Vibration type linear transport device

Abstract

To make pitching less likely to occur and to make adverse effects from the mounting base or stand less likely to occur in a vibratory linear conveying device which is provided with a first vibrating body and a second vibrating body as two mass bodies, in which the first vibrating body having a conveying path for conveying parts and the second vibrating body are connected at least at two points by a first plate-like elastic body, and the second vibrating body and a fixed mounting base are connected at least at two points by a second plate-like elastic body. [Solution] In a vibratory linear conveying device having a first vibrating body 1 and a second vibrating body 2 as two mass bodies, the first vibrating body 1 having a conveying path 3 for conveying parts W and the second vibrating body 2 connected at least at two points by a first plate-shaped elastic body 10, and the second vibrating body 2 connected to a fixed mounting base 4 by a second plate-shaped elastic body 20 at least at two points, the vertical spring constant of the second plate-shaped elastic body 20 is set to be less than 14 times but more than twice the horizontal spring constant.

Description

[Technical field]

[0001] The present invention relates to a vibration type linear transport device that uses vibration to transport parts linearly, and more particularly to a vibration type linear transport device that is attached to a stand and has a vibration isolation mechanism supported by a plate-shaped elastic member. [Background technology]

[0002] In conventional vibration-type linear transport devices, where plate-shaped elastic members are used as a vibration isolation mechanism for the stand, the transport conditions change significantly depending on the rigidity, mass, and installation conditions of the stand, and it is generally difficult to take measures against this. From the viewpoint of vibration theory, this problem can be solved if the stand has nearly infinite rigidity and mass, but it is difficult to achieve this under actual operating conditions.

[0003] The details are explained below.

[0004] Common vibration-type linear transport devices that are often used to transport small parts in factories etc. can be classified into the following three types based on their components.

[0005] <First Device> The first device is a device in which the vibration system is directly fastened to a fixed member such as a stand 5, as shown in FIG. Since this device has only one vibrating part, the inertial mass of the mass body (first vibrating body) 1 including the transport path 3 and the elastic force of the first plate-shaped elastic body (hereinafter also referred to as a leaf spring) 10 form a vibration system with one degree of freedom as defined by vibration engineering. 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 given by the following equation:

[0006]

number

[0007] The vibrations that occur at the natural frequency of ω1 are immediately damped and stopped due to losses such as friction. In order to maintain a constant vibration, a driving mechanism using an AC electromagnet or the like is provided between the first vibrating body 1 and the mounting base 4, but this is not shown in the examples of this figure and the following figures. In this type of device, the reaction force caused by the vibration of the first vibrating body 1 is transmitted directly from the mounting base 4 to the base 5, so if the base 5 is firmly fixed and does not displace in response to this force, it can be used without any problems. However, if the base 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 part W may stagnate on the transport path 3 or move backwards. Therefore, it is not practical unless the first vibrating body 1 is made as light as possible to minimize the reaction force acting on the mounting base 4. Manufacturers commercialize devices of this type only for lightweight, compact applications.

[0008] <Second Device> The second device is a device in which the first and second vibrating bodies 1, 2 are connected by leaf springs 10 arranged in front and behind them as shown in FIG. 2, and further the second vibrating body 2 is connected to the mounting base 4 by a second plate-shaped elastic body (hereinafter also referred to as an anti-vibration spring) 20.

[0009] <Third Device> The third device is as shown in Figure 3, and is the most commonly used type of vibration-type linear conveyor device. The difference from the device shown in Figure 2 is that the part equivalent to the vibration-proof spring is replaced with a vibration-proof rubber 20G.

[0010] These second and third devices are both composed of a first and a second vibrating body 1, 2, and the spring constant of the vibration isolation spring 20 or vibration isolation rubber 20G that supports them is set to be sufficiently small compared to the leaf spring 10 that generates vibration, so the structure can be said to be close to a two-degree-of-freedom vibration system in vibration engineering (the spring constant of a vibration isolation material cannot be made completely zero, so it is sometimes called a quasi-two-degree-of-freedom system). If we assume that the spring constant of the vibration-proof spring 20 or the vibration-proof 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, causing the vibration system to 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, the natural circular frequency ω2 of this system is given by the following equation.

[0011]

number

[0012] In this way, the masses m1 and m2 of both mass bodies 1 and 2 are involved. If m2 is set to infinity, it becomes the same as the example in Figure 1.

[0013] The problem with the formats of FIGS. 2 and 3 is the pitching phenomenon that occurs in the vibration system (for example, in FIG. 3, the leading end of the transport path 3 vibrates in a swinging manner (pitching motion) in the direction of the arrow X).

[0014] As shown in FIG. 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, 2 vibrates in opposite phases toward a direction perpendicular to the leaf spring 10 (the direction of the dashed line). If we assume that the spring constant of the vibration-proof rubber 20G is 0, as mentioned above, then this vibration system is essentially floating in the air, and a pitching motion occurs due to a moment force that is proportional to the deviation in the direction of force action (dimension L), the masses m1 and m2 of each vibrating body 1 and 2, and the magnitude of the amplitude. At this time, if observed from a viewpoint integrated with the second vibrating body 2, the transport path 3 operates at the same vibration angle (direction perpendicular to the longitudinal direction of the leaf spring 10) over its entire length in a direction perpendicular to the leaf spring 10; however, since the above-mentioned pitching motion is superimposed, when viewed from outside this vibration system (in a fixed gravitational field), the vibration angles will be different over the entire length of the transport path 3. As a result, the conveyance of the parts W may stagnate, or in extreme cases, the parts may move in the opposite direction. In this type of vibratory linear conveying device, this pitching phenomenon always occurs, so as shown in Figure 3, it is necessary to make the line connecting the center of gravity points GC1 and GC2 of the first and second vibrating bodies 1 and 2 perpendicular to the leaf spring 10 (bringing the dimension L close to 0) and adjust the center of gravity positions of both vibrating bodies 1 and 2 to cancel out the moment force that causes pitching.

