Vibration-type linear conveying device

Abstract

In a vibrating linear conveying device comprising a first vibrating body and a second vibrating body as two mass bodies, the first vibrating body having a conveying path for conveying parts is connected to the second vibrating body at least at two locations by a first plate-shaped elastic body, and the second vibrating body is connected to a fixed mounting base at least at two locations by a second plate-shaped elastic body, the objective is to reduce pitching and reduce adverse effects from the mounting base or frame. [Solution] A vibrating linear conveying device comprising a first vibrating body 1 and a second vibrating body 2 as two mass bodies, having a conveying path 3 for conveying parts W, wherein the first vibrating body 1 and the second vibrating body 2 are connected at least at two places by a first plate-shaped elastic body 10, and the second vibrating body 2 and a fixed mounting base 4 are connected at least at two places by a second plate-shaped elastic body 20, wherein the vertical spring constant of the second plate-shaped elastic body 20 is set to be less than 14 times but 2 times or more the horizontal spring constant.

Description

Technical Field

[0001] The present invention relates to a vibration type linear conveying device that linearly conveys components using vibration. In particular, it relates to a vibration type linear conveying device that constitutes a mounting and anti-vibration mechanism with a pedestal by supporting a plate-like elastic member.

Background Art

[0002] In a conventional vibration type linear conveying device that uses a plate-like elastic member as an anti-vibration mechanism against a pedestal, the conveying situation changes significantly depending on the rigidity, mass, and mounting conditions of the pedestal, and it has generally been difficult to take countermeasures. From the perspective of vibration theory, it would be solved if the pedestal had rigidity and mass infinitely close to infinity, but it is difficult to achieve this under actual usage conditions.

[0003] The following will be described in detail.

[0004] Generally, vibration type linear conveying devices commonly used for conveying small components in factories and the like can be classified into the following three types according to their components.

[0005] <The First Device> As shown in FIG. 1, the first device is a device in which the vibration system is directly fastened to a fixed member such as a pedestal 5. Since this device has only one vibrating part, it constitutes a one-degree-of-freedom vibration system in vibration engineering by the inertial mass of the mass body (the first vibrating body) 1 including the conveying path 3 and the elastic force of the first plate-like elastic body (hereinafter also referred to as a leaf spring) 10. If the mass of the first vibrating body 1 is m and the total spring constant of the front and rear leaf springs 10 is K, the natural circular frequency ω1 of this system is as follows

[0006]

Equation

[0007] The vibration generated at the natural frequency ω1 immediately decays and stops due to losses such as friction. To maintain a constant vibration, a drive mechanism, such as an AC electromagnet, is provided between the first vibrating body 1 and the mounting base 4, but this mechanism is omitted from the illustration in this figure and the following figures. In this type of device, the reaction force due to the vibration of the first vibrating body 1 is transmitted directly from the mounting base 4 to the frame 5. If the frame 5 is firmly fixed without displacement under this force, it can be used without problems. However, if the frame 5 is weak, the transport path 3 attached to the first vibrating body 1 will not operate as designed (the reason will be explained later), and the parts W may stagnate or move backward on the transport path 3. Therefore, the device cannot be put into practical use unless the first vibrating body 1 is made lighter and the reaction force acting on the mounting base 4 is minimized. Manufacturers have limited the commercialization of this type of device to lightweight and compact applications.

[0008] <Second device> The second device, as shown in Figure 2, connects two vibrating bodies 1 and 2, the first and second, with leaf springs 10 positioned before and after them, and further connects the second vibrating body 2 to the mounting base 4 with a second plate-shaped elastic body (hereinafter also referred to as a vibration-damping spring) 20.

[0009] <Third device> The third device is the one shown in Figure 3, and is the most commonly used type of vibratory linear conveying device. The difference from the device shown in Figure 2 is that the part equivalent to the vibration-damping spring has been replaced with vibration-damping rubber 20G.

[0010] These second and third devices are both composed of the first and second vibrating bodies 1 and 2, and the spring constants of the vibration-damping springs 20 or vibration-damping rubber 20G that support them are set to be sufficiently smaller than those of the leaf springs 10 for vibration, so they can be said to be a structure close to a two-degree-of-freedom vibration system as defined in vibration engineering (it is sometimes called a quasi-two-degree-of-freedom system because the spring constants of the vibration-damping members cannot be made completely zero). If we assume that the spring constant of the vibration-damping spring 20 or vibration-damping rubber 20G is 0, then only the elastic force of the leaf spring 10 connecting the first vibrating body 1 and the second vibrating body 2 acts on it, and the vibrating system will float in the air. In this case, if the mass of the first vibrating body 1 is m1, the mass of the second vibrating body 2 is m2, and the total spring constant of the front and rear leaf springs 10 is K, then the intrinsic circular frequency ω2 of this system is given by the following equation.

[0011]

number

[0012] Thus, the masses m1 and m2 of both mass bodies 1 and 2 are involved. Here, we can see that when m2 is set to infinity, the result is the same as the example in Figure 1.

[0013] The problem in the format shown in Figures 2 and 3 is the pitching phenomenon that occurs in the vibration system (for example, in Figure 3, the tip of the transport path 3 vibrates in a swaying motion (pitching motion) in the direction of arrow X).

[0014] As shown in Figure 3, when the center of gravity of the first vibrating body 1 is GC1 and the center of gravity of the second vibrating body 2 is GC2, each vibrating body 1 and 2 vibrates in opposite phases to each other in a direction perpendicular to the leaf spring 10 (the direction of the dashed line). Assuming the spring constant of the vibration-damping rubber 20G is 0, this vibration system is essentially floating in the air. Therefore, a pitching motion occurs due to a moment force that is proportional to the displacement of the direction of force application (dimension L), the masses m1 and m2 of each vibrating body 1 and 2, and the amplitude. At this time, if observed from a viewpoint integrated with the second vibrating body 2, the transport path 3 appears to be operating at the same vibration angle (perpendicular to the longitudinal direction of the leaf spring 10) along its entire length in a direction perpendicular to the leaf spring 10. However, because the aforementioned pitching motion is superimposed, when viewed from outside this vibration system (a fixed gravitational field), the vibration angles appear to be different along the entire length of the transport path 3. As a result, the transport of part W may stall, or in severe cases, it may even move in reverse. In this type of vibrating linear conveying device, this pitching phenomenon always occurs. Therefore, as shown in Figure 3, it is necessary to adjust the positions of the centers of gravity of both vibrating bodies 1 and 2 by making the line connecting the centers of gravity GC1 and GC2 of the first and second vibrating bodies 1 and 2 perpendicular to the leaf spring 10 (making dimension L approach 0) in order to cancel out the moment force that causes pitching.

