JP2007136528A - Stroke variable device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a stroke variable device where a stroke can be easily made variable even under driving, and further, miniaturization and the reduction of cost are made possible even with a relatively simple constitution. <P>SOLUTION: The stroke variable device is equipped with: a first eccentric shaft 32 provided at a first main rotary body 20; a second eccentric shaft 33 provided at a second main rotary body 21; a ram 19 supported in a state of being linearly movable back and forth; a transfer mechanism 35 of transferring the displacement of the first eccentric shaft 32 and the second eccentric shaft 33 in the upper and lower directions to one end side of the ram 19; a stroke setting means of setting the stroke of the ram 19; a phase difference deciding means of deciding the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33; a phase difference adjustment controlling means of making the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33 coincident to the decided phase difference; and a reciprocation controlling means of rotating the first main rotary body 20 and the second main rotary body 21 at the same speed and reciprocating the ram 19. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a stroke variable device, and more particularly to a stroke variable device that can vary a linear movement distance in a reciprocating linear motion of a rod member.

  As a press machine, one having a crank mechanism is known. This transmits the rotational motion of a rotating body rotated by an electric motor to a rod member such as a ram, and causes the rod member to reciprocate linearly (for example, up and down motion). By the way, a conventional press machine has a configuration in which the position of the crankpin is changed, and the stroke (linear movement distance) of the rod member can be switched by changing the position. However, in any of the apparatuses, the stroke can be switched only while the press machine is stopped, and the range of use is limited. Further, an operation such as changing the position of the crank pin is necessary. For example, when the stroke is frequently switched, a lot of inspection man-hours are required, and the burden on the operator is increased.

Therefore, the applicant of the present application has previously proposed a stroke variable device that can easily change the stroke and that can accurately set the stroke (Patent Document 1). This will be specifically described with reference to FIG. The stroke variable device A includes a lever D supported so as to be swingable about a fulcrum shaft C, a driving means E connected to one end of the lever D for reciprocating the lever D within a predetermined range, A follower G connected to the other end of the lever D for transmitting the reciprocating angular motion of the lever D to the movable object F, and provided between the lever D and the fulcrum shaft C, slides the fulcrum shaft C relative to the lever D. A first slide means H that is supported in a movable state; a second slide means I that is provided between the fulcrum shaft C and the gantry B and supports the fulcrum shaft C in a slidable state with respect to the gantry B; A fulcrum shaft moving means J for moving the shaft C in the longitudinal direction of the lever D and a restricting means K for restricting the movement of the lever D in the moving direction of the fulcrum shaft C are provided. According to this, by moving the fulcrum shaft C by the fulcrum shaft movable means J, the relative position of the fulcrum shaft C with respect to the lever D changes, and one end side of the lever D (the drive means E is connected from the fulcrum axis C). The ratio of the length X to the portion) and the length Y from the fulcrum shaft C to the other end side of the lever D (the portion to which the driven means G is connected) changes. By changing the ratio in this way, the amplitude (that is, the amplification factor) on the other end side of the lever D with respect to the amplitude on one end side of the lever D changes. That is, the stroke of the driven means G is changed by changing the relative position of the fulcrum shaft C.
JP 2001-305010 A

  However, in the above stroke variable device A, the ratio of the length X from the fulcrum shaft C to one end of the lever D and the length Y from the fulcrum shaft C to the other end of the lever D is changed. A plurality of mechanisms for changing the relative position of the fulcrum shaft C, that is, two sets of slide means H and I, a fulcrum shaft movable means J, and the like must be provided. As a result, the overall configuration becomes complicated and the manufacturing cost increases. It was bulky.

  Further, in the above stroke variable device A, the reciprocating angular motion of the lever D around the fulcrum shaft C is converted into the reciprocating linear motion of the driven device G, so that even if the position of the fulcrum shaft C moves, the driven device. In order to secure a certain G stroke, the lever D extending in the horizontal direction must be formed relatively long, and as a result, a relatively wide space must be ensured between the driven means G and the driving means E. It was. Further, in order to move the fulcrum shaft C over the entire range of the lever D, a large fulcrum shaft moving means J has to be employed. For this reason, it has been difficult to apply the variable stroke device A to a comparatively small inspection device and a press machine provided with many other mechanisms.