[0015] In actual equipment, adjustment is often performed by moving back and forth the weight behind the second vibrating body 2. However, it is not easy to set the center of gravity at an ideal position. In this case, if vibration is isolated using anti-vibration rubber 20G as shown in Figure 3, the characteristics of rubber allow for an appropriate spring constant in all directions, so problems such as those described below do not occur very often and adjustments tend to be easier.

[0016] In contrast to this, when a leaf spring-like elastic body (vibration isolation spring) 20 is used for vibration isolation as shown in FIG. 2, the following problem arises in addition to the pitching problem.

[0017] The problem will be explained with reference to FIG.

[0018] First, a case where the line connecting the centers of gravity GC1, GC2 of the first and second vibrating bodies 1, 2 is perpendicular to the leaf spring 10 (FIG. 4-B) will be described. In this case, both vibrators 1 and 2 vibrate in the same direction but in opposite directions. The mounting angles γ1 and γ2 of the leaf spring 10 and the anti-vibration spring 20 relative to the horizontal plane are usually designed to be the same, so the force vector [F] shown in Figure 4-2 (detail of part B) is mainly in the direction [E], which is the direction of the plate thickness of the anti-vibration spring 20, and almost no force [G] is generated in the direction perpendicular to the plate thickness. Therefore, the displacement of the first and second vibrating bodies 1, 2 in the [E] direction can be easily released by the thin vibration-proof spring 20 (which has a small spring constant), and the transmission of vibration to the mounting base 4 is kept to a minimum.

[0019] Next, a case where the line connecting the centers of gravity GC1 and GC2 of the first and second vibrating bodies 1 and 2 is not perpendicular to the leaf spring 10 will be described. In this case, as mentioned above, a large moment arm [L] shown in Figure 4-A is generated, causing a pitching motion in an X·Y arc around GC0, the common center of gravity of both vibrating bodies 1 and 2. As a result, the vibration direction of the second vibrating body 2 tends to be in the [F] direction (vertical direction) as shown in Figure 4-1. The [G] component obtained by vector decomposition of this force is the component in the direction perpendicular to the plate thickness of the vibration-proof spring 20 (compressive or tensile force G=Fcos(90-γ2)). Depending on the pitching state, G=F. The vibration-proof spring 20 exerts great rigidity in this G direction, and only allows deformation according to the modulus of longitudinal elasticity of the material (in the case of a normal spring steel plate, the ratio of the spring constant in the [E] direction to that in the [G] direction is more than 20,000 times the actual measured value for the commonly used dimensions = span C, plate thickness t, width B dimensions = each dimension shown in Figure 4-2). This means that a large force is applied to the mounting base 4, which is essentially almost the same as the fixed type in Figure 1. Even if such a large force acts on the mounting base 4 and the base 5, there is no problem in principle if the structure is strong and can be reliably fixed as explained in FIG. However, in the actual usage environment, it is often impossible to create a highly rigid base 5 that does not allow even minute displacements (especially in the vertical direction). If the center of gravity is well aligned as described above, the vector [E] will be in a direction that is easy for the vibration-proof spring 20 to displace as shown in Figure 4-2, so pitching problems will hardly occur, but in reality, it is often difficult to match them correctly. Therefore, it is unavoidable to operate the device in a situation where it is attached to a base 5 with limited rigidity and where the component of vector [G] occurs more or less.

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

[0021] First, as shown in Figures 4-A and 4-1, the force [G] is transmitted in a direction perpendicular to the thickness of the vibration-proof spring 20, passes through the mounting base 4, and reaches the frame 5. The base 5 responds to the force [G] and undergoes a displacement according to its strength. If the strength is sufficient, no problem will occur, but even a slight displacement will have a negative effect on the transportation of the parts W. The displacements and the like mentioned so far are static explanations, but in reality it is a vibrating device, which gives rise to more complex dynamic problems. The alternating push-pull force [G] causes the frame 5 to generate not a simple static displacement but a vibratory 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, perpendicular to the plate thickness of the vibration-proof spring 20, just like the previous force [G], and as a result, it vibrates the second vibrating body 2. Since this force contains components of various frequencies, waveforms, and phases, when it is transmitted to the second vibrating body 2, it is added to the vibration direction of the first vibrating body 1, and the conveying condition of the part W is deteriorated. In this way, under the above conditions, the conventional example of FIG. 2 is directly affected by the strength of the frame 5, and also involves interaction with the vibration system of FIG. 2, making countermeasures complex and difficult to implement.

[0022] That is, in a vibratory linear conveying device as shown in FIG. 2, which comprises a first vibrating body (1) and a second vibrating body (2) as two mass bodies, and in which the first vibrating body (1) having a conveying path (3) for conveying parts (W) and the second vibrating body (2) are connected at least at two points by a first plate-shaped elastic body (10), and the second vibrating body (2) is connected at least at two points 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 stand to the vibration type linear transport device can have a detrimental effect. To prevent pitching Problem 2: To make it difficult for vibration to be transmitted from the vibration type linear transport device to the mounting base or stand. and

[0024] Conventionally, a technique such as that shown in Patent Document 1, for example, has been known.

