Abstract: The rotational stiffness of the zero-stiffness flexible hinge is approximately zero, which overcomes the defect that ordinary flexible hinges require driving torque, and can be applied to flexible grippers and other fields. Taking the inner and outer ring flexible hinges under the action of pure torque as the positive stiffness subsystem, the research Negative stiffness mechanism and matching positive and negative stiffness can construct zero stiffness flexible hinge. Propose a negative stiffness rotation mechanism——Crank spring mechanism, modeled and analyzed its negative stiffness characteristics; by matching positive and negative stiffness, analyzed the influence of structural parameters of crank spring mechanism on zero stiffness quality; proposed a linear spring with customizable stiffness and size——Diamond-shaped leaf spring string, the stiffness model was established and the finite element simulation verification was carried out; finally, the design, processing and testing of a compact zero-stiffness flexible hinge sample were completed. The test results showed that: under the action of pure torque,±18°In the range of rotation angles, the rotational stiffness of the zero-stiffness flexible hinge is 93% lower than that of the inner and outer ring flexible hinges on average. The constructed zero-stiffness flexible hinge has a compact structure and high-quality zero-stiffness; the proposed negative-stiffness rotation mechanism and the linear The spring has great reference value for the study of flexible mechanism.

0 Preface

Flexible hinge (bearing)

^[1-2]

Relying on the elastic deformation of the flexible unit to transmit or convert motion, force and energy, it has been widely used in precision positioning and other fields. Compared with traditional rigid bearings, there is a restoring moment when the flexible hinge rotates. Therefore, the drive unit needs to provide output torque to drive and Keep the rotation of the flexible hinge. Zero stiffness flexible hinge

^[3]

(Zero stiffness flexural pivot, ZSFP) is a flexible rotary joint whose rotational stiffness is approximately zero. This type of flexible hinge can stay at any position within the stroke range, also known as static balance flexible hinge

^[4]

, are mostly used in fields such as flexible grippers.

Based on the modular design concept of the flexible mechanism, the entire zero-stiffness flexible hinge system can be divided into two subsystems of positive and negative stiffness, and the zero-stiffness system can be realized through the matching of positive and negative stiffness

^[5]

. Among them, the positive stiffness subsystem is usually a large-stroke flexible hinge, such as a cross-reed flexible hinge

^[6-7]

, generalized three-cross reed flexible hinge

^[8-9]

and inner and outer ring flexible hinges

^[10-11]

etc. At present, the research on flexible hinges has achieved a lot of results, therefore, the key to design zero-stiffness flexible hinges is to match suitable negative stiffness modules for flexible hinges[3].

Inner and outer ring flexible hinges (Inner and outer ring flexural pivots, IORFP) have excellent characteristics in terms of stiffness, precision and temperature drift. The matching negative stiffness module provides the construction method of the zero-stiffness flexible hinge, and finally, completes the design, sample processing and testing of the zero-stiffness flexible hinge.

1 crank spring mechanism

1.1 Definition of negative stiffness

The general definition of stiffness K is the rate of change between the load F borne by the elastic element and the corresponding deformation dx

K= dF/dx (1)

When the load increment of the elastic element is opposite to the sign of the corresponding deformation increment, it is negative stiffness. Physically, the negative stiffness corresponds to the static instability of the elastic element

^[12]

.Negative stiffness mechanisms play an important role in the field of flexible static balance. Usually, negative stiffness mechanisms have the following characteristics.

(1) The mechanism reserves a certain amount of energy or undergoes a certain deformation.

(2) The mechanism is in a critical instability state.

(3) When the mechanism is slightly disturbed and leaves the equilibrium position, it can release a larger force, which is in the same direction as the movement.

1.2 Construction principle of zero-stiffness flexible hinge

The zero-stiffness flexible hinge can be constructed by using positive and negative stiffness matching, and the principle is shown in Figure 2.

(1) Under the action of pure torque, the inner and outer ring flexible hinges have an approximately linear torque-rotation angle relationship, as shown in Figure 2a. Especially, when the intersection point is located at 12.73% of the reed length, the torque-rotation angle relationship is linear

^[11]

, at this time, the restoring moment Mpivot (clockwise direction) of the flexible hinge is related to the bearing rotation angleθ(counterclockwise) the relationship is

Mpivot=(8EI/L)θ (2)

In the formula, E is the elastic modulus of the material, L is the length of the reed, and I is the moment of inertia of the section.

(2) According to the rotational stiffness model of the inner and outer ring flexible hinges, the negative stiffness rotating mechanism is matched, and its negative stiffness characteristics are shown in Figure 2b.

(3) In view of the instability of the negative stiffness mechanism

^[12]

, the stiffness of the zero-stiffness flexible hinge should be approximately zero and greater than zero, as shown in Figure 2c.

1.3 Definition of crank spring mechanism

According to literature [4], a zero-stiffness flexible hinge can be constructed by introducing a pre-deformed spring between the moving rigid body and the fixed rigid body of the flexible hinge. For the inner and outer ring flexible hinge shown in FIG. 1, a spring is introduced between the inner ring and the outer ring, I .e., a spring-crank mechanisms (SCM) is introduced. Referring to the crank slider mechanism shown in Figure 3, the related parameters of the crank spring mechanism are shown in Figure 4. The crank-spring mechanism is composed of a crank and a spring (set stiffness as k). the initial angle is the included angle between the crank AB and the base AC when the spring is not deformed. R represents the crank length, l represents the base length, and defines the crank length ratio as the ratio of r to l, I .e. = r/l (0<<1).

The construction of the crank-spring mechanism requires the determination of 4 parameters: the base length l, the crank length ratio , the initial angle and the spring stiffness K.

The deformation of the crank spring mechanism under force is shown in Figure 5a, at the moment M

_γ

Under the action, the crank moves from the initial position AB

_Beta

turn to AB

_γ

, during the rotation process, the included angle of the crank relative to the horizontal position

_γ

called the crank angle.

Qualitative analysis shows that the crank rotates from AB (initial position, M & gamma; Zero) to AB0 (“dead point”location, M

_γ

is zero), the crank-spring mechanism has a deformation with negative stiffness characteristics.

1.4 The relationship between torque and rotation angle of crank spring mechanism

In Fig. 5, the torque M & gamma; clockwise is positive, the crank angle & gamma; counterclockwise is positive, and the moment load M is modeled and analyzed below.

_γ

with crank angle

_γ

The relationship between the modeling process is dimensioned.

As shown in Figure 5b, the torque balance equation for crank AB & gamma is listed.

In the formula, F & gamma; is the spring restoring force, d & gamma; is F & gamma; to point A. Assume that the displacement-load relation of the spring is

In the formula, K is the spring stiffness (not necessarily a constant value),δ

xγ

is the amount of spring deformation (shortened to positive),δ

xγ

=|B

_Beta

C| – |B

_γ

C|.

Simultaneous type (3)(5), moment M

_γ

with corner

_γ

The relationship is

1.5 Analysis of the negative stiffness characteristics of the crank-spring mechanism

In order to facilitate the analysis of the negative stiffness characteristics of the crank-spring mechanism (moment M

_γ

with corner

_γ

relationship), it may be assumed that the spring has a linear positive stiffness, then formula (4) can be rewritten as

In the formula, Kconst is a constant greater than zero. After the size of the flexible hinge is determined, the length l of the base is also determined. Therefore, assuming that l is a constant, formula (6) can be rewritten as

where Kconstl2 is a constant greater than zero, and the moment coefficient m & gamma; has a dimension of one. The negative stiffness characteristics of the crank-spring mechanism can be obtained by analyzing the relationship between the torque coefficient m & gamma; and the rotation angle & gamma.

From equation (9), Figure 6 shows the initial angle =π relationship between m & gamma; and crank length ratio and rotation angle & gamma;, & isin;[0.1, 0.9],& gamma;& isin;[0, π]. Figure 7 shows the relationship between m & gamma; and rotation angle & gamma; for = 0.2 and different . Figure 8 shows =π When, under different , the relationship between m & gamma; and angle & gamma.

According to the definition of crank spring mechanism (section 1.3) and formula (9), when k and l are constant, m & gamma; Only related to angle & gamma;, crank length ratio and crank initial angle .

(1) If and only if & gamma; is equal to 0 orπ or ,m & gamma; is equal to zero; & gamma; & isin;[0, ],m & gamma; is greater than zero; & gamma; & isin;[,π],m & gamma; less than zero. & isin;[0, ],m & gamma; is greater than zero; & gamma;& isin;[,π],m & gamma; less than zero.

(2) & gamma; When [0, ], the rotation angle & gamma; increases, m & gamma; increases from zero to the inflection point angle & gamma;0 takes the maximum value m & gamma;max, and then gradually decreases.

(3) The negative stiffness characteristic range of the crank spring mechanism: & gamma;& isin;[0, & gamma;0], at this time & gamma; increases (counterclockwise), and the torque M & gamma; increases (clockwise). The inflection point angle & gamma;0 is the maximum rotation angle of the negative stiffness characteristic of the crank-spring mechanism and & gamma;0 & isin;[0, ];m & gamma;max is the maximum negative moment coefficient. Given and , the derivation of equation (9) yields & gamma;0

(4) the larger the initial angle , & gamma; the larger 0, m

_γmax

bigger.

