Evaluation method of asymmetric force of toggle clamping mechanism

Abstract

The present invention provides an evaluation method for the magnitude of the asymmetric force of an elbow-type mold clamping mechanism, the evaluation method comprising: calculating the first maximum vertical force F1 received by the guide rod under the friction coefficient μ1, and calculating the second maximum vertical force F2 received by the guide rod under the friction coefficient μ2 according to the first maximum vertical force F1; obtaining the difference △F between the maximum vertical force F1 received by the guide rod under the friction coefficient μ1 and the maximum vertical force F2 received by the guide rod under the friction coefficient μ2, and the value of the asymmetric force of the elbow-type mold clamping mechanism is △F. The technical solution provided by the present invention can solve the technical problem in the prior art that the guide rod and the platen clamping hand are severely deformed during the mold closing process due to ignoring the asymmetric force in the elbow-type mold clamping mechanism.

Description

Technical Field

[0001] The invention relates to the field of calculation of asymmetric force of a toggle-type clamping mechanism, and in particular to a method for evaluating the magnitude of asymmetric force of a toggle-type clamping mechanism. Background Art

[0002] At present, for the five-point oblique double toggle three-link clamping mechanism, the two toggle components of the mechanism cannot be completely consistent, which will cause asymmetric force to be generated during the clamping force establishment process. There is no method in the prior art to accurately predict the magnitude of the asymmetric force; this will lead to a great deal of blindness in the design of the guide rod and the clamping arm of the adjustment plate, which is generally designed based on the designer's experience or rough analogy based on existing models.

[0003] However, the above method often causes the guide rod and the template adjustment arm to be severely deformed during the mold closing process, and modifications are required to control the deformation within a reasonable range. Summary of the invention

[0004] The main purpose of the present invention is to provide a method for evaluating the asymmetric force of an elbow-type clamping mechanism, so as to solve the technical problem in the prior art that the guide rod and the adjusting plate clamping arm are severely deformed during the mold closing process due to ignoring the asymmetric force.

[0005] In order to achieve the above-mentioned purpose, the present invention provides a method for evaluating the asymmetric force of an elbow-type clamping mechanism. The method for evaluating the asymmetric force of an elbow-type clamping mechanism is used to evaluate the asymmetric force generated by two crankshaft components of the elbow-type clamping mechanism. The method for evaluating the asymmetric force of an elbow-type clamping mechanism comprises: obtaining the deformation of the elbow-type clamping mechanism under the maximum clamping force, and solving the corresponding crosshead stroke according to the deformation of the elbow-type clamping mechanism under the maximum clamping force; obtaining the friction coefficients of the two crankshaft components as μ1 and μ2, respectively, wherein μ1>μ2; calculating the first maximum vertical force F1 received by the guide rod under the friction coefficient μ1, and calculating the second maximum vertical force F2 received by the guide rod under the friction coefficient μ2 according to the first maximum vertical force F1; obtaining the difference △F between the maximum vertical force F1 received by the guide rod under the friction coefficient μ1 and the maximum vertical force F2 received by the guide rod under the friction coefficient μ2, and the value of the asymmetric force of the elbow-type clamping mechanism is △F.

[0006] Furthermore, the method for calculating the first maximum vertical force F1 of the guide rod under the friction coefficient μ1 includes: calculating the magnitude and action position of the first maximum vertical force F1 of the guide rod under the friction coefficient μ1.

[0007] Furthermore, the method for calculating the second maximum vertical force F2 received by the guide rod under the friction coefficient μ2 according to the first maximum vertical force includes: obtaining the action position of the first maximum vertical force F1, and calculating the second maximum vertical force F2 received by the guide rod at the action position of the first maximum vertical force F1.

[0008] Furthermore, the method for calculating the first maximum vertical force F1 that the guide rod is subjected to under the friction coefficient μ1 includes: calculating the magnitude of the clamping force Pm of the toggle-type clamping mechanism, and solving the first maximum vertical force F1 according to the magnitude of the clamping force Pm.