[0025] <Patent Document 1> JP 2021-109721 A Patent Document 1 states: The objective of the project is to provide a vibration conveying device having a vibration-proof structure that allows easy adjustment of pitching without incurring significant increases in cost or complexity of the structure. "A vibrating conveying device X that conveys an object W to be conveyed on a linear conveying surface by vibration, the device comprising a first mass body 1 having a linear conveying surface, a second mass body 2 that vibrates in the opposite phase to the first mass body 1, a first elastic body 3 that connects the first mass body 1 and the second mass body 2, and a second elastic body 5 that connects a base 4 and the first elastic body 3, and is configured such that, with regard to the horizontal elastic coefficient of the second elastic body 5 and the vertical elastic coefficient of the second elastic body 5, at least the vertical elastic coefficient of the second elastic body 5 can be changed independently." A vibrating conveying device is described (ibid. Abstract).

[0026] Paragraph 0022 of the same document states: "According to the present invention, by focusing on the second elastic body that connects the base to the second mass body or the first elastic body, and configuring the second elastic body so that the elastic modulus in the vertical direction can be changed independently without affecting the elastic modulus in the horizontal direction of the second elastic body, it is possible to provide a vibrating conveyor device having a vibration-proof structure that can easily adjust pitching." It is stated that: However, the document states that "there is a possibility that the vibration from the mounting base or stand to the vibration type linear conveying device may have a detrimental effect on the device. There is no mention of "making pitching less likely to occur." Furthermore, no consideration is given to the relationship between the vertical spring constant and the horizontal spring constant of the second plate-shaped elastic body. [Prior art documents] [Patent documents]

[0027] [Patent Document 1] Patent Publication No. 2021-109721 Summary of the Invention [Problem to be solved by the invention]

[0028] The problem to be solved by the present invention is as described above, A vibratory linear transport device is provided with a first vibrating body and a second vibrating body as two mass bodies, the first vibrating body having a transport path for transporting parts is connected to the second vibrating body by a first plate-like elastic body at at least two points, and the second vibrating body is connected to a fixed mounting base by a second plate-like elastic body at at least two points, Harmful vibrations from the mounting base or stand to the vibrating linear transport device Making pitching less likely to occur (issue 1) To prevent vibration transmission from the vibration type linear transport device to the mounting base or stand. (Task 2) is located. [Means for solving the problem]

[0029] In order to solve the above problems, the vibration type linear conveying device of the present invention is A vibratory linear transport device is provided with a first vibrating body and a second vibrating body as two mass bodies, the first vibrating body having a transport path for transporting parts is connected to the second vibrating body by a first plate-like elastic body at at least two points, and the second vibrating body is connected to a fixed mounting base by a second plate-like elastic body at at least two points, The second plate-shaped elastic body has a vertical spring constant that is less than 14 times but at least 2 times the horizontal spring constant.

[0030] According to this vibratory linear transport device, the spring constant in the vertical direction of the second plate-like elastic body is less than 14 times the spring constant in the horizontal direction, so that the following operational effects are obtained. The inventors of the present application have conducted various experiments using a vibratory linear conveying device (hereinafter also referred to as the basic component device of the present application) which is provided with a first vibrating body and a second vibrating body as two mass bodies, in which the first vibrating body having a conveying path for conveying parts is connected to the second vibrating body at at least two points by a first plate-shaped elastic body, and the second vibrating body is connected to a fixed mounting base at at least two points by a second plate-shaped elastic body.As a result, the following has been discovered.

[0031] If the spring constant in the vertical direction of the second elastic plate is 14 times or more the spring constant in the horizontal direction, the vertical component of the vibration of the second vibrating body (displacement in the vertical direction) is less likely to be absorbed by the second elastic plate, and is more likely to be transmitted to the mounting base or stand (hereinafter also simply referred to as the mounting base). Conversely, therefore, the reaction from the mounting base is more likely to be transmitted to the second vibrating body via the second elastic plate. In this way, the second vibrating body is adversely affected by the mounting base, and the vibration of the second vibrating body and the mounting base becomes more complex, and as a result, pitching is more likely to occur.

[0032] In response to this, If the spring constant in the vertical direction of the second elastic plate is less than 14 times the spring constant in the horizontal direction, the vertical component of the vibration of the second vibrating body is easily absorbed by the second elastic plate and is not easily transmitted to the mounting base. Therefore, a reaction from the mounting base is not easily generated, and adverse effects from the mounting base or the rack are not easily generated. As a result, pitching is not easily generated.

[0033] According to the vibratory linear conveying device of the present invention, the vertical spring constant of the second plate-shaped elastic body is less than 14 times the horizontal spring constant, so that the vertical component of the vibration of the second vibrating body is more easily absorbed by the second plate-shaped elastic body and is less likely to be transmitted to the mounting base, thereby reducing the likelihood of adverse effects from the mounting base or stand and also reducing the likelihood of pitching.

[0034] Furthermore, if the vertical spring constant of the second plate-shaped elastic body is less than twice its horizontal spring constant, the support strength of the second vibrating body via the second plate-shaped elastic body by the mounting base will be small, making it difficult to establish a vibratory linear conveying device. However, according to the present invention, the vertical spring constant of the second plate-shaped elastic body is more than twice its horizontal spring constant, so that the viability of the vibratory linear conveying device is not compromised.

[0035] In this vibration type linear conveying device, The second plate-shaped elastic body is Two plate-shaped elastic divisions divided into upper and lower parts; a rectangular member that is sandwiched between the plate-like elastic divided bodies and has two parallel surfaces that face each other and are parallel to each other; One of the plate-shaped elastic divided bodies has a lower portion joined to one of the parallel surfaces of the rectangular member and an upper portion fastened to the second vibrating body, The other of the plate-like elastic divided bodies may have an upper portion joined to the other parallel surface of the rectangular member and a lower portion fastened to the mounting base.