  SUMMARY OF THE INVENTION In view of the above situation, the present invention has an object to provide a stroke variable device that can easily change the stroke even during driving, and that can be reduced in size and cost with a relatively simple configuration. It is.

  The stroke variable device according to the present invention is “a first main rotating body and a second main rotating body that are arranged in parallel in a housing and can be separately rotated, and the first main rotating body is rotated about a first axis. A first drive source, a second drive source for rotating the second main rotor around the second axis, and a first projecting from the first main rotor and eccentric with respect to the first axis An eccentric shaft, a second eccentric shaft that is formed to protrude from the second main rotating body and is eccentric with respect to the second axis, a rod member that is supported so as to be capable of reciprocating linear movement, and the rod A transmission mechanism for transmitting the displacement of the first eccentric shaft and the second eccentric shaft to the one end side of the rod member in the movable direction of the member, a stroke setting means for setting a stroke of the rod member, and the stroke Based on the stroke set by the setting means, A phase difference determining means for determining a phase difference between the first eccentric shaft and the second eccentric shaft; and operating at least one of the first drive source or the second drive source; and the first eccentric shaft; The phase difference adjustment control means for matching the phase difference with the second eccentric shaft to the phase difference determined by the phase difference determination means, while maintaining the phase difference adjusted by the phase difference adjustment control means The reciprocating motion in which the first main rotating body and the second main rotating body are rotated at the same speed by the first driving source and the second driving source, and the rod member is reciprocated through the transmission mechanism. Control means ”.

  Here, as the “first driving source” and the “second driving source”, the first main rotating body and the second main rotating body are separately rotated, and predetermined power is applied to the rod member via the transmission mechanism. If it is a thing, it will not specifically limit. Specific examples include an electric motor using electric power and a motor using fluid pressure such as air pressure, hydraulic pressure, and water pressure. The “rod member” is a rod-like or column-like member, and examples thereof include a ram used in a press machine and an excitation shaft used in a vibration test apparatus. Further, the “movable direction of the rod member” is a direction in which the rod member reciprocates linearly. For example, when the axial direction of the rod member is a vertical direction, the vertical direction is the movable direction.

  The “stroke setting means” is a means for setting the linear movement distance of the rod member, and may be input by an operator, and is calculated based on a prestored calculation. There may be. In other words, the stroke length may be directly input or selected, but the motion conditions related to the stroke length (for example, the moving speed of the rod member and the bottom dead center position) are input or selected. The necessary stroke may be obtained based on these motion conditions.

  According to the present invention, when the stroke of the rod member is set, the phase difference determining means determines the phase difference between the first eccentric shaft and the second eccentric shaft based on the stroke. Here, the first eccentric shaft is formed so as to protrude from the first main rotating body and is eccentric with respect to the first axis. Further, the second eccentric shaft is formed so as to protrude from the second main rotating body and is eccentric with respect to the second axis. Therefore, in the present invention, when the phase difference is determined, at least one of the first driving source and the second driving source is operated (that is, at least one of the first main rotating body and the second main rotating body is relatively rotated). And the phase difference between the first eccentric shaft and the second eccentric shaft is matched with the phase difference determined by the phase difference determining means. When it is instructed to reciprocate the rod member, or when it has already been instructed, the first main rotation is performed by the first drive source and the second drive source while maintaining the adjusted phase difference. The body and the second main rotating body are rotated at the same speed.

