, the mass of the balancing mass may be determined using the following formula:
in the formula: m is1Is the mass of the balancing mass block; l1A distance between a center of mass of the balance mass and a center of stiffness of the guide portion; m is2A mass of a second portion, the second portion being the cutting portion excluding the other portion of the balance mass; l2Is the distance between the center of mass of the second portion and the center of stiffness of the guide portion.
As described above, when the balance mass is not mounted, the blade mounting bracket, and the blade clamp are connected to the lower end surface of the vibration mass. At this time, the center of mass of the cutting portion of the vibration cutting device is located at point M2Is lower than the centroid position of the vibrating mass (i.e., the center of stiffness M of the guide portion)1). The magnitude of the offset being determined by the mass m of the second part2Determining that the distance between the center of mass of the second portion and the center of stiffness of the guide portion is l2. The second part is the mass sum of the other parts of the balance mass removed by the cutting part, and specifically comprises the following steps: the vibration mass block, the blade mounting frame and the blade clamp.
Therefore, in order to adjust the position of the mass center, a balance mass block is added right above the vibrating mass block, and the distance l between the mass center of the balance mass block and the rigidity center is set1The mass m of the balance mass block can be obtained by mechanical design knowledge1The requirement of formula (1) needs to be satisfied.
In the specific calculation, the mass distribution due to the vibrating mass is symmetrical with respect to the X-direction symmetrical plane and the Y-direction symmetrical plane of the vibrating mass. To simplify the calculation, the mass m is calculated2The weight of the vibrating mass may not be considered.
Step 102 b: a first mass is determined based on the mass of the balancing mass.
The first mass is the mass of the first part, and the first part is the mass of the vibrating part of the vibrating cutting device, and comprises a cutting part and a driving part. Specifically, the first mass may be a sum of masses of the vibrating mass, the blade, the balance mass, the blade mounting bracket, the blade clamp, and the mover of the voice coil motor.
Step 103: and determining the rigidity of the vibration direction according to the vibration frequency and the first mass, wherein the vibration direction is the reciprocating linear motion direction of the cutting part.
Further, the stiffness in the vibration direction can be determined by using the following formula:
K＝4π2mf2
in the formula: k is the stiffness in the vibration direction; m is a first mass; f is the natural frequency of the spring-mass system.
Step 104: determining the width b and the length l of the flexible plate spring;
fig. 6 is a schematic structural diagram of a vibration cutting apparatus according to an embodiment of the present invention, and as shown in fig. 6, a width of a flexible leaf spring in a Z direction is b, a width of the flexible leaf spring in a Y direction is l, and a width of the flexible leaf spring in an X direction is t.
Specifically, the width b of the flexible plate spring and the length l of the flexible plate spring are set to constant values, respectively, according to space restrictions. When the design is allowed by space, b is set as large as possible to increase the rigidity of the Z direction and reduce Z-direction parasitic movement caused by the deviation of the driving force direction.
Step 105: the thickness of the flexible leaf spring is determined according to the rigidity in the vibration direction, the width of the flexible leaf spring, and the length of the flexible leaf spring. Specifically, the thickness is determined using the following formula:
in the formula: k is the stiffness in the vibration direction; b is the width of the flexible plate spring; l is the length of the flexible plate spring; and E is the elastic modulus of the flexible plate spring.
Optionally, after determining the thickness t of the flexible plate spring, the stiffness K and the natural frequency f of the double parallelogram flexure mechanism may be checked according to the width b of the flexible plate spring, the length l of the flexible plate spring, the elastic modulus E of the flexible plate spring, and the first mass m.
Specifically, the stiffness of the double-parallelogram flexible mechanism can be verified by adopting the following formula:
K＝4π2f2m
in the formula: k is the stiffness in the vibration direction; m is a first mass; f is the natural frequency of the spring-mass system.
The natural double parallelogram flexure mechanism frequency of the spring-mass system can be verified using the following formula:
in the formula: k is the stiffness in the vibration direction; b is the width of the flexible plate spring; l is the length of the flexible plate spring; and E is the elastic modulus of the flexible plate spring.
According to the design method in the embodiment of the invention, the characteristic that the rigidity difference of the flexible plate spring in different directions is utilized, the required displacement is generated in the direction of small rigidity, the unnecessary error is restrained in the direction of large rigidity, the rigidity in the vibration direction is set to be a specific value according to the requirement of vibration frequency and the mass of the cutting part, and the rigidity in the non-vibration direction is set to be as large as possible, so that the parasitic motion error caused by periodic reciprocating motion is reduced, and the guide function of the guide part on the cutting part in the motion direction is realized.
The invention is not to be considered as limited to the particular embodiments shown and described, but is to be understood that various modifications, equivalents, improvements and the like can be made without departing from the spirit and scope of the invention.