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

[0037] In this vibration type linear conveying device, the second plate-like elastic body has upper and lower mounting portions when viewed from the front, and is constituted by an assembly in which a pair of crank-like elastic bodies having a crank-like bent portion between the mounting portions are assembled in a point-symmetrical manner, The upper mounting portion of this assembly may be fastened to the second vibrating body, and the lower mounting portion may be fastened to the mounting base.

[0038] According to this configuration, when a force in the vertical direction acts on the crank-shaped elastic body, the crank-shaped bent portion can be easily deformed, so that it becomes easy to reduce the spring constant in the vertical direction. Therefore, with this configuration, it becomes easy to make the spring constant in the vertical direction of the second plate-shaped elastic body less than 14 times the spring constant in the horizontal direction. Furthermore, since the pair of crank-shaped elastic bodies are combined in point symmetry, the rolling rigidity as viewed from the front-rear direction can be improved.

[0039] In this vibration type linear conveying device, the second plate-like elastic body is configured as an L-shaped elastic body as a whole, in which an upper and lower mounting parts, one of which extends in the horizontal direction and the other of which extends in the vertical direction, are bent into an L-shape between the upper and lower mounting parts, when viewed from the front, One of the mounting portions 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 laterally extending mounting portion among the fastening portions may be configured to have a gap that partially allows the laterally extending mounting portion to bend in the up-down direction.

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

[0041] In order to solve the above problems, the vibration type linear conveying device of the present invention comprises: A vibratory linear transport device is provided with a first vibrating body and a second vibrating body as two mass bodies, the first vibrating body having a transport path for transporting parts is connected to the second vibrating body by a first plate-like elastic body at at least two points, and the second vibrating body is connected to a fixed mounting base by a second plate-like elastic body at at least two points, a coupling portion of the mounting base with the second plate-like elastic body is separated from a fixing object of the mounting base, and a flexible portion is provided between the fixing portion of the mounting base to the fixing object and the coupling portion, which allows the mounting base itself to bend in the vertical direction; The spring constant in the vertical direction of the second plate-shaped elastic body and the flexible portion of the mounting base is set to be less than 14 times but at least 2 times the spring constant in the horizontal direction.

[0042] With this configuration as well, it is possible to obtain the same effect as that obtained when the spring constant in the vertical direction of the second plate-shaped elastic body is less than 14 times the spring constant in the horizontal direction, as described above.

[0043] In this vibration type linear conveying device, A stopper member for preventing plastic deformation of the second plate-shaped elastic body may be provided between the second vibrating body and the mounting base.

[0044] With this configuration, it is possible to prevent permanent deformation of the second plate-shaped elastic body due to an excessive load in the vertical direction. [Brief description of the drawings]

[0045] [Figure 1] FIG. 1 is a diagram showing a first example of a conventional general vibration-type linear conveying device. [Diagram 2] FIG. [Diagram 3] FIG. 13 shows a third example. [Figure 4] FIG. 1 is an explanatory diagram of problems with a conventional general vibration type linear conveying device. [Diagram 5]1 is a diagram illustrating the structure and operation of an embodiment of a vibration type linear transport device according to the present invention; [Figure 6] FIG. 13 is a diagram showing the structure of another embodiment. [Figure 7] FIG. 11 is an explanatory diagram of the main parts and operation of still another embodiment. [Figure 8] FIG. 13 is a diagram showing a structure of still another embodiment. [Figure 9] FIG. 2 is a diagram showing an embodiment of the vibration-type linear transport device LC used in the experiment. [Figure 10] FIG. 4 is a diagram showing an example of a second plate-shaped elastic body 20 used in an experiment. [Figure 11] FIG. [Figure 12] FIG. [Figure 13] FIG. [Figure 14] FIG. 1 is an explanatory diagram of a spring constant measuring device. [Figure 15] 6 is a graph showing the relationship between the thickness T of a rectangular member 23 in a second plate-shaped elastic body 20 and the vertical spring constant. [Figure 16] 4 is a graph showing the relationship between the thickness T of a rectangular member 23 and the spring constant ratio (vertical / horizontal). [Figure 17] 7 is a diagram showing a specific example of the second plate-shaped elastic body 20 shown in FIG. 6. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0046] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of a vibration type linear transport device according to the present invention will be described with reference to the drawings. In each drawing, the same or corresponding parts are denoted by the same reference numerals.

[0047] The vibration type linear conveying devices shown in Figs. 5, 6, 7, and 8 are all A vibratory linear transport device LC is provided with a first vibrating body 1 and a second vibrating body 2 as two mass bodies, the first vibrating body 1 having a transport path 3 for transporting a part W, and the second vibrating body 2 are connected to each other at at least two points (two points in the illustrated example are front and rear (left and right in the figure), but three or more points are also possible) by a first plate-like elastic body 10, and the second vibrating body 2 is connected to a mounting base 4 fixed to a stand 5 by a second plate-like elastic body 20 at at least two points (two points in the illustrated example are front and rear (left and right in the figure), but three or more points are also possible), The spring constant in the vertical direction of the second plate-shaped elastic body 20 is characterized in being less than 14 times but not less than twice the spring constant in the horizontal direction.

[0048] According to such a vibration type linear transport device LC, the spring constant in the vertical direction of the second plate-shaped elastic body 20 is less than 14 times the spring constant in the horizontal direction, so that the following operational effects are obtained.

[0049] The present inventors have conducted various experiments (experimental examples will be described later) using a vibratory linear conveying device comprising a first vibrating body 1 and a second vibrating body 2 as two mass bodies, the first vibrating body 1 having a conveying path 3 for conveying parts W, and the second vibrating body 2 being connected at least at two points by a first plate-shaped elastic body 10, and the second vibrating body 2 being connected at least at two points by a second plate-shaped elastic body 20, and the following has been discovered.