  When the first main rotating body and the second main rotating body rotate, the first eccentric shaft and the second eccentric shaft rotate and displace around the first axis and the second axis, respectively, while maintaining the phase difference. It becomes. A transmission mechanism is interposed between the first eccentric shaft and the second eccentric shaft and the rod member, whereby the first eccentric shaft and the second eccentric shaft in the movable direction of the rod member. The displacement is transmitted to one end side of the rod member. That is, the component in the movable direction (for example, the vertical direction) of the rod member is transmitted to the rod member out of the displacement of the portion (hereinafter referred to as the intermediate portion) at a substantially intermediate position between the first eccentric shaft and the second eccentric shaft. The rod member is reciprocated. Here, the displacement of the intermediate portion differs depending on the phase difference between the first eccentric shaft and the second eccentric shaft. For example, when the phase difference between the first eccentric shaft and the second eccentric shaft is 0 °, the line segment connecting the first eccentric shaft and the second eccentric shaft is always perpendicular to the movable direction and in a parallel state. It will be displaced in the direction of motion while maintaining That is, the amount of displacement at the intermediate portion is about twice the amount of eccentricity. On the other hand, when the phase difference between the first eccentric shaft and the second eccentric shaft is 180 °, the line segment connecting the first eccentric shaft and the second eccentric shaft moves reciprocally around the intermediate portion. Will be. That is, even if the first main rotator and the second main rotator are rotated, the intermediate portion is not displaced in the movable direction, and the displacement amount is substantially zero. Thus, the displacement is maximum when the phase difference between the first eccentric shaft and the second eccentric shaft is 0 °, and the displacement is minimum when the phase difference is 180 °. Along with this, the amount of displacement changes. And the amplitude added to a rod member changes by changing the amount of displacement in an intermediate part, and the stroke of a rod member changes by extension. In other words, the stroke of the rod member can be changed only by changing the phase difference between the first eccentric shaft and the second eccentric shaft. Note that the phase difference can be easily changed not only when the machine is stopped but also during driving. Furthermore, in the present invention, it is possible to continuously change the phase difference between the first eccentric shaft and the second eccentric shaft, and thus it is possible to change the stroke of the rod member proportionally.

  In the stroke variable device according to the present invention, “the transmission mechanism is supported to be swingable with respect to one end side of the rod member, and is extended in a direction substantially perpendicular to the movable direction of the rod member. A swing member, a guide rail formed on the first eccentric shaft side and the second eccentric shaft side of the swing member and extending along an extending direction of the swing member, and the first eccentric member. A first sub-rotary body supported rotatably about an axis, a second sub-rotary body supported rotatably about the second eccentric shaft, and connected to the first sub-rotary body A first slide member slidably fitted to the guide rail located on one side of the swing shaft of the swing member, and the second sub-rotator, and the swing member Slidable with respect to the guide rail located on the other side of the swing shaft of the moving member It can be mated with and a second slide member "configuration.

  According to this, the 1st subrotation body is supported so that rotation is possible around the 1st eccentric shaft, and the 1st slide member is connected with the 1st subrotation body. Similarly, a second sub rotator is rotatably supported around the second eccentric shaft, and a second slide member is connected to the second sub rotator. On the other hand, on one end side of the rod member, there is provided a swinging member supported so as to be swingable about the swinging shaft on the one end side, and further, a first slide member and a second slide in the swinging member are provided. A guide member extending along the extending direction of the swing member is formed on the surface facing the member. The first slide member and the second slide member are slidably fitted to the guide rail, and are guided in a certain direction along the guide rail (a direction substantially perpendicular to the movable direction of the rod member). It has come to be. Therefore, when the first eccentric shaft and the second eccentric shaft rotate around the first axis and the second axis, the first eccentric shaft and the second eccentric shaft are substantially perpendicular to the movable direction as well as the movable direction of the rod member. Although it will also be displaced in the direction, by sliding the first slide member and the second slide member with respect to the guide rail, the movement in the substantially vertical direction is absorbed, and only the displacement in the movable direction is the rod member. Can be communicated to.

  In the stroke variable device according to the present invention, the phase difference adjusted by the phase difference adjustment control unit and the first main rotating body and the second main rotating body at a constant speed while maintaining the phase difference. The phase difference is determined by the waveform information storage means that stores the relationship between the motion waveform of the rod member obtained when the rod member is rotated and the linear waveform previously associated with the motion waveform, and the phase difference determination means. Then, every unit time at the rotational speeds of the first main rotor and the second main rotor so that the motion waveform corresponding to the phase difference becomes the linear waveform associated with the motion waveform. Correction amount determination means for determining the correction amount of the first reciprocating motion control means, wherein the reciprocating motion control means is the first main speed at a fluctuation rate that takes into account the correction amount per unit time determined by the correction amount determination means. Rolling body and rotating the second main rotating member "can also be configured.