[0009] Furthermore, the method for calculating the clamping force Pm of the toggle-type clamping mechanism includes: obtaining the horizontal displacement Sm of the movable platen of the toggle-type clamping mechanism relative to the center of the hinge ear of the adjustment platen, max(Sm)=(L1+L2)*cos(c); calculating the clamping force Pm of the toggle-type clamping mechanism according to the horizontal displacement Sm of the movable platen of the toggle-type clamping mechanism relative to the center of the hinge ear of the adjustment platen, P m =k*(Sm i -Sm0); where k is the stiffness of the toggle-type clamping mechanism.

[0010] Further, after calculating the magnitude of the clamping force Pm of the toggle-type clamping mechanism, the method for evaluating the magnitude of the asymmetric force of the toggle-type clamping mechanism also includes:

[0011] Obtain the force amplification ratio M of the toggle clamping mechanism,

[0012] According to the formula Solve the crosshead force Po of the toggle-type clamping mechanism; where a1 is the angle between L2 and the horizontal line during the mold closing process, h is the angle between the line of action of the force at point O and the horizontal direction, and b is the angle between L4 and the horizontal line.

[0013] Furthermore, after solving the crosshead output force Po of the toggle-type clamping mechanism, the evaluation method of the asymmetric force of the toggle-type clamping mechanism further includes: solving the first maximum vertical force F1 according to the formula F1=P0*tg(b-Δb).

[0014] Further, the method for calculating the second maximum vertical force F2 includes:

[0015] Obtain the force amplification ratio M1 of the toggle clamping mechanism,

[0016] According to the formula Solve the crosshead output Po1 of the toggle-type clamping mechanism.

[0017] Further, after solving the crosshead force Po of the toggle-type clamping mechanism, the evaluation method of the asymmetric force of the toggle-type clamping mechanism also includes: according to the formula F2 = P 01 *tg(b) solves for the second maximum vertical force F2.

[0018] The application of the technical solution of the present invention can facilitate accurate calculation of the asymmetric force generated by the two crankshaft components, provide a design basis for the guide rod and the platen clamp, control the deformation within a reasonable range at one time, and reduce the research and development cost. Therefore, the technical solution provided by the present invention can solve the technical problem that the guide rod and the platen clamp in the prior art are severely deformed due to ignoring the asymmetric force in the toggle-type clamping mechanism, which causes the asymmetric force to be ignored. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0020] Figure 1 A flow chart showing a method for evaluating the magnitude of asymmetric force of a toggle-type clamping mechanism provided according to an embodiment of the present invention is shown;

[0021] Figure 2 An explanatory diagram of the length and displacement parameters of a toggle-type clamping mechanism provided according to an embodiment of the present invention is shown;

[0022] Figure 3 A schematic diagram of angle parameters of a toggle-type clamping mechanism according to an embodiment of the present invention is shown;

[0023] Figure 4 A force action diagram of a toggle type mold clamping mechanism provided according to an embodiment of the present invention is shown;

[0024] Figure 5 A schematic structural diagram of a toggle-type clamping mechanism provided according to an embodiment of the present invention is shown.

[0025] The above drawings include the following reference numerals:

[0026] 10. Adjusting template; 20. Cross head; 30. Guide rod; 40. First connecting rod; 50. Second connecting rod. DETAILED DESCRIPTION

[0027] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0028] like Figures 1 to 5As shown, an embodiment of the present invention provides a method for evaluating the asymmetric force of an elbow-type clamping mechanism. The method for evaluating the asymmetric force of an elbow-type clamping mechanism is used to evaluate the asymmetric force generated by two crankshaft components of the elbow-type clamping mechanism. The method for evaluating the asymmetric force of an elbow-type clamping mechanism includes: obtaining the deformation of the elbow-type clamping mechanism under the maximum clamping force, and solving the corresponding stroke of the crosshead 20 according to the deformation of the elbow-type clamping mechanism under the maximum clamping force; obtaining the friction coefficients of the two crankshaft components as μ1 and μ2, respectively, wherein μ1>μ2; calculating the first maximum vertical force F1 received by the guide rod 30 under the friction coefficient μ1, and calculating the second maximum vertical force F2 received by the guide rod 30 under the friction coefficient μ2 according to the first maximum vertical force F1; obtaining the difference △F between the maximum vertical force F1 received by the guide rod 30 under the friction coefficient μ1 and the maximum vertical force F2 received by the guide rod 30 under the friction coefficient μ2, and the value of the asymmetric force of the elbow-type clamping mechanism is △F. Figure 5 The structure diagram of the toggle type mold locking mechanism provided in this embodiment is shown. The toggle type mold locking mechanism includes an adjustment plate 10, a crosshead 20, a guide rod 30, a first connecting rod 40 and a second connecting rod 50. The crosshead 20 is a slider structure.

