JP2016129901A - Pressure buffer device for rotary powder compression molding apparatus, and rotary type compression molding apparatus with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pressure buffer device for a rotary powder compression molding apparatus that can reduce noise and vibration generated as overpressure generated in compression molding by a rotary powder compression molding machine is buffered.SOLUTION: A pressure buffer device 3 comprises: a main body case 51 having a support surface 54a; a piston (spring case 61) having a contact surface 62a made to contact and leave the support surface 54a and housed vertically movably in the main body case 51, pushed with reaction force to molding pressure applied to one of upper and lower pressure rolls in compression molding by a rotary powder compression molding apparatus; a compression coil spring 71 pressing the contact surface 62a against the support surface 54a; and damper means 74 of utilizing fluid resistance of a non-compressive fluid (oil 77). When overpressure is generated in the compression molding, this overpressure is buffered by the compression coil spring 71 and a moving speed of the piston is reduced by the damper means 74.SELECTED DRAWING: Figure 4

Description

  The present invention is attached to a rotary powder compression molding machine such as a rotary tableting machine, and when pressure exceeding a set pressure (hereinafter referred to as over-pressurization) is generated in the compression molding of powder in this molding machine. The present invention relates to a pressure buffer device for a rotary powder compression molding apparatus that buffers this overpressurization, and a rotary powder compression molding apparatus including the pressure buffer device.

  A spring-type pressure shock absorber is known as a pressure shock absorber attached to a rotary tableting machine (see, for example, Patent Document 1).

  In this pressure buffer device, a movable member that can move up and down with respect to the casing is pushed upward by a compression coil spring housed in the casing. A part (second plate) of the movable member is hooked on the step surface of the housing from below, and the spring force of the compression coil spring is supported by the step surface. The reaction force of the molding pressure acting on the pressure roll in compression molding is configured to act downward on the movable member protruding upward from the housing. In this case, the pressure roll can rotate around the eccentric portion of the support shaft that supports the roll, and the eccentric joint (transmission arm) connected to the end portion of the support shaft can rotate with the support shaft. The reaction force is applied to the movable member.

  In compression molding, an excessive pressurization greater than the spring force (set pressure) set for the compression coil spring may occur due to an excessive amount of powder taken into the die. In this case, the movable member of the pressure buffering device to which the overpressure is applied is moved while compressing the compression coil spring. As a result, pressure exceeding the set pressure (abnormal load) is not applied to the bag or pressure roll, etc., so that over-pressurization is buffered and the bag or pressure roll resulting from over-pressure during compression molding Etc. are prevented from being damaged.

JP 2011-56572 A

  When the bag passes between the upper and lower pressure rolls as the turntable rotates, the overpressure is released. Accordingly, in the conventional pressure buffer device, the movable member is rapidly pushed back by the compression coil spring. If it does so, the 2nd plate of this movable member will collide with the level | step difference surface of a housing | casing vigorously, and immediately after that, a movable member will be rebounded. Such a collision and a rebounding action of the movable member against the step surface are repeated while weakening. FIG. 6C shows an image of the repeated behavior.

Causes the behavior of such a movable member, in the conventional pressure damper generates a large vibration and shock every time buffering the overpressure generated in the compression molding, vibration occurred continues until convergence. In FIG. 6C, symbol x1 indicates a time point when the movable member collides with the stepped surface, and t1 indicates a time zone in which vibration generated from the time point x1 of the collision may continue. Therefore, there is a problem that abnormal wear occurs in the loud noise, the movable member, etc., based on the vibration and impact generated when the second plate suddenly collides with the stepped surface.

  Further, in a configuration in which the pressure buffer device has a load cell for detecting the reaction force of the molding pressure, when an over pressurization occurs in the compression molding, the reaction force of the molding pressure is applied to the compression coil spring via the load cell. Acts in the direction of compressing. In this type of pressure buffering device, the vibrations and impacts associated with buffering over-pressurization that occurs in compression molding are large.

  In addition, in the configuration of the conventional pressure buffer device in which the first plate and the load cell for detecting the reaction force of the molding pressure and the movable members of the second plate are not connected but are simply in contact, As the two plates collide, the movable member connected to the eccentric joint may be moved away from the first plate. When a gap is generated between the movable member connected to the eccentric joint and the first plate in this way, before the movable member connected to the eccentric joint returns to the position in contact with the first plate, the next wrinkle is a pressure roll. When the reaction force of the molding pressure occurs and the movable member connected to the eccentric joint is returned toward the first plate, the movable member connected to the eccentric joint is violently applied to the first plate. It will collide.

  FIG. 6D shows the behavior of the eccentric joint (transmission arm) that operates with such a connected movable member. In the figure, reference numeral x1 indicates a point in time when the second plate collides with the step surface due to overpressurization buffering, and reference numeral x2 indicates that the next wrinkle reaches the pressure roll and a reaction force of the molding pressure is generated. Accordingly, the time point when the movable member connected to the eccentric joint collides with the first plate is shown, and the time zone t1 between the time point x1 and the time point x2 indicates the movable member connected to the eccentric joint and the first plate. And / or a time zone in which a gap is formed with the load cell that detects the reaction force of the molding pressure.

  Therefore, there is a high possibility that damage and breakage of the load cell, performance deterioration, life reduction, and the like are brought about by the vibration and impact generated by the over-pressurization buffer as described above.

  Accordingly, an object of the present invention is to provide a pressure buffering device for a rotary powder compression molding apparatus that can mitigate noise and vibration associated with buffering over-pressurization that occurs in compression molding in a rotary powder compression molding machine, and this pressure. An object of the present invention is to provide a rotary powder compression molding apparatus including a shock absorber.

  In order to solve the above-mentioned problems, the pressure buffering device for a rotary powder compression molding apparatus of the present invention has a main body case having a support surface and a contact surface that is in contact with and separated from the support surface, and can move up and down with respect to the main body case. A piston that is pressed by the reaction force of the molding pressure applied to one of the upper and lower pressure rolls in compression molding with a rotary powder compression molding machine, and a compression coil spring that presses the contact surface against the support surface, Damper means for utilizing the fluid resistance of the incompressible fluid. When over-pressurization occurs in compression molding, the over-pressurization is buffered by elastic deformation of the compression coil spring, and the moving speed of the piston is reduced by the damper means.

  According to the pressure buffering device for a rotary powder compression molding apparatus and the rotary powder compression molding apparatus having the same according to the present invention, noise caused by buffering overpressure generated in compression molding in the rotary powder compression molding machine. It has the effect of reducing vibration.

FIG. 1 is a diagram schematically showing an exploded configuration of the rotary tableting device according to the first embodiment of the present invention. FIG. 2 is a cross-sectional view showing the periphery of the upper pressure roll provided in the tableting device of FIG. FIG. 3 is a cross-sectional view showing the relationship between a part of the pressure roll of FIG. 2 and a roll shaft that supports the pressure roll, along the line F3-F3 in FIG. FIG. 4 is a cross-sectional view showing the pressure buffering device provided in the tableting device of FIG. 1 in a non-overpressurized state. FIG. 5 is a cross-sectional view showing a part of the pressure buffering device of FIG. 4 in an over-pressurized state. 6A is a diagram showing the behavior of the spring case included in the pressure damper of FIG. 4, FIG. 6B is a diagram showing the behavior of the transmission arm that pushes up the spring case, and FIG. FIG. 6D is a diagram showing the behavior of the movable member included in the pressure buffer, and FIG. 6D shows the connection between the first plate, the load cell for detecting the reaction force of the molding pressure, and each movable member of the second plate in the conventional pressure buffer. It is a figure which shows the behavior of the eccentric joint in the case where it is contacting without being done. FIG. 7 is a cross-sectional view showing a part of the pressure buffering device provided in the rotary tableting device according to the second embodiment of the present invention in an overpressurized state. FIG. 8 is a cross-sectional view showing a part of the pressure buffer device of FIG. 7 in a non-overpressurized state. FIG. 9 is a side view showing a spring case provided in the pressure damper of FIG. FIG. 10: is sectional drawing which shows the pressure buffer apparatus with which the rotary tableting apparatus which concerns on the 3rd Embodiment of this invention is provided in a non-overpressure state. FIG. 11 is a diagram schematically showing a configuration of a rotary tableting device according to the fourth embodiment of the present invention. FIG. 12 is a cross-sectional view showing the pressure buffering device provided in the tableting device of FIG. 11 in a non-overpressurized state. FIG. 13: is sectional drawing which shows a part of pressure buffer apparatus with which the rotary tableting apparatus which concerns on the 5th Embodiment of this invention is provided in a non-overpressure state.