  According to this, the rod member can be moved at a constant speed. Specifically, when the phase difference is determined, the motion waveform corresponding to the phase difference (that is, the motion waveform of the rod member obtained when the first main rotor and the second main rotor are rotated at a constant speed (sine wave)). ) Is determined to be a linear waveform previously associated with the motion waveform, and the correction amount per unit time in the rotational speeds of the first main rotating body and the second main rotating body is determined. When the second main rotor is rotated, the rotation is controlled at a variable speed determined based on a predetermined constant speed and a correction amount per unit time. The displacement at the intermediate portion between the two eccentric shafts changes at a constant speed, and the rod member can be reciprocated at a constant speed.

  As described above, in the stroke variable device of the present invention, the stroke of the rod member can be easily and accurately adjusted even during driving. For example, the machining according to the optimum machining conditions can be efficiently performed. Can do. In addition, since it can be realized with a simple configuration, the apparatus can be reduced in price and can be suitably applied to a machine that is required to be downsized or a machine that has a complicated mechanism. Furthermore, since the stroke can be continuously changed, the range of use can be expanded.

  Hereinafter, a press machine provided with a stroke variable device according to an embodiment of the present invention will be described with reference to FIGS. 1 to 6. FIG. 1 is a front view showing the overall configuration of the press 1, FIG. 2 is a cross-sectional view showing the configuration of the stroke variable device 2, and FIG. 3 is a right side view showing the configuration of the stroke variable device 2. 4 is an explanatory diagram showing the operation of the stroke variable device 2, FIG. 5 is a block diagram showing the functional configuration of the stroke variable device 2, and FIG. 6 is a waveform diagram showing the displacement state of each part. 2 represents the XX cross section in the right side view of FIG.

(Overall configuration of press machine)
As shown in FIG. 1, a press machine 1 according to the present embodiment is a press machine that continuously punches a product from a fed material, and includes a vertically long casing 3 that accommodates a variable stroke device 2 and the like, and a material And a horizontally long frame 4 functioning as a gantry for supplying and discharging. Further, on the upper surface of the frame 4, an input material reel 5 on which the material is wound, a material feed mechanism 6 for conveying the material fed from the input material reel 5, and a punching die 7 for punching the supplied material. And are provided. Further, a product receiving box 8 for receiving the punched product is provided below the punching die 7 in the housing 3, and an end material is stored on the side of the frame 4 (right side of the paper). An end material receiving box 9 is provided.

  The material feed mechanism 6 includes a pair of feed rollers 11 that sandwich the material from above and below and convey the material in a certain direction by rotation, and a pressure cylinder 12 for feeding that biases the upper feed roller 11 toward the material, An upper and lower guide roller 13 and a side guide roller 14 are provided that restrict the movement of the material in the vertical direction and the front-rear direction and guide it in a certain direction. The punching die 7 is composed of a die die 17 fixed to the frame 4 and a punch die 16 that moves in the vertical direction and punches a product of a predetermined shape in cooperation with the die die 17. ing. A columnar ram 19 is connected to the punch die 16 so that the punch die 16 can be reciprocated linearly up and down by the stroke variable device 2 and the stroke can be arbitrarily changed. . The ram 19 is supported by the guide member 18 so as to be slidable in the vertical direction. Here, the ram 19 corresponds to the rod member of the present invention.

(Configuration of stroke variable device)
Next, the configuration of the variable stroke device 2 will be described. As shown in FIGS. 2 and 3, the stroke variable device 2 includes a first main rotating body 20 and a second main rotating body 21 that are arranged in parallel within the housing 3 and are separately rotatably supported. A first electric motor 22 and a second electric motor 23 (see FIG. 5) that rotate the main rotors 20 and 21 around the axis are provided. The first electric motor 22 and the second electric motor 23 of this example are connected to the main rotors 20 and 21 via couplings 25, respectively. Here, the first electric motor 22 corresponds to the first drive source of the present invention, and the second electric motor 23 corresponds to the second drive source of the present invention.

  The first main rotator 20 is divided into a front main rotator 26 and a rear main rotator 27 that have the same axis and are arranged in parallel in the front-rear direction. The front main rotor 26 is rotatably supported inside the support frame member 31 via a bearing 29, and the rear main rotor 27 is rotatably supported inside the support frame member 30 via a bearing 28. . The support frame members 30 and 31 are attached in a state of hanging from the upper surface of the housing 3. The front main rotor 26 and the rear main rotor 27 are connected by a first eccentric shaft 32 that protrudes from the front surface of the rear main rotor 27 and penetrates the front main rotor 26. It rotates integrally through the shaft 32. That is, the first eccentric shaft 32 is formed at a position eccentric from the axis of the first main rotating body 20, and around the axis of the first main rotating body 20 as the rear main rotating body 27 rotates. , Turning force is applied to the front main rotor 26. In FIG. 3, the configuration of the second main rotor 21 is not shown, but the second main rotor 21 is the same as the configuration of the first main rotor 20, and the front main rotor 26 and the rear side The main rotor 27 is divided and connected by a second eccentric shaft 33.