[0015] In actual devices, the weight behind the second vibrating body 2 is often adjusted by moving it back and forth. However, setting it to the ideal center of gravity is not easy. In this case, when vibration isolation is performed using vibration-damping rubber 20G as shown in Figure 3, the rubber's characteristic of providing an appropriate spring constant in all directions means that the problems described later do not occur as frequently, making adjustment easier.

[0016] In contrast, when a leaf spring-shaped elastic body (vibration-damping spring) 20 is used for vibration damping, as shown in Figure 2, the following problems occur in addition to the pitching problem.

[0017] This problem will be explained with reference to Figure 4.

[0018] First, we will explain the case where the line connecting the center of gravity points GC1 and GC2 of the first and second vibrating bodies 1 and 2 is perpendicular to the leaf spring 10 (Figure 4-B). In this case, both vibrating bodies 1 and 2 vibrate in opposite directions but in the same direction. Since the mounting angles γ1 and γ2 of the leaf spring 10 and the vibration-damping spring 20 with respect to the horizontal plane are usually designed to be the same angle, the force vector [F] shown in Figure 4-2 (Details of Part B) is mainly in the direction [E], which is the direction of the plate thickness of the vibration-damping spring 20, and there is almost no force [G] in the direction perpendicular to the plate thickness. Therefore, the displacement of the first and second vibrating bodies 1 and 2 in the [E] direction can be easily dissipated by the thin vibration-damping spring 20 (which has a small spring constant), and vibration transmission to the mounting base 4 is minimized.

[0019] Next, we will explain the case where the line connecting the center of gravity points GC1 and GC2 of the first and second vibrating bodies 1 and 2 is perpendicular to the leaf spring 10. In this case, as described above, a large moment arm [L] shown in FIG. 4-A occurs, and pitching motion occurs in an arc of X·Y about GC0, which is the common center of gravity of the two vibrating bodies 1 and 2. As a result, the vibration direction of the second vibrating body 2 becomes mostly in the [F] direction (vertical direction) as shown in FIG. 4-1. The [G] component obtained by vectorially decomposing this force is a component in a direction orthogonal to the plate thickness of the vibration isolator spring 20 (compressive or tensile force G = Fcos(90 - γ2)). Depending on the pitching state, G = F may result. The vibration isolator spring 20 exhibits a large rigidity in this G direction and allows only a deformation amount corresponding to the longitudinal elastic modulus of the material (in the case of a normal spring steel plate, the ratio of the spring constants in the [E] direction and the [G] direction generally reaches more than 20,000 times the measured values according to the dimensions = span C, plate thickness t, width B dimensions described in FIG. 4-2). This will inevitably exert a large force on the mounting base 4, and substantially it will be almost the same as the fixed type in FIG. 1. Even if such a large force acts on the mounting base 4 and the pedestal 5, there is no problem in principle if the structure can be firmly and reliably fixed as described in the explanation of FIG. 1. However, it is often impossible to create a pedestal 5 with extremely high rigidity that does not allow even minute displacements (especially in the vertical direction) in the actual usage environment. If the center of gravity points can be well aligned as described above, the vector [E] will be in the direction where the vibration isolator spring 20 is likely to be displaced as shown in FIG. 4-2, so the pitching problem hardly appears. However, in reality, it is often difficult to correctly align them. Therefore, operation in a situation where the pedestal 5 with limited rigidity is attached and the component of the vector [G] is generated more or less is inevitable.

[0020] When operating under such conditions, the behavior in the conventional example of FIG. 2 will be described below.

[0021] First, as shown in FIGS. 4-A and 4-1, the force of [G] is transmitted in the direction perpendicular to the plate thickness of the vibration isolator spring 20 and reaches the pedestal 5 through the mounting base 4. The pedestal 5 undergoes a displacement corresponding to the force [G] according to its strength. If the strength is sufficient, there will be no problem, but even a slight displacement will negatively affect the transport of part W. The displacements and other phenomena described so far are static explanations, but in reality, since it is a vibrating device, it causes more complex and dynamic problems. Due to the alternating push-pull force [G], the support structure 5 does not undergo simple static displacement, but rather generates vibrational displacement with various frequency components determined by the rigidity and mass of its vicinity. Although this displacement is minute, it is transmitted in the opposite direction to the force [G] mentioned earlier, perpendicular to the plate thickness of the vibration-damping spring 20, and as a result, the second vibrating body 2 is shaken. Since this contains components of various frequencies, waveforms, and phases, when transmitted to the second vibrating body 2, it is superimposed in the direction of vibration of the first vibrating body 1, worsening the transport condition of the component W. Thus, in the conventional example shown in Figure 2 under the above conditions, the structure is directly affected by the strength of the support frame 5, and the interaction with the vibration system in Figure 2 is also involved, making countermeasures complex and difficult to implement.

[0022] In other words, in a vibrating linear conveying device as shown in Figure 2, which comprises a first vibrating body (1) and a second vibrating body (2) as two mass bodies, and has a conveying path (3) for conveying parts (W), the first vibrating body (1) and the second vibrating body (2) are connected at least at two places by a first plate-shaped elastic body (10), and the second vibrating body (2) and a fixed mounting base (4) are connected at least at two places by a second plate-shaped elastic body (20), the following problems 1 and 2 must be solved.

[0023] Problem 1. Vibrations from the mounting base or frame to the vibrating linear conveyor system have adverse effects. To make pitching less likely Problem 2. To reduce the transmission of vibrations from the vibrating linear conveying device to the mounting base or frame. and

[0024] Conventionally, technologies such as those described in Patent Document 1 are known.