  Hereinafter, a first embodiment of the present invention will be described in detail with reference to FIGS.

  As shown in FIG. 1, for example, a rotary powder compression molding apparatus (hereinafter abbreviated as a molding apparatus) for producing tablets as a compression molded product. For example, a rotary tableting apparatus 1 is a rotary powder compression molding machine such as a rotary type. The tableting machine 2, the pressure buffer 3 and the control panel 4 are provided.

  The frame included in the tableting machine 2 includes a lower frame member (not shown), an upper frame member 10 shown in FIGS. 2 and 3, and a frame pillar (not shown) that connects these lower frame members. A driving device is disposed inside the lower frame member. The tableting machine 2 includes a turntable 11 having a mortar mounting portion. The turntable 11 is disposed between the upper frame member 10 and the lower frame member, and is rotationally driven by the driving device.

  A plurality of mortars 12 are attached to the peripheral portion of the mortar mounting portion in the circumferential direction of the turntable 11 at regular intervals. The upper surfaces of the mortars 12 are the same height as the upper surface of the mortar mounting portion. The mortar 12 is also called a die and has a mortar hole (that is, a molding hole) penetrating in the vertical direction. The molding hole is rotated at the same angle together with the turntable 11. In addition, in the structure which combined the some segment (namely, die | dye) by which the die attachment part was divided | segmented into the circumferential direction of the turntable 11, each segment may function as a die | dye which has a some shaping | molding hole.

  The tableting machine 2 includes a powder supplier 14 disposed at the powder supply position. The powder feeder 14 is arranged so that the lower surface opening thereof is in contact with the upper surface of the mortar mounting portion of the rotating disk 11. As the rotator 11 rotates, the mortar 12 passes through the lower surface opening of the powder supplier 14, whereby the powder in the powder supplier 14 is supplied (filled) into the mortar hole of the mortar 12. The powder feeder 14 may be a powder feeder configured to contain a stirring member (not shown) that is rotated to make the density of the powder supplied to the mortar 12 uniform.

  The tableting machine 2 is provided with an upper punch 15 and a lower punch 16 that are individually disposed corresponding to each mortar hole. The upper punch 15 may be referred to as an upper punch, and the lower punch 16 may be referred to as a lower punch. The upper rod 15 and the lower rod 16 are supported by the turntable 11 so as to be movable up and down. Therefore, the upper rod 15 and the lower rod 16 are rotated at the same angle together with the turntable 11.

  The distal end portion (lower end portion) of the upper punch 15 is inserted into and removed from the mortar hole of the mortar 12 from above. The distal end portion (upper end portion) of the lower punch 16 holds the state of being inserted upward from below into the mortar hole of the mortar 12 and forms the bottom of the mortar hole. The upper punch 15 and the lower punch 16 slide on various guide tracks (not shown) (excluding the mass adjustment track described below) provided in the tableting machine 2 as the rotating plate 11 rotates, The required amount is moved in the direction in which the axis extends (vertical direction).

  A mass adjusting track (also referred to as a weight adjusting track) 17 on which the lower end of the lower punch 16 slides at the powder supply position is disposed below the mortar mounting portion of the rotating disk 11. The mass adjusting track 17 is supported by a track lifting mechanism 19 so as to be lifted and lowered. The track elevating mechanism 19 includes a track elevating motor 19a, an elevating shaft 19b, a gear 19c, and a drive gear 19d.

  For example, a servo motor can be suitably used for the orbit raising / lowering motor 19a, but a general-purpose motor can also be used. A rotary encoder 19e is attached to the track elevating motor 19a. It is possible to know the height position of the mass adjusting track 17 based on the detection of the rotation amount by the encoder 19e. The elevating shaft 19b is moved up and down along a guide (not shown), and the mass adjusting track 17 is connected to the upper end portion thereof. The gear 19c has an inner peripheral gear portion and an outer peripheral gear portion, and the inner peripheral gear portion is meshed with a male screw portion formed at the lower portion of the elevating shaft 19b. The drive gear 19d is meshed with the outer peripheral gear portion of the gear 19c, and is rotated by the orbit raising / lowering motor 19a. Therefore, the mass adjusting track 17 is lifted and lowered together with the lifting shaft 19b according to the forward and reverse rotation of the track lifting motor 19a of the track lifting mechanism 19.

  The various guide tracks (not shown) include a lowering track disposed below the powder feeder 14 and immediately before the mass adjusting track 17. When the lower punch 16 is lowered according to the lowering trajectory, the powder in the powder feeder 14 is sucked into the mortar hole and supplied (filled). Immediately after this, as the lower iron 16 slides up the inclined surface of the mass adjusting orbit 17 from the lowering orbit, excess powder is discharged into the powder feeder 14. Next, as the lower iron 16 slides on a horizontal plane continuous with the upper end of the inclined surface of the mass adjusting track 17, the upper surface of the die 12 is scraped off at the lower end of the downstream side wall 14a of the powder supplier 14. Thereby, the amount of powder supplied to the mortar 12, in other words, the mass (weight) of the tablet to be manufactured is weighed. Therefore, the mass of the tablet to be manufactured is changed by changing the height position of the mass adjusting track 17.

  The tableting machine 2 includes an upper pressure roll 21 and a lower pressure roll 22 arranged at the compression molding position. The compression molding position is set on the downstream side in the rotation direction of the turntable 11 with respect to the powder supply position. The upper pressure roll 21 is disposed above the mortar mounting portion of the turntable 11, and the lower pressure roll 22 is disposed below the mortar mounting portion of the turntable 11. The pressure rolls 21 and 22 are rotatable around the axis of the roll shaft that supports each of the pressure rolls 21 and 22. The pressure rolls 21 and 22 are provided to move the upper punch 15 and the lower punch 16 toward each other while freely rotating as the upper punch 15 and the lower punch 16 pass between them. Yes. By such movement of the upper punch 15 and the lower punch 16, the powder taken into the mortar 12 is compression molded.

  The upper pressure roll 21 is supported by the upper frame member 10 as shown in FIG.

  That is, the first bearing 41 and the second bearing 42 are attached to the upper frame member 10. The first bearing 41 and the second bearing 42 are arranged on both sides of the escape hole 10a so as to sandwich the escape hole 10a of the upper frame member 10. The first bearing 41 is supported by a bearing holder 43 fixed to the upper frame member 10 with a plurality of bolts.

  One end and the other end of the roll shaft 44 are rotatably supported by the first bearing 41 and the second bearing 42, respectively. The roll shaft 44 crosses the escape hole 10a. The roll shaft 44 has an eccentric shaft portion 44a having a diameter larger than the diameter of these end portions between one end portion and the other end portion thereof. In FIG. 3, the roll axis center is indicated by reference numeral S1, the eccentric shaft part center is indicated by reference numeral S2, and the distance between the eccentric shaft part center S2 and the roll axis center S1, that is, the amount of eccentricity is indicated by reference numeral e. ing.

  The upper pressure roll 21 is supported via a bearing 45 so as to be rotatable about the axis of the eccentric shaft portion 44a. Accordingly, the pressure roll 21 is supported by the upper frame member 10 so as to penetrate the escape hole 10a in the vertical direction and not move in the vertical direction. The center of the pressure roll 21 coincides with the eccentric shaft portion center S2.