  On the other hand, between the first eccentric shaft 32 and the second eccentric shaft 33 and the ram 19, a transmission mechanism that transmits the displacement of the first eccentric shaft 32 and the second eccentric shaft 33 in the vertical direction to the ram 19. 35 and a connecting member 36 are provided. The connecting member 36 is a member having an approximately U-shaped cross-section with an open upper surface, and is fastened to the upper end of the ram 19. A through hole (not shown) is formed in both wall portions of the coupling member 36 facing each other, and a swing shaft 37 is fitted into the through hole. Further, a swing member 38 is fitted on the outer peripheral surface of the swing shaft 37 via a bearing 39. The swing member 38 extends in the left-right direction about the swing shaft 37, and can swing like a seesaw with reference to a direction (horizontal direction) perpendicular to the movement direction of the ram 19. It has become. Further, a linear guide rail 40 extending along the longitudinal direction of the swing member 38 is provided on the upper surface of the swing member 38.

  On the other hand, at the root portion of the first eccentric shaft 32 located between the front main rotating body 26 and the rear main rotating body 27, the first sub rotating body 43 is rotatable through a bearing 42. A first slide member 46 that is externally fitted and is slidably fitted to the right side portion of the guide rail 40 is provided below the first auxiliary rotating body 43. The second sub-rotating body 45 is also fitted on the second eccentric shaft 33 via a bearing 44, and slides with respect to the left portion of the guide rail 40 at the lower portion of the second sub-rotating body 45. A second slide member 47 which is fitted together is provided.

(Control means for variable stroke device and operation in variable stroke device)
By the way, the press machine 1 is provided with a control device for performing press working, and material feeding processing and product punching processing are executed based on conditions detected by sensors and switches. ing. In particular, as a control means for the stroke variable device 2, as shown in FIG. 5, a controller 51 is provided, and its input terminal includes a stroke setting means 52, a first encoder 53, a second encoder 54, A start switch 55 and a stop switch 56 are connected, while the first motor 22 and the second motor 23 are connected to the output terminal of the controller 51.

  Here, the stroke setting means 52 is for causing the operator to set the stroke (linear movement distance) of the ram 19 and can be composed of, for example, operation keys. The first encoder 53 detects the rotation angle of the first main rotor 20, particularly the position of the first eccentric shaft 32 (relative angle with respect to the origin). The second encoder 54 detects the rotation angle of the second main rotor 21, particularly the position of the second eccentric shaft 33 (relative angle with respect to the origin). That is, it is possible to recognize the phase difference (angle difference) between the first eccentric shaft 32 and the second eccentric shaft 33 based on the first encoder 53 and the second encoder 54. The start switch 55 is an operation switch for starting the vertical movement of the ram 19, that is, the continuous punching process by the punching die 7, and the stop switch 56 is an operation switch for stopping the continuous punching process. .

  The controller 51 includes a phase difference determination unit 58, a phase difference adjustment control unit 59, a reciprocating motion control unit 60, a waveform information storage unit 61, and a correction amount determination unit 62 as functional configurations. The phase difference determining unit 58 determines the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33 based on the stroke set by the stroke setting unit 52. Specifically, the relationship between the necessary stroke and the corresponding phase difference is stored in advance, and when the stroke is set, the phase difference determining means 58 extracts the corresponding phase difference. .

  The phase difference adjustment control means 59 operates at least one of the first electric motor 22 and the second electric motor 23, and determines the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33 as the phase difference determination means 58. To match the phase difference determined by. That is, one of the first electric motor 22 or the second electric motor 23 is rotated relative to the other until the output difference between the first encoder 53 and the second encoder 54 becomes the determined phase difference. . This process can be executed not only when the press machine 1 is stopped but also during the continuous punching process (during driving). Specifically, if one of the first electric motor 22 and the second electric motor 23 rotating at the same speed is decelerated for a predetermined time, or conversely, the rotational speed is increased, the first eccentricity is achieved. A predetermined phase difference can be created between the shaft 32 and the second eccentric shaft 33.