(5) the larger the length ratio , & gamma; the smaller 0, m

_γmax

bigger.

In particular, =πThe negative stiffness characteristics of the crank spring mechanism are the best (the negative stiffness angle range is large, and the torque that can be provided is large). =πAt the same time, under different conditions, the maximum rotation angle & gamma of the negative stiffness characteristic of the crank spring mechanism; 0 and the maximum negative torque coefficient m & gamma; Max is listed in table 1.

2 Construction of zero-stiffness flexible hinge

The matching of positive and negative stiffness of the 2.1 is shown in Figure 9, n(n 2) groups of parallel crank spring mechanisms are evenly distributed around the circumference, forming a negative stiffness mechanism matched with the inner and outer ring flexible hinges.

Using the inner and outer ring flexible hinges as the positive stiffness subsystem, construct a zero-stiffness flexible hinge. In order to achieve zero stiffness, match the positive and negative stiffness

simultaneous (2), (3), (6), (11), and & gamma;=θ, the load F & gamma of the spring can be obtained; and displacementδThe relationship of x & gamma; is

According to section 1.5, the negative stiffness angle range of the crank spring mechanism: & gamma;& isin;[0, & gamma;0] and & gamma;0 & isin;[0, ], the stroke of the zero stiffness flexible hinge shall be less than & gamma;0, I .e. the spring is always in a deformed state (δxγ≠0). The rotation range of the inner and outer ring flexible hinges is±0.35 rad(±20°), simplify the trigonometric functions sin & gamma; and cos & gamma; as follows

After simplification, the load-displacement relationship of the spring

2.2 Error analysis of positive and negative stiffness matching model

Evaluate the error caused by the simplified treatment of equation (13). According to the actual processing parameters of zero stiffness flexible hinge (Section 4.2):n = 3,l = 40mm, =π, = 0.2,E = 73 GPa; The dimensions of the inner and outer ring flexible hinge reed L = 46mm,T = 0.3mm,W = 9.4mm; The comparison formulas (12) and (14) simplify the load displacement relationship and relative error of the front and rear springs as shown in Figures 10a and 10b respectively.

As shown in Figure 10, & gamma; is less than 0.35 rad (20°), the relative error caused by the simplified treatment to the load-displacement curve does not exceed 2.0%, and the formula

The simplified treatment of (13) can be used to construct zero-stiffness flexible hinges.

2.3 Stiffness characteristics of the spring

Assuming the stiffness of the spring is K, the simultaneous (3), (6), (14)

According to the actual processing parameters of zero stiffness flexible hinge (Section 4.2), the change curve of spring stiffness K with angle & gamma; is shown in Figure 11. In particular, when & gamma;= 0, K takes the minimum value.

For the convenience of design and processing, the spring adopts a linear positive stiffness spring, and the stiffness is Kconst. In the whole stroke, if the total stiffness of the zero stiffness flexible hinge is greater than or equal to zero, Kconst should take the minimum value of K

Equation (16) is the stiffness value of the linear positive stiffness spring when constructing the zero stiffness flexible hinge. 2.4 Analysis of zero-stiffness quality The load-displacement relationship of the constructed zero-stiffness flexible hinge is

Simultaneous formula (2), (8), (16) can be obtained

In order to evaluate the quality of zero stiffness, the reduction range of flexible hinge stiffness before and after adding the negative stiffness module is defined as the zero stiffness quality coefficientη

η The closer to 100%, the higher the quality of zero stiffness. Figure 12 is 1-η Relationship with crank length ratio and initial angle η It is independent of the number n of parallel crank-spring mechanisms and the length l of the base, but only related to the crank length ratio , the rotation angle & gamma; and the initial angle .

(1) The initial angle increases and the zero stiffness quality improves.

(2) The length ratio increases and the zero stiffness quality decreases.

(3) Angle & gamma; increases, zero stiffness quality decreases.

In order to improve the zero stiffness quality of the zero stiffness flexible hinge, the initial angle should take a larger value; the crank length ratio should be as small as possible. At the same time, according to the analysis results in Section 1.5, if is too small, the ability of the crank-spring mechanism to provide negative stiffness will be weak. In order to improve the zero stiffness quality of the zero stiffness flexible hinge, the initial angle =π, crank length ratio = 0.2, that is, the actual processing parameters of section 4.2 zero stiffness flexible hinge.

According to the actual processing parameters of the zero-stiffness flexible hinge (Section 4.2), the torque-angle relationship between the inner and outer ring flexible hinges and the zero-stiffness flexible hinge is shown in Figure 13; the decrease in stiffness is the zero-stiffness quality coefficientηThe relationship with the corner & gamma; is shown in Figure 14. By Figure 14: In 0.35 rad (20°) rotation range, the stiffness of the zero-stiffness flexible hinge is reduced by an average of 97%; 0.26 rad(15°) corners, it is reduced by 95%.

3 Design of linear positive stiffness spring

The construction of zero stiffness flexible hinge is usually after the size and stiffness of the flexible hinge are determined, and then the stiffness of the spring in the crank spring mechanism is reversed, so the stiffness and size requirements of the spring are relatively strict. In addition, the initial angle =π, from Figure 5a, during the rotation of the zero-stiffness flexible hinge, the spring is always in a compressed state, that is“Compression spring”.

The stiffness and size of traditional compression springs are difficult to customize precisely, and a guide mechanism is often required in applications. Therefore, a spring whose stiffness and size can be customized is proposed——Diamond-shaped leaf spring string. The diamond-shaped leaf spring string (Figure 15) is composed of multiple diamond-shaped leaf springs connected in series. It has the characteristics of free structural design and high degree of customization. Its processing technology is consistent with that of flexible hinges, and both are processed by precision wire cutting.

3.1 Load-displacement model of diamond-shaped leaf spring string

Due to the symmetry of the rhombic leaf spring, only one leaf spring needs to be subjected to stress analysis, as shown in Figure 16. α is the angle between the reed and the horizontal, the length, width and thickness of the reed are Ld, Wd, Td respectively, f is the dimensionally unified load on the rhombus leaf spring,δy is the deformation of rhombic leaf spring in the y direction, force fy and moment m are equivalent loads on the end of a single reed, fv and fw are component forces of fy in the wov coordinate system.

According to the beam deformation theory of AWTAR[13], the dimensionally unified load-displacement relation of single reed

Due to the constraint relationship of the rigid body on the reed, the end angle of the reed before and after deformation is zero, that isθ = 0. Simultaneous (20)(22)

Equation (23) is the load-displacement dimensional unification model of rhombic leaf spring. n2 rhombic leaf springs are connected in series, and its load-displacement model is

From formula (24), whenαWhen d is small, the stiffness of the diamond-shaped leaf spring string is approximately linear under typical dimensions and typical loads.

3.2 Finite element simulation verification of the model

The finite element simulation verification of the load-displacement model of the diamond-shaped leaf spring is carried out. Using ANSYS Mechanical APDL 15.0, the simulation parameters are shown in Table 2, and a pressure of 8 N is applied to the diamond-shaped leaf spring.

The comparison between the model results and the simulation results of the rhombus leaf spring load-displacement relationship is shown in Fig. 17 (dimensionalization). For four rhombus leaf springs with different inclination angles, the relative error between the model and the finite element simulation results does not exceed 1.5%. The validity and accuracy of the model (24) has been verified.

4 Design and test of zero-stiffness flexible hinge

4.1 Parameter design of zero-stiffness flexible hinge

To design a zero-stiffness flexible hinge, the design parameters of the flexible hinge should be determined according to the service conditions first, and then the relevant parameters of the crank spring mechanism should be calculated inversely.

4.1.1 Flexible hinge parameters

The intersection point of the inner and outer ring flexible hinges is located at 12.73% of the reed length, and its parameters are shown in Table 3. Substituting into equation (2), the torque-rotation angle relationship of the inner and outer ring flexible hinges is

4.1.2 Negative stiffness mechanism parameters

As shown in fig. 18, taking the number n of crank spring mechanisms in parallel as 3, the length l = 40 mm is determined by the size of the flexible hinge. according to the conclusion of section 2.4, the initial angle =π, crank length ratio = 0.2. According to equation (16), the stiffness of the spring (I .e. diamond leaf spring string) is Kconst = 558.81 N/m (26)

4.1.3 Diamond leaf spring string parameters

by l = 40mm, =π, = 0.2, the original length of the spring is 48mm, and the maximum deformation (& gamma;= 0) is 16mm. Due to structural limitations, it is difficult for a single rhombus leaf spring to produce such a large deformation. Using four rhombus leaf springs in series (n2 = 4), the stiffness of a single rhombus leaf spring is

Kd=4Kconst=2235.2 N/m (27)

According to the size of the negative stiffness mechanism (Figure 18), given the reed length, width and reed inclination angle of the diamond-shaped leaf spring, the reed can be deduced from formula (23) and the stiffness formula (27) of the diamond-shaped leaf spring Thickness. The structural parameters of rhombus leaf springs are listed in Table 4.

surface4

In summary, the parameters of the zero-stiffness flexible hinge based on the crank spring mechanism have all been determined, as shown in Table 3 and Table 4.