[0029] The use of such an evaluation method can facilitate accurate calculation of the asymmetric forces generated by the two crankshaft components, provide a design basis for the guide rod 30 and the adjustment template 10, control the deformation within a reasonable range at one time, and reduce R&D costs.

[0030] In this embodiment, the method for calculating the first maximum vertical force F1 of the guide rod 30 under the friction coefficient μ1 includes: calculating the magnitude and action position of the first maximum vertical force F1 of the guide rod 30 under the friction coefficient μ1. By adopting such a method, it is possible to better determine the value of the asymmetric force according to the magnitude and action position of the first vertical force F1.

[0031] Specifically, the method for calculating the second maximum vertical force F2 received by the guide rod 30 under the friction coefficient μ2 according to the first maximum vertical force includes: obtaining the action position of the first maximum vertical force F1, and calculating the second maximum vertical force F2 received by the guide rod 30 at the action position of the first maximum vertical force F1. By adopting such a method, it is easy to obtain the vertical force difference of the two crankshaft components at the action position of the first maximum vertical force F1, and the vertical force difference is the evaluation value of the asymmetric force magnitude.

[0032] In this embodiment, the method for calculating the first maximum vertical force F1 on the guide rod 30 under the friction coefficient μ1 includes: calculating the magnitude of the clamping force Pm of the toggle-type clamping mechanism, and solving the first maximum vertical force F1 according to the magnitude of the clamping force Pm. This method can facilitate accurate calculation of the value of the first maximum vertical force F1 and improve the accuracy of the solution.

[0033] Specifically, the method for calculating the clamping force Pm of the toggle-type clamping mechanism includes: obtaining the horizontal displacement Sm of the movable platen of the toggle-type clamping mechanism relative to the center of the hinge ear of the adjustment platen 10, max(Sm)=(L1+L2)*cos(c); calculating the clamping force Pm of the toggle-type clamping mechanism according to the horizontal displacement Sm of the movable platen of the toggle-type clamping mechanism relative to the center of the hinge ear of the adjustment platen 10, P m =k*(Sm i -Sm0); wherein k is the stiffness of the toggle-type clamping mechanism. By adopting this method, according to the above calculation formula, it is easy to accurately calculate the size of the clamping force Pm of the clamping mechanism, so as to accurately obtain the value of the first maximum vertical force F1.

[0034] In this embodiment, after calculating the magnitude of the clamping force Pm of the toggle-type clamping mechanism, the method for evaluating the magnitude of the asymmetric force of the toggle-type clamping mechanism further includes:

[0035] Obtain the force amplification ratio M of the toggle clamping mechanism,

[0036] According to the formula Solve the crosshead force Po of the toggle-type clamping mechanism; where a1 is the angle between L2 and the horizontal line during the mold-closing process, h is the angle between the line of action of the force at point O and the horizontal direction, and b is the angle between L4 and the horizontal line. This method can be used to easily solve the size of the crosshead force according to the force amplification ratio of the toggle-type clamping mechanism, thereby facilitating better improvement of the accuracy of solving the first maximum vertical force F1.

[0037] In this embodiment, after solving the output Po of the crosshead 20 of the toggle-type clamping mechanism, the evaluation method of the asymmetric force of the toggle-type clamping mechanism further includes: solving the first maximum vertical force F1 according to the formula F1=P0*tg(b-Δb). By adopting such a method, it is convenient to accurately obtain the magnitude of the first maximum vertical force F1 according to the above formula, so as to more accurately obtain the value of ΔF.