[0025] <Patent Document 1> Japanese Unexamined Patent Publication No. 2021-109721 Patent Document 1 contains: The objective is to "provide a vibration-damping transport device with a vibration-damping structure that allows for easy adjustment of pitching without causing a significant increase in cost or structural complexity." "A vibratory conveying device X that conveys an object W on a linear conveying surface by vibration, comprising: a first mass body 1 having a linear conveying surface; a second mass body 2 that vibrates in opposite phase to the first mass body 1; a first elastic body 3 connecting the first mass body 1 and the second mass body 2; and a second elastic body 5 connecting a base 4 and the first elastic body 3, wherein the device is configured such that at least the vertical elastic modulus of the second elastic body 5 can be independently changed." A vibration transport device is described (in the abstract section of the same document).

[0026] Paragraph 0022 of the same document states: "According to the present invention, by focusing on a second elastic body connecting the base and a second mass body or a first elastic body, and by providing a configuration that allows the vertical elastic modulus of the second elastic body to be changed independently without affecting the horizontal elastic modulus of the second elastic body, it is possible to provide a vibration-damping conveying device having a vibration-damping structure that allows for easy adjustment of pitching." It is stated as follows. However, the same document states that "vibrations that have adverse effects on the vibration-type linear conveyor from the mounting base or frame to the vibrating linear conveyor." There is no mention of "making pitching less likely to occur." Furthermore, no consideration has been given to the relationship between the vertical spring constant and the horizontal spring constant of the second plate-like elastic body. [Prior art documents] [Patent Documents]

[0027] [Patent Document 1] Japanese Patent Publication No. 2021-109721 [Overview of the project] [Problems that the invention aims to solve]

[0028] The problems that this invention aims to solve are as described above. A vibrating linear conveying device comprising a first vibrating body and a second vibrating body as two mass bodies, wherein the first vibrating body and the second vibrating body are connected at least at two locations by a first plate-shaped elastic body, and the second vibrating body and a fixed mounting base are connected at least at two locations by a second plate-shaped elastic body, Vibrations from the mounting base or frame to the vibrating linear conveyor can have adverse effects. To reduce the likelihood of pitching (Problem 1) To reduce the transmission of vibrations from the vibrating linear conveying device to the mounting base or frame. (Assignment 2) It is located there. [Means for solving the problem]

[0029] To solve the above problems, the present invention provides a vibratory linear conveying device. A vibrating linear conveying device comprising a first vibrating body and a second vibrating body as two mass bodies, wherein the first vibrating body and the second vibrating body are connected at least at two locations by a first plate-shaped elastic body, and the second vibrating body and a fixed mounting base are connected at least at two locations by a second plate-shaped elastic body, The second plate-shaped elastic body is characterized in that the vertical spring constant is less than 14 times but 2 times or more the horizontal spring constant.

[0030] According to this vibrating linear conveying device, the vertical spring constant of the second plate-shaped elastic body is less than 14 times the horizontal spring constant, so the following effects can be obtained. The inventors of the present invention conducted various experiments using a vibrating linear conveying device (hereinafter also referred to as the basic configuration device of the present invention), which comprises a first vibrating body and a second vibrating body as two mass bodies, the first vibrating body having a conveying path for conveying parts, the second vibrating body and the second vibrating body being connected at least at two points by a first plate-shaped elastic body, and the second vibrating body being connected at least at two points by a second plate-shaped elastic body. As a result, they found the following:

[0031] If the vertical spring constant of the second plate-shaped elastic body is 14 times or more than the horizontal spring constant, the vertical component of the vibration of the second vibrating body (displacement in the vertical direction) becomes less easily absorbed by the second plate-shaped elastic body and is more easily transmitted to the mounting base or frame (hereinafter also simply referred to as the mounting base). Conversely, the reaction force from the mounting base is more easily transmitted to the second vibrating body via the second plate-shaped elastic body. In this way, adverse effects from the mounting base occur in the second vibrating body, the vibrations of the second vibrating body and the mounting base become more complex, and as a result, pitching is more likely to occur.

[0032] In response to this, If the vertical spring constant of the second plate-shaped elastic body is less than 14 times the horizontal spring constant, the vertical component of the vibration of the second vibrating body is more easily absorbed by the second plate-shaped elastic body and less likely to be transmitted to the mounting base. Consequently, the reaction force from the mounting base is also less likely to occur, and adverse effects from the mounting base or frame are less likely to occur. As a result, pitching is also less likely to occur.

[0033] According to the vibrating linear conveying device of the present invention, since the vertical spring constant of the second plate-shaped elastic body is less than 14 times the horizontal spring constant, the vertical component of the vibration of the second vibrating body is more easily absorbed by the second plate-shaped elastic body and less likely to be transmitted to the mounting base. As a result, adverse effects from the mounting base or frame are less likely to occur, and pitching is also less likely to occur.

[0034] Furthermore, if the vertical spring constant of the second plate-shaped elastic body is less than twice the horizontal spring constant, the support strength of the second vibrating body via the second plate-shaped elastic body by the mounting base becomes small, making it difficult to establish a vibrating linear conveying device. However, according to the present invention, since the vertical spring constant of the second plate-shaped elastic body is twice or more the horizontal spring constant, the feasibility of establishing a vibrating linear conveying device is not impaired.

[0035] In this vibrating linear conveying device, The second plate-shaped elastic body is Two plate-shaped elastic divisions that are split vertically, It comprises a rectangular member sandwiched between these plate-like elastic divisions and having two parallel surfaces that are opposite to each other, One of the plate-shaped elastic segments is joined at its lower end to one parallel surface of the rectangular member, and its upper end is fastened to the second vibrating body. The other plate-shaped elastic segment of the plate-shaped elastic segment can be configured such that its upper part is joined to the other parallel surface of the rectangular member, and its lower part is fastened to the mounting base.

[0036] In this configuration, when a vertical force acts on the plate-shaped elastic segments arranged on both sides of the rectangular member, the force causes the rectangular member to rotate, and this rotational force causes the plate-shaped elastic segments arranged on both sides of the rectangular member to bend in the thickness direction. In other words, the vertical force acting on the plate-shaped elastic segments is converted by the rectangular member into a force that bends the plate-shaped elastic segments in the thickness direction. Therefore, when considering the second plate-like elastic body as a whole, it becomes easier to reduce the spring constant in the vertical direction. As a result, this configuration makes it easy to set the vertical spring constant of the second plate-like elastic body to less than 14 times the horizontal spring constant.