4.2 Design and processing of the zero-stiffness flexible hinge sample Refer to literature [8] for the processing and testing method of the flexible hinge. The zero-stiffness flexible hinge is composed of a negative stiffness mechanism and an inner and outer ring flexible hinge in parallel. The structural design is shown in Figure 19.

Both the inner and outer ring flexible hinges and diamond-shaped leaf spring strings are processed by precision wire-cutting machine tools. The inner and outer ring flexible hinges are processed and assembled in layers. Figure 20 is the physical picture of three sets of diamond-shaped leaf spring strings, and Figure 21 is the assembled zero-stiffness The physical picture of the flexible hinge sample.

4.3 The rotational stiffness test platform of the zero-stiffness flexible hinge Referring to the rotational stiffness test method in [8], the rotational stiffness test platform of the zero-stiffness flexible hinge is built, as shown in Figure 22.

4.4 Experimental data processing and error analysis

The rotational stiffness of the inner and outer ring flexible hinges and zero-stiffness flexible hinges was tested on the test platform, and the test results are shown in Figure 23. Calculate and draw the zero-stiffness quality curve of the zero-stiffness flexible hinge according to formula (19), as shown in Fig. 24.

The test results show that the rotational stiffness of the zero-stiffness flexible hinge is close to zero. Compared with the inner and outer ring flexible hinges, the zero-stiffness flexible hinge±0.31 rad(18°) stiffness was reduced by an average of 93%; 0.26 rad (15°), the stiffness is reduced by 90%.

As shown in Figures 23 and 24, there is still a certain gap between the test results of the zero stiffness quality and the theoretical model results (the relative error is less than 15%), and the main reasons for the error are as follows.

(1) The model error caused by the simplification of trigonometric functions.

(2) Friction. There is friction between the diamond leaf spring string and the mounting shaft.

(3) Processing error. There are errors in the actual size of the reed, etc.

(4) Assembly error. The gap between the installation hole of the diamond-shaped leaf spring string and the shaft, the installation gap of the test platform device, etc.

4.5 Performance comparison with a typical zero-stiffness flexible hinge In literature [4], a zero-stiffness flexible hinge ZSFP_CAFP was constructed using a cross-axis flexural pivot (CAFP), as shown in Figure 25.

Comparison of the zero-stiffness flexible hinge ZSFP_IORFP (Fig. 21) and ZSFP_CAFP (Fig. 25) constructed using the inner and outer ring flexible hinges

(1) ZSFP_IORFP, the structure is more compact.

(2) The corner range of ZSFP_IORFP is small. The corner range is limited by the corner range of the flexible hinge itself; the corner range of ZSFP_CAFP80°, ZSFP_IORFP corner range40°.

(3) ±18°In the range of corners, ZSFP_IORFP has higher quality of zero stiffness. The average stiffness of ZSFP_CAFP is reduced by 87%, and the average stiffness of ZSFP_IORFP is reduced by 93%.

5 Conclusion

Taking the flexible hinge of the inner and outer rings under pure torque as the positive stiffness subsystem, the following work has been done in order to construct a zero-stiffness flexible hinge.

(1) Propose a negative stiffness rotation mechanism——For the crank spring mechanism, a model (Formula (6)) was established to analyze the influence of structural parameters on its negative stiffness characteristics, and the range of its negative stiffness characteristics was given (Table 1).

(2) By matching the positive and negative stiffnesses, the stiffness characteristics of the spring in the crank spring mechanism (Equation (16)) are obtained, and the model (Equation (19)) is established to analyze the effect of the structural parameters of the crank spring mechanism on the zero stiffness quality of the zero stiffness flexible hinge Influence, theoretically, within the available stroke of the flexible hinge of the inner and outer rings (±20°), the average reduction in stiffness can reach 97%.

(3) Propose a customizable stiffness“spring”——A diamond-shaped leaf spring string was established to establish its stiffness model (Equation (23)) and verified by finite element method.

(4) Completed the design, processing and testing of a compact zero-stiffness flexible hinge sample. The test results show that: under the action of pure torque, the36°In the range of rotation angles, compared with the inner and outer ring flexible hinges, the stiffness of the zero-stiffness flexible hinge is reduced by 93% on average.

The constructed zero-stiffness flexible hinge is only under the action of pure torque, which can realize“zero stiffness”, without considering the case of bearing complex loading conditions. Therefore, the construction of zero-stiffness flexible hinges under complex load conditions is the focus of further research. In addition, reducing the friction that exists during the movement of zero-stiffness flexible hinges is an important optimization direction for zero-stiffness flexible hinges.

references

[1] HOWELL L L. Compliant Mechanisms[M]. New York: John Wiley&Sons, Inc, 2001.

[2] Yu Jingjun, Pei Xu, Bi Shusheng, etc. Research progress on design methods of flexible hinge mechanism[J]. Chinese Journal of Mechanical Engineering, 2010, 46(13):2-13. Y u jin champion, PEI X U, BIS call, ETA up. State-of-arts of Design Method for Flexure Mechanisms[J]. Journal of Mechanical Engineering, 2010, 46(13):2-13.

[3] MORSCH F M, Herder J L. Design of a Generic Zero Stiffness Compliant Joint[C]// ASME International Design Engineering Conferences. 2010:427-435.

[4] MERRIAM E G, Howell L L. Non-dimensional approach for static balancing of rotational flexures[J]. Mechanism & Machine Theory, 2015, 84(84):90-98.

[5] HOETMER K, Woo G, Kim C, et al. Negative Stiffness Building Blocks for Statically Balanced Compliant Mechanisms: Design and Testing[J]. Journal of Mechanisms & Robotics, 2010, 2(4):041007.

[6] JENSEN B D, Howell L L. The modeling of cross-axis flexural pivots[J]. Mechanism and machine theory, 2002, 37(5):461-476.

[7] WITTRICK W H. The properties of crossed flexure pivots and the influence of the point at which the strips cross[J]. The Aeronautical Quarterly, 1951, II: 272-292.

[8] l IU l, BIS, yang Q, ETA. Design and experiment of generalized triple-cross-spring flexure pivots applied to the ultra-precision instruments[J]. Review of Scientific Instruments, 2014, 85(10): 105102.

[9] Yang Qizi, Liu Lang, Bi Shusheng, etc. Research on rotational stiffness characteristics of generalized three-cross reed flexible hinge[J]. Chinese Journal of Mechanical Engineering, 2015, 51(13): 189-195.

yang Q I word, l IU Lang, BIS voice, ETA. Rotational Stiffness Characterization of Generalized Triple-cross-spring Flexure Pivots[J]. Journal of Mechanical Engineering, 2015, 51(13):189-195.

[10] l IU l, Zhao H, BIS, ETA. Research of Performance Comparison of Topology Structure of Cross-Spring Flexural Pivots[C]// ASME 2014 International Design Engineering Technical Conferences and Computers and Information in Engineering Conference, August 17–20, 2014, Buffalo, New York, USA. ASME, 2014 : V05AT08A025.

[11] l IU l, BIS, yang Q. Stiffness characteristics of inner–outer ring flexure pivots applied to the ultra-precision instruments[J]. ARCHIVE Proceedings of the Institution of Mechanical Engineers Part C Journal of Mechanical Engineering Science 1989-1996 (vols 203-210), 2017:095440621772172.

[12] SANCHEZ J A G. Criteria for the Static Balancing of Compliant Mechanisms[C]// ASME 2010 International Design Engineering Technical Conferences and Computers and Information in Engineering Conference, August 15–18, 2010, Montreal, Quebec, Canada. ASME, 2010:465-473.

[13] AWTAR S, Sen S. A generalized constraint model for two-dimensional beam flexures: Nonlinear strain energy formulation[J]. Journal of Mechanical Design, 2010, 132: 81009.

About the author: Bi Shusheng (corresponding author), male, born in 1966, doctor, professor, doctoral supervisor. His main research direction is fully flexible mechanism and bionic robot.