[0038] Specifically, the method for calculating the second maximum vertical force F2 includes:

[0039] Obtain the force amplification ratio M1 of the toggle clamping mechanism,

[0040] According to the formula Solve the output Po1 of the crosshead 20 of the toggle-type clamping mechanism. This method can improve the accuracy of solving the second maximum vertical force.

[0041] In this embodiment, after solving the output force Po of the crosshead 20 of the toggle-type clamping mechanism, the evaluation method of the asymmetric force of the toggle-type clamping mechanism also includes: according to the formula F2=P 01 *tg(b) solves the second maximum vertical force F2. By adopting this method, it is convenient to accurately obtain the magnitude of the second maximum vertical force according to the above formula.

[0042] In the present invention, the reason for the asymmetric force is that the friction coefficients of the two elbows are not equal, and the friction coefficient is μ1>μ2. The vertical force of the axis of the vertical guide rod 30 is calculated under the condition of a friction coefficient of μ1 for one elbow; and the vertical force of the axis of the vertical guide rod 30 is calculated under the condition of a friction coefficient of μ2 for the other elbow. In the process of establishing the clamping force, the vertical force first increases monotonically, then decreases monotonically, and the vertical force has a maximum value. Based on this feature, the position where the maximum vertical force is generated in the process of establishing the maximum clamping force under the condition of a friction coefficient of μ1 is calculated, and the difference in the vertical forces of the two elbows at this position is the evaluation value of the asymmetric force magnitude.

[0043] One elbow is calculated with the friction coefficient of boundary lubrication, and the other elbow is calculated with no friction. Figure 2 , fix the origin of the rectangular coordinate system at point O, and point D is in the first quadrant.

[0044] max(Sm)=(L1+L2)*cos(c) (1)

[0045] The rigidity of the mechanism is represented by k, so the clamping force is:

[0046] P m =k*(Sm i -Sm0) (2)

[0047] Friction conditions:

[0048] Force amplification ratio:

[0049]

[0050] Vertical force:

[0051] F1=P0*tg(b-Δb) (4)

[0052] Under frictionless conditions:

[0053] The force amplification ratio is:

[0054]

[0055] Vertical force:

[0056] F2=P 01 *tg(b) (6)

[0057]

[0058]

[0059] Find Sm from Sg:

[0060]

[0061]

[0062]

[0063] Sm=L1*cos(a+c)+L2*cos(a1) (12)

[0064]

[0065]

[0066]

[0067] Find Sg from Sm:

[0068]

[0069]

[0070] Sg=L5*cos(a+c+w)-L4*cos(b) (18)

[0071]

[0072]

[0073]

[0074]

[0075] The coordinates of the intersection point E are

[0076] x=(h2-h1-L1*sin(a+c)+Sg*tg(b-△b)+L5*sin(a+c+w)+Sm*tg(a1-△e)+L1*co s(a+c)*tg(a1-△e)+L5*tg(b-△b)*cos(a+c+w)) / (2*(tg(b-△b)+tg(a1-△e))) (twenty three)

[0077] y=(h1*tg(b-△b)+h2*tg(a1-△e)+Sg*tg(b-△b)*tg(a1-△e)-Sm*tg(b-△b)*tg(a1-△e)+L5*sin(a+c+w)*tg(a1-△e)+L1*sin( a+c)*tg(b-△b)-L1*cos(a+c)*tg(b-△b)*tg(a1-△e)+L5*tg(b-△b)*cos(a+c+w)*tg(a1-△e)) / (2*(tg(b-△b)+tg(a1-△e))) (twenty four)

[0079]

[0080] a is the angle between L1 during mold closing and its position at the end of mold closing;

[0081] a1 is the angle between L2 and the horizontal line during the touching process;

[0082] b is the angle between L4 and the horizontal line;

[0083] c is the angle between L1 and the horizontal line at the end of mold closing;

[0084] d is ∠OAB;

[0085] e is ∠OBA;

[0086] w is the angle between L1 and L5;