  As shown in FIG. 1, the lower pressure roll 22 is rotatably supported by a roll support 23 and can be moved up and down together with the roll support 23 by a tip interval adjusting mechanism 24 in order to adjust the molding pressure. is there.

  The tip spacing adjustment mechanism 24 is provided to change the tip spacing between the upper punch 15 and the lower punch 16 that is about to pass between the upper pressure roll 21 and the lower pressure roll 22. Yes. The tip clearance adjusting mechanism 24 has the same configuration as the track elevating mechanism 19 and includes a roll elevating motor 24a, an elevating shaft 24b, a gear 24c, and a drive gear 24d.

  For example, a servo motor can be suitably used as the roll lifting motor 24a, but a general-purpose motor can also be used. A rotary encoder 24e is attached to the roll lifting / lowering motor 24a. Based on the detection of the rotation amount of the roll raising / lowering motor 24a by the encoder 24e, the height position of the lower pressure roll 22, and hence the height position of the lower punch 16 at the compression molding position, and consequently the lower punch 16 It is possible to know the tip interval between the upper arm 15 and the upper arm 15.

  The elevating shaft 24b is moved up and down along a guide (not shown), and the upper end portion supports the roll support 23 from below. The gear 24c has an inner peripheral gear portion and an outer peripheral gear portion, and the inner peripheral gear portion is meshed with a male screw portion formed at the lower portion of the elevating shaft 24b. The drive gear 24d is meshed with the outer peripheral gear portion of the gear 24c and is rotated by the roll lifting / lowering motor 24a. Accordingly, the lower pressing roll 22 is moved up and down together with the lifting shaft 24b in accordance with the forward / reverse rotation of the roll lifting motor 24a of the tip spacing adjusting mechanism 24. Accordingly, the height position of the lower punch 16 is changed. As a result, the tip interval at the compression molding position is changed.

  The tableting machine 2 is provided with defective product discharge means 31 and non-defective product discharge means 37 at the discharge position. The discharge position is set on the downstream side in the rotation direction of the turntable 11 with reference to the compression molding position. Further, the powder supply position is set on the downstream side in the rotation direction of the turntable 11 with reference to the discharge position.

  The defective product discharging means 31 is arranged on the upstream side in the rotation direction of the turntable 11 with respect to the non-defective product discharging means 37. The defective product discharging means 31 is not limited to the following configuration, but includes, for example, a chamber 32, a chute 33, a jet nozzle 34, and a vent pipe 35.

  The lower end of the chamber 32 is provided in close proximity so as not to contact the upper surface of the mortar mounting portion of the turntable 11. The chamber 32 intersects the rotational trajectory of the mortar 12. A chute 33 is connected to the chamber 32. The chute 33 extends outside the rotating disk 11 and obliquely downward. The blast nozzle 34 is supported by the chamber 32 so as to eject compressed air from the area toward the chute 33 disposed outside the area surrounded by the rotation locus of the mortar 12.

  One end of the vent pipe 35 is connected to the jet nozzle 34, and the other end of the vent pipe 35 is connected to a compressed air source (not shown). An electromagnetic valve 36 is provided in the middle portion of the vent pipe 35. A valve opening signal is input to the electromagnetic valve 36 based on a pressure sensor (to be described later) detecting a pressure abnormality. The electromagnetic valve 36 is opened for a predetermined short time as a valve opening signal is input, and is kept closed at other times (normally).

  The chamber 32 has an entrance-side passage port (not shown) and an exit-side passage port 32a that are located on the rotation locus of the mortar 12. These passage openings are provided so as to cut out the side wall of the chamber 32 from the lower end, and the tablets pushed out by the lower punch 16 can pass through the upper surface of the mortar mounting portion of the turntable 11. Therefore, a tablet (usually a good product) determined to be within the standard range based on the molding pressure can pass through the chamber 32 through an inlet side passage port and an outlet side passage port 32a (not shown). During this passage, the compressed air is not ejected from the jet nozzle 34.

  However, when a tablet (usually a defective product) determined to be out of the standard range based on the molding pressure has been carried into the chamber 32, the electromagnetic valve 36 is opened and compressed from the squirt nozzle 34 at the same timing. Air is ejected and this compressed air is sprayed onto the defective product on the lower rod 16. Therefore, the tablet determined to be out of the standard range is peeled off from the lower punch 16 and simultaneously blown off toward the chute 33 and discharged out of the turntable 11.

  The non-defective product discharging means 37 is, for example, connected to the chamber 32 of the defective product discharging means 31 so as to be immovable, and includes a scraper 38 that intersects with the rotational trajectory of the mortar 12 and a discharge chute 39 connected thereto. A tablet (good product) that passes through the chamber 32 and is determined to be within the standard range is removed from the lower punch 16 by the scraper 38 of the good product discharge means 37 and guided toward the discharge chute 39 to be discharged. It passes through the chute 39 and is taken out of the rotating disk 11 from the mortar mounting portion of the rotating disk 11.

  Next, the pressure damper 3 attached to the upper frame member 10 of the frame will be described. As shown in FIG. 4, the pressure damper 3 includes a main body case 51, a piston, for example, a spring case 61, a scale bar 66, a compression coil spring 71, and preferably an oil-type damper means 74, In the embodiment, for example, a load cell 81 is provided as a pressure sensor.

  The main body case 51 includes a case tube portion 52 and a spring receiving member 55.

  The case cylinder 52 is cylindrical and has a mounting flange 53 and a protrusion 54. The mounting flange 53 is formed to project outward from the upper portion of the case tube portion 52, for example, the upper end portion, and is continuous in the circumferential direction of the case tube portion 52. The protrusion 54 is provided below the mounting flange 53, for example, at the lower end of the case cylinder 52 in the first embodiment, and forms the bottom of the main body case 51.

  The protruding portion 54 protrudes into the case cylindrical portion 52 and is continuous and annular in the circumferential direction of the case cylindrical portion 52, and defines the minimum inner diameter of the case cylindrical portion 52. The upper surface of the protrusion 54 forms a support surface 54a. It is preferable that the angle formed by the support surface 54a and the inner peripheral surface 52a of the case cylinder portion 52 continuous on the upper side is a right angle.

  The case cylinder 52 is fixed to, for example, the upper frame member 10 of the frame so that the center line thereof is substantially vertical (including vertical). This fixing is performed by connecting the mounting flange 53 to the device mounting portion 10b with a bolt in a state where the case tube portion 52 is passed through the horizontal device mounting portion 10b of the upper frame member 10 downward from above. Yes. The apparatus mounting portion 10 b is located above the roll shaft 44.

  The spring receiving member 55 has a cylindrical shape with an open lower end, and a male screw portion 55a is formed on the outer peripheral portion thereof. The spring receiving member 55 has its male threaded portion 55a screwed into an internally threaded groove 52c formed on the upper inner peripheral surface of the case tube portion 52 from above the case tube portion 52, and is rotated. It is possible to advance and retreat in the vertical direction.

  The inner diameter of the upper part of the case cylinder part 52 is larger than the diameter of the lower inner peripheral surface 52a. The upper portion of the spring receiving member 55 protrudes above the case tube portion 52. The spring receiving member 55 has, for example, an operation hole 55b that opens to the peripheral surface at the top thereof. The height of the spring receiving member 55 can be changed by rotating the spring receiving member 55 using this tool in a state where a hand turning tool (not shown) is inserted into the operation holes 55b.

  The spring case 61 includes a cylindrical portion 62 whose upper end is opened, and a bottom portion 63 that has a smaller diameter than the cylindrical portion 62 and is integrally continuous below the cylindrical portion 62. Therefore, the spring case 61 has a recess 61a having an open upper end, and a lower portion of a compression coil spring 71 described later is accommodated in the recess 61a. In addition, although the recessed part 61a is not essential for a piston and can also be abbreviate | omitted, when shortening the length of the height direction of the pressure buffer device 3, the spring case 61 with the recessed part 61a should be used as a piston. Is preferred.