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ປະຕູເລື່ອນຕູ້ເສື້ອຜ້າທີ່ມີຄຸນນະພາບດີມີເນື້ອຫາດ້ານວິຊາການສູງ, ແຕ່ມັນເປັນເລື່ອງຍາກສໍາລັບຜູ້ບໍລິໂພກທີ່ຈະກໍານົດພວກມັນຈາກຮູບລັກສະນະ. ໃນຄວາມເປັນຈິງ, ທ່ານສາມາດຮູ້ສຶກແລະປະສົບກັບຜົນກະທົບເລື່ອນຂອງມັນຢູ່ໃນຄົນ. ປະຕູເລື່ອນຕູ້ເສື້ອຜ້າຄຸນນະພາບດີຈະບໍ່ເລື່ອນເກີນໄປໃນເວລາເລື່ອນ. ແສງສະຫວ່າງແລະບໍ່ຫນັກເກີນໄປ, ແຕ່ມີນ້ໍາຫນັກທີ່ແນ່ນອນຂອງປະຕູ, ບໍ່ມີການສັ່ນສະເທືອນໃນເວລາທີ່ເລື່ອນ, ກ້ຽງແລະໂຄງສ້າງ. ລາ​ຄາ​ຂອງ​ປະ​ຕູ sliding wardrobe ສະ​ເຫມີ​ໄປ​ຈະ​ໄດ້​ຮັບ​ຜົນ​ກະ​ທົບ​ໂດຍ​ອຸ​ປະ​ກອນ​ການ​, ຂະ​ຫນາດ​ແລະ​ຍີ່​ຫໍ້​, ສະ​ນັ້ນ​ລະ​ດັບ​ລາ​ຄາ​ແມ່ນ​ຂ້ອນ​ຂ້າງ​ຫຼາຍ​ຂອງ​ລາ​ຄາ​ຂອງ​ປະ​ຕູ sliding wardrobe ໄດ້​.

part2 Wardrobe sliding ວັດສະດຸປະຕູ

ໃນປັດຈຸບັນ, ອຸປະກອນການຂອງ wardrobe sliding ປະຕູແມ່ນໂດຍພື້ນຖານແລ້ວກະດານ melamine, ແລະບາງຮູບແບບຢູ່ໃນກະດານແລະແກ້ວ. ກະດານ melamine ພາຍໃນປະເທດເຊັ່ນ: Lushuihe ແມ່ນດີ. ປະຕູເລື່ອນຕູ້ເສື້ອຜ້າທີ່ເຮັດເອງແລະການຜະລິດຢູ່ໃນບ່ອນມີຂໍ້ດີຂອງຕົນເອງ. , ມີຮູບແບບພື້ນຖານທີ່ສາມາດເລືອກໄດ້ສໍາລັບຮູບແບບທີ່ກໍາຫນົດເອງ, ແລະສາມາດປ່ຽນແປງໄດ້ຢ່າງຍືດຫຍຸ່ນໃນເວັບໄຊທ໌. ທ່ານ​ຕ້ອງ​ໄດ້​ເອົາ​ໃຈ​ໃສ່​ກັບ​ການ​ຄັດ​ເລືອກ​ຂອງ​ປະ​ຕູ​ທີ່​ເຮັດ​ດ້ວຍ​ຕົນ​ເອງ​ເພື່ອ​ປ້ອງ​ກັນ​ບໍ່​ໃຫ້​ເຂົາ​ເຈົ້າ​ຈາກ​ການ​ເປັນ shoddy​. Wardrobe sliding ວັດສະດຸປະຕູ

part3 wardrobe ຂະຫນາດປະຕູເລື່ອນ

ຂະຫນາດຂອງກ່ອງຕິດຕາມຢູ່ສ່ວນເທິງຂອງປະຕູເລື່ອນຄວນຈະສູງ 12 ຊຕມແລະກວ້າງ 9 ຊຕມ. ເຊັ່ນດຽວກັນກັບກ່ອງຜ້າມ່ານ, ຕິດຕາມໄດ້ຖືກຕິດຕັ້ງຢູ່ໃນກ່ອງຕິດຕາມ, ແລະປະຕູເລື່ອນສາມາດຖືກຫ້ອຍຢູ່ເທິງຕິດຕາມ. ໃນ​ເວ​ລາ​ທີ່​ລະ​ດັບ​ຄວາມ​ສູງ​ຂອງ​ປະ​ຕູ​ຕ​່​ໍ​າ​ກ​່​ວາ 1.95 ແມັດ​, ປະ​ຊາ​ຊົນ​ມີ​ຄວາມ​ຮູ້​ສຶກ​ຕົກ​ຕໍ່າ​ຫຼາຍ​. ດັ່ງນັ້ນ, ເມື່ອເຮັດປະຕູເລື່ອນ, ຄວາມສູງຕ້ອງມີຢ່າງຫນ້ອຍ 19512 = 207 ຊມ. ຂະຫນາດຂອງປະຕູເລື່ອນ wardrobe ໄດ້

part4 wardrobe ຕິດຕາມປະຕູເລື່ອນ

ເມື່ອຕິດຕັ້ງການຕິດຕາມປະຕູເລື່ອນ, ແກ້ໄຂເສັ້ນທາງເທິງ, ວາງ 3 ຈຸດຢູ່ເທິງສອງສົ້ນແລະຈຸດກາງຂອງເສັ້ນທາງເທິງດ້ວຍໂກນແຮງໂນ້ມຖ່ວງ (ຄ້ອນ suspension), ແຕ້ມ 3.3 ຈຸດຄົງທີ່ຢູ່ເທິງພື້ນດິນດ້ວຍປາກການ້ໍາມັນ. , ຕິດ​ຕັ້ງ​ທາງ​ເທິງ​ແລ້ວ​ຫັນ​ໜ້າ​ກັບ​ທາງ​ເທິງ​ເອົາ​ຄ້ອນ​ຫ້ອຍ​ກັບ​ພື້ນ​ທີ່​ຈຸດ​ກາງ​ຂອງ​ເສັ້ນ​ທາງ, ເອົາ​ເສັ້ນ​ຕັ້ງ​ຢູ່​ສົ້ນ​ທັງ​ສອງ​ຂອງ​ເສັ້ນ​ທາງ, ແລະ​ສ້ອມ​ແປງ​ທາງ​ລຸ່ມ​ຢູ່​ສາມ​ຈຸດ​ນີ້​ເພື່ອ​ຮັບ​ປະ​ກັນ. ວ່າທາງເທິງແລະຕ່ໍາແມ່ນຂະຫນານຫມົດ, ແລະປະຕູເລື່ອນແມ່ນຢູ່ໃນສະພາບທີ່ດີທີ່ສຸດ. wardrobe sliding ຕິດຕາມປະຕູ

ວິ​ທີ​ການ​ບໍາ​ລຸງ​ຮັກ​ສາ Wardrobe sliding door ວິ​ທີ​ການ​ຕິດ​ຕັ້ງ wardrobe sliding door rail installation precautions

1. ສະຫຼຸບວິທີການບໍາລຸງຮັກສາສໍາລັບ wardrobe sliding ປະຕູ

1. Wardrobe sliding door ບໍາລຸງຮັກສາ - ວິທີການທໍາມະດາ

(1) ມີ screw ຢູ່ດ້ານເທິງຂອງປະຕູຂອງ railing sliding ປະຕູ, ເຊິ່ງສ່ວນໃຫຍ່ແມ່ນໃຊ້ເພື່ອແກ້ໄຂ rail ເລື່ອນ. ຫຼັງຈາກຖອດ screws ທັງສອງດ້ານຂອງປະຕູ, ພະຍາຍາມຍົກປະຕູແລະແກ້ໄຂມັນຢູ່ໃນຕໍາແຫນ່ງທີ່ສອດຄ້ອງກັນ, ແລະຫຼັງຈາກນັ້ນໃຊ້ screwdriver ເພື່ອແກ້ໄຂ rail ເລື່ອນ. ເລື່ອນອອກໄປໃນທິດທາງກົງກັນຂ້າມຂອງການຕິດຕາມ.

(2) ເມື່ອສອງ pulleys ຖືກແຍກອອກ, ປະຕູຈະຫຼຸດລົງອັດຕະໂນມັດ. ເຈົ້າ​ຕ້ອງ​ຍຶດ​ມັນ​ດ້ວຍ​ຕົວ​ເຈົ້າ​ເອງ, ຢ່າ​ທຳ​ຮ້າຍ​ຄົນ, ແລະ​ຢ່າ​ຕີ​ພື້ນ​ດິນ​ໂດຍ​ກົງ. ອຸປະກອນເສີມທີ່ຈໍາເປັນສໍາລັບປະຕູເລື່ອນແລະປ່ອງຢ້ຽມມີ pulleys. ເນື່ອງຈາກຄຸນນະພາບທີ່ແຕກຕ່າງກັນ, ລາຄາແມ່ນແຕກຕ່າງກັນຫຼາຍ. ຄວາມແຕກຕ່າງໃຫຍ່.

(3) ປະຕູຮົ້ວຂົວຫັກທີ່ມີ insulated ຄວາມຮ້ອນເປັນຮູແກ້ວທີ່ດີໂດຍທົ່ວໄປແລ້ວລາຄາປະມານ 7 ຢວນ. ຊີວິດການບໍລິການຂອງ pulley ແມ່ນຈໍາກັດ. ຫຼັງຈາກຈໍານວນທີ່ແນ່ນອນຂອງການນໍາໃຊ້ປີ, ທ່ານຈໍາເປັນຕ້ອງກວດເບິ່ງມັນຕົວທ່ານເອງ.

2. Wardrobe sliding door ບໍາລຸງຮັກສາ - ວິທີການທົ່ວໄປ

ຫຼັງຈາກແຍກ pulley, ບໍ່ຫັນທິດທາງຂອງ pulley ໄດ້, ທ່ານຈະພົບເຫັນຮ່ອງຮອຍຂະຫນາດນ້ອຍຢູ່ດ້ານເທິງຂອງປະຕູເລື່ອນໄດ້, ນີ້ແມ່ນບັນຫາຂອງຄວາມລົ້ມເຫຼວ, ພະຍາຍາມໃຊ້ວິທີການແກ້ໄຂປະຕູໄດ້, ແລ້ວຕິດຕັ້ງມັນກັບຄືນໄປບ່ອນ. ອີງຕາມວິທີການຕົ້ນສະບັບ.