[0087] h1 The vertical distance between the center of the hinge ear of the adjustment template 10 and the center of the hinge ear of the moving template;

[0088] h2 is the vertical distance between the center of the hinge ear of the crosshead 20 and the center of the hinge ear of the adjustment template 10;

[0089] Sg horizontal displacement of the center of the hinge ear of the crosshead 20 relative to the center of the hinge ear of the adjustment template 10;

[0090] Sm is the horizontal displacement of the movable template relative to the center of the hinge ear of the adjustment template 10;

[0091] d1 is the diameter of the A, B, and O pins;

[0092] d2 is the diameter of C and D pins;

[0093] r1 is the radius of the dynamic friction circle of the L1 and L2 hinges;

[0094] r2 is the radius of the dynamic friction circle of the L4 hinge;

[0095] u is the friction coefficient of the rotary pair;

[0096] h is the angle between the line of action of the force at point O and the horizontal direction;

[0097] j is the angle between the line of action of the force at point O and the line of action of the force at point B;

[0098] n is the angle between the line of action of the force at point O and the line of action of the force at point D;

[0099] L1 is the length of OA, L2 is the length of AB, L3 is the length of CA, and L4 is the length of CD.

[0100] Pm is the clamping force, Po is the crosshead 20 output, and there is a toggle force amplification mechanism between them. The relationship between them is similar to the pressure of a hydraulic system determined by the load, Pm is the load, so Po needs to be calculated through the force amplification ratio.

[0101] 1) From equations (1) and (2), calculate the initial position Sm0 and final position max(Sm) of the movable platen that establishes the maximum clamping force.

[0102] 2) From Sm0 and max(Sm), use equations (7), (8), (16), (17), and (18) to calculate the initial position Sg0 and the final position max(Sg).

[0103] 3) Divide the range from Sg0 to max(Sg) into n equal parts, Sg i =Sg0, Sg0+△Sg, Sg0+2△Sg...Sg0+n△Sg, and the corresponding Sm is obtained by equations (7), (8), (9), (10), (11), and (12) i (i=0, 1……n).

[0104] 4) Based on step 3), calculate Sg by formula (2): i (i=0, 1……n) corresponding clamping force.

[0105] 5) Calculate Sg from equations (8), (10), (11), (19), (20), (21), (22), (23), (24), (25), and (3) i (i=0, 1...n) corresponding force amplification ratio.

[0106] 6) Based on steps 4) and 5), calculate Sg by formula (4): i (i=0, 1...n) corresponding vertical force.

[0107] 7) In Sg i (i=0、1……n) increasing direction, compare the adjacent F1(Sg i ) and F1(Sg i+1 ), first time "F1 (Sg i )>F1(Sg i+1 )”, F1(Sg i ) is max(F1), Sgi is Sg(max(F1)).

[0108] 8) The vertical component force F2 (Sg(max(F1))) is calculated from Sg(max(F1)) using equations (7), (8), (9), (10), (11), (12), (13), (14), (15), (5), and (6).

[0109] 9)max(F1)-F2(Sg(max(F1))) is the evaluation value of the asymmetric force.

[0110] From the above description, it can be seen that the above-mentioned embodiments of the present invention achieve the following technical effects: provide a design basis for the guide rod 30 and the adjustment template 10, provide a calculation formula, control the deformation within a reasonable range at one time, and reduce R&D costs.

[0111] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0112] Unless otherwise specifically stated, the relative arrangement, numerical expressions and numerical values ​​of the parts and steps set forth in these embodiments do not limit the scope of the present application. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to the actual proportional relationship. The technology, method and equipment known to those of ordinary skill in the relevant field may not be discussed in detail, but in appropriate cases, the technology, method and equipment should be considered as a part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so that once a certain item is defined in an accompanying drawing, it does not need to be further discussed in subsequent drawings.

[0113] In the description of the present application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings, and are only for the convenience of describing the present application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction, and therefore cannot be understood as limiting the scope of protection of the present application; the directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

[0114] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0115] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of this application.