  The spring case 61 has a contact surface 62 a that is brought into contact with and separated from the support surface 54 a, and the contact surface 62 a is formed by an annular lower surface of the cylindrical portion 62. Furthermore, in the first embodiment, a communication groove 62b is formed below the cylindrical portion 62, specifically, above the contact surface 62a. The communication groove 62 b is annular and is open inside the spring case 61. In the first embodiment, the bottom 63 has a central protrusion 63a that protrudes downward.

  The spring case 61 is slidably brought into contact with the inner peripheral surface 52 a of the case tube portion 52 so that the outer periphery surface of the cylinder portion 62 is slidably fitted to the case tube portion 52, and is movable in the vertical direction with respect to the main body case 51. Is provided. At the same time, the bottom 63 of the spring case 61 is slidably fitted into a hole formed by the protruding portion 54 of the case cylinder 52. The spring case 61 is prevented from coming off below the main body case 51 by the contact of the contact surface 62a with the support surface 54a.

  In the first embodiment, the bottom 63 penetrates the hole formed by the protrusion 54, and thereby the lower part of the bottom 63 protrudes downward from the main body case 51. At the same time, the lower part of the bottom part 63 is covered with a cap-shaped connecting part 64 fitted to the central convex part 63a.

  The scale bar 66 is attached to the spring case 61 by a connecting screw 67. Specifically, the upper portion of the scale bar 66 passes through a through hole formed in the central portion of the upper wall portion of the spring receiving member 55, and the lower end portion of the scale bar 66 is fitted into a recess 63 b formed in the bottom portion 63. Yes. The scale bar 66 has a cylindrical shape, and has a scale 66a that displays a set pressure defined by a compression coil spring 71, which will be described later, on an upper outer peripheral surface thereof. The coupling screw 67 penetrates the scale bar 66 in the axial direction, and further penetrates the central convex portion 63a of the bottom 63 in the first embodiment and is screwed into the connection component 64. The head 67 a of the connecting screw 67 presses the upper end of the scale bar 66. Therefore, the scale bar 66 is attached to the spring case 61 in a form sandwiched from above and below by the bottom surface of the concave portion 63b of the bottom portion 63 and the head portion 67a of the connecting screw 67.

  The upper end of the compression coil spring 71 is supported by the spring receiving member 55 via the thrust bearing 72, and the lower end of the compression coil spring 71 is supported by the bottom 63. Thus, the compression coil spring 71 sandwiched between the spring receiving member 55 and the bottom 63 holds the elastically deformed state and always urges the spring case 61 downward. Thereby, the contact surface 62 a of the spring case 61 is pressed against the support surface 54 a of the main body case 51.

  By changing the height position of the spring receiving member 55 relative to the main body case 51, the compressed state of the compression coil spring 71 can be changed. Specifically, when the height position of the spring receiving member 55 is lowered, the degree of compression of the compression coil spring 71 is increased. Conversely, when the height position of the spring receiving member 55 is increased, the compression coil spring 71 The degree of compression is weakened. The degree of compression of the compression coil spring 71 is the set pressure of the pressure buffer device 3, and this pressure can be known by the operator visually reading the scale 66 a of the scale bar 66.

  The damper means 74 relieves the moving speed of the spring case 61 using the fluid resistance of an incompressible fluid when over-pressurization occurs in compression molding. In the first embodiment, the damper means 74 At least one preferably provided a plurality of orifices 75, an incompressible fluid such as oil 77, and the communication groove 62b are provided.

  The orifice 75 is, for example, parallel to the central axis of the spring case 61 and extends in the vertical direction, and its upper end (one end) is open to the communication groove 62b. Therefore, the orifice 75 is communicated with the inside of the spring case 61 through the communication groove 62b. The lower end (the other end) of the orifice 75 is open to the contact surface 62a.

  The oil 77 forms a liquid surface at a position higher than the orifice 75 and is stored in a spring case 61 disposed inside the main body case 51, specifically, in the main body case 51 in the case of the first embodiment. The oil 77 can also be stored inside the main body case 51 by forming a liquid level at a position higher than the upper end of the spring case 61.

  Further, as shown in FIGS. 4 and 5, the pressure buffer 3 has an annular first sealing material 78 and an annular second sealing material 79 for preventing leakage of the oil 77 below the orifice 75. Is preferred. As the first seal material 78 and the second seal material 79, an O-ring, a cylinder packing, or the like can be suitably used. The first sealing material 78 is attached to the outer peripheral portion of the portion above the central convex portion 63a of the bottom portion 63 of the spring case 61, and the hole formed by the projecting portion 54 of the main body case 51 and the bottom 63 passing through this hole. The space between the parts is sealed. The second sealing material 79 is attached to the outer peripheral portion of the lower end portion of the scale bar 66 and seals between the recess 63 b formed in the bottom portion 63 and the lower end portion of the scale bar 66.

  The first seal material 78 and the second seal material 79 prevent the oil 77 from leaking out of the pressure buffering device 3, and the liquid level of the oil 77 falls below the upper end of the orifice 75, so that the required amount of oil is reduced. You can keep it short. Thereby, it is possible to avoid malfunctions such as a reduction in the damper effect described later and the failure of the damper action, which is preferable. Furthermore, in the first embodiment, the bottom 63 of the spring case 61 and components disposed below the bottom case 63, for example, the load cell 81 described later in the first embodiment can be prevented from being contaminated with leaked oil. However, it is preferable.

  The load cell 81 is disposed below the spring case 61. Specifically, the spring case 61 is attached to the connection component 64 with a plurality of bolts 82 in contact with the lower surface of the connection component 64 that covers the bottom of the spring case 61 from below. The load cell 81 has a pressure receiving portion 81a that protrudes downward from the lower surface thereof. Therefore, the load cell 81 is arranged so that a reaction force P, which will be described later, acts through the load cell 81 in a direction in which the compression coil spring 71 is compressed.

  Next, a transmission arm 85 that applies a reaction force P of the molding pressure applied to the upper pressure roll 21 along with compression molding to the load cell 81, and a preload means 91 that holds the transmission arm 85 in contact with the pressure receiving portion 81a. Will be described.

  The transmission arm 85 includes an arm base portion 86 that is formed in a ring shape with a gap 86 a, an arm portion 87, and a contact 88.

  As shown in FIG. 2, the arm base 86 is fitted to the outer periphery of one end of the roll shaft 44 supported by the first bearing 41, and is tightened by a fixing bolt 89 screwed into the arm base 86 across the gap 86a. The end of the roll shaft 44 is fixed. The arm base 86 is prevented from rotating with respect to the roll shaft 44 by a key 90.

  As shown in FIGS. 4 and 5, the arm portion 87 is integral with the arm base portion 86. The tip of the arm part 87 faces the load cell 81 from below. The arm portion 87 has a contact 88 that is attached to the tip portion so as to protrude upward. The upper surface of the contact 88 is a part of a spherical surface, and the upper surface is in contact with the pressure receiving portion 81a from below.

  As shown in FIG. 4, the preload means 91 is attached to the means installation portion 10 d of the upper frame member 10 disposed on the lower side of the arm portion 87. The preload means 91 is provided to maintain a state in which the contact 88 of the arm portion 87 is pressed against the pressure receiving portion 81a of the load cell 81, and includes an adjusting screw 92, a lock nut 93, and a preload spring 94. .

  The adjustment screw 92 has a spring accommodating recess that extends in the axial direction and opens on the upper surface. The adjustment screw 92 is screwed into the screw hole 10c formed in the means installation portion 10d so as to be able to advance and retreat from above. The lock nut 93 is screwed to the adjustment screw 92. The preload spring 94 is accommodated in the spring accommodating recess with its upper portion protruding above the adjustment screw 92. The upper end of the preload spring 94 is in contact with the tip of the arm portion 87 from below. In this state, the preload spring 94 maintains an elastically deformed state, and urges the tip of the arm base 86 upward.