3. Wardrobe sliding door ບໍາລຸງຮັກສາ - ບໍາລຸງຮັກສາເປັນມືອາຊີບ

(1) ຖ້າເຈົ້າບໍ່ສາມາດແກ້ໄຂໄດ້ດ້ວຍຕົວເຈົ້າເອງແທ້ໆ, ເຈົ້າສາມາດຊອກຫາແມ່ແບບບໍລິການຫຼັງການຂາຍເພື່ອແກ້ໄຂໄດ້. ນີ້ແມ່ນເນື້ອໃນການບໍລິການທີ່ທ່ານຄວນເພີດເພີນ, ແລະທ່ານສາມາດປະຫຍັດເງິນໄດ້.

(2) ເມື່ອຕິດຕັ້ງປະຕູເລື່ອນ rail hanging, ຄວາມກວ້າງຂອງສອງປະຕູຄວນຈະຖືກປະໄວ້. ໃນເວລາທີ່ພື້ນທີ່ດ້ານຫນ້າແລະຫລັງແມ່ນຂ້ອນຂ້າງນ້ອຍ, ທ່ານສາມາດພິຈາລະນານໍາໃຊ້ປະຕູເລື່ອນທາງລົດໄຟຫ້ອຍ.

(3) ເມື່ອຕິດຕັ້ງປະຕູເລື່ອນ, ພະຍາຍາມຫຼຸດຜ່ອນສາເຫດຂອງສິ່ງລົບກວນ. ຄຸນນະພາບຂອງ rail hanging ຈະຕ້ອງດີແລະຄວາມສາມາດຮັບການໂຫຼດໄດ້ຕ້ອງມີຄວາມເຂັ້ມແຂງ, ຖ້າບໍ່ດັ່ງນັ້ນມັນຈະສົ່ງຜົນກະທົບຕໍ່ການນໍາໃຊ້ຕໍ່ມາ.

2. ເລື່ອງທີ່ຕ້ອງການຄວາມສົນໃຈໃນການຕິດຕັ້ງ wardrobe sliding door rails

1. ປະຕູເລື່ອນແມ່ນຕິດຕໍ່ກັບກໍາແພງຫີນຫຼືທັງສອງດ້ານຂອງຮ່າງກາຍຕູ້. ຢູ່ທີ່ຕໍາແຫນ່ງຕິດຕໍ່, ບໍ່ຄວນມີວັດຖຸອື່ນທີ່ຂັດຂວາງການປິດປະຕູເລື່ອນ.

2. ຕໍາແຫນ່ງຂອງລິ້ນຊັກໃນຕູ້ຄວນຫຼີກເວັ້ນຈຸດຕັດກັນຂອງປະຕູເລື່ອນ, ແລະມັນຄວນຈະສູງກວ່າແຜ່ນລຸ່ມ 1 ຊມ; ລີ້ນຊັກໃນຕູ້ປະຕູພັບຄວນຢູ່ຫ່າງຈາກຝາດ້ານຂ້າງຢ່າງໜ້ອຍ 15 ຊມ, ໃຫ້ເອົາໃຈໃສ່ກັບສະວິດໄຟ ແລະ ເຕົ້າສຽບໃສ່ຝາ, ຖ້າມັນຖືກກີດຂວາງ ເມື່ອປະຕູເລື່ອນຖືກປິດ, ຕຳແໜ່ງຂອງມັນຄວນຈະຖືກແກ້ໄຂໃຫ້ທັນເວລາ. .

ໃນປັດຈຸບັນການປັບແຕ່ງເຮືອນທັງຫມົດແມ່ນແຜ່ຂະຫຍາຍຢູ່ໃນຕະຫຼາດ, ຫຼາຍຍີ່ຫໍ້ແລະບໍ່ແມ່ນຍີ່ຫໍ້ແມ່ນ Crazy ທີ່ຈະຕົກລົງໃນ, ລາຄາຕະຫຼາດແມ່ນ chaotic, ແລະຄຸນນະພາບຍັງບໍ່ສະເຫມີ. ໃຫ້ພິຈາລະນາສິ່ງທີ່ຄວນເອົາໃຈໃສ່ໃນເວລາເລືອກເຟີນີເຈີທີ່ກໍາຫນົດເອງ?

ອຸປະກອນເສີມຮາດແວທີສອງ pulleys ແລະຄູ່ມື rails

ນອກ ເໜືອ ໄປຈາກແຜ່ນ, ເຄື່ອງເຟີນີເຈີທີ່ເຮັດເອງແມ່ນຮາດແວ, ແຜ່ນແມ່ນກວມເອົາອັດຕາສ່ວນໃຫຍ່, ແຕ່ບົດບາດຂອງຮາດແວກໍ່ແມ່ນການສໍາພັດສໍາເລັດຮູບ. ຄຸນນະພາບຂອງຮາດແວໂດຍກົງຜົນກະທົບຕໍ່ຊີວິດຂອງເຟີນີເຈີ. ມີຮາດແວຫຼາຍປະເພດຫຼາຍກ່ວາແຜ່ນຢູ່ໃນຕະຫຼາດ. ຈໍານວນຫຼາຍ, ມື້ນີ້ພວກເຮົາໃຊ້ເວລາເບິ່ງຢູ່ໃນຫນຶ່ງຂອງ wardrobe ຮາດແວ sliding ປະຕູ pulleys rollers ແລະ rails.

pulleys ແລະ rails ນໍາພາໃນ wardrobe ປະຕູເລື່ອນແມ່ນອຸປະກອນເສີມທີ່ໃຊ້ເລື້ອຍໆທີ່ສຸດ, ດັ່ງນັ້ນຄຸນນະພາບຂອງພວກມັນມີຜົນກະທົບໂດຍກົງຕໍ່ຊີວິດການບໍລິການຂອງ wardrobe. ຄຸນະພາບຍັງບໍ່ສະຫມໍ່າສະເຫມີຢູ່ໃນຕະຫຼາດ, ແລະມີທຸກປະເພດຂອງລາຄາ. ດັ່ງນັ້ນສິ່ງທີ່ແນ່ນອນມັນຄວນຈະມີ? ຫນ້າທີ່ແລະວັດສະດຸສາມາດຕອບສະຫນອງຄວາມຕ້ອງການຂອງປະຊາຊົນ.

ການຕິດຕາມຂອງປະຕູເລື່ອນສາມາດແບ່ງອອກໄດ້ປະມານ: ສອງທິດທາງສາມາດຍູ້ແລະດຶງ, ແບບຫນຶ່ງ push ແລະດຶງແລະພັບ, ລູກຄ້າສາມາດເລືອກໄດ້ຕາມສະຖານະການຕົວຈິງ.

pulley ໃນ sliding door track pulley ເປັນອຸປະກອນເສີມທີ່ສໍາຄັນຫຼາຍໃນປະຕູເລື່ອນໄດ້. ເມື່ອຊື້, ເຈົ້າຕ້ອງຮູ້ວ່າວັດສະດຸຂອງເຈົ້າແມ່ນຫຍັງ. ອຸ​ປະ​ກອນ​ການ pulley ໃນ​ປັດ​ຈຸ​ບັນ​ໄດ້​ແບ່ງ​ອອກ​ເປັນ​ສາມ​ປະ​ເພດ​: pulley ພາດ​ສະ​ຕິກ​, ທີ່​ແຂງ​ແຕ່ fragile​. ການນໍາໃຊ້ຫຼັງຈາກໄລຍະເວລາ, ປະຕູເລື່ອນຈະບໍ່ລຽບ; ຄຸນນະພາບຂອງ pulley ໂລຫະແມ່ນດີກວ່າ, ແຕ່ສິ່ງລົບກວນແມ່ນ loud ຫຼາຍ; pulley ແກ້ວແມ່ນດີທີ່ສຸດຂອງສາມ pulleys ເຫຼົ່ານີ້, ມີຄວາມທົນທານທີ່ດີເລີດແລະທົນທານຕໍ່ການສວມໃສ່, ແລະມັນແມ່ນສະດວກຫຼາຍທີ່ຈະຍູ້ແລະດຶງ, ແລະມີຊີວິດການບໍລິການຍາວ.