[0037] In this vibrating linear conveying device, The second plate-shaped elastic body, when viewed from the front, has mounting portions at the top and bottom, and is composed of an assembly in which a pair of crank-shaped elastic bodies, each having a crank-shaped bend between these mounting portions, are combined in a point-symmetrical manner. The upper mounting portion of this assembly can be fastened to the second vibrating body, and the lower mounting portion can be fastened to the mounting base.

[0038] With this configuration, when a vertical force acts on the crank-shaped elastic body, the crank-shaped bent portion can easily deform, making it easy to reduce the spring constant in the vertical direction. Therefore, with this configuration, it becomes easy to set the vertical spring constant of the second plate-like elastic body to less than 14 times the horizontal spring constant. Furthermore, since a pair of crank-shaped elastic bodies are combined in a point-symmetrical manner, the rolling rigidity can be improved when viewed from the front-to-back direction.

[0039] In this vibrating linear conveying device, The second plate-shaped elastic body, when viewed from the front, is an L-shaped elastic body in which one end extends laterally and the other end extends vertically, and the space between the upper and lower mounting portions is bent in an L-shape. One mounting portion of this L-shaped elastic body is fastened to the fastening portion of the second vibrating body, and the other mounting portion is fastened to the fastening portion of the mounting base. The fastening portion of the mounting portion that extends laterally can be configured to have a gap that partially allows for vertical deflection of the mounting portion that extends laterally.

[0040] With this configuration, when a vertical force acts on the L-shaped elastic body, the horizontal portion can easily be displaced vertically, making it easy to reduce the spring constant in the vertical direction. Therefore, with this configuration, it becomes easy to set the vertical spring constant of the second plate-like elastic body to less than 14 times the horizontal spring constant. Furthermore, since the second plate-shaped elastic body can be constructed from a single L-shaped elastic body, it is possible to simplify the structure and reduce the number of parts.

[0041] Furthermore, in order to solve the above problems, the vibratory linear conveying device of the present invention is A vibrating linear conveying device comprising a first vibrating body and a second vibrating body as two mass bodies, wherein the first vibrating body and the second vibrating body are connected at least at two locations by a first plate-shaped elastic body, and the second vibrating body and a fixed mounting base are connected at least at two locations by a second plate-shaped elastic body, The connection portion between the mounting base and the second plate-shaped elastic body is spaced apart from the object to be fixed to the mounting base, and a flexible portion is provided between the fixing portion to the object and the connection portion of the mounting base that allows the mounting base itself to bend in the vertical direction. The invention is characterized in that the vertical spring constant of the flexible portion of the second plate-shaped elastic body and the mounting base is less than 14 times but 2 times or more the horizontal spring constant.

[0042] This configuration also yields the same effect as described above, which is achieved when the vertical spring constant of the second plate-like elastic body is less than 14 times the horizontal spring constant.

[0043] In this vibrating linear conveying device, A stopper member can be provided between the second vibrating body and the mounting base to prevent plastic deformation of the second plate-shaped elastic body.

[0044] This configuration prevents permanent deformation of the second plate-shaped elastic body due to overload in the vertical direction. [Brief explanation of the drawing]

[0045] [Figure 1] A diagram showing the first example of a conventional, general-purpose vibratory linear conveying device. [Figure 2] The second example is shown in the same figure. [Figure 3] The third example is shown in the same figure. [Figure 4] A diagram illustrating the problems with conventional, general-purpose vibratory linear conveying systems. [Figure 5]A diagram illustrating the structure and operation of one embodiment of a vibratory linear conveying device according to the present invention. [Figure 6] This diagram also shows the structure of another embodiment. [Figure 7] Furthermore, a diagram illustrating the main parts and operation of another embodiment. [Figure 8] A diagram showing the structure of yet another embodiment. [Figure 9] A diagram showing an example of the vibrating linear conveying device (LC) used in the experiment. [Figure 10] A figure showing an example of the second plate-shaped elastic body 20 used in the experiment. [Figure 11] A diagram showing another example. [Figure 12] A diagram showing another example. [Figure 13] A diagram showing another example. [Figure 14] Diagram illustrating a device for measuring spring constants. [Figure 15] A graph showing the relationship between the thickness T of the rectangular member 23 and the vertical spring constant in the second plate-shaped elastic body 20. [Figure 16] A graph showing the relationship between the thickness T of the rectangular member 23 and the spring constant ratio (vertical / horizontal). [Figure 17] Figure 6 shows a specific example of the second plate-shaped elastic body 20. [Modes for carrying out the invention]

[0046] Hereinafter, embodiments of the vibratory linear conveying device according to the present invention will be described with reference to the drawings. In each figure, the same parts or corresponding parts are denoted by the same reference numerals.

[0047] The vibrating linear conveying devices shown in Figures 5, 6, 7, and 8 are all, A vibrating linear conveying device LC comprises a first vibrating body 1 and a second vibrating body 2 as two mass bodies, and has a conveying path 3 for conveying parts W. The first vibrating body 1 and the second vibrating body 2 are connected at least at two places (two places in the front and rear (left and right in the figure), but it is also possible to have three or more places) by a first plate-shaped elastic body 10, and the second vibrating body 2 and the mounting base 4 fixed to the frame 5 are connected at least at two places (two places in the front and rear (left and right in the figure), but it is also possible to have three or more places) by a second plate-shaped elastic body 20. The second plate-shaped elastic body 20 is characterized in that the vertical spring constant is less than 14 times but 2 times or more the horizontal spring constant.

[0048] In this type of vibrating linear conveying device LC, the vertical spring constant of the second plate-shaped elastic body 20 is less than 14 times the horizontal spring constant, so the following effects can be obtained.

[0049] The inventor of the present invention conducted various experiments (experimental examples will be described later) using a vibrating linear conveying device comprising a first vibrating body 1 and a second vibrating body 2 as two mass bodies, having a conveying path 3 for conveying parts W, the first vibrating body 1 and the second vibrating body 2 connected at least at two places by a first plate-shaped elastic body 10, and the second vibrating body 2 and a fixed mounting base 4 connected at least at two places by a second plate-shaped elastic body 20, and the following was found.