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

[0051] On the other hand, 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 likely to be absorbed by the second plate-shaped elastic body 20 and is less likely to be transmitted to the mounting base 4. Therefore, a reaction from the mounting base 4 is less likely to occur, and adverse effects from the mounting base 4 or the base are less likely to occur. As a result, pitching is less likely to occur.

[0052] In this way, according to the vibratory linear conveying device of the present invention, the vertical spring constant of the second plate-shaped elastic body 20 is less than 14 times its horizontal spring constant, so that 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 is less likely to be transmitted to the mounting base 4, thereby reducing the likelihood of adverse effects from the mounting base 4 or the stand and also reducing the likelihood of pitching.

[0053] Furthermore, if the vertical spring constant of the second plate-shaped elastic body 20 is less than twice its 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 will be small, making it difficult to establish a vibratory linear conveying device. However, according to the present invention, the vertical spring constant of the second plate-shaped elastic body 20 is more than twice its horizontal spring constant, so that the viability of the vibratory linear conveying device LC is not impaired.

[0054] The vibration type linear transport device LC according to each embodiment will be described below. Conventional anti-vibration springs have a large 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 spring constant ratio between the vertical and horizontal directions when the anti-vibration spring is mounted 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] In the vibration type linear conveying device LC shown in FIG. 5, the second plate-shaped elastic body 20 is, as shown in FIG. 5-1 and FIG. 5-5, Two plate-shaped elastic divided bodies 21 and 22 divided into upper and lower parts; a rectangular member 23 that is sandwiched between the plate-like elastic divisions 21, 22 and has two parallel surfaces 23a, 23b that face each other and are parallel to each other; One of the plate-like elastic divided bodies 21 and 22, the plate-like elastic divided body 21, has its lower portion 21a joined to one parallel surface 23a of the rectangular member 23 and its upper portion 21b fastened to the second vibrating body 2, The other of the plate-like elastic divided bodies 22 has its upper portion 22b joined to the other parallel surface 23b of the rectangular member 23 and its lower portion 22a fastened to the mounting base 4.

[0056] According to such a device LC, when a vertical force FV acts on the plate-like elastic divided bodies 21, 22 arranged on both sides of the rectangular member 23 while sandwiching the rectangular member 23, as shown in Fig. 5-2 and Fig. 5-3, the force acts to rotate the rectangular member 23 (counterclockwise in Fig. 5-2, clockwise in Fig. 5-3), and this rotational force FR acts to bend the plate-like elastic divided bodies 21, 22 arranged on both sides of the rectangular member 23 in the plate thickness direction (the bent parts are shown by symbols 21c, 22c). In other words, the vertical force FV acting on the plate-like elastic divided bodies 21, 22 is converted by the rectangular member 23 into a force (FR) that bends the plate-like elastic divided bodies 21, 22 in the plate thickness direction.

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

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

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

[0060] In Fig. 5-1 and Fig. 5-5, reference numeral 24b denotes a bolt, which fastens and fixes the plate-shaped elastic divided bodies 21 and 22 to the rectangular member 23 via a plate nut 24n and a presser plate 24c. Reference numeral 2b denotes a bolt which fastens the upper portion 21b of the plate-shaped elastic divided body 21 to the second vibrating body 2 via a pressure plate 2c, and reference numeral 4b denotes a bolt which fastens the lower portion 22a of the plate-shaped elastic divided body 22 to the mounting base 4 via a pressure plate 4c.

[0061] According to the structures shown in Figures 5-1 and 5-5, the following further effects can be obtained. The simple structure in which the rectangular member 23 and the plate-shaped elastic divisions 21, 22 are fastened together with the bolt 24b requires only minor machining of standard steel materials, and can be manufactured at low cost. The spring constant in the vertical direction can be easily adjusted by inserting a shim between the rectangular member 23 and the plate-like elastic divided body 21 and / or 22. (The inventors' experiments have revealed that the spring constant in the vertical direction and the thickness T of the rectangular member 23 are inversely proportional to each other.) The inventors' experiments have shown that inserting shims between the rectangular member 23 and the plate-shaped elastic divisions 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 vibratory linear conveying device LC shown in FIG. 6 is configured such that the second plate-like elastic body 20 has upper and lower mounting portions 25a (25b), 25b (25a) when viewed from the front as shown in FIG. 6-1, and is configured as an assembly 20A in which a pair of crank-like elastic bodies 25 having a crank-like bent portion 25c between the mounting portions 25a (25b), 25b (25a) are assembled in a point-symmetrical manner. An upper attachment portion 20A1 of this assembly 20A is fastened to the second vibrating body 2, and a lower attachment portion 20A2 is fastened to the mounting base 4.

[0063] According to such a configuration, when a force in the vertical direction acts on the crank-shaped elastic body 25, the crank-shaped bent portion 25c can be easily deformed, so that it becomes easy to reduce the spring constant in the vertical direction.

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

[0065] By appropriately designing the length [J] of the horizontal part shown in Figure 6-1 (the spring constant is inversely proportional to the cube of [J], assuming other conditions are the same), the required vertical spring constant can be obtained, and the vertical displacement of the second vibrating body 2 can be effectively dissipated. Since the structure is simple and fewer element parts are required, it can be manufactured at lower cost than Example 1. In Fig. 6, two sets of vibration-proof springs 20 of the present invention are provided at the front and rear, but it may be applied to only one side.

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

[0067] Even with this configuration, when a force in the vertical direction acts on the crank-shaped elastic body 25, the crank-shaped bent portion 25c is easily deformed, so that it becomes easy to reduce the spring constant in the vertical direction. In this case, the second plate-shaped elastic body 20 can be configured from one crank-shaped elastic body 25, which makes it possible to simplify the structure and reduce the number of parts.