ແຖບຄູ່ມືປະຕູເລື່ອນມີຄວາມສໍາຄັນກວ່າສໍາລັບປະຕູເລື່ອນ. ຄຸນນະພາບວັດສະດຸທີ່ແຕກຕ່າງກັນສົ່ງຜົນກະທົບຕໍ່ຄຸນນະພາບແລະການນໍາໃຊ້ທີ່ແຕກຕ່າງກັນຂອງປະຕູເລື່ອນ, ແລະຊີວິດການບໍລິການຂອງວັດສະດຸປະຕູເລື່ອນທີ່ມີຄຸນນະພາບສູງຈະຍາວກວ່າ. ສິ່ງ​ທີ່​ສໍາ​ຄັນ​ທີ່​ສຸດ​ສໍາ​ລັບ​ການ​ຕິດ​ຕາມ​ແມ່ນ​ວ່າ​ມັນ​ສາ​ມາດ​ເຂົ້າ​ກັນ​ໄດ້​ກັບ​ການ pulley ເຫມາະ​ສົມ​ບູນ​ແລະ​ຂະ​ຫນາດ​ແມ່ນ​ພຽງ​ແຕ່​ເຫມາະ​ສົມ​. ນີ້ແມ່ນສິ່ງທີ່ສໍາຄັນທີ່ສຸດ. ປະຕູເລື່ອນດັ່ງກ່າວເລື່ອນໄດ້ອຍ່າງລຽບງ່າຍ, ມີການດູດຊຶມດີແລະທົນທານຕໍ່ສຽງ, ແລະມີຜົນກະທົບທາງສຽງທີ່ດີກວ່າ. ໃນເວລາທີ່ຜູ້ບໍລິໂພກເລືອກ rails ປະຕູ, ພວກເຂົາເຈົ້າຕ້ອງເລືອກ rail ຄູ່ມືທີ່ມີຄຸນນະພາບດີທີ່ເຫມາະສົມກັບປະເພດຂອງເຮືອນຂອງທ່ານ, ເລືອກ rail ຄູ່ມືທີ່ທົນທານຕໍ່ການສວມໃສ່, ບໍ່ງ່າຍທີ່ຈະຜິດປົກກະຕິ, ແລະມີຄວາມຮູ້ສຶກ push-pull ທີ່ດີ.

ສໍາລັບລາຍລະອຽດອື່ນໆ, ບໍ່ວ່າຈະເປັນ rails ຄູ່ມືແລະ pulleys ແມ່ນງ່າຍທີ່ຈະເຮັດຄວາມສະອາດ, ບໍ່ວ່າຈະງຽບ, ບໍ່ວ່າຈະມີ locks ແລະໂຄງສ້າງພາຍໃນ, ບໍ່ວ່າຈະທົນທານຕໍ່ອຸນຫະພູມສູງແລະການຜຸພັງຄວນໄດ້ຮັບການຖາມຢ່າງຊັດເຈນ. ຂະຫນາດຂອງການຕິດຕາມຂອງປະຕູເລື່ອນ wardrobe ແມ່ນຫຍັງ?

ການຕິດຕາມປະຕູເລື່ອນທົ່ວໄປແມ່ນ 84 ມມ, ແລະຕໍາແຫນ່ງສະຫງວນໂດຍທົ່ວໄປແມ່ນ 100 ມມ. ໃນປັດຈຸບັນມີຄວາມກວ້າງຂອງການຕິດຕາມຂອງ 70 ມມ, ແຕ່ກອບປະຕູເລື່ອນທີ່ສອດຄ້ອງກັນກັບການຕິດຕາມນີ້.

ຄວາມສູງຂອງປະຕູແມ່ນດີກວ່າ 207 ຊຕມ, ເພື່ອບໍ່ໃຫ້ຫ້ອງທັງຫມົດເບິ່ງຄືວ່າຕົກຕໍ່າເກີນໄປ. ຂະຫນາດຕິດຕາມປະຕູເລື່ອນທີ່ດີທີ່ສຸດແມ່ນປະມານ 80 ຊຕມ x 200 ຊຕມ, ດັ່ງນັ້ນຄວາມສູງຂອງປະຕູແມ່ນມີຄວາມຫມັ້ນຄົງຫຼາຍແລະເບິ່ງດີ.

ຜູ້ບໍລິໂພກຄວນຮູ້ວ່າມີການຕິດຕາມຂະຫນາດໃດກ່ອນທີ່ຈະຮູ້ຂະຫນາດຂອງການຕິດຕາມປະຕູເລື່ອນ. ການຕິດຕາມຂອງປະຕູເລື່ອນສາມາດແບ່ງອອກເປັນປະມານ: ຕິດຕາມທີ່ສາມາດຍູ້ແລະດຶງໄດ້ສອງທິດທາງ, ທາງຫນຶ່ງແລະປະຕູເລື່ອນພັບ. ໃນ​ບັນ​ດາ​ສາມ​ປະ​ເພດ​ເຫຼົ່າ​ນີ້​, ປະ​ຕູ sliding folding ປະ​ຕູ​ຈະ​ຊ່ວຍ​ປະ​ຢັດ​ພື້ນ​ທີ່​. ຖ້າຜູ້ບໍລິໂພກເລືອກເຮັດປະຕູເລື່ອນ, ຄວາມສູງຂອງປະຕູຄວນໄດ້ຮັບການເລືອກສູງກວ່າ 207 ຊຕມ, ເພື່ອບໍ່ໃຫ້ຫ້ອງທັງຫມົດເບິ່ງຄືວ່າຕົກຕໍ່າເກີນໄປ. ຂະຫນາດຕິດຕາມປະຕູເລື່ອນທີ່ດີທີ່ສຸດແມ່ນ 80 ຊຕມ x ມີຄວາມສູງປະມານ 200 ຊຕມ, ປະຕູມີຄວາມຫມັ້ນຄົງຫຼາຍແລະເບິ່ງດີ.

ແນ່ນອນ, ຍັງມີເຮືອນຂະຫນາດໃຫຍ່ຈໍານວນຫຼາຍ (ການຕົກແຕ່ງຂອງເຮືອນຂະຫນາດໃຫຍ່). ຖ້າຜູ້ບໍລິໂພກເຫຼົ່ານີ້ຕ້ອງການເຮັດໃຫ້ຂະຫນາດຕິດຕາມປະຕູເລື່ອນທີ່ສູງຫຼາຍ, ພວກເຂົາຄວນເອົາໃຈໃສ່ກັບມັນ, ເພາະວ່າປະຕູແມ່ນສູງຫຼາຍ, ແລະຖ້າມັນຖືກຍູ້ແລະດຶງເລື້ອຍໆ, ປະຕູຂອງມັນເອງຈະເສຍຫາຍ. ຖ້າ​ສູງ​ເກີນ​ໄປ, ມັນ​ຈະ​ບໍ່​ໝັ້ນ​ທ່ຽງ, ​ແລະ​ຈະ​ເຮັດ​ໃຫ້​ປະຕູ​ແຕກ​ໄດ້​ຫຼາຍ​ກວ່າ. ຖ້າ​ຫາກ​ວ່າ​ບາງ​ປະ​ຕູ sliding ເຮັດ​ໄດ້​ດີ​, ມັນ​ສາ​ມາດ​ເຮັດ​ໃຫ້​ຄົນ​ເບິ່ງ​ເຫັນ​ວ່າ​ຫ້ອງ​ກາຍ​ເປັນ​ຂະ​ຫນາດ​ໃຫຍ່​, ສໍາ​ລັບ​ການ​ຍົກ​ຕົວ​ຢ່າງ​, ໃນ​ເຮ​​ືອນ​ຄົວ (ການ​ຕົບ​ແຕ່ງ​ຫ້ອງ​ຄົວ​) ການ​ນໍາ​ໃຊ້​ປະ​ຕູ sliding ເປີດ​, ຊຶ່ງ​ບໍ່​ພຽງ​ແຕ່​ມີ​ການ​ປິ່ນ​ປົວ​ຂອງ​ພາ​ທິ​ຊັນ (ການ​ຕົບ​ແຕ່ງ partition renderings​. ), ແຕ່ຍັງເຮັດໃຫ້ພື້ນທີ່ທັງຫມົດຂະຫນາດໃຫຍ່. ດັ່ງນັ້ນ, ຜູ້ບໍລິໂພກຄວນເອົາໃຈໃສ່ຫຼາຍຕໍ່ທາງເລືອກຂອງວັດສະດຸປະຕູເລື່ອນ. ປະຕູເລື່ອນຂອງວັດສະດຸທີ່ແຕກຕ່າງກັນມີຜົນກະທົບທີ່ແຕກຕ່າງກັນ, ແຕ່ມັນດີທີ່ສຸດທີ່ຈະບໍ່ເລືອກແກ້ວທີ່ມີຄວາມໂປ່ງໃສຢ່າງເຕັມທີ່, ເຊິ່ງມີຄວາມສ່ຽງຕໍ່ມົນລະພິດແສງສະຫວ່າງ.

ມີສາມປະເພດຂອງ pulleys ໃນຕະຫຼາດ: pulleys ພາດສະຕິກ, pulleys ໂລຫະແລະ pulleys fiberglass. ຕົວຢ່າງ, ບາງຍີ່ຫໍ້ໃຫຍ່ເຊັ່ນ: ປະຕູແລະປ່ອງຢ້ຽມ Meizhixuan ໃຊ້ pulleys fiberglass ກາກບອນ.

1. ຮູລີ່ໂລຫະມີຄວາມສາມາດຮັບມືທີ່ແຂງແຮງຫຼາຍ, ແລະສາມາດທົນກັບຄວາມແຮງ ແລະແຮງກົດດັນຂອງ frictional ທີ່ຍິ່ງໃຫຍ່, ແລະບໍ່ງ່າຍທີ່ຈະ deform.

2. ລໍ້ຢາງແມ່ນເຮັດຈາກ fiberglass ກາກບອນຫຼືວັດສະດຸ nylon, ເຊິ່ງສາມາດເຮັດໃຫ້ກິດຈະກໍາການຍູ້ແລະດຶງກ້ຽງຫຼາຍ, ແລະມັນບໍ່ງ່າຍທີ່ຈະເຮັດໃຫ້ສຽງ friction harsh.