[0050] If the vertical spring constant of the second plate-shaped elastic body 20 is 14 times or more than the horizontal spring constant, the vertical component of the vibration of the second vibrating body 2 (displacement in the vertical direction) becomes less easily absorbed by the second plate-shaped elastic body 20 and is more easily transmitted to the mounting base 4 or support 5 (hereinafter also simply referred to as mounting base 4). Conversely, the reaction force from the mounting base 4 is more easily transmitted to the second vibrating body 2 via the second plate-shaped elastic body 20. In this way, adverse effects from the mounting base 4 occur in the second vibrating body 2, and the vibrations of the second vibrating body 2 and the mounting base 4 become more complex, and as a result, pitching is also more likely to occur.

[0051] In contrast, if the vertical spring constant of the second plate-shaped elastic body 20 is less than 14 times the horizontal spring constant, the vertical component of the vibration of the second vibrating body 2 is more easily absorbed by the second plate-shaped elastic body 20 and less likely to be transmitted to the mounting base 4. Consequently, the reaction force from the mounting base 4 is also less likely to occur, and adverse effects from the mounting base 4 or the frame are less likely to occur. As a result, pitching is also less likely to occur.

[0052] Thus, according to the vibrating linear conveying device of the present invention, the vertical spring constant of the second plate-shaped elastic body 20 is less than 14 times the horizontal spring constant. Therefore, the vertical component of the vibration of the second vibrating body 2 is more easily absorbed by the second plate-shaped elastic body 20 and less easily transmitted to the mounting base 4. As a result, adverse effects from the mounting base 4 or frame are less likely to occur, and pitching is also less likely to occur.

[0053] Furthermore, if the vertical spring constant of the second plate-shaped elastic body 20 is less than twice the horizontal spring constant, the support strength of the second vibrating body 2 via the second plate-shaped elastic body 20 by the mounting base 4 becomes small, making it difficult to establish the device as a vibrating linear conveying device. However, according to the present invention, since the vertical spring constant of the second plate-shaped elastic body 20 is twice or more the horizontal spring constant, the feasibility of the vibrating linear conveying device LC is not impaired.

[0054] The following describes the vibratory linear conveying devices LC of each embodiment. Conventional vibration-damping springs have high rigidity in the direction perpendicular to the plate thickness (as described in paragraph "0019", the spring constant ratio is 20,000 times or more), and the ratio of the spring constants in the vertical and horizontal directions in the mounted state of the vibration-damping spring is approximately 30 times or more. In contrast, in the embodiment described below, the vertical spring constant of the second plate-shaped elastic body 20 can be reduced to less than 14 times the horizontal spring constant.

[0055] The vibrating linear conveying device LC shown in Figure 5 has a second plate-shaped elastic body 20, as shown in Figures 5-1 and 5-5. Two plate-shaped elastic divisions 21 and 22 are divided vertically, It comprises a rectangular member 23 that is sandwiched between these plate-shaped elastic divided bodies 21 and 22 and has two parallel surfaces 23a and 23b that are opposite to each other. Of the plate-shaped elastic segmented bodies 21 and 22, one plate-shaped elastic segmented body 21 has its lower part 21a joined to one parallel surface 23a of the rectangular member 23, and its upper part 21b fastened to the second vibrating body 2. Of the plate-shaped elastic segmented members, the other plate-shaped elastic segmented member 22 has its upper part 22b joined to the other parallel surface 23b of the rectangular member 23, and its lower part 22a is fastened to the mounting base 4.

[0056] In such a device LC, when a vertical force FV acts on the plate-shaped elastic divisions 21 and 22, which are positioned on both sides of the rectangular member 23, as shown in Figures 5-2 and 5-3, this force causes the rectangular member 23 to rotate (counterclockwise in Figure 5-2, and clockwise in Figure 5-3). This rotational force FR bends the plate-shaped elastic divisions 21 and 22 in the thickness direction (the bent parts are indicated by reference numerals 21c and 22c). In other words, the vertical force FV acting on the plate-shaped elastic divisions 21 and 22 is converted by the rectangular member 23 into a force (FR) that bends the plate-shaped elastic divisions 21 and 22 in the thickness direction.

[0057] Therefore, when considering the second plate-shaped elastic body 20 as a whole, it becomes easier to reduce the spring constant in the vertical direction. As a result, this configuration makes it easy to set the vertical spring constant of the second plate-shaped elastic body 20 to less than 14 times the horizontal spring constant.

[0058] Furthermore, by changing the thickness T of the rectangular member 23 (Figure 5-1), the vertical spring constant can be finely adjusted to the required value (see Figure 16). In this embodiment, two sets of vibration-damping springs 20, as shown in Figure 5-1, are provided at the front and rear, but the above configuration may be applied to only one of them.

[0059] Furthermore, as shown in Figure 5-4, for example, when a horizontal force FH acts on the second plate-shaped elastic body 20, the connecting portion by the rectangular member 23 rotates (clockwise in the illustrated case), and accordingly the plate-shaped elastic segments 21 and 22 bend in the thickness direction (the bent portions are indicated by reference numerals 21c and 22c).

[0060] In Figures 5-1 and 5-5, 24b is a bolt, which fastens and fixes the plate-shaped elastic segments 21 and 22 to the rectangular member 23 via a plate nut 24n and a retaining plate 24c. 2b is a bolt that fastens and fixes the upper part 21b of the plate-shaped elastic segment 21 to the second vibrating body 2 via a retaining plate 2c, and 4b is a bolt that fastens and fixes the lower part 22a of the plate-shaped elastic segment 22 to the mounting base 4 via a retaining plate 4c.

[0061] The structures shown in Figures 5-1 and 5-5 provide the following additional benefits. Due to its simple structure, in which the rectangular member 23 and the plate-shaped elastic segmented bodies 21 and 22 are fastened together with bolts 24b, it can be made with only minor processing of standard steel materials and can be manufactured at low cost. The vertical spring constant can be easily adjusted by inserting a shim between the rectangular member 23 and the plate-shaped elastic segment 21 and / or 22. (The inventor's experiments have shown that the vertical spring constant and the thickness T of the rectangular member 23 are inversely proportional.) Experiments by the inventors of this invention have shown that inserting a shim between the rectangular member 23 and the plate-shaped elastic segment 21 and / or 22 has almost no effect on the horizontal spring constant, making it easy to set the spring constant ratio in conjunction with the vertical spring constant.