[0068] In this embodiment, two pairs of vibration-proof springs 20 having the structure shown in Fig. 6-1 are provided, one at the front and one at the back, but the above structure may be applied to only one of them. The same applies when a single crank-shaped elastic body 25 is used, and the structure may be applied to only one of the front and rear.

[0069] In the vibratory linear transport device LC, only the essential parts of which are shown in FIG. 7, the second plate-like elastic body 20 is composed of an elastic body 26 that is L-shaped as a whole, in which the upper and lower mounting parts 26h, 26v, one of which extends in the horizontal direction and the other of which extends in the vertical direction, are bent into an L shape when viewed from the front. One of the mounting portions (26h in the figure) of this L-shaped elastic body 26 is fastened to the fastening portions (2c1, 2c2) of the second vibrating body 2, and the other mounting portion (26v in the figure) is fastened to the fastening portions (4b, 4c) of the mounting base 4. Among the above fastening portions, the fastening portion of the laterally extending mounting portion 26h is provided with a gap 27 that partially allows the laterally extending mounting portion 26h to bend in the vertical direction (an example is shown by h in Figures 7-1 and 7-2).

[0070] According to such a configuration, when a vertical force acts on the L-shaped elastic body 26, the horizontal portion 26h can be easily displaced in the up-down direction, so that it becomes easy to reduce the spring constant in the vertical direction.

[0071] Therefore, with this configuration, it becomes easy to make the spring constant in the vertical direction of the second plate-shaped elastic body 20 less than 14 times the spring constant in the horizontal direction. Furthermore, since the second plate-shaped elastic body 20 can be configured from one L-shaped elastic body 26, it is possible to simplify the structure and reduce the number of parts.

[0072] In the illustrated example, the horizontal portion 26h is fastened to the second vibrating body 2 and the vertical portion 26v is fastened to the mounting base 4, but it is also possible to fasten the horizontal portion 26h to the mounting base 4 and the vertical portion 26v to the second vibrating body 2.

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

[0074] In this embodiment, the horizontal portion 26h is fastened to the second vibrating body 2 by the first and second presser feet 2c1 and 2c2 and the bolt 2b. The gap 27 is defined by curved surfaces 2d1 and 2d2 that are formed on the ends of the first and second presser feet 2c1 and 2c2, respectively, and that are smoothly curved in an arc shape in a front view.

[0075] With this configuration, when the second vibrating body 2 descends, as shown in Figure 7-2, for example, the curved surface 2d1 of the first presser foot 2c1 gradually moves toward the bent portion of the vibration-proof spring 20 and comes into contact with it while changing the contact position, so that the span from the bent portion of the vibration-proof spring 20 becomes continuously shorter and the spring constant in the vertical direction becomes continuously larger. Conversely, the same thing happens when the second vibrating body 2 ascends due to the second presser foot 2c2.

[0076] The spring constant in the vertical direction is changed in this manner in order to increase the rigidity when a large displacement occurs in the vertical direction. The spring constant in the vertical direction should be as small as possible in order to obtain the vibration-isolating support structure that is the object of the present invention, and the influence of the base 5 can be reduced.

[0077] However, if the vertical spring constant is reduced and no measures are taken, there is a risk that the vibration-damping spring 20 will 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 above-mentioned configuration increases the rigidity of the vibration-proof spring 20, reducing the risk of the vibration-proof spring 20 becoming permanently deformed.

[0079] During normal operation of the vibrating linear transport device, the amount of vertical amplitude of the second vibrating body 2 is very small, so this type of structure is suitable for increasing rigidity only when a large deformation occurs due to an external force.

[0080] In the vibration type linear transport device LC shown in FIG. 8, the connecting portion (2b, 2c) between the mounting base 4 and the second plate-shaped elastic body 20 is separated from the base 5 to which the mounting base 4 is fixed, and a flexible portion 4f that allows the mounting base 4 itself to bend in the vertical direction is provided between the fixing portion 4d of the mounting base 4 to the fixing object 5 and the connecting portion (2b, 2c); The vertical spring constant of the second plate-shaped elastic body 20 and the flexible portion 4f of the mounting base 4 (an elastic body consisting of the second plate-shaped elastic body 20 and the flexible portion 4f of the mounting base 4) is set to less than 14 times but more than twice the horizontal spring constant.

[0081] With this configuration as well, it is possible to obtain the same effect as that obtained when the spring constant in the vertical direction of the second plate-shaped elastic body 20 is less than 14 times the spring constant in the horizontal direction, as described above.

[0082] As described above, with any of the vibration type linear transport devices LC shown in Figs. 5, 6, 7 and 8, the following further operational effects (a), (b), (c), (d) and (e) can be obtained.

[0083] (a) Similar to the case of the device that is vibration-isolated using the vibration-isolation rubber 20G shown in FIG. 3, it is possible to block the reflection and transmission of vibration. This makes it less susceptible to the effects of the stiffness and strength of the mounting base 5, allowing operation under a wide range of mounting conditions and eliminating the hassle of interactions that are difficult to understand.

[0084] (b) Since vibration is damped by a leaf spring, there is no lack of "positioning" (resistance to misalignment) of the transport path 3 due to the weakness of the vibration-proof rubber 20G, which is its softness in all directions. In addition, the meaning of "localization" in this application is as follows. The vibration-type linear transport device according to the present invention is constantly vibrating during operation, so that the connection parts cannot be connected to other devices, and it is essential that a certain gap be maintained. Under these conditions, the three-dimensional positional relationship at each connection part between the upstream side where parts W flow into the transport path 3 of this device and the downstream side where parts W flow out from the transport path 3 to other devices is called "positioning." A positional relationship with little displacement (deviation) throughout the entire operation period from installation (including the transportation stage from removal to installation) is said to be "good positioning."