3. rollers ເສັ້ນໄຍແກ້ວ, ອຸປະກອນການນີ້ແມ່ນທົ່ວໄປທີ່ສຸດໃນການນໍາໃຊ້ wardrobe sliding ປະຕູ, ເນື່ອງຈາກວ່າມັນບໍ່ງ່າຍທີ່ຈະ deform, ແລະ sliding ຍັງກ້ຽງຫຼາຍ.

ຂໍ້ມູນຂະຫຍາຍ:

pulleys Fiberglass ແມ່ນດີ. ໃນປັດຈຸບັນ, ໂດຍທົ່ວໄປແລ້ວມີສອງປະເພດຂອງ pulleys ໃນຕະຫຼາດ: pulleys ພາດສະຕິກແລະ fiberglass pulleys. pulleys ພາດສະຕິກແມ່ນແຂງ, ແຕ່ພວກເຂົາເຈົ້າແມ່ນງ່າຍທີ່ຈະແຕກ. ຫຼັງຈາກການນໍາໃຊ້ເວລາດົນນານ, ພວກມັນຈະກາຍເປັນລົດສະຫຼາຍ, ແລະຄວາມຮູ້ສຶກທີ່ຖືກກົດດັນຈະກາຍເປັນທີ່ບໍ່ດີຫຼາຍ. ລາຄາ ມັນຍັງຖືກກວ່າ; pulley fiberglass ມີຄວາມທົນທານທີ່ດີ, ທົນທານຕໍ່ການສວມໃສ່, ເລື່ອນລຽບ, ແລະຄວາມທົນທານ. ໃນເວລາທີ່ຊື້, ໃຫ້ແນ່ໃຈວ່າຈະຮັບຮູ້ວັດສະດຸຂອງ pulley ໄດ້.

ເລື່ອງທີ່ຕ້ອງການຄວາມສົນໃຈໃນການຕິດຕັ້ງ wardrobe sliding ຕິດຕາມປະຕູ

ໃນປັດຈຸບັນ, ຄອບຄົວທັງຫມົດມັກປັບແຕ່ງ wardrobes. ໃນຖານະເປັນ facade ຂອງ wardrobe ໄດ້, ປະຕູເລື່ອນເປັນປັດໄຈ intuitive ທີ່ສຸດຜົນກະທົບຕໍ່ຮູບແບບໂດຍລວມແລະຮູບລັກສະນະຂອງ wardrobe ໄດ້, ແລະປະຕູເລື່ອນຍັງເປັນຫນຶ່ງໃນພາກສ່ວນ wardrobe ທີ່ສຸດທີ່ຈະຕິດຕໍ່ກັບຮ່າງກາຍຂອງມະນຸດແລະວັດຖຸ. ໃນຊີວິດຈິງ. ສໍາລັບຜູ້ບໍລິໂພກຈໍານວນຫຼາຍມີຄວາມສັບສົນບາງຢ່າງກ່ຽວກັບການຕິດຕັ້ງປະຕູເລື່ອນ wardrobe. ຫຼັກຂອງການຕິດຕັ້ງປະຕູເລື່ອນ wardrobe ແມ່ນຢູ່ໃນການຕິດຕັ້ງຕິດຕາມ. ເພາະສະນັ້ນ, ຂ້າພະເຈົ້າຂໍແນະນໍາທ່ານຕໍ່ໄປ.

Wardrobe sliding door ຕິດຕັ້ງຕິດຕາມ

ຄໍາອະທິບາຍລະອຽດ.

ຕິດຕາມປະຕູເລື່ອນແມ່ນອົງປະກອບຫຼັກຂອງປະຕູເລື່ອນ. ສິ່ງທີ່ສໍາຄັນທີ່ສຸດໃນການຕິດຕັ້ງປະຕູເລື່ອນແມ່ນ

Wardrobe sliding door ຕິດຕັ້ງຕິດຕາມ

, ການຕິດຕັ້ງຕິດຕາມແມ່ນເກືອບສໍາເລັດ.

1. ຂະຫນາດຂອງກ່ອງຕິດຕາມຢູ່ສ່ວນເທິງຂອງປະຕູເລື່ອນຄວນຈະສູງ 12 ຊຕມແລະກວ້າງ 9 ຊຕມ. ເຊັ່ນດຽວກັນກັບກ່ອງຜ້າມ່ານ, ຕິດຕາມໄດ້ຖືກຕິດຕັ້ງຢູ່ໃນກ່ອງຕິດຕາມ, ແລະປະຕູເລື່ອນສາມາດຖືກຫ້ອຍຢູ່ເທິງຕິດຕາມ. ເມື່ອ​ຄວາມ​ສູງ​ຂອງ​ປະ​ຕູ​ຕ່ຳ​ກວ່າ 1,95 ແມັດ, ມັນ​ເຮັດ​ໃຫ້​ຜູ້​ຄົນ​ມີ​ຄວາມ​ທຸກ​ໃຈ. ດັ່ງນັ້ນ, ເມື່ອເຮັດປະຕູເລື່ອນ, ຄວາມສູງຄວນຈະມີຢ່າງຫນ້ອຍ 19512 = 207 ຊຕມຫຼືຫຼາຍກວ່ານັ້ນ.

2. ຂະຫນາດທອງຂອງປະຕູທໍາມະດາແມ່ນປະມານ 80 ຊຕມ 200 ຊຕມ. ພາຍໃຕ້ໂຄງສ້າງນີ້, ປະຕູແມ່ນຂ້ອນຂ້າງຫມັ້ນຄົງແລະສວຍງາມ. ດັ່ງນັ້ນ, ອັດຕາສ່ວນຂອງຄວາມກວ້າງກັບຄວາມສູງຂອງປະຕູເລື່ອນຄວນຈະຄ້າຍຄືກັນກັບຂະຫນາດທອງ.

3. ໃຊ້ຢ່າງລະມັດລະວັງປະຕູເລື່ອນຈາກພື້ນໄປຫາເທິງ (ກ່ອງຕິດຕາມເປີດ). ເນື່ອງຈາກການ swing ຫຼາຍເກີນໄປໃນເວລາທີ່ຍູ້ແລະດຶງ, ປະຕູເລື່ອນແມ່ນງ່າຍທີ່ຈະ deform ຕາມເວລາ. ຫຼັງຈາກການຜິດປົກກະຕິ, ປະຕູບໍ່ສາມາດເປີດໄດ້, ຊຶ່ງຫມາຍຄວາມວ່າມັນບໍ່ສາມາດສ້ອມແປງໄດ້ແລະບໍ່ສາມາດໃຊ້ໄດ້.

4. ສຸດທ້າຍ, ຕິດຕັ້ງການຕິດຕາມປະຕູເລື່ອນ: ແກ້ໄຂເສັ້ນທາງເທິງ, ວາງ 3 ຈຸດໃນສອງສົ້ນແລະຈຸດກາງຂອງເສັ້ນທາງເທິງດ້ວຍໂກນແຮງໂນ້ມຖ່ວງ (ໄມ້ຄ້ອນ suspension), ແຕ້ມພື້ນທີ່ຄົງທີ່ 3.3 ຈຸດຢູ່ເທິງພື້ນດິນດ້ວຍນ້ໍາມັນ. ​ໃສ່​ໄມ້​ຄ້ອນ​ຂ້າງ​ເທິງ, ​ແລ້ວ​ເອົາ​ຄ້ອນ​ແຂວນ​ໃສ່​ພື້ນ​ກັບ​ຈຸດ​ກາງ​ຂອງ​ທາງ​ເທິງ, ​ເອົາ​ເສັ້ນ​ຕັ້ງ​ໃສ່​ສອງ​ສົ້ນ​ຂອງ​ທາງ​ລົດ​ໄຟ, ​ແລະ​ສ້ອມ​ແປງ​ທາງ​ລຸ່ມ​ທັງ 3 ຈຸດ ​ເພື່ອ​ໃຫ້​ແນ່​ໃຈ​ວ່າ. ເສັ້ນທາງເທິງແລະລຸ່ມແມ່ນຂະຫນານກັນຢ່າງສົມບູນ, ແລະປະຕູເລື່ອນແມ່ນຢູ່ໃນຕໍາແຫນ່ງທີ່ດີທີ່ສຸດ. Stat.