  The reciprocating motion control means 60 performs a continuous punching process by moving the ram 19 and the punch die 16 up and down. The reciprocating motion control means 60 starts the operation based on the operation of the start switch 55 and operates based on the operation of the stop switch 56. Operation is stopped. When the operation is started, the first main rotating body 20 and the second main rotating body 21 are moved by the first electric motor 22 and the second electric motor 23 while maintaining the phase difference adjusted by the phase difference adjusting control means 59. Rotate at the same speed.

  Then, the first eccentric shaft 32 and the second eccentric shaft 33 are turned and displaced around the axes of the first main rotating body 20 and the second main rotating body 21 while maintaining the phase difference. A transmission mechanism 35 is interposed between the first eccentric shaft 32 and the second eccentric shaft 33 and the ram 19, whereby the first eccentric shaft in the movable direction (vertical direction) of the ram 19. The displacement of the 32 and the second eccentric shaft 33 is transmitted to one end side of the ram 19. That is, as shown in FIG. 4B, the first eccentric shaft 32 and the second eccentric shaft 33 are moved from (1) to (4) by the rotation of the first main rotating body 20 and the second main rotating body 21. When displaced in order, the component in the vertical direction is transmitted to the ram 19 out of the displacement at a portion (referred to as an intermediate portion) at a substantially intermediate position between the first eccentric shaft 32 and the second eccentric shaft 33, and the ram 19 is reciprocated. Exercise. Here, the displacement amount of the intermediate portion (that is, the stroke of the ram 19) varies depending on the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33. For example, as shown in FIG. 4A, when the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33 is 0 °, the first eccentric shaft 32 and the second eccentric shaft 33 are connected. The line segment 50 is always perpendicular to the movable direction (that is, in a horizontal state), and is displaced in the vertical direction without swinging. At this time, the state (1) is the top dead center, the state (3) is the bottom dead center, and the states (2) and (4) are the positions of the displacement “0”. That is, the displacement amount L1 at the intermediate portion is about twice the eccentric amount.

  On the other hand, as shown in FIG. 4B, when the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33 is 90 °, the first eccentric shaft 32 and the second eccentric shaft 33 are connected. The line segment 50 is displaced while swinging, and the displacement at the intermediate portion is such that the state (1) and the state (4) coincide with each other, and the state (2) and the state (3) are mutually different. Will match. The displacement amount L2 at the intermediate portion is shorter than the displacement amount L1 when the phase difference is 0 °. FIG. 6A shows a temporal change (namely, motion waveform) of the displacement of each part when the phase difference is 90 °, and “first” is the displacement of the first eccentric shaft 32, “Second” represents the displacement of the second eccentric shaft 33, and “intermediate part” represents the displacement at the intermediate part of the line segment 50. As can be seen from this waveform, the amount of displacement at the intermediate portion is substantially equal to the average value of the amount of displacement of the first eccentric shaft 32 and the amount of displacement of the second eccentric shaft 33. In this example, The displacement amount L2 is set to 42.42 mm. When the phase difference is 60 °, the displacement amount is 51.96 mm in the waveform shown in FIG. 6B, and when the phase difference is 30 °, the displacement amount is as shown in FIG. 6C. Is 57.98 mm.

  Although not shown in FIG. 4, when the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33 is 180 °, the first eccentric shaft 32 and the second eccentric shaft 33 are connected. The line segment 50 reciprocally swings around the intermediate portion. That is, even if the first main rotating body 20 and the second main rotating body 21 are rotated, the intermediate portion is not displaced in the vertical direction, and the displacement amount is always substantially zero. Thus, the amount of displacement at the intermediate portion is maximum when the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33 is 0 °, and is minimum when the phase difference is 180 °. It decreases as the phase difference increases. Then, by changing the amount of displacement at the intermediate portion, the amplitude applied to the ram 19 changes, and as a result, the stroke of the ram 19 can be changed. Further, since the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33 can be continuously changed, the stroke of the ram 19 can be changed proportionally.