  Therefore, the preload means 91 presses the contact 88 against the pressure receiving portion 81a by the spring force of the preload spring 94. In a state where the adjusting screw 92 is rotated and arranged at an arbitrary screwing depth, the lock nut 93 is rotated and brought into close contact with the upper surface of the means installation portion 10d, thereby changing the height position of the adjusting screw 92, and a preload spring. The spring force of 94 can be adjusted.

  The control panel 4 that controls the overall operation of the tableting machine 2 is a touch panel type input device (not shown) provided exposed on the surface of the control panel casing (not shown), and built in the control panel casing. The control device 4a is provided. The control device 4a has a microcomputer or the like.

  The detection output of the load cell 81, that is, the reaction force P of the molding pressure applied to the pressure roll 21 in the compression molding is supplied to the control device 4a. In accordance with the input detection output, the control device 4a determines whether or not to perform mass control, and when necessary, drives and controls the orbit raising / lowering motor 19a. Further, the control device 4a determines whether or not the manufactured molded product is a defective product based on the detection output, and when the manufacture of the defective product is determined, the control device 4a performs control for opening the electromagnetic valve 36 for a predetermined time. Do. Furthermore, when it is necessary to change the thickness of the molded product to be manufactured, the control device 4a drives and controls the roll lifting / lowering motor 24a.

  When the tableting machine 2 of the first embodiment is operated, the upper punch 15 and the lower punch 16 which are paired up and down at the powder compression molding position become the upper pressure roll 21 and the lower pressure roll 22. The upper rod 15 and the lower rod 16 are moved so as to approach each other as they enter between them while coming into contact with each other. Therefore, the powder taken into the mortar 12 before reaching the powder compression molding position is compression molded.

  In this compression molding, the pressure roll 21 and the pressure roll 22 are rotated around the axis of the roll shaft supporting each of them. In this case, the upper pressure roll 21 is rotated around the axis of the eccentric shaft portion 44 a of the roll shaft 44. At this time, a reaction force P (shown in FIG. 4) of the molding pressure is applied upward to the roll shaft 44 via the pressure roll 21.

  In a non-overpressurized state (normal state) described later, with respect to a vertical line passing through the roll axis center S1, the eccentric shaft part center S2 passes through the roll axis center S1 on a straight line perpendicular to the vertical line. They are arranged with an eccentricity e therebetween. Therefore, the reaction force P acts on the eccentric shaft center S2 so as to rotate the roll shaft 44 counterclockwise around the roll shaft center S1 in FIGS. Thus, the transmission arm 85 connected to the roll shaft 44 tries to rotate counterclockwise. Thereby, the reaction force P is applied upward to the spring case 61 via the load cell 81 and the connection component 64.

  The transmission arm 85 is urged downward by the compression coil spring 71 to the spring case 61 via the connection part 64 and the load cell 81. By adjusting the height position of the spring receiving member 55 with respect to the main body case 51, the magnitude of the spring force (set pressure) of the compression coil spring 71 is set. With this spring force, the transmission arm 85 is held so as not to rotate counterclockwise in FIG.

  For this reason, when the reaction force P is equal to or less than the spring force of the compression coil spring 71 set by the adjustment, in other words, in a state where no overpressurization occurs in the compression molding (non-overpressure state), The roll shaft 44 and the transmission arm 85 maintain the state shown in FIG. 4 without being rotated. In this non-overpressurized state, the contact surface 62a of the spring case 61 is pressed against the support surface 54a of the main body case 51 by the spring force of the compression coil spring 71, and a gap is formed between the contact surface 62a and the support surface 54a. It is kept so that there is nothing. Therefore, the reaction force P can be detected as a molding pressure in the load cell 81.

  On the other hand, when the reaction force P of the molding pressure exceeds the set spring force of the compression coil spring 71, in other words, when the overpressure is generated in the compression molding (overpressure state), the roll The shaft 44 and the transmission arm 85 rotate counterclockwise in FIG. 4 while further compressing the compression coil spring 71. Even in this overpressurized state, the load cell 81 can detect the molding pressure.

  Thus, as the transmission arm 85 rotates counterclockwise in FIG. 4, the spring case 61 is pushed up with respect to the main body case 51. As a result, the contact surface 62a is separated from the support surface 54a, and a gap C (see FIG. 5) is formed between them. The gap C is such that the reaction force P of the molding pressure and the spring force of the compression coil spring 71 are mutually connected. Expand to equilibrium.

  When the gap C is formed in this way, the gap C and the inside of the spring case 61 are communicated with each other through a communication path including the orifice 75 and the communication groove 62b, so that the oil 77 in the spring case 61 passes through the orifice 75. It flows into the gap C.

  Therefore, the moving speed of the pushed-up spring case 61 is relaxed (decreased) by the mass of the oil 77 and the compression coil spring 71 that is compressed. In addition, the moving speed of the spring case 61 is further relaxed by the fluid resistance of the oil 77 flowing through the orifice 75.

  The over-pressurized state is released when the upper rod 15 and the lower rod 16 pass between the upper pressure roll 21 and the lower pressure roll 22. Along with this release, the spring case 61 is pushed back by the spring force of the compression coil spring 71, and the contact surface 62a contacts the support surface 54a. At this time, the damper means 74 functions as a shock absorber. That is, since the oil in the gap C flows into the spring case 61 through the orifice 75, the moving speed of the spring case 61 pushed down by the compression coil spring 71 is reduced by the fluid resistance of the oil 77 flowing through the orifice 75. .

  As described above, the fluid resistance of the oil 77 flowing through the orifice 75 reduces the moving speed when the spring case 61 is pushed up and down. For this reason, the contact surface 62a of the spring case 61 does not hit the support surface 54a of the main body case 51 strongly, and the impact is mitigated accordingly. Therefore, immediately after the spring case 61 pushed back downward is bounced upward on the support surface 54a, the behavior that the spring case 61 is pushed back downward again and hits the support surface 54a is repeated while being attenuated. Can be prevented.

  At the same time, a gap is generated between the pressure buffer 3 and the transmission arm 85, specifically, between the pressure receiving portion 81a of the load cell 81 and the contact 88 of the transmission arm 85 due to the buffering of the overpressure. Is prevented. That is, as described above, the moving speed and the impact when the spring case 61 is pushed down are alleviated, so that the downward direction acting on the contact 88 of the transmission arm 85 in accordance with the collision of the contact surface 62a with the support surface 54a. Therefore, the transmission arm 85 is not rotated clockwise in FIG. 4 due to the buffering of the overpressure. Accordingly, a gap is prevented from being generated between the pressure receiving portion 81a and the contact 88, and the contact of the contact 88 with the pressure receiving portion 81a is maintained. For this reason, the behavior patterns of the spring case 61 and the transmission arm 85 are substantially the same. At the same time, when the next upper collar 15 reaches the upper pressure roll 21 and a reaction force of the molding pressure is generated, the transmission arm 85 is forcibly rotated counterclockwise in FIG. As the 88 does not collide violently with the pressure receiving portion 81a, the vibration of the transmission arm 85 and the generation of noise caused thereby can be suppressed.

  An image of the behavior of the spring case 61 in the pressure damper 3 described above is shown in FIG. 6A. In contrast, the behavior of the spring case 61 in the conventional pressure damper without the damper means 74 is shown. An image is shown by (C) in FIG. 6A and 6C, the vertical axis indicates the displacement (amount) of the spring case or the movable member corresponding thereto, and the horizontal axis indicates time. 6B is an image of the behavior of the transmission arm 85 shown in relation to the behavior image of the spring case 61. FIG. In FIG. 6B, the vertical axis indicates the displacement (amount) of the transmission arm 85, and the horizontal axis indicates time.

  As described above, when over-pressurization occurs in compression molding, the impact at the pressure buffer device 3 can be reduced as the moving speed of the spring case 61 of the pressure buffer device 3 is reduced. Accordingly, vibrations in the pressure buffer 3 and the transmission arm 85 can be reduced, and the tableting machine 2 can be operated with low noise. At the same time, it is possible to suppress abnormal wear, damage and breakage of the contact portion in the pressure buffering device 3 based on intense impact and intense vibration.