ຮັບປະກັນ

Wardrobe sliding door ຕິດຕັ້ງຕິດຕາມ

ຄວາມ​ຄືບ​ຫນ້າ​ກ້ຽງ​, ຈໍາ​ເປັນ​ຕ້ອງ​ໄດ້​ເອົາ​ໃຈ​ໃສ່​ກັບ​ຈຸດ​ດັ່ງ​ຕໍ່​ໄປ​ນີ້​

1. ນັບຕັ້ງແຕ່ປະຕູເລື່ອນແມ່ນຕິດຕໍ່ກັບກໍາແພງຫີນຫຼືທັງສອງດ້ານຂອງຮ່າງກາຍຂອງຕູ້, ບໍ່ຄວນມີວັດຖຸອື່ນທີ່ຂັດຂວາງການປິດປະຕູເລື່ອນຢູ່ທີ່ຕໍາແຫນ່ງຕິດຕໍ່. ສໍາ​ລັບ​ຕົວ​ຢ່າງ​, ຕໍາ​ແຫນ່ງ​ຂອງ drawer ໃນ​ຕູ້​ຄວນ​ຈະ​ຫຼີກ​ເວັ້ນ​ການ​ຕັດ​ກັນ​ຂອງ​ປະ​ຕູ sliding ແລະ​ສູງ​ກ​່​ວາ​ແຜ່ນ​ລຸ່ມ​ສຸດ​ຢ່າງ​ຫນ້ອຍ 1cm​; ລີ້ນຊັກໃນຕູ້ປະຕູພັບຢູ່ຫ່າງຈາກຝາຂ້າງຢ່າງໜ້ອຍ 15 ຊມ. ໃນທີ່ນີ້, ໃຫ້ເອົາໃຈໃສ່ເປັນພິເສດຕໍ່ສະວິດໄຟແລະເຕົ້າສຽບໃສ່ຝາ. ຖ້າການປິດປະຕູເລື່ອນໄດ້ຖືກກີດຂວາງ, ຕໍາແຫນ່ງຂອງສະຫວິດແລະເຕົ້າສຽບຄວນໄດ້ຮັບການປ່ຽນແປງ.

2. ບໍ່ວ່າທ່ານຈະເຮັດວັດສະດຸໃດຢູ່ເທິງພື້ນດິນ, ທ່ານຕ້ອງຮັບປະກັນວ່າມັນເປັນລະດັບ, ແລະຝາສີ່ດ້ານຂອງການເປີດປະຕູຍັງຕ້ອງຖືກຮັກສາໄວ້ຕາມແນວນອນແລະແນວຕັ້ງ. ຖ້າບໍ່ດັ່ງນັ້ນ, ປະຕູຈະຖືກ skewed ຫຼັງຈາກການຕິດຕັ້ງ. ຄວາມຜິດພາດທີ່ສາມາດປັບໄດ້ບໍ່ເກີນ 10mm.

3. ກະລຸນາຢ່າຕິດຕັ້ງສາຍມຸມຢູ່ໃນຕໍາແຫນ່ງການຕິດຕັ້ງ. ສາຍ gypsum ສາມາດໄດ້ຮັບການຕິດຕັ້ງຢູ່ໃນແຜ່ນປະທັບຕາຂ້າງເທິງ closet ໄດ້. ຖ້າປະຕູແມ່ນກົງກັບດ້ານເທິງ, ຢ່າຕິດຕັ້ງສາຍ gypsum. ສໍາລັບຜ້າພົມທີ່ມີຄວາມຫນາຫນ້ອຍກວ່າ 5 ມມ, ຕັດຜ້າພົມທີ່ຕັ້ງໄວ້ແລະວາງມັນໂດຍກົງຖ້າຜ້າພົມທີ່ມີຄວາມຫນາຫຼາຍກວ່າ 5 ມມຖືກຕິດຕັ້ງຢູ່ເທິງລາງລົດໄຟຕ່ໍາ, ມັນສາມາດຖືກແກ້ໄຂໂດຍກົງໃສ່ຜ້າພົມດ້ວຍສະກູ. ; ຖ້າ​ຫາກ​ວ່າ​ມັນ​ໄດ້​ຮັບ​ການ​ຕິດ​ຕັ້ງ​ດ້ວຍ​ລາງ​ລົດ​ໄຟ​ດຽວ​, ຜ້າ​ພົມ​ຢູ່​ໃນ​ຕໍາ​ແຫນ່ງ​ຕ້ອງ​ໄດ້​ຮັບ​ການ​ຕັດ​ອອກ​, ແລະ​ແຖບ​ໄມ້​ຫນາ 3-5 ມ​ມ​ໄດ້​ຖືກ​ວາງ​ໄວ້​ໃນ​ຜ້າ​ພົມ​ລ່ວງ​ຫນ້າ​, ດັ່ງ​ນັ້ນ monorail ແມ່ນ pasted ໂດຍ​ກົງ​ເທິງ​.

ສຸດທ້າຍ, ເຕືອນໄພທີ່ອົບອຸ່ນ,

wardrobe sliding ຕິດຕາມປະຕູ

ມັນເປັນສິ່ງສໍາຄັນ, ດັ່ງນັ້ນພວກເຮົາກໍາລັງເຮັດ

Wardrobe sliding door ຕິດຕັ້ງຕິດຕາມ

ມັນດີກວ່າທີ່ຈະລະມັດລະວັງຫຼາຍ. ຂ້າພະເຈົ້າຫວັງວ່າການຕິດຕັ້ງຕິດຕາມປະຕູເລື່ອນ wardrobe ທີ່ຂ້າພະເຈົ້າໄດ້ນໍາສະເຫນີໃນມື້ນີ້ຈະເປັນປະໂຫຍດກັບທຸກຄົນ.

ຂັ້ນຕອນການຕິດຕັ້ງຂອງ wardrobe ປະຕູເລື່ອນແມ່ນຫຍັງ

Wardrobe sliding ປະຕູເລື່ອນ ຂັ້ນຕອນການຕິດຕັ້ງ;

1. ຂະຫນາດຂອງກ່ອງຕິດຕາມຢູ່ສ່ວນເທິງຂອງປະຕູເລື່ອນຕ້ອງສູງ 12 ຊຕມແລະກວ້າງ 9 ຊຕມ. ເຊັ່ນດຽວກັນກັບກ່ອງຜ້າມ່ານ, ຕິດຕາມໄດ້ຖືກຕິດຕັ້ງຢູ່ໃນກ່ອງຕິດຕາມ, ແລະປະຕູເລື່ອນສາມາດຖືກຫ້ອຍຢູ່ເທິງຕິດຕາມ. ເມື່ອ​ຄວາມ​ສູງ​ຂອງ​ປະ​ຕູ​ຕ​່​ໍ​າ​ກ​່​ວາ 1.95 ແມັດ​, ມັນ​ເຮັດ​ໃຫ້​ຜູ້​ຄົນ​ມີ​ຄວາມ​ຮູ້​ສຶກ​ຊຶມ​ເສົ້າ​ຫຼາຍ​. ດັ່ງນັ້ນ, ເມື່ອເຮັດປະຕູເລື່ອນ, ຄວາມສູງຄວນຈະມີຢ່າງຫນ້ອຍ 19512 = 207 ຊມ.

2. ຂະຫນາດທອງຂອງປະຕູທໍາມະດາແມ່ນປະມານ 80 ຊຕມ x 200 ຊຕມ. ພາຍໃຕ້ໂຄງສ້າງນີ້, ປະຕູແມ່ນຂ້ອນຂ້າງຫມັ້ນຄົງແລະສວຍງາມໃນເວລາດຽວກັນ. ດັ່ງນັ້ນ, ອັດຕາສ່ວນຂອງຄວາມກວ້າງກັບຄວາມສູງຂອງປະຕູເລື່ອນຄວນຈະຄ້າຍຄືກັນກັບຂະຫນາດທອງ.

3. ໃຊ້ປະຕູເລື່ອນຈາກພື້ນໄປຫາດ້ານເທິງດ້ວຍຄວາມລະມັດລະວັງ (ເປີດກ່ອງຕິດຕາມ). ເນື່ອງຈາກການ swing ຫຼາຍເກີນໄປໃນເວລາທີ່ຍູ້ແລະດຶງ, ປະຕູເລື່ອນແມ່ນງ່າຍທີ່ຈະ deform ຕາມເວລາ. ຫຼັງຈາກການຜິດປົກກະຕິ, ປະຕູບໍ່ສາມາດເປີດໄດ້, ຊຶ່ງຫມາຍຄວາມວ່າມັນບໍ່ສາມາດສ້ອມແປງໄດ້ແລະບໍ່ສາມາດໃຊ້ໄດ້.

4. ເມື່ອຕິດຕັ້ງປະຕູເລື່ອນ, ແກ້ໄຂທາງເທິງ, ວາງ 3 ຈຸດຢູ່ສອງສົ້ນແລະຈຸດກາງຂອງເສັ້ນທາງເທິງດ້ວຍໂກນແຮງໂນ້ມຖ່ວງ (ໄມ້ຄ້ອນຫ້ອຍ) ແລະແຕ້ມຫນ້າຄົງທີ່ 3.3 ຈຸດຢູ່ເທິງພື້ນດິນດ້ວຍປາກການ້ໍາມັນ, ຕິດຕັ້ງທາງເທິງ, ແລະຫຼັງຈາກນັ້ນເອົາໄມ້ຄ້ອນຕີກັບດິນຢູ່ໃຈກາງຂອງເສັ້ນທາງເທິງ, ເອົາເສັ້ນຕັ້ງຢູ່ໃນທັງສອງສົ້ນຂອງຕິດຕາມ, ແລະແກ້ໄຂທາງລຸ່ມໃນສາມຈຸດນີ້ເພື່ອຮັບປະກັນວ່າທາງເທິງແລະຕ່ໍາ. ຂະຫນານຢ່າງສົມບູນ, ແລະປະຕູເລື່ອນແມ່ນຢູ່ໃນສະພາບທີ່ດີທີ່ສຸດ. ຂຶ້ນ.