[0085] (c) In the above embodiment, the mounting surfaces of the anti-vibration spring 20 are all perpendicular to the horizontal, making them easy to process and easy to maintain high precision, resulting in low processing costs. Also, in the embodiment shown in Figure 5, the rectangular member 23 sandwiched in between also has an orthogonal cross section (rectangular parallelepiped), so for the same reason, processing costs can be reduced.

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

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

[0088] In the vibratory linear conveying device LC as described above, for example, as shown by the phantom lines in FIG. 5, a stopper member 30 for preventing plastic deformation of the second plate-shaped elastic body 20 can be provided between the second vibrating body 2 and the mounting base 4.

[0089] With this configuration, it is possible to prevent permanent deformation of the second plate-shaped elastic body 20 due to an excessive load in the vertical direction.

[0090] The stopper member 30 is a bolt or the like that is fixed to the mounting base 4 and maintains a small gap between the bottom surface of the second vibrating body 2 and the stopper member 30, or a vibration isolating 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 and configured to keep a small gap between the upper surface of the mounting base 4 and the stopper member 30 .

[0091] Four embodiments have been described above, and they will be summarized below. There are three types of vibratory linear transport devices, depending on the vibration system configuration and vibration isolation support method. As shown in Figure 1, this is a so-called fixed type with no vibration isolation mechanism and only one mass vibrating. As shown in FIG. 2, the vibration-proof mechanism is a leaf spring 10. As shown in Figure 3, a vibration-proof mechanism using vibration-proof rubber 20G is used instead of leaf spring 10.

[0092] The leaf spring vibration isolation type in Figure 2, given as a conventional example, is a compromise between the pros and cons of the other two types, and although it leaks less vibration (transmission) to the mounting base 5 etc. than the fixed type, it is inferior to the vibration isolation rubber type. Its "positioning" is close to that of the fixed type and far better than the vibration isolation rubber type. The leaf spring vibration isolation type seems to be a good method that fills in the weaknesses of the other two methods, but in reality it only works under special conditions, i.e. when there is only a slight deviation in the center of gravity position, which is the root cause of the pitching motion, and there is little leakage of vibration to the mounting base 4 through the vibration isolation spring 20. This is one of the reasons why this method has not become widespread. Therefore, when conditions are poor, the conventional type in Figure 2 ends up being 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 countermeasure by lowering the spring constant of the vibration isolation spring 20 in the vertical direction. This ensures a wide range of design freedom (mass, length, center of gravity position, etc.) for the transport path 3, while also ensuring performance without compromising the above-mentioned "positioning," and makes it possible to use the transport path 3 with a reasonable structure without increasing the rigidity and mass of the mounting parts such as the stand 5. This makes it possible to apply the technology to larger models, whereas in the past it was only applicable to small and medium-sized models.

[0094] In addition, when viewed from the stand 5 side, the transmission of vibrations (especially harmful vibrations in the vertical direction) is reduced, thereby suppressing noise generation. If a similar type of vibration device is installed, it is possible to reduce the phenomenon of vibration even when the power is turned off and to suppress unintended work transport.

[0095] Examples and experimental examples will be described below.

[0096] FIG. 9 is a diagram showing an embodiment of the vibration type linear transport device LC used in the experiment. The main specifications of this vibration-type linear transport device LC are as follows: Mass of the first vibrating body 1 including the conveying path 3=3720 g Mass of the second vibrating body 2 including the vibration imparting mechanism 6=3190 g Mass of the first plate-shaped elastic body 10 = 215g (total of front and rear) Spring constant of the first plate-shaped elastic body 10 = 614N (total of front and rear) Mounting angle of the first plate-shaped elastic body 10=72° Mass of mounting base 4 fixed to mounting base 5 = 1497 g (Note that since mounting base 4 is fixed to mounting base 5, the mass of mounting base 4 does not affect the experimental results) Structure of the second plate-shaped elastic body 20=structure explained in FIG. 5 Structure of vibration imparting mechanism 6 = "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, and 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 above-described vibration type linear conveying device LC, the second plate-shaped elastic body 20 as shown in Fig. 10 to Fig. 13 was attached as the second plate-shaped elastic body 20, and the vibration type linear conveying device LC was operated to convey the part W. In Fig. 10 and Fig. 11, h is an opening for reducing rigidity. As a result, when the second plate-shaped elastic body 20 shown in Figures 10, 11 and 12 (spring constant ratio = vertical / horizontal = 3.21, 7.49, 8.95) was used, pitching did not occur and the part W could be transported, but when the second plate-shaped elastic body 20 shown in Figure 13 (same as 14.0) was used, pitching 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 1,175 g) on ​​a spring constant measuring device 50 shown in Figure 14 and measuring the displacement of both ends of the second vibrating body 2 with displacement sensors 51, 51, and the horizontal spring constant was measured by rotating the same device 90 degrees and measuring the displacement.

[0099] FIG. 15 is a graph showing the relationship between the thickness T of the rectangular member 23 (spacer) in the second plate-shaped elastic body 20 and the vertical spring constant, measured using the above-mentioned device, and FIG. 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] "y" in FIG. 15 is the spring constant in the vertical direction, and "y" in FIG. 16 is the spring constant ratio. In Figures 15 and 16, "R2" is the coefficient of determination. Although there is no numerical standard, the coefficient of determination "R2" is 0.95 or more, which means that there is a sufficiently strong correlation.