  Here, the contact portion indicates the support surface 54a and the contact surface 62a in contact with the support surface 54a, the both ends of the compression coil spring 71 and the portion in contact with the both ends, the pressure receiving portion 81a and the contact 88 in contact with the pressure receiving portion 81a. . If intense vibration is generated in the spring case 61, the pressure receiving portion 81a and the contact 88 collide violently in the contact relationship between the pressure receiving portion 81a and the contact 88, and the pressure received by the intense impact generated therewith. The portion 81a and the contact 88 cause damage such as metal wear, and a severe impact caused by the collision spreads to the surroundings and adversely affects surrounding parts such as the load cell 81. Further, as described above, since severe impact and intense vibration can be suppressed, damage or breakage of the load cell 81, performance deterioration, and life reduction can also be suppressed.

  Along with this, it is possible to avoid a situation in which replacement of a part that has failed due to wear or damage, replacement of the load cell 81, readjustment of the display value of the molding pressure, recalibration, or the like. Therefore, it is also possible to avoid the problem that the operation of the tablet press 2 is forced to be interrupted for maintenance to repair the situation.

  Further, the damper means 74 of the above-described pressure damper 3 processes the communication groove 62b in the spring case 61 and communicates the inside of the spring case 61 with the gap C formed when the spring case 61 is pushed up. It is configured by processing one or more orifices 75 in the spring case 61 so that the oil 77 is accumulated in the spring case 61. For this reason, the processing is relatively easy, and the pressure buffer 3 can be configured easily.

  A second embodiment of the present invention will be described with reference to FIGS. Since the second embodiment is the same as the first embodiment except for the configuration described below, the same reference numerals as the corresponding configuration of the first embodiment are used for the same configuration or the same function as the first embodiment. The description is omitted.

  The second embodiment differs from the first embodiment in the configuration in which the gap C formed between the support surface 54a and the contact surface 62a and the inside of the spring case 61 are communicated. 9 is the same as that of the first embodiment including the configuration not shown in FIG.

  In the second embodiment, the communication groove 62b of the damper means 74 is provided on the outer peripheral surface of the lower portion of the cylindrical portion 62 of the spring case 61, as shown in FIG. Yes. The lower ends of the communication grooves 62b are opened to the contact surface 62a of the spring case 61, respectively. As shown in FIG. 8, the lower end of the communication groove 62b is closed by the support surface 54a of the main body case 51 when the molding pressure is in a non-overpressurized state. Each orifice 75 is provided through the cylindrical portion 62 in the radial direction. One end of these orifices 75 is opened to the inner peripheral surface of the spring case 61, and the other end of the orifice 75 is opened, for example, to the upper part of the communication groove 62b.

  Also in the pressure buffer device 3 of the second embodiment, the gap C (see FIG. 7) formed between the support surface 54a and the contact surface 62a when the molding pressure is in an overpressurized state and the inside of the spring case 61. As described in the first embodiment, the fluid resistance of the oil 77 flowing through the orifice 75 that forms a communication path that communicates with the communication groove 62b can reduce the moving speed when the spring case 61 is pushed up and down. The same effect as that of can be obtained.

  For this reason, the pressure buffer 3 which can relieve the impact, noise, and vibration accompanying buffering the over-pressurization which generate | occur | produces in compression molding, and a rotary tableting machine provided with the same can be provided. Furthermore, in the second embodiment, the orifice 75 and the communication groove 62b that form a communication path that connects the inside of the spring case 61 and the gap C can be processed from the outside of the spring case 61, respectively. Excellent in terms of good nature.

  A third embodiment of the present invention will be described with reference to FIG. Since the third embodiment is the same as the second embodiment except for the configuration described below, the same reference numerals as the corresponding configuration of the second embodiment are used for the same configuration or the same function as the second embodiment. The description is omitted.

  The third embodiment is different from the second embodiment in that the direct pressure type pressure buffer device 3 in which the reaction force of the molding pressure acting on the upper pressure roll 21 directly affects the load cell 81 is used. .

  Specifically, the main body case 51 included in the pressure buffer device 3 has a case lower portion 51a that protrudes downward from the protruding portion 54 and is open at the lower end. The inner diameter of the case lower part 51 a is larger than the inner diameter of the protruding part 54.

  The upper part of the roll receiver 101 is inserted into the case lower part 51 a, and the lower part of the roll receiver 101 protrudes below the main body case 51. The roll receiver 101 is movable in the vertical direction (the direction in which the central axis of the main body case 51 extends). The upper pressure roll 21 is supported at a lower portion of the roll receiver 101 via a roll shaft 44 supported at both ends at the lower portion. The pressure roll 21 is supported by a roll shaft 44 via a ball bearing (not shown), and is rotatable about the roll shaft 44. The center of the roll shaft 44 is coincident with the center of the pressure roll 21.

  A stopper 102 for preventing the roll receiver 101 from dropping off is bolted to the case lower part 51a. The stopper 102 has a cylindrical portion, and the roll receiver 101 is penetrated through the cylindrical portion so as to be movable up and down. A sliding key 103 attached to the roll receiver 101 is fitted in a key groove 102a formed to extend in the vertical direction on the inner surface of the cylindrical portion of the stopper 102. The roll receiver 101 is prevented from rotating by this fitting.

  A plurality of springs 104 (only one is shown in FIG. 10) are attached to the cylindrical portion so as to protrude from the upper end thereof. The upper ends of the springs 104 are in contact with an overhanging portion 101 a formed on the upper portion of the roll receiver 101 so as to face the upper end of the cylindrical portion. Thereby, the roll receiver 101 is urged upward.

  A load cell 81 protruding from the upper surface of the roll receiver 101 is attached. Therefore, the pressure receiving portion 81 a of the load cell 81 is pressed against the lower surface of the spring case 61 by each spring 104. That is, in the third embodiment, the bottom portion 63 of the spring case 61 does not have a configuration corresponding to the central convex portion described in the first embodiment or the like, so that the pressure receiving portion 81a is pressed against the lower surface of the bottom portion 63. Yes.

  Furthermore, the connecting screw 67 included in the pressure damper 3 in the third embodiment is attached without screwing the lower end portion into the bottom portion 63 of the spring case 61 and penetrating the bottom portion 63. As described above, since the connecting screw 67 does not penetrate the bottom portion 63, the second sealing material described in the first embodiment and the like is omitted. At the same time, the scale bar 66 of the pressure buffer 3 is sandwiched between the bottom 63 and the head 67 a of the connecting screw 67 with its lower end in contact with the inner bottom surface of the bottom 63.

  The spring case 61 is held by the compression coil spring 71 so as not to move in a non-overpressurized state in which the reaction force P of the upward molding pressure accompanying compression molding is equal to or lower than the set pressure set by the compression coil spring 71. . When the tableting machine is operated and is in a non-overpressurized state, an upward molding pressure reaction force P accompanying compression molding acts on the upper pressure roll 21. Since the reaction force P is applied upward to the load cell 81 via the roll receiver 101, the molding pressure can be detected in the load cell 81.

  On the other hand, when the reaction force P exceeds the set spring force (set pressure) of the compression coil spring 71, in other words, when overpressurization has occurred in compression molding (overpressurization state), The spring case 61 is pushed up with respect to the main body case 51 while further compressing the compression coil spring 71. As a result, the contact surface 62a is separated from the support surface 54a, and a gap (not shown in FIG. 10) is formed between them, and the reaction force P of the molding pressure and the spring force of the compression coil spring 71 are balanced with each other. Enlarge until you do. Accordingly, the oil 77 flows into the gap through the orifice 75 and the communication groove 62b. Even in this overpressurized state, the load cell 81 can detect the molding pressure. When the overpressurized state is released, the oil 77 in the gap is returned to the inside of the spring case 61 through the communication groove 62b and the orifice 75.