[0062] The vibrating linear conveying device LC shown in Figure 6 has a second plate-shaped elastic body 20, as also shown in Figure 6-1, which is composed of an assembly 20A in which a pair of crank-shaped elastic bodies 25 are combined in a point-symmetrical manner, each having mounting parts 25a(25b), 25b(25a) at the top and bottom, and a crank-shaped bent part 25c between these mounting parts 25a(25b), 25b(25a). The upper mounting portion 20A1 of this assembly 20A is fastened to the second vibrating body 2, and the lower mounting portion 20A2 is fastened to the mounting base 4.

[0063] With this configuration, when a vertical force is applied to the crank-shaped elastic body 25, the crank-shaped bent portion 25c can be easily deformed, making it easy to reduce the spring constant in the vertical direction.

[0064] Therefore, with this configuration, it becomes easy to set the vertical spring constant of the second plate-shaped elastic body 20 to less than 14 times the horizontal spring constant.

[0065] By appropriately designing the length [J] of the horizontal section shown in Figure 6-1 (the spring constant is inversely proportional to the cube of [J] if all other conditions are equal), the required vertical spring constant can be obtained, and the vertical displacement of the second vibrating body 2 can be effectively released. Because the structure is simple and requires fewer components, it can be manufactured at a lower cost than Example 1. In Figure 6, two sets of the vibration-damping spring 20 of the present invention are provided at the front and rear, but it may also be applied to only one side.

[0066] In the vibrating linear conveying device LC shown in Figure 6, a pair of crank-shaped elastic bodies 25 are combined in a point-symmetrical manner to form the assembly 20A (second plate-shaped elastic body 20). However, the second plate-shaped elastic body 20 can also be made from either of the crank-shaped elastic bodies 25.

[0067] With this configuration, when a vertical force is applied to the crank-shaped elastic body 25, the crank-shaped bent portion 25c deforms easily, making it easy to reduce the spring constant in the vertical direction. In this case, the second plate-shaped elastic body 20 can be made from a single crank-shaped elastic body 25, thus simplifying the structure and reducing the number of parts.

[0068] In this embodiment, two sets of vibration-damping springs 20, as shown in Figure 6-1, are provided at the front and rear, but the above configuration may be applied to only one of them. The same applies when a single crank-shaped elastic body 25 is used; it may be applied to only one of the front or rear.

[0069] The vibrating linear conveying device LC, whose main parts are shown in Figure 7, is composed of an L-shaped elastic body 26 in which, in a front view, one end extends laterally and the other extends vertically, and the space between the upper and lower mounting portions 26h and 26v is bent into an L shape. One mounting portion of this L-shaped elastic body 26 (26h in the illustration) is fastened to the fastening portions (2c1, 2c2) of the second vibrating body 2, and the other mounting portion (26v in the illustration) is fastened to the fastening portions (4b, 4c) of the mounting base 4. The fastening portion of the mounting portion 26h that extends laterally is provided with a gap 27 that partially allows for vertical deflection of the mounting portion 26h that extends laterally (an example of which is shown as h in Figures 7-1 and 7-2).

[0070] With this configuration, when a vertical force acts on the L-shaped elastic body 26, the horizontal portion 26h can easily be displaced vertically, making it easy to reduce the spring constant in the vertical direction.

[0071] Therefore, with this configuration, it becomes easy to set the vertical spring constant of the second plate-shaped elastic body 20 to less than 14 times the horizontal spring constant. Furthermore, since the second plate-shaped elastic body 20 can be constructed from a single L-shaped elastic body 26, the structure can be simplified and the number of parts can be reduced.

[0072] In the diagram, the horizontal section 26h is fastened to the second vibrating body 2 and the vertical section 26v is fastened to the mounting base 4, but the horizontal section 26h may be fastened to the mounting base 4 and the vertical section 26v to the second vibrating body 2.

[0073] This L-shaped elastic body 26 may be applied to both the front and back of the device, or to only one of them.

[0074] In this embodiment, the horizontal section 26h is fastened to the second vibrating body 2 with first and second retaining plates 2c1 and 2c2 and bolts 2b. The gap 27 is formed by curved surfaces 2d1 and 2d2 that are smoothly curved in an arc shape when viewed from the front, and are formed at the ends of the first and second retaining plates 2c1 and 2c2, respectively.

[0075] With this configuration, for example, as shown in Figure 7-2, when the second vibrating body 2 goes down, the curved surface 2d1 of the first retaining plate 2c1 makes contact with the vibration-damping spring 20 in such a way that the contact position gradually changes towards the bent portion of the vibration-damping spring 20. As a result, the span from the bent portion of the vibration-damping spring 20 continuously shortens, and the vertical spring constant continuously increases. Conversely, the same thing happens when the second vibrating body 2 goes up due to the second retaining plate 2c2.

[0076] The reason for changing the spring constant in the vertical direction is to increase the stiffness when a large displacement occurs in the vertical direction. By minimizing the vertical spring constant, the vibration-damping support structure desired by the present invention can be obtained, and the influence from the mounting frame 5 can be reduced.

[0077] However, if the vertical spring constant is reduced and no countermeasures are taken, there is a risk that the vibration-damping spring 20 may be permanently deformed if a large force is applied when transporting or maintaining the device.

[0078] In contrast, according to this embodiment, even if a large force is applied when transporting or maintaining the device, the rigidity of the vibration-damping spring 20 is increased by the above configuration, thus reducing the risk of the vibration-damping spring 20 undergoing permanent deformation.

[0079] Furthermore, during normal operation as a vibrating linear conveying device, the vertical amplitude of the second vibrating body 2 is very small, so a structure like this, which allows for increased rigidity only when there is a large deformation due to an external force, is suitable.

[0080] The vibrating linear conveying device LC shown in Figure 8 has the connection points (2b, 2c) between the mounting base 4 and the second plate-shaped elastic body 20 separated from the frame 5 to which the mounting base 4 is fixed, and a flexible portion 4f is provided between the fixing portion 4d of the mounting base 4 to the fixing target 5 and the aforementioned connection points (2b, 2c) to allow the mounting base 4 itself to deflect in the vertical direction. The spring constant in the vertical direction of the second plate-shaped elastic body 20 and the flexible portion 4f of the mounting base 4 (the elastic body consisting of the second plate-shaped elastic body 20 and the flexible portion 4f of the mounting base 4) is set to be less than 14 times but 2 times or more the spring constant in the horizontal direction.