Claims (10)
1. A vibration cutting apparatus, characterized in that the vibration cutting apparatus comprises:
a cutting portion (100), the cutting portion (100) comprising a vibrating mass (110) and a blade (120), the vibrating mass (110) comprising first and second relatively parallel sides and third and fourth sides connecting the first and second sides, the blade (120) being connected to the third side;
a driving part (200), wherein the driving part (200) comprises a fixing part (210) and a driving part (220), the driving part (220) is connected with the fourth side, the driving part (220) is used for providing power for the cutting part (100) to perform reciprocating linear motion, and the motion direction of the reciprocating linear motion is parallel to the extension direction of the blade (120); and the number of the first and second groups,
a guide portion (300), wherein the guide portion (300) comprises a pair of guide blocks (310) symmetrically connected to the first side surface and the second side surface, each guide block (310) is provided with a double-parallelogram flexible mechanism, the pair of double-parallelogram flexible mechanisms and the cutting portion form a spring mass system, the driving frequency of the driving portion (200) is the same as the natural frequency of the spring mass system, and the driving frequency is the movement frequency of the driving portion (220) for driving the cutting portion (100) to perform reciprocating linear movement;
each double-parallelogram flexible mechanism comprises four flexible plate springs (311), a first connecting block (312) and a second connecting block (313), the four flexible plate springs (311) are symmetrically arranged in parallel, one end of each flexible plate spring (311) is connected with the first connecting block (312), the other ends of two symmetrical flexible plate springs (311) are connected with the vibrating mass (110), and the other ends of the other two symmetrical flexible plate springs (311) are connected with the second connecting block (313), a gap is formed between the first connection block (312) and the second connection block (313), a first end (313a) of the second connecting block (313) is connected with a fixing member (210) of the driving part (200), the first end (313a) is the end of the second connecting block (313) far away from the flexible plate spring (311).
2. The vibration cutting device according to claim 1, wherein the driving part (200) is a voice coil motor, the fixing part (210) comprises a stator (211) of the voice coil motor, the driving part (220) comprises a mover of the voice coil motor, and a center line of the mover passes through a center of mass of the cutting part (100).
3. The vibrating cutting device according to claim 2, wherein the cutting portion (100) further comprises a balance mass (140), the vibrating mass (110) further comprises a fifth side connecting the first side and the second side, the fifth side being a side relatively parallel to the third side, the balance mass (140) being connected to the fifth side of the vibrating mass (110) such that a center of mass of the cutting portion (100) coincides with a center of stiffness of the guide portion (300).
4. The vibration cutting device according to claim 3, wherein the fixing member (210) further comprises a mounting seat (212), one end of the stator (211) remote from the driving member (220) is fixed on an end surface of the mounting seat (212), and opposite side surfaces of the mounting seat (212) respectively interact with the first ends (313a) of the two second connecting blocks (313) through set screws (213) for adjusting a gap between the mounting seat (212) and the second connecting blocks (313).
5. The vibrating cutting device according to any one of claims 1-4, wherein the cutting portion (100) further comprises a mounting bracket (131) and a clamp (132), the mounting bracket (131) being connected to the vibrating mass (110), the blade (120) being fixed to the mounting bracket (131) by the clamp (132).
6. A method of designing a vibration cutting apparatus, applied to the vibration cutting apparatus of claim 1, the method comprising:
determining a demand frequency, and determining the natural frequency of the spring mass system according to the demand frequency;
determining a first mass, the first mass being a mass of a first portion, the first portion including the cutting portion and the driver;
determining the rigidity of a vibration direction according to the natural frequency and the first mass, wherein the vibration direction is the reciprocating linear motion direction of the cutting part;
determining a width of the flexible leaf spring and a length of the flexible leaf spring;
determining the thickness of the flexible plate spring according to the rigidity of the vibration direction, the width of the flexible plate spring and the length of the flexible plate spring.
7. The design method according to claim 6, wherein the stiffness in the vibration direction is determined by using the following formula:
K＝4π2mf2
in the formula: k is the stiffness in the vibration direction; m is the first mass; f is the natural frequency of the spring-mass system.
8. The design method of claim 6, wherein the thickness of the compliant leaf spring is determined using the following equation:
in the formula: k is the stiffness in the vibration direction; b is the width of the flexible leaf spring; l is the length of the flexible leaf spring; e is the elastic modulus of the flexible plate spring.
9. The design method of claim 6, wherein when the cutting portion includes a balance mass, the determining a first mass comprises:
determining a mass of the balancing mass;
determining a first mass based on the mass of the balancing mass.
10. The design method of claim 9, wherein the mass of the proof mass is determined using the following equation:
in the formula: m is1Is the mass of the balancing mass block; l1A distance between a center of mass of the balance mass and a center of stiffness of the guide portion; m is2Is the mass of the second part, which removes the cutting part from the cutting partOther parts of the balance mass; l2Is the distance between the center of mass of the second portion and the center of stiffness of the guide portion.
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