  Therefore, when an overpressurized state occurs in compression molding, a communication path that communicates the gap formed between the support surface 54a of the pressure buffer 3 and the contact surface 62a with the inside of the spring case 61 is formed as a communication groove 62b. In addition, the fluid resistance of the oil 77 flowing through the orifice 75 formed together with the fluid pressure of the oil case 77 reduces the behavior of the spring case 61 accompanying the overpressure buffering, that is, the moving speed when the spring case 61 is pushed up and down. The same effect as described in the second embodiment can be obtained. For this reason, the pressure buffer 3 which can relieve the noise, the impact, and the vibration accompanying buffering the over-pressurization which generate | occur | produces in compression molding, and a rotary tableting machine provided with this can be provided.

  Further, in the third embodiment, since the pressure buffer device 3 is a direct receiving type, the eccentric shaft portion described in the first embodiment is not required, so the configuration of the roll shaft 44 is simple. In addition, according to the third embodiment, the eccentric cam and the transmission arm described in the first embodiment and the like are not required, which is excellent in that the configuration of the tableting machine can be simplified.

  A fourth embodiment of the present invention will be described with reference to FIGS. Since the fourth embodiment is the same as the first embodiment except for the configuration described below, the same reference numerals as the corresponding configuration of the first embodiment are used for the same configuration or the same function as the first embodiment. The description is omitted.

  In the fourth embodiment, the pressure buffer 3 is configured not to include the load cell 81. For this reason, as shown in FIG. 12, the connection component 64 has a pressure receiving protrusion 64a protruding downward at the center of the lower surface thereof. Further, the contact 88 of the transmission arm 85 is in contact with the pressure receiving convex portion 64 a of the connection component 64 coupled to the spring case 61 from below.

  In the fourth embodiment, as described in the third embodiment, the lower end of the connection screw 67 is screwed into the bottom 63 of the spring case 61 and the lower end of the scale bar 66 is brought into contact with the inner bottom of the bottom 63. The connecting part 64 and the second sealing material described in the first embodiment can be omitted by sandwiching the scale bar 66 between the bottom 63 and the head 67a of the connecting screw 67.

  Further, as shown in FIG. 11, the load cell 81 for detecting the molding pressure at the time of molding is disposed so as to be sandwiched from above and below by the roll support 23 and the elevating shaft 24b of the tip interval adjusting mechanism 24. The load cell 81 is fixed to the upper end of the elevating shaft 24b and receives the lower surface of the roll support 23 by the pressure receiving portion 81a. In the fourth embodiment, the molding pressure is applied to the load cell 81 via the lower punch 16, the lower pressure roll 22, and the roll support 23.

  Also in the fourth embodiment, a gap (not shown in FIG. 12) and a spring formed between the support surface 54a of the pressure buffer 3 and the contact surface 62a when overpressure occurs in compression molding. A first embodiment in which the moving speed when the spring case 61 is pushed up and down can be reduced by the fluid resistance of the oil 77 flowing through the orifice 75 that forms the communication path communicating with the inside of the case 61 together with the communication groove 62b. It is possible to obtain the same effect as described in the above. In the fourth embodiment, the pressure buffering device 3 and the transmission arm 85 are caused by the buffering of the overpressure, specifically, the pressure receiving convex portion 64a of the connection part 64 and the contact 88 of the transmission arm 85. Since a gap is prevented from being generated between them, the behavior patterns of the spring case 61 and the transmission arm 85 are substantially the same.

  For this reason, the pressure buffer 3 which can relieve the noise, the shock, and vibration accompanying buffering the over-pressurization which generate | occur | produces in compression molding, and the rotary tableting machine 2 provided with this can be provided.

  A fifth embodiment of the present invention will be described with reference to FIG. Since the fifth embodiment is the same as the first embodiment except for the configuration described below, the same configuration as the first embodiment or the configuration having the same function is the same as the corresponding configuration of the first embodiment. Reference numerals are assigned and explanations thereof are omitted.

  The fifth embodiment is different from the first embodiment in that the orifice is formed between, for example, a spring case that forms a piston and a case cylinder, and does not require drilling to provide the orifice in the spring case. Unlike this, the rest is the same as the first embodiment, including the configuration not shown in FIG.

  Specifically, as shown in FIG. 13, the diameter of the outer peripheral surface of the cylindrical portion 62 of the spring case 61 is smaller than the diameter of the inner peripheral surface 52 a of the case cylindrical portion 52, whereby the outer peripheral surface of the cylindrical portion 62 and the case cylindrical portion 52. An orifice 75 made of a gap is formed between the inner peripheral surface 52a of the two. It is preferable that the orifice 75 has an annular shape that is continuous around the circumferential direction of the cylindrical portion 62. The orifice 75 extends in the vertical direction with the same length as the entire length of the cylindrical portion 62 in the axial direction. Therefore, one end (lower end) of the orifice 75 reaches the contact surface 62 a, and the other end (upper end) of the orifice 75 reaches the vicinity of the upper end of the spring case 61 and communicates with the inside of the case cylinder portion 52. The oil 77 is stored in a state where the spring case 61 is submerged in the main body case 51, and the liquid level of the oil 77 is formed at a position higher than the upper end of the orifice 75. Thereby, in the fifth embodiment, the damper means 74 is formed by the oil 77 and the orifice 75 formed by the gap.

  Also in the pressure damper 3 of the fifth embodiment, when the molding pressure is in an overpressurized state, a gap (not shown in FIG. 13) formed between the support surface 54a and the contact surface 62a and the main body case 51. The fluid resistance of the oil 77 flowing through the orifice 75 that communicates with the inside of the spring can reduce the moving speed when the spring case 61 is pushed up and down, thereby obtaining the same effect as described in the first embodiment. It is done.

  For this reason, the pressure buffer 3 which can relieve the impact, noise, and vibration accompanying buffering the over-pressurization which generate | occur | produces in compression molding, and a rotary tableting machine provided with the same can be provided.

  Furthermore, in the fifth embodiment, since the orifice 75 is formed by an annular gap provided between the spring case 61 and the case cylinder portion 52, a hole is formed in the spring case 61 in order to provide the orifice 75. It is not necessary to perform the opening process, and the process and structure can be further simplified.

  In the fifth embodiment, the orifice 75 is preferably annular, but may not be annular. That is, on one surface of the outer peripheral surface of the cylindrical portion 62 of the spring case 61 and the inner peripheral surface 52a of the case cylindrical portion 52, a plurality of convex portions extending in the axial direction thereof are preferably evenly provided in three or more circumferential directions. It is also possible to have a configuration in which a plurality of orifices 75 are provided in the circumferential direction of the cylindrical portion 62 by forming the distribution and bringing the other surface into contact with the convex portion. By doing in this way, although the labor of processing increases, it is possible to reduce the possibility that the spring case 61 will fall or twist due to the swinging phenomenon associated with the vibration relaxation operation.

  In addition, this invention is not restrict | limited to the said each embodiment. For example, in the pressure buffer device 3 in the first to fourth embodiments, the pressure receiving area related to the hole diameter, shape, length, and number of the orifices 75 and the flow rate of the orifice 75 when the pressure buffer device 3 is operated (that is, The area of the contact surface 62a of the spring case 61), the viscosity and the amount of the oil 77, etc. are not particularly limited, and the design specifications of the tableting machine (rotary powder compression molding machine) 2 and the pressure buffer device 3 are not limited. It can be set accordingly.

  Furthermore, in each embodiment, when pressure is applied to the pressure buffer device 3 that holds the upper pressure roll 21 in a non-overpressurized state in a stationary state, this overpressure is applied when overpressure occurs in compression molding. This is not limited to this. For example, in the fourth embodiment, a roll shaft having an eccentric shaft portion is used as a roll shaft that supports the lower pressure roll 22, and the pressure roll 22 is rotatably supported on the eccentric shaft portion. At the same time, a transmission arm 85 is connected to the end of the roll shaft that supports the pressure roll 22, and a pressure buffering device is provided so that a reaction force of the molding pressure acts upward on the transmission arm 85 via the transmission arm 85. 3 is arranged. The pressure buffering device 3 having such an arrangement holds the lower pressure roll 22 in a stationary state in a non-overpressurized state. Therefore, when overpressurization occurs in compression molding, It is possible to buffer with the pressure buffer 3. In this case, the load cell 81 may be arranged as in the fourth embodiment, or when the pressure damper 3 includes the load cell 81 as in the first embodiment, the load cell 81 is connected to the transmission arm 85 and the spring case. Alternatively, the load cell 81 may be disposed so as to detect a reaction force of the molding pressure applied to the upper pressure roll 21.