[0101] The numerical values ​​here are inversely proportional. The numerical values ​​themselves are limited to the dimensions of this device, but the inversely proportional relationship itself can be said to be universal for the structure of the above embodiment. Based on this relationship, by inserting shims as explained with reference to Figures 5-1 and 5-5, it is possible to predict and adjust the spring constant in the vertical direction.

[0102] FIG. 17 is a diagram showing a specific example of the second plate-shaped elastic body 20 shown in FIG.

[0103] Although the embodiment of the present invention has been described above, the present invention is not limited to the above embodiment, and various modifications can be made within the scope of the gist of the present invention. For example, the gap in FIG. 7 may be filled with an elastic material (eg, rubber). [Explanation of symbols]

[0104] 1: First vibrator 2: Second vibrator 3: Transport path 10: First plate-shaped elastic body 20: Second plate-like elastic body

Claims

1. A vibratory linear conveying device is provided with a first vibrating body (1) and a second vibrating body (2) as two mass bodies, the first vibrating body (1) having a conveying path (3) for conveying a part (W) and the second vibrating body (2) being connected at least at two points by a first plate-like elastic body (10), and the second vibrating body (2) being connected at least at two points by a second plate-like elastic body (20), The spring constant in the vertical direction of the second plate-shaped elastic body (20) is set to be less than 14 times and at least 2 times the spring constant in the horizontal direction; The second plate-shaped elastic body (20) is Two plate-shaped elastic divided bodies (21, 22) divided into upper and lower parts; a rectangular member (23) sandwiched between the plate-like elastic divided bodies (21, 22) and made of a rectangular parallelepiped having two parallel surfaces facing each other, One of the plate-shaped elastic divided bodies (21, 22) has a lower portion joined to one parallel surface of the rectangular member (23) and an upper portion fastened to the second vibrating body (2); The other of the plate-shaped elastic divided bodies (21, 22) has an upper portion joined to the other parallel surface of the rectangular member (23) and a lower portion fastened to the mounting base (4); Each of these plate-shaped elastic divided bodies (21, 22) is flat and does not have a bent portion in the article conveying direction, the overall shape of the rectangular member (23) and the two plate-like elastic division bodies (21, 22) of the second plate-like elastic body (20) is point-symmetrical with respect to the center of the rectangular member (23) in the up-down direction when viewed from the front, The vibratory linear conveying device is characterized in that the rectangular member (23) and the two plate-like elastic divided bodies (21, 22) are fastened together with a bolt (24b).

2. A vibration device comprising a first vibrating body (1) and a second vibrating body (2) as two mass bodies, the first vibrating body (1) having a transport path (3) for transporting a part (W) and the second vibrating body (2) being connected at least at two points by a first plate-like elastic body (10), and the second vibrating body (2) being connected at least at two points by a second plate-like elastic body (20) to a fixed mounting base (4), In the vibration type linear conveying device, the spring constant in the vertical direction of the second plate-shaped elastic body (20) is set to be less than 14 times and at least 2 times the spring constant in the horizontal direction, The second plate-like elastic body (20) is constituted by an assembly (20A) in which a pair of crank-like elastic bodies (25) having upper and lower mounting portions (25a, 25b) and a crank-like bent portion (25c) between the mounting portions (25a, 25b) are assembled in a point-symmetrical manner when viewed from the front, A vibratory linear conveying device characterized in that an upper mounting portion (20A1) of this assembly (20A) is fastened to the second vibrating body (2) and a lower mounting portion (20A2) is fastened to the mounting base (4).

3. A vibration device comprising a first vibrating body (1) and a second vibrating body (2) as two mass bodies, the first vibrating body (1) having a transport path (3) for transporting a part (W) and the second vibrating body (2) being connected at least at two points by a first plate-like elastic body (10), and the second vibrating body (2) being connected at least at two points by a second plate-like elastic body (20) to a fixed mounting base (4), In the vibration type linear conveying device, the spring constant in the vertical direction of the second plate-shaped elastic body (20) is set to be less than 14 times and at least 2 times the spring constant in the horizontal direction, The second plate-like elastic body (20) is composed of an elastic body (26) having an overall L-shape, one side of which extends in the horizontal direction and the other side of which extends in the vertical direction when viewed from the front, and which is bent into an L-shape between the upper and lower mounting parts, One mounting portion of the L-shaped elastic body (26) is fastened to a fastening portion of the second vibrating body (2), and the other mounting portion is fastened to a fastening portion of the mounting base (4), A gap (27) is provided in the fastening portion of the horizontally extending mounting portion (26h) among the fastening portions, which allows partial deflection of the horizontally extending mounting portion (26h) in the up-down direction, the mounting portion (26h) extending in the horizontal direction is fastened to the second vibrating body 2 by first and second presser plates (2c1, 2c2) which sandwich the mounting portion (26h) from above and below, and the gap (27) is formed by curved surfaces (2d1, 2d2) which are formed at the ends of the first and second presser plates (2c1, 2c2), respectively, and which are smoothly curved in an arc shape when viewed from the front.

4. A vibratory linear conveying device is provided with a first vibrating body (1) and a second vibrating body (2) as two mass bodies, the first vibrating body (1) having a conveying path (3) for conveying a part (W) and the second vibrating body (2) being connected at least at two points by a first plate-like elastic body (10), and the second vibrating body (2) being connected at least at two points by a second plate-like elastic body (20), a connecting portion of the mounting base (4) with the second plate-like elastic body (20) is separated from the object to which the mounting base (4) is fixed, and a flexible portion (4f) is provided between the fixing portion of the mounting base (4) to the object to which the mounting base (4) is fixed and the connecting portion, the flexible portion allowing the mounting base (4) itself to bend in the vertical direction; A vibratory 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 more than twice the horizontal spring constant.

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

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