  By the way, when the first eccentric shaft 32 and the second eccentric shaft 33 turn around the axes of the first main rotating body 20 and the second main rotating body 21, the ram 19 can move in the up and down direction. In addition to the displacement, the displacement also occurs in a direction (horizontal direction) that is substantially perpendicular to the movable direction. However, in the present embodiment, as shown in FIG. 2, the first sub-rotary body 43 including the first slide member 46 is rotatably supported around the first eccentric shaft 32, and the second eccentric shaft is provided. A second sub-rotary body 45 having a second slide member 47 is rotatably supported around 33. For this reason, the first slide member 46 and the second slide member 47 can be slid along the guide rail 40. As a result, the movement in the horizontal direction is absorbed, and only the displacement in the vertical direction is applied to the ram 19. Communicated.

  Incidentally, in the waveform information storage means 61 shown in FIG. 5, the phase difference adjusted by the phase difference adjustment control means 59 and the first main rotating body 20 and the second main rotating body 21 are kept constant while maintaining the phase difference. The relationship between the motion waveform of the intermediate portion (that is, the motion waveform applied to the ram 19) obtained when rotating at a speed and the linear waveform related to the motion waveform is stored. Specifically, as shown in FIG. 6 (c), a straight line connecting the motion waveform (SIN wave) of the intermediate portion and the top dead center and the bottom dead center in this motion waveform with respect to each phase difference (30 ° in this case). Waveforms (RAMP waves) are stored in association with each other. Then, when the phase difference is determined by the phase difference determining unit 58, the correction amount determining unit 62 generates a motion waveform (SIN wave) and a linear waveform (RAMP wave) corresponding to the phase difference from the waveform information storage unit 61. The correction amount per unit time in the rotational speeds of the first main rotating body 20 and the second main rotating body 21 is determined so that the read and motion waveform (SIN wave) becomes a linear waveform (RAMP wave). Instead of storing the waveform in the waveform information storage unit 61, the phase difference and the correction amount are stored in association with each other, and when the phase difference is determined, the correction amount corresponding to the phase difference is stored in the waveform information storage unit. You may make it extract from 61. FIG. The correction amount determined in this way is output to the reciprocating motion control means 60, and the reciprocating motion control means 60 is based on the predetermined constant speed and the determined correction amount per unit time. The fluctuation speeds of the one main rotor 20 and the second main rotor 21 (speeds that change every unit time) are determined. Thereby, the displacement in the intermediate part of the 1st eccentric shaft 32 and the 2nd eccentric shaft 33 will change at constant velocity, and it becomes possible to make the reciprocating motion of the ram 19 into constant velocity linear motion.

  As described above, in the variable stroke device 2 of this example, the stroke of the ram 19 can be easily and accurately adjusted not only during the stop but also during the continuous punching process. Machining can be performed efficiently. Further, since the stroke can be changed only by changing the phase difference between the first eccentric shaft 32 and the second eccentric shaft 33, it can be realized with a relatively simple configuration. Therefore, the cost of the apparatus can be reduced, and the present invention can be suitably applied to a small press. Furthermore, since the stroke can be continuously changed, highly accurate processing and testing are possible.

  In the stroke variable device 2 of the present example, the first eccentric shaft 32 and the second eccentric shaft are interposed via the first slide member 46 and the second slide member 47, the guide rail 40, and the swing member 38. Since the displacement of 33 is transmitted to the ram 19, only the displacement in the vertical direction among the displacements of the first eccentric shaft 32 and the second eccentric shaft 33 can be transmitted to the ram 19. Accordingly, the two rotational motions can be combined and converted into a linear motion, and the ram 19 can be moved smoothly.

  Furthermore, in the stroke variable device 2 of this example, it is possible to make the motion of the ram 19 a constant-velocity linear motion as necessary, and further expansion of the usage range can be expected. For example, if the movement form of the ram 19 is switched in accordance with the type of workpiece, etc., machining with higher accuracy can be realized.

  The present invention has been described with reference to preferred embodiments. However, the present invention is not limited to these embodiments, and various modifications can be made without departing from the spirit of the present invention as described below. And design changes are possible.

  In other words, the stroke variable device 2 described above is applied to the press machine 1, but the present invention can be applied to any machine provided with a rod member. As an example, a vibration tester, an assembly machine, a molding machine, a cutting machine, or a caulking machine can be exemplified.