  In each of the first to fourth embodiments, the orifice 75 and the communication groove 62b form a communication path that connects the inside of the spring case 61 and the gap C when overpressure occurs in compression molding. However, the communication groove 62b is not essential. Specifically, one end of the orifice 75 is opened to the contact surface 62a so that a straight line extending in the longitudinal direction of the orifice 75 obliquely intersects the central axis of the spring case 61, and the other end is connected to the inner periphery of the spring case 61. An oblique orifice 75 may be provided in the cylindrical portion 62 so as to open to the surface, or one end of the orifice 75 is contacted so that a straight line extending in the longitudinal direction of the orifice 75 is orthogonal to the central axis of the spring case 61. The orifice 75 may be provided in the spring case 61 with the other end opened to the inner peripheral surface of the spring case 61 while being continuous with the surface 62a and being open to the peripheral surface of the bottom 63. A communication path is formed.

  DESCRIPTION OF SYMBOLS 1 ... Tableting device (rotary powder compression molding apparatus), 2 ... Tableting machine (rotary powder compression molding machine), 3 ... Pressure buffering device, 12 ... Dice with mortar hole (molding hole), 15 ... Upper arm , 16 ... lower collar, 21 ... upper pressure roll, 22 ... lower pressure roll, 51 ... main body case, 54a ... support surface, 61 ... spring case (piston), 61a ... recess, 62a ... contact surface, 62b ... communication groove, 71 ... compression coil spring, 74 ... damper means, 75 ... orifice, 77 ... oil (incompressible fluid), 78 ... first seal, 81 ... load cell (pressure sensor), C ... gap, P ... Reaction force of molding pressure

In order to solve the above-mentioned problems, the pressure buffering device for a rotary powder compression molding apparatus of the present invention has a main body case having a support surface and a contact surface that is in contact with and separated from the support surface, and can move up and down with respect to the main body case. A piston that is pressed by the reaction force of the molding pressure applied to one of the upper and lower pressure rolls in compression molding with a rotary powder compression molding machine, and a compression coil spring that presses the contact surface against the support surface, Damper means for utilizing the fluid resistance of the incompressible fluid. The damper means includes an orifice communicating with a gap formed between the support surface and the contact surface as the piston is moved upward, and a liquid surface at a position higher than the orifice so as to be inside the main body case. The fluid stored. When the piston is a spring case having a concave portion in which at least a part of the fluid is accommodated together with a part of the compression coil spring, and overpressurization occurs in compression molding, this overpressure is reduced by the elasticity of the compression coil spring. It is characterized by buffering by deformation and relaxing the moving speed of the piston by utilizing the fluid resistance in the damper means.

The spring case 61 includes a cylindrical portion 62 whose upper end is opened, and a bottom portion 63 that has a smaller diameter than the cylindrical portion 62 and is integrally continuous below the cylindrical portion 62. Therefore, the spring case 61 has a recess 61a having an open upper end, and a lower portion of a compression coil spring 71 described later is accommodated in the recess 61a . In order to shorten the length of the pressure buffer 3 in the height direction, a spring case 61 having a recess 61a is used as a piston.

By changing the height position of the spring receiving member 55 relative to the main body case 51, the compressed state of the compression coil spring 71 can be changed. Specifically, when the height position of the spring receiving member 55 is lowered, the degree of compression of the compression coil spring 71 is increased. Conversely, when the height position of the spring receiving member 55 is increased, the compression coil spring 71 The degree of compression is weakened. The degree of compression of the compression coil spring 71 is the set pressure of the pressure buffer 3, and this pressure can be known by the operator visually reading the scale 66 a of the scale bar 66.

DESCRIPTION OF SYMBOLS 1 ... Tableting device (rotary powder compression molding apparatus), 2 ... Tableting machine (rotary powder compression molding machine), 3 ... Pressure buffering device, 12 ... Dice with mortar hole (molding hole), 15 ... Upper arm , 16 ... lower collar, 21 ... upper pressure roll, 22 ... lower pressure roll, 51 ... main body case, 52 ... case cylinder part, 52c ... female screw groove, 54 ... protrusion, 54a ... support surface, 55 DESCRIPTION OF SYMBOLS ... Spring receiving member, 55a ... Male thread part 61 ... Spring case (piston), 61a ... Recess, 62a ... Contact surface, 62b ... Communication groove, 66 ... Scale bar, 66a ... Scale, 71 ... Compression coil spring, 74 ... Damper Means: 75 ... Orifice, 77 ... Oil (incompressible fluid), 78 ... First seal, 81 ... Load cell (pressure sensor), C ... Clearance, P ... Reaction force of molding pressure

Claims (8)

A rotary type that compresses and molds powder taken in a molding hole that rotates together with a rotating disk by passing the upper and lower irons rotated together with the rotating disk between upper and lower pressure rolls according to the rotation of the rotating disk. In a pressure buffer device for a rotary powder compression molding apparatus that is attached to a powder compression molding machine and overpressurizes the compression molding,
A body case having a support surface;
A piston that has a contact surface that is in contact with and away from the support surface, is provided so as to be movable in the vertical direction with respect to the main body case, and is pressed by a reaction force of a molding pressure applied to one of the upper and lower pressure rolls; ,
A compression coil spring that urges the piston and presses the contact surface against the support surface;
Damper means for relaxing the moving speed of the piston using the fluid resistance of the incompressible fluid when the over-pressurization occurs;
A pressure buffering device for a rotary powder compression molding apparatus.   The damper means has an orifice communicating with a gap formed between the support surface and the contact surface as the piston is moved upward, and forms a liquid surface at a position higher than the orifice. The pressure buffering device for a rotary powder compression molding apparatus according to claim 1, further comprising: the incompressible fluid stored inside the main body case.   The pressure buffer for a rotary powder compression molding apparatus according to claim 2, wherein the orifice is formed by a gap provided between an inner peripheral surface of the main body case and an outer peripheral surface of the piston. . The piston is a spring case having a recess in which a part of the compression coil spring is accommodated;
3. The pressure buffer for a rotary powder compression molding apparatus according to claim 2, wherein the orifice is provided in the spring case so as to communicate with the inside of the spring case and is open to the contact surface. apparatus.   The damper means further includes a communication groove formed on the outer peripheral surface of the spring case so as to open to the contact surface, and one end of the orifice is open to the inner peripheral surface of the spring case, and the other end of the orifice The pressure buffer device for a rotary powder compression molding apparatus according to claim 4, wherein the communication groove is open to the communication groove.   The said damper means is further equipped with the cyclic | annular sealing material which seals between the said main body case and the said piston below the said orifice, The Claim 1 characterized by the above-mentioned. Pressure buffer device for rotary powder compression molding equipment.   The pressure sensor further comprising a pressure sensor for detecting the reaction force, wherein the pressure sensor is arranged so that the reaction force acts on the compression coil spring in a direction of compressing the compression coil spring via the pressure sensor. Item 7. The pressure buffering device for a rotary powder compression molding apparatus according to any one of Items 1 to 6. Rotation that compresses and molds powder taken into molding holes provided in the rotating disk by passing the upper and lower irons rotated together with the rotating disk between upper and lower pressure rolls according to the rotation of the rotating disk. Type powder compression molding machine,
The pressure buffer device according to any one of claims 1 to 7, which is attached to a frame included in the rotary powder compression molding machine,
A rotary powder compression molding apparatus.

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