[0116] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A method for evaluating the asymmetric force of a toggle-type clamping mechanism, characterized in that: The method for evaluating the asymmetric force of the toggle-type clamping mechanism is used to evaluate the asymmetric force generated by two crankshaft components of the toggle-type clamping mechanism. The method for evaluating the asymmetric force of the toggle-type clamping mechanism includes: Obtaining the friction coefficients of the two crankshaft components as μ1 and μ2, respectively, where μ1>μ2; calculating the first maximum vertical force F1 received by the guide rod under the friction coefficient μ1, and calculating the second maximum vertical force F2 received by the guide rod under the friction coefficient μ2 according to the first maximum vertical force F1; Obtain the difference △F between the maximum vertical force F1 received by the guide rod under the friction coefficient μ1 and the maximum vertical force F2 received by the guide rod under the friction coefficient μ2, and the value of the asymmetric force of the toggle-type clamping mechanism is △F; The method for calculating the first maximum vertical force F1 received by the guide rod under the friction coefficient μ1 includes: calculating the magnitude of the clamping force Pm of the toggle-type clamping mechanism, and solving the first maximum vertical force F1 according to the magnitude of the clamping force Pm; The method for calculating the clamping force Pm of the toggle-type clamping mechanism comprises: obtaining the horizontal displacement Sm of the movable platen of the toggle-type clamping mechanism relative to the center of the hinge ear of the adjustment platen, max(Sm)=(L1+L2)*cos(c); calculating the clamping force Pm of the toggle-type clamping mechanism according to the horizontal displacement Sm of the movable platen of the toggle-type clamping mechanism relative to the center of the hinge ear of the adjustment platen, P m =k*(Sm i -Sm0) wherein k is the stiffness of the toggle type clamping mechanism; Obtain the force amplification ratio M of the toggle-type clamping mechanism, According to the formula Solve the crosshead output Po of the toggle-type clamping mechanism; Among them, a1 is the angle between L2 and the horizontal line during the composite mold process, h is the angle between the line of action of the force at point O and the horizontal direction, and b is the angle between L4 and the horizontal line; According to the formula F1=P0*tg(b-Δb), solve the first maximum vertical force F1; The method for calculating the second maximum vertical force F2 includes: Obtain the force amplification ratio M1 of the toggle-type clamping mechanism, According to the formula Solve the crosshead output Po1 of the toggle-type clamping mechanism; According to the formula F2 = P 01 *tg(b) solves for the second maximum vertical force F2; Wherein, L1 is the length of OA, L2 is the length of AB, L4 is the length of CD, L5 is the length of OC, c is the angle between L1 and the horizontal line at the end of mold clamping, Smi is the value corresponding to the i-th equal part (Sg0+i△Sg) of dividing the interval from Sg0 to max(Sg) into n equal parts, Sg0 is the initial position of the horizontal displacement of the center of the hinge ear of the crosshead relative to the center of the hinge ear of the adjustment plate, max(Sg) is the final position of the horizontal displacement of the center of the hinge ear of the crosshead relative to the center of the hinge ear of the adjustment plate, and Sm0 is the initial position of the movable plate at the maximum mold clamping force; f is the angle between OB and the horizontal direction, d is ∠OAB, w is the angle between L1 and L5; e is ∠OBA; r1 is the radius of the dynamic friction circle of the L1 and L2 hinges, r2 is the radius of the dynamic friction circle of the L4 hinge, and tg is the tangent of the mathematical trigonometric function.

2. The method for evaluating the asymmetric force of a toggle-type clamping mechanism according to claim 1, characterized in that: The method for calculating the first maximum vertical force F1 of the guide rod under the friction coefficient μ1 includes: Calculate the size and action position of the first maximum vertical force F1 of the guide rod under the friction coefficient μ1.

3. The method for evaluating the asymmetric force of a toggle-type clamping mechanism according to claim 2, characterized in that: The method for calculating the second maximum vertical force F2 exerted on the guide rod under the friction coefficient μ2 according to the first maximum vertical force comprises: The action position of the first maximum vertical force F1 is acquired, and the second maximum vertical force F2 received by the guide rod at the action position of the first maximum vertical force F1 is calculated.

Images