[0081] This configuration also yields the same effect as described above, which is achieved when the vertical spring constant of the second plate-shaped elastic body 20 is less than 14 times the horizontal spring constant.

[0082] As described above, the following effects (a)(b)(c)(d)(e) can be obtained with any of the vibrating linear conveying devices LC shown in Figures 5, 6, 7, and 8.

[0083] (a) Similar to the case of a device with vibration isolation using the vibration-damping rubber 20G shown in Figure 3, the reflection and transmission of vibrations can be blocked. This makes the system less susceptible to the influence of the rigidity and strength of the mounting frame 5, allowing it to operate under a wide range of mounting conditions and eliminating the need to deal with interactions that are difficult to understand.

[0084] (b) Since vibration isolation is provided by a leaf spring, it does not cause the "positioning" (resistance to misalignment) of the transport path 3 due to the softness in all directions which is a weakness of the vibration-damping rubber 20G. Furthermore, the meaning of "positioning" in this application is as follows: The vibrating linear conveying device according to the present invention vibrates constantly during operation, so it is not possible to connect the connection points with other devices, and maintaining a constant air gap is an essential condition. Under these conditions, the three-dimensional positional relationship at each connection point between the upstream side where parts W flow into the conveying path 3 of this device and the downstream side where parts flow out of the conveying path 3 to other devices is called "positioning". A device in which the displacement (deviation) of the positional relationship is small throughout the entire period from installation (including the transport stage from unloading to installation) to operation is described as having "good positioning".

[0085] (c) In the above embodiment, since all mounting surfaces of the vibration-damping spring 20 are perpendicular to the horizontal, it is easy to process and maintain high precision, and as a result, processing costs can be reduced. Also, in the embodiment shown in Figure 5, the rectangular member 23 sandwiched in the middle also has an orthogonal cross-section (cuboid), so processing costs can be reduced for the same reason.

[0086] (d) Because the material can be made of metal, it has excellent heat resistance, cold resistance, oil resistance, and durability.

[0087] (e) Although vibration-damping rubber is not recommended for use in the tensile direction, the present invention can be used without problems in the tensile direction, making it possible to suspend the device from the ceiling.

[0088] In the vibrating linear conveying device LC described above, for example, as shown by the dashed line in Figure 5, a stopper member 30 is provided between the second vibrating body 2 and the mounting base 4 to prevent plastic deformation of the second plate-shaped elastic body 20.

[0089] This configuration prevents permanent deformation of the second plate-shaped elastic body 20 due to overload in the vertical direction.

[0090] The stopper member 30 is fixed to the mounting base 4 and is a bolt or the like that maintains a small gap with the bottom surface of the second vibrating body 2, or is a vibration-damping rubber that connects the mounting base 4 and the second vibrating body 2. The stopper member 30 may be fixed to the second vibrating body 2, while maintaining a small gap between it and the upper surface of the mounting base 4.

[0091] The four embodiments have been described above, and they will be summarized below. Vibration-type linear conveying devices can be classified into three types based on the configuration of the vibration system and the method of vibration isolation support. As shown in Figure 1, this is a so-called fixed type with no vibration isolation mechanism, vibrating only a single mass. A vibration isolation mechanism using a leaf spring 10, as shown in Figure 2. As shown in Figure 3, a vibration damping mechanism using vibration-damping rubber 20G is employed instead of the leaf spring 10.

[0092] The leaf spring vibration isolation type shown in Figure 2, cited as a conventional example, is a compromise between the advantages and disadvantages of the other two types. While it reduces vibration leakage (transmission) to the mounting base 5, etc., compared to the fixed type, it is inferior to the vibration isolation rubber type. However, its "positioning" quality is close to that of the fixed type and far better than the vibration isolation rubber type. The leaf spring vibration isolation type seems like a good method that fills the weaknesses of the other two methods, but in reality, it only functions under special conditions, namely when the shift in the center of gravity, which is the source of the pitching motion, is minimal and vibration leakage to the mounting base 4 through the vibration isolation spring 20 is small. This is one of the reasons why this method has not become widespread. Therefore, under unfavorable conditions, the conventional type in Figure 2 ultimately becomes equivalent to the fixed type in Figure 1 and suffers from the same problems as the fixed type.

[0093] In view of this, the present invention provides an effective and practical solution by reducing the vertical spring constant of the vibration-damping spring 20. This ensures a wide range of design flexibility for the transport path 3 (mass, length, center of gravity, etc.), maintains performance without degrading the aforementioned "positioning," and makes it possible to use a reasonably priced structure without increasing the rigidity or mass of the mounting parts such as the frame 5. This makes it possible to apply the technology to larger models, which in previous examples could only be applied to medium and small models.

[0094] Furthermore, when viewed from the frame 5 side, the transmission of vibrations is reduced (especially harmful vibrations in the vertical direction), which suppresses noise generation. In the case of similar vibration devices installed, this reduces the phenomenon of vibration occurring even when the power is off, and can suppress unintended workpiece transport.

[0095] Examples and experimental examples are described below.

[0096] Figure 9 shows an example of the vibrating linear conveying device LC used in the experiment. The main specifications of this vibrating linear conveying device LC are as follows: Mass of the first vibrating body 1 including the transport path 3 = 3720g Mass of the second vibrating body 2, including the vibration imparting mechanism 6 = 3190g The mass of the first plate-shaped elastic body 10 = 215g (total of front and rear) The spring constant of the first plate-shaped elastic body 10 is 614 N (total for both front and rear). Mounting angle of the first plate-shaped elastic body 10 = 72° The mass of the mounting base 4 fixed to the frame 5 is 1497g (Note that since the mounting base 4 is fixed to the frame 5, the mass of the mounting base 4 does not affect the experimental results). Structure of the second plate-like elastic body 20 = Structure explained in Figure 5 The structure of the vibration-generating mechanism 6 is described as "a structure that generates vibration by applying an AC voltage to an electromagnetic magnet (coil) and periodically applying an attractive force to an iron core." (Generally, the electromagnetic magnet is attached to the second vibrating body 2, and the iron core is attached to the first vibrating body 1; the structure used in this embodiment is similar.) The part to be transported is a washer for W=M8 (outer diameter φ17.6mm, inner diameter φ8.9mm, thickness 1.6mm).