  In the stroke variable device 2 described above, the first main rotating body 20 and the second main rotating body 21 are rotated in the same direction when the continuous punching process is executed. You may do it. Even in this case, by changing the phase difference (initial phase difference) in the stopped state, the amount of displacement at the intermediate portion changes, and the stroke of the ram 19 can be changed.

It is a front view showing the whole press machine composition provided with the stroke variable device of the present invention. It is sectional drawing which shows the structure of a stroke variable apparatus. It is a right view which shows the structure of a stroke variable apparatus. It is explanatory drawing for demonstrating operation | movement of a stroke variable apparatus. It is a block diagram which shows the functional structure in a stroke variable apparatus. It is a wave form diagram which shows the displacement state of each site | part. It is explanatory drawing which shows the structure of the conventional stroke variable apparatus typically.

Explanation of symbols

2 Stroke variable device 3 Housing 19 Ram (rod member)
20 1st main rotator 21 2nd main rotator 22 1st electric motor (1st drive source)
23 Second motor (second drive source)
32 First Eccentric Shaft 33 Second Eccentric Shaft 35 Transmission Mechanism 37 Oscillating Shaft 38 Oscillating Member 40 Guide Rail 43 First Secondary Rotating Body 45 Second Secondary Rotating Body 46 First Slide Member 47 Second Slide Member 52 Stroke Setting means 58 Phase difference determination means 59 Phase difference adjustment control means 60 Reciprocating motion control means 61 Waveform information storage means 62 Correction amount determination means

Claims (3)

A first main rotating body and a second main rotating body, which are arranged in parallel in the housing and can be rotated separately;
A first drive source for rotating the first main rotor around a first axis;
A second drive source for rotating the second main rotor around a second axis;
A first eccentric shaft that is formed to protrude from the first main rotor and is eccentric with respect to the first axis;
A second eccentric shaft that protrudes from the second main rotor and is eccentric with respect to the second axis;
A rod member supported in a reciprocating linear motion state;
A transmission mechanism for transmitting the displacement of the first eccentric shaft and the second eccentric shaft in the movable direction of the rod member to one end side of the rod member;
Stroke setting means for setting a stroke of the rod member;
A phase difference determining means for determining a phase difference between the first eccentric shaft and the second eccentric shaft based on the stroke set by the stroke setting means;
Operate at least one of the first drive source and the second drive source, and match the phase difference between the first eccentric shaft and the second eccentric shaft with the phase difference determined by the phase difference determining means. Phase difference adjustment control means for causing;
The first main rotating body and the second main rotating body are rotated at the same speed by the first driving source and the second driving source while maintaining the phase difference adjusted by the phase difference adjusting control means. And a reciprocating motion control means for reciprocating the rod member via the transmission mechanism. The transmission mechanism is
A swinging member supported so as to be swingable with respect to one end side of the rod member and extending in a direction substantially perpendicular to the movable direction of the rod member;
A guide rail formed on the first eccentric shaft side and the second eccentric shaft side of the swing member and extending along the extending direction of the swing member;
A first auxiliary rotating body supported rotatably about the first eccentric shaft;
A second auxiliary rotating body supported rotatably about the second eccentric shaft;
A first slide member coupled to the first sub-rotator and slidably fitted to the guide rail located on one side of the swing shaft of the swing member;
A second slide member coupled to the second auxiliary rotating body and slidably fitted to the guide rail located on the other side of the swing shaft of the swing member. The stroke variable device according to claim 1, wherein The phase difference adjusted by the phase difference adjustment control means, and the rod member obtained when the first main rotating body and the second main rotating body are rotated at a constant speed while maintaining the phase difference. Waveform information storage means for storing a relationship between the motion waveform and a linear waveform previously associated with the motion waveform;
When the phase difference is determined by the phase difference determining means, the first main rotating body and the first main body and the first main rotating body are arranged so that the motion waveform corresponding to the phase difference becomes the linear waveform associated with the motion waveform. A correction amount determining means for determining a correction amount per unit time in the rotational speed of the two main rotors,
The reciprocating motion control means rotates the first main rotating body and the second main rotating body at a fluctuating speed in consideration of the correction amount per unit time determined by the correction amount determining means. The stroke variable device according to claim 1 or 2.

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