[0097] In the vibratory linear conveying device LC described above, the second plate-shaped elastic body 20 as shown in Figures 10 to 13 was attached, and the vibratory linear conveying device LC was operated to convey the parts W. In Figures 10 and 11, h is an opening to reduce rigidity. As a result, when using the second plate-shaped elastic body 20 shown in Figures 10, 11, and 12 (spring constant ratio = vertical / horizontal = 3.21, 7.49, and 8.95), pitting did not occur and the part W could be transported. However, when using the second plate-shaped elastic body 20 shown in Figure 13 (spring constant ratio = 14.0), pitting occurred.

[0098] The vertical spring constant of the second plate-shaped elastic body 20 shown in Figures 10 to 13 was measured by placing a weight W (approximately 1175 g) on ​​the spring constant measuring device 50 shown in Figure 14 and measuring the displacement at both ends of the second vibrating body 2 with displacement sensors 51, 51. The horizontal spring constant was measured by rotating the same device 90 degrees and measuring the displacement.

[0099] Figure 15 is a graph showing the relationship between the thickness T of the rectangular member 23 (spacer) and the vertical spring constant in the second plate-shaped elastic body 20, as measured by the above apparatus, and Figure 16 is a graph showing the relationship between the thickness T of the rectangular member 23 (spacer) and the spring constant ratio (vertical / horizontal).

[0100] In Figure 15, "y" represents the spring constant in the vertical direction, and in Figure 16, "y" represents the ratio of the spring constants. In Figures 15 and 16, "R²" is the coefficient of determination, and although there is no numerical standard, a coefficient of determination of "R²" of 0.95 or higher indicates a sufficiently strong correlation.

[0101] The values ​​here represent an inverse relationship. While the values ​​themselves are limited to the dimensions of this particular device, the inverse relationship itself is universal for any structure of the embodiment described above. Based on this relationship, as explained with reference to Figures 5-1 and 5-5, it becomes possible to predict and adjust the vertical spring constant by inserting shims.

[0102] Figure 17 shows a specific example of the second plate-shaped elastic body 20 shown in Figure 6.

[0103] Although embodiments of the present invention have been described above, the present invention is not limited to the embodiments described above, and can be appropriately modified and implemented within the scope of the gist of the present invention. For example, the gap in Figure 7 may be filled with an elastic material (e.g., rubber). [Explanation of Symbols]

[0104] 1: First vibrating body 2: Second vibrating body 3: Conveyor path 10: First plate-like elastic body 20: Second plate-like elastic body

Claims

1. In a vibrating linear conveying device comprising a first vibrating body (1) and a second vibrating body (2) as two mass bodies, and having a conveying path (3) for conveying parts (W), the first vibrating body (1) and the second vibrating body (2) are connected at least at two places by a first plate-shaped elastic body (10), and the second vibrating body (2) and a fixed mounting base (4) are connected at least at two places by a second plate-shaped elastic body (20), A vibrating linear conveying device characterized in that the vertical spring constant of the second plate-shaped elastic body (20) is less than 14 times but 2 times or more the horizontal spring constant.

2. In claim 1, The second plate-shaped elastic body (20) is Two plate-shaped elastic divisions (21, 22) divided into upper and lower sections, The rectangular member (23) is provided sandwiched between these plate-shaped elastic divisions (22, 22) and has two parallel surfaces that are opposite to each other. One of the plate-shaped elastic segments (21, 22) has its lower part joined to one parallel surface of the rectangular member (23), and its upper part fastened to the second vibrating body (2). A vibrating linear conveying device characterized in that the other plate-shaped elastic segment (21, 22) has its upper part joined to the other parallel surface of the rectangular member (23) and its lower part fastened to the mounting base (4).

3. In claim 1, The second plate-shaped elastic body (20) is composed of an assembly (20A) in which a pair of crank-shaped elastic bodies (25) are combined in a point-symmetrical manner, each having mounting portions (25a, 25b) at the top and bottom, and a crank-shaped bent portion (25c) between these mounting portions (25a, 25b). A vibrating linear conveying device characterized in that the upper mounting portion (20A1) of the assembly (20A) is fastened to the second vibrating body (2), and the lower mounting portion (20A2) is fastened to the mounting base (4).

4. In claim 1, The second plate-shaped elastic body (20) is composed of an L-shaped elastic body (26) in a front view, with one end extending laterally and the other extending vertically, and the space between the upper and lower mounting portions being bent in an L-shape. One mounting portion of this L-shaped elastic body (26) is fastened to the fastening portion of the second vibrating body (2), and the other mounting portion is fastened to the fastening portion of the mounting base (4). A vibrating linear conveying device characterized in that the fastening portion of the mounting portion (26h) that extends laterally is provided with a gap (27) that partially allows for vertical deflection of the mounting portion (26h) that extends laterally.

5. In a vibrating linear conveying device comprising a first vibrating body (1) and a second vibrating body (2) as two mass bodies, and having a conveying path (3) for conveying parts (W), the first vibrating body (1) and the second vibrating body (2) are connected at least at two places by a first plate-shaped elastic body (10), and the second vibrating body (2) and a fixed mounting base (4) are connected at least at two places by a second plate-shaped elastic body (20), The connection portion between the mounting base (4) and the second plate-shaped elastic body (20) is spaced apart from the object to be fixed to the mounting base (4), and a flexible portion (4f) is provided between the fixing portion of the mounting base 4 to the object and the connection portion, which allows the mounting base (4) itself to bend in the vertical direction. A vibrating linear conveying device characterized in that the vertical spring constant of the second plate-shaped elastic body (20) and the flexible portion (4f) of the mounting base (4) is less than 14 times but 2 times or more the horizontal spring constant.

6. In any one of claims 1 to 5, A vibrating linear conveying device characterized in that a stopper member (30) is provided between the second vibrating body (2) and the mounting base (4) to prevent plastic deformation of the second plate-shaped elastic